CN101405513A - Fluid bearing device - Google Patents
Fluid bearing device Download PDFInfo
- Publication number
- CN101405513A CN101405513A CNA2007800100900A CN200780010090A CN101405513A CN 101405513 A CN101405513 A CN 101405513A CN A2007800100900 A CNA2007800100900 A CN A2007800100900A CN 200780010090 A CN200780010090 A CN 200780010090A CN 101405513 A CN101405513 A CN 101405513A
- Authority
- CN
- China
- Prior art keywords
- bearing
- dynamic pressure
- hydrodynamic
- sleeve
- shaft component
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Abstract
The present invention provides a fluid bearing device which has excellent moment rigidity and an improved working efficiency in assembling and parts control, and in which a bearing sleeve can be easily manufactured. A plurality of bearing sleeves are axially disposed in the fluid bearing device. The bearing sleeves (3, 4) are so formed that their axial lengths are different from each other.
Description
Technical field
The present invention relates to a kind of hydrodynamic bearing device.
Background technique
The hydrodynamic bearing device utilization is formed at the oil film supporting shaft component of bearing play and makes its rotation freely.This FDB has features such as high speed rotating, high running accuracy, low noise, effectively utilize its feature being equipped on for example disk such as HDD, FDD device of information equipment in recent years, optical disk unit such as CD-ROM, CD-R/RW, DVD-ROM/RAM, the spindle drive motor on the magneto-optical disc apparatus such as MD, MO etc. is used; Or be equipped on bearing that the fan motor that carries out the heating source cooling on the personal computer (PC) etc. uses etc. and extensive use.
For example, in the hydrodynamic bearing device of the spindle drive motor of disk drive devices such as the HDD that packs into, be formed in the radial bearing portion of upper support shaft component radially and these both sides of thrust bearing division of supporting axle member in the axial direction by hydraulic bearing sometimes.As the radial bearing portion in this hydrodynamic bearing device is known following structure arranged: for example, TOHKEMY 2003-239951 communique (patent documentation 1) is put down in writing, on the either party of the outer peripheral surface of the inner peripheral surface of bearing sleeve and shaft component opposed, form dynamic pressure groove, and between two surfaces, form the radial bearing gap as dynamic pressure generating section with it.
At the information equipment of the hydrodynamic bearing device that is incorporated with said structure for example in the disk drive device such as HDD, with the high capacity is purpose, requires to carry many dishes, still, in this case, act on supporting spindle and make torque load of its rotation bearing portion freely become big.Be increase, be necessary radial bearing portion is arranged on a plurality of positions that separate in the axial direction, and the span that strengthens between the radial bearing portion improves torque rigidity corresponding to this torque load.The structure that these a plurality of radial bearing portions are located at interior all sides of a bearing sleeve comprises that also above-mentioned patent documentation 1 is widely adopted like that, but proposed the miniaturization of motor and followed its main shaft and the requirement of the pathization of bearing sleeve, therefore exist be difficult to make can be corresponding the situation of the bearing sleeve that increases of span between radial bearing portion.
Improve torque rigidity as the span that increases between the radial bearing portion, make the means of easy to manufactureization of bearing sleeve consider following structure simultaneously: for example Japanese kokai publication hei 11-269475 communique (patent documentation 2) and No. 3602707 communique of Japan special permission (patent documentation 3) put down in writing like that, on bearing sleeve configuration a plurality of positions (for example two positions) in the axial direction.But, in the hydrodynamic bearing device of this structure, though each bearing sleeve make consider sense of rotation and be located at the dynamic pressure groove on the inner peripheral surface etc. Pareto diagram, form the position difference and enter, it is identical that its axial dimension forms, apparent difference is extremely small.Therefore, there are not only mistaken easily installation direction and mounting point, and the also miscellaneous problem of component management.If installation directions etc. are made mistakes, the possibility that can not bring into play its function as bearing means is then arranged, therefore,, make the manufacture cost of bearing means surging installing and need noting especially.
In addition, other means as the torque rigidity raising, also can adopt the structure of the bearing span that enlarges thrust bearing division, have as the hydrodynamic bearing device with this structure is known: for example disclosed at TOHKEMY 2005-321089 communique (patent documentation 4), be provided with thrust bearing division in the both end sides of bearing sleeve.And, be purpose with further raising torque rigidity, can also adopt structure with the textural association of above-mentioned patent documentation 2 (or patent documentation 3) and patent documentation 4.Adopt under the situation of this structure, the dynamic pressures such as dynamic pressure groove that produce hydrodynamic in the thrust-bearing gap produce means, mostly consider formability under the situation and the end face of the bearing sleeve of the sintering metal system of being arranged at, but concerning each dynamic pressure groove, consider that sense of rotation is necessary to make the true dip direction difference.Therefore, need two kinds of bearing sleeves, but, therefore, make a mistake installation direction and mounting point easily because they form roughly the same shape with the visual degree that is difficult to differentiate.If mistaken installation direction then has the possibility that can not bring into play its function as bearing equally with above-mentioned, therefore, need to note especially installing, make the manufacture cost of bearing means surging.
But, in the structure of above-mentioned patent documentation 2 (or 3),, the situation that produces following problem is arranged when bearing means is installed though the bearing span that can increase between the radial bearing portion improves torque rigidity, and makes easy to manufactureization of bearing sleeve.That is in this structure, for example, even each bearing sleeve all forms accurately, eccentric possibility takes place utilizing bonding, means such as be pressed into also to have when being fixed on each bearing sleeve on the shell.The reduction of the coaxality between the both sides' that off-centre causes the radial bearing surface can cause the inequality of bearing rigidity, has the anxiety with the bearing performance reduction headed by the torque rigidity thus.
In addition, the verticity of script hydrodynamic bearing device is decided by the width accuracy in bearing play (for example radial bearing gap).Therefore, spend time with the outer peripheral surface of the shaft component that is formed for forming the radial bearing gap accurately and the inner peripheral surface of bearing sleeve (bearing components).For example TOHKEMY 2004-132402 communique (patent documentation 5) is put down in writing, and the gap width in this radial bearing gap is formed uniformly on whole entire axial length under the situation mostly.
When packing motor into, though various solid of rotation are installed on the shaft component of hydrodynamic bearing device, because the size of the solid of rotation of installing, weight etc. are different because of motor, so the position of centre of gravity of solid of rotation is all different at every turn.Therefore, when the gap width that makes the radial bearing gap as mentioned above like that evenly forms on whole entire axial length, in the load of convection cell bearing means under vibration or the situation of impacting, the bearing rigidity deficiency that causes with headed by the torque rigidity is arranged, the increase of the amount of waving of solid of rotation, the possibility of resonance phenomenon.
In addition, for example, in the hydrodynamic bearing device of spindle drive motor of packing into, not only require raising, also require to improve running accuracy as above-mentioned torque rigidity.Corresponding with it, be necessary further to be processed to form accurately the inner peripheral surface of bearing components in radial bearing gap and the outer peripheral surface of shaft component, but, usually process inner peripheral surface ratio processing excircles side face difficulty accurately accurately, in addition, it is limited improving machining accuracy in common machining.
[patent documentation 1] TOHKEMY 2003-239951 communique;
[patent documentation 2] Japanese kokai publication hei 11-269475 communique;
No. 3602707 communique of [patent documentation 3] Japan special permission;
[patent documentation 4] TOHKEMY 2005-321089 communique;
[patent documentation 5] TOHKEMY 2004-132402 communique.
Summary of the invention
The present invention makes in view of the above problems, and its first problem is to provide that a kind of torque rigidity is good, bearing sleeve is easy to manufacture and can improve the hydrodynamic bearing device of the operating efficiency of assembling and component management.
In addition, second problem of the present invention is to provide a kind of reduction of avoiding the bearing performance that assembly precision causes as far as possible, and can bring into play the hydrodynamic bearing device of high torque rigidity.
In addition, the 3rd problem of the present invention is to provide a kind of width accuracy that improves the radial bearing gap at low cost, with the good hydrodynamic bearing device of the bearing performance headed by the torque rigidity
For solving above-mentioned first problem, the invention provides a kind of hydrodynamic bearing device, it comprises: bearing sleeve, it has radial bearing surface; Shaft component, it is inserted into the interior week of this bearing sleeve; And radial bearing portion, it passes through the hydrodynamic effect that the radial bearing gap between the outer peripheral surface of the radial bearing surface of bearing sleeve and shaft component produces, at non-contact supporting axle member in the radial direction, described hydrodynamic bearing device is characterised in that, dispose a plurality of bearing sleeves in the axial direction, and each bearing sleeve forms axial length difference each other.
According to said structure, because bearing sleeve is disposed at axial a plurality of positions, therefore, can strengthen the span between the radial bearing portion, improve load capacity, and can make the easy to manufacture of bearing sleeve torque load.In addition, because the axial length at a plurality of bearing sleeves of axial arrangement is differed from one another, therefore, make to prevent assembly defect reliably by apparent obvious difference, and can realize the simplification of component management.
For example, under the situation that bearing sleeve is disposed at two axial positions, from the viewpoint of the bearing span that strengthens radial bearing portion, convention is that the radial bearing surface of a bearing sleeve is arranged at another bearing sleeve and deviates from week in the end of a side.But, at this moment, be difficult to especially to guarantee that axial dimension grows up between the two end part of bearing sleeve of the side changed, and bearing sleeve (radial bearing surface) coaxality to each other, the anxiety of harmful effect being brought to the verticity of bearing means is arranged.
Therefore, provide in the present invention to be provided with on the some at least inner peripheral surfaces in two adjacent bearing sleeves and the same protuberance directly of radial bearing surface, this protuberance is positioned at specific diameter and more leans on another bearing sleeve side to bearing surface.According to this structure, can be under the situation of for example inserting the assembling pin, can guarantee between the two end part of bearing sleeve of monomer and bearing sleeve coaxality each other, carry out assembling operation simultaneously easily.And, if forming, protuberance has the shape that dynamic pressure produces function, then cause moment of torsion to improve, therefore be preferably formed to not having the shape that dynamic pressure produces function (for example, band shape etc.).But if can guarantee can not bring the coaxial of harmful effect degree to verticity, protuberance also can be the diameter different slightly with radial bearing surface.Therefore, said here " with the protuberance in footpath " also comprises the protuberance that diameter is slightly different.
In addition, in said structure, can on shaft component, be provided with to the side-prominent protuberance of external diameter, and between the end face of the end face of protuberance and bearing sleeve, thrust bearing division being set, this thrust bearing division utilizes the hydrodynamic effect that produces in thrust-bearing gap non-contact supporting axle member in the axial direction.Protuberance can be integrally formed with shaft component, also can be fixed in shaft component.In addition, the dynamic pressure that produces the dynamic pressure groove etc. of dynamic pressure effect in the thrust-bearing gap of thrust bearing division produces means, as long as be formed at some at least the going up in the end face of the end face of protuberance and bearing sleeve.
In addition, also can form seal space at the outer circumferential side of being located at the protuberance on the shaft component.The sealing space have the volume-variation (expansion) that absorption causes along with the temperature variation of the fluid that is filled in bearing means inside (for example, lubricant oil) function, be so-called pooling feature.
In addition, other structures as solving above-mentioned first problem the invention provides a kind of hydrodynamic bearing device, and it comprises: bearing components; Solid of rotation, it has the shaft component that is inserted into week in the bearing components; First and second bearing play, it is formed between bearing components and the solid of rotation; The first dynamic pressure groove zone, it produces hydrodynamic in the first thrust-bearing gap; And the second dynamic pressure groove zone, it produces hydrodynamic in the second thrust-bearing gap, described hydrodynamic bearing device is characterised in that, bearing components has two bearing sleeves of alignment arrangements in the axial direction, these two bearing sleeves all have the first dynamic pressure groove zone and the second dynamic pressure groove zone in both ends of the surface, and the first dynamic pressure groove area surface that makes a bearing sleeve is to the first thrust-bearing gap, and the second dynamic pressure groove area surface that makes another bearing sleeve is to the second thrust-bearing gap.
As mentioned above,, therefore can increase the bearing span of radial bearing portion, improve torque rigidity, and can make easy to manufactureization of bearing sleeve because bearing components has two bearing sleeves.In addition, above-mentioned bearing sleeve all has the first dynamic pressure groove zone and the second dynamic pressure groove zone on both ends of the surface, and the first dynamic pressure groove area surface that makes a bearing sleeve is to the first thrust-bearing gap, the second dynamic pressure groove area surface that makes another bearing sleeve is to the second thrust-bearing gap, in other words, mean two arranged side by side in the axial direction of same bearing sleeve.Thereby, each bearing sleeve can be installed on the shell even do not consider configuration up and down yet, thus, distolaterally possess the first thrust-bearing gap at one of bearing components, another is distolateral to possess the second thrust-bearing gap, can form the good hydrodynamic bearing device of torque rigidity more easily.In addition, can with bearing sleeve intensive be a kind of, correspondingly can reduce the parts unit price, can also reduce the administration cost of parts.
If first dynamic pressure groove zone forms different shapes with the second dynamic pressure groove zone, then can easily discern each bearing sleeve about, can further realize the facilitation of installing.Here said " different shapes " are meant, except a plurality of formed structure of dynamic pressure groove of the helically shaped a plurality of dynamic pressure grooves of for example alignment arrangements, another alignment arrangements adult word shape, also comprise both different structures such as groove number with the dynamic pressure groove of shape alignment arrangements of the same race.If consider the former structure optimization from the viewpoint that improves identity.In addition, according to the purposes of hydrodynamic bearing device, under the different situation of the required pressure in the first thrust-bearing gap and the second thrust-bearing gap, can change the Pareto diagram of dynamic pressure groove with it accordingly.
Can be between two bearing sleeves the installation interval member.This spacer member is for example being formed under the situation of bearing sleeve by the oil-containing sintering metal, can form with the material that does not have porous matter tissue (non-porous material).At this moment, owing to can reduce the lubricants capacity that is included in the bearing means, therefore total oil mass has reduced respective amount, can realize cost degradation.And, can be corresponding the amount that reduces of oil mass come the volume of corresponding minimizing seal space, thereby can further enlarge the bearing span of radial bearing portion, promptly can further improve torque rigidity.
Hydrodynamic bearing device with above structure can be at the motor with this hydrodynamic bearing device, stator coil and rotor magnet, wherein preferably be used in the weightization of following high speed rotatingization and solid of rotation, in the motor of especially demanding torque rigidity.
In addition, for solving above-mentioned second problem, the invention provides a kind of hydrodynamic bearing device, it comprises: bearing components, and it separately is provided with a plurality of radial bearing surface in the axial direction on interior week; Solid of rotation, it has the shaft component that is inserted into week in the bearing components; A plurality of radial bearing portion, it is by the dynamic pressure effect non-contact rotating body for supporting of the fluid of the generation of the radial bearing gap between the outer peripheral surface of radial bearing surface and shaft component, described hydrodynamic bearing device is characterised in that, bearing components has a plurality of bearing sleeves of alignment arrangements in the axial direction, be contained on the clutch shaft bearing sleeve in a plurality of bearing sleeves a plurality of radial bearing surface all are set, and the clutch shaft bearing ferrule configuration is in the axial position of centre of gravity side near solid of rotation.Here, solid of rotation is meant the object integral body that the main shaft as hydrodynamic bearing device is rotated, as long as mean and for example be installed on shaft component, and can just comprise the object that they are whole with the member of shaft component one rotation.For example under the situation that disk drive devices such as HDD that hydrodynamic bearing device is packed into use, solid of rotation is meant whole assemblying body of the hub that comprises shaft component, the magnet that constitutes drive portion or dish or these magnet or dish are installed on shaft component etc. (other as pincers etc.).In addition, above-mentioned hydrodynamic bearing device is packed under the situation that fan motor etc. uses, solid of rotation is meant the whole assemblying bodys such as fan that hub etc. is fixed in shaft component that pass through beyond the magnet that comprises shaft component, constitutes drive portion.
As mentioned above, the invention is characterized in, in a plurality of bearing sleeves that constitute bearing components, on a bearing sleeve, whole radial bearing surface is set, and this bearing sleeve is configured near the axial position of centre of gravity side that becomes the solid of rotation that is supported body.That is,, can avoid on a plurality of bearing sleeves, respectively radial bearing surface being set and the reduction of the coaxality that causes and then the reduction of bearing rigidity by whole radial bearing surface is intensive to a bearing sleeve.In addition, and between a plurality of bearing sleeves, carry out comparing, can especially improve operating efficiency, realize the reduction of processing cost thus with the situation of axial adjustment.And, because in the present invention, this bearing sleeve is configured in the axial position of centre of gravity side of close solid of rotation, in other words, form radial bearing portion at position as far as possible near the axial position of centre of gravity of solid of rotation, therefore can be at the suitable position upper support solid of rotation of the position of centre of gravity that meets the solid of rotation that will support.Thus, poor with bearing span between the situation lower radial bearing portion that divides the radial bearing surface that is arranged on a plurality of bearing sleeves respectively can be compensated, high torque rigidity can be guaranteed.
As concrete structure, for example can exemplify in a plurality of bearing sleeves that constitute bearing components, be configured in the structure of axial side's side of clutch shaft bearing sleeve at second bearing sleeve that does not have radial bearing surface interior week.In addition, at this moment, bearing components also can have the shell that keeps a plurality of bearing sleeves in interior week, and shell and second bearing sleeve are integrally formed.In addition, bearing components also can also be included the week do not have radial bearing surface the 3rd bearing sleeve.At this moment, the 3rd bearing sleeve can be disposed at axial the opposing party's side of clutch shaft bearing sleeve.In addition, bearing components has under the situation of the shell that second bearing sleeve is integrally formed, can dispose the clutch shaft bearing sleeve in axial side's side of second bearing sleeve, and dispose the 3rd bearing sleeve in axial the opposing party's side.
With further raising torque rigidity is target, for example can adopt in the end face of a plurality of bearing sleeves that constitute bearing components at last distolateral first end face and structure that thrust bearing surface is set respectively on second end face away from first end face in the axial direction on being positioned at axially.According to this structure, each thrust bearing surface can be arranged at bearing components axially on the position of separating as far as possible.Thus, can increase as far as possible and solid of rotation between the axial distance of separation of the thrust bearing division that forms, can realize the further raising of torque rigidity.
In addition, for solving above-mentioned the 3rd problem, the invention provides a kind of hydrodynamic bearing device, it comprises: bearing components; Solid of rotation, it has the shaft component that is inserted into week in the bearing components; Radial bearing portion, it supports the solid of rotation with shaft component diametrically by the fluid film that the radial bearing gap that forms produces between bearing components and shaft component, described hydrodynamic bearing device is characterised in that, the gap width in radial bearing gap is different in the axial direction, in narrow of the little width of wide of the big width of this gap width and gap width, make the narrow portion of width be disposed at the position of centre of gravity side of solid of rotation, make being formed in the electroforming portion that constitutes by precipitating metal towards the zone in radial bearing gap at least of bearing components.And said here " solid of rotation " be meant and comprise and all be installed on shaft component, and can with the object of the member of shaft component one rotation.For example, under the situation that spindle drive motors such as the HDD that packs into use, magnet or whole object such as dish and then pincers that solid of rotation is meant the dish hub that comprises shaft component, is located at shaft component and is fixed in the dish hub.In addition, under the situation that the fan motor of for example packing into uses, solid of rotation is meant the whole objects such as fan, magnet that comprise shaft component, are fixed in shaft component by hub etc.
Usually, along with the gap width in radial bearing gap diminishes, the rigidity (bearing rigidity) that is formed at the fluid film in radial bearing gap uprises.Therefore, as mentioned above, make the gap width in radial bearing gap different in the axial direction, in narrow of the little width of wide of big width of this gap width and gap width, if the narrow portion of width is disposed at the position of centre of gravity side of solid of rotation, then near the center of gravity of solid of rotation, bearing rigidity can be improved, on the other hand, bearing rigidity can be reduced away from the center of gravity zone.Thus, can realize guaranteeing and low moment of torsionization of bearing rigidity simultaneously, and can improve the supporting precision of solid of rotation.In addition, also can shorten the span of the position of centre of gravity of the bearing centre of radial bearing portion and solid of rotation, and can improve torque rigidity.Said structure can obtain in the following manner, for example, on the axial region in radial bearing gap, make shaft component form diameter and make bearing components form different-diameter certain the time or to make when making shaft component form different-diameter bearing components form diameter certain.
In addition, the invention is characterized in being arranged in the electroforming portion that precipitating metal constitutes towards the zone (so-called radial bearing surface) in radial bearing gap at least of bearing components.Electroforming portion can plate (plating) or electroless plating (chemical plating) method based on electrolysis and form.Aspect the characteristic of this method, the face of separating out the beginning side for electroforming portion, because forming the surface configuration of its pattern forms with micron-sized grade by the dense face of transfer printing accurately, therefore, if with the surface of the accuracy to shape processing pattern of regulation, then do not implement the inner peripheral surface precision that special fine finishing etc. just can easily improve bearing components.Therefore, as long as in electroforming portion, especially it is separated out radial bearing surface is set on the beginning face, then can be easily and improve the width accuracy in radial bearing gap at low cost.In addition, if adopt this structure,, therefore can suppress to follow the characteristic variations of the radial bearing surface of temperature variation, and suppress the reduction of running accuracy as much as possible because radial bearing surface is metal covering.
In said structure, the gap width that can guarantee the radial bearing gap of required running accuracy can define with the minimum diameter gap delta in the radial bearing gap ratio δ/d with respect to the diameter of axle d of shaft component, according to the inventor's checking as can be known, than δ/d preferably in 1/1000≤δ/d≤1/250 scope.It the reasons are as follows described.
At first, can be than the lower limit 1/1000 of δ/d according to derivation such as the circularity of the outer peripheral surface of pattern or shaft component and electroforming portion inner peripheral surface, cylindricities.Promptly as diametric clearance δ during less than the circularity of the inner peripheral surface of the outer peripheral surface of shaft component or bearing components, cylindricity, between shaft component and bearing components, produce and contact, be difficult to guarantee the performance of stipulating.Though can further improve the circularity etc. of the inner peripheral surface of the outer peripheral surface of shaft component or bearing components, still, follow high precision int can cause that unavoidably cost improves.Therefore, during balance aspect considering function aspects and cost, more preferred more than 1/1000 than δ/d.On the other hand, the CLV ceiling limit value 1/250 than δ/d can derive according to the viewpoint of running accuracy or torque rigidity.That is,, then can not guarantee required bearing rigidity, torque rigidity, produce the bad phenomenon that running accuracy deterioration or shaft component contact with bearing components etc. if strengthen the minimum diameter gap delta in radial bearing gap.Therefore, preferably adopt below 1/250 than δ/d.
In addition, in said structure, active research according to the inventor is found, for example the end in the radial bearing gap is provided with the wide portion of width, at the other end the narrow portion of width is set, and make from wide of width to the narrow portion of width under the situation that gap width successively decreases, ratio ε/L of the axial length L in radial bearing gap and the reduction ε of the radius clearance of the entire axial length in radial bearing gap, in other words inclination ε/L is preferably 1/1000≤ε/L≤1/500.Its reason is, when than the value of ε/L less than 1/1000 the time, be difficult to fully obtain the raising effect and the low effect of torque drop of above-mentioned bearing rigidity.On the other hand, when greater than 1/500 the time, the value of the wide portion of width is excessive, and the possibility that causes bearing rigidity deficiency, running accuracy to worsen is arranged.In addition, the degree of extracting reluctantly of pattern becomes big when bearing components is shaped, and causes the risk of radial bearing surface damage to improve.
At above-mentioned hydrodynamic bearing device, can be provided for producing the dynamic pressure generating section of hydrodynamic in the radial bearing gap, thus, can constitute radial bearing portion by the good hydraulic bearing of enough running accuracies.Dynamic pressure generating section can be arranged at the inner peripheral surface of electroforming portion or the outer peripheral surface of shaft component, but only by the mould portion corresponding with dynamic pressure generating section is set on the cam surface of using in electroforming processing in advance, just can be easily and form dynamic pressure generating section accurately.Therefore, dynamic pressure generating section more preferably is arranged at the inner peripheral surface of electroforming portion on the outer peripheral surface that is arranged on shaft component.Dynamic pressure generating section can adopt known different shapes such as tipper, axial groove or arc surface.And, be provided with under the situation of this dynamic pressure generating section, in the gap between the outer peripheral surface of inner peripheral surface that is formed at bearing components and shaft component, be known as the radial bearing gap in this application towards the zone of dynamic pressure generating section.
The invention effect
As mentioned above, by disposing a plurality of bearing sleeves vertically, and each bearing sleeve forms axial length difference each other, thus, can provide that torque rigidity is good, bearing sleeve is easy to manufacture, and can improve the hydrodynamic bearing device of the operating efficiency of assembling and component management.
In addition, as mentioned above, by adopting following structure: bearing components has two bearing sleeves of alignment arrangements in the axial direction, these two bearing sleeves all have the first dynamic pressure groove zone and the second dynamic pressure groove zone in both ends of the surface, and the first dynamic pressure groove area surface that makes a bearing sleeve is to the first thrust-bearing gap, the second dynamic pressure groove area surface that makes another bearing sleeve is to the second thrust-bearing gap, thus, can provide that torque rigidity is good, bearing sleeve is easy to manufacture, and can improve the hydrodynamic bearing device of the operating efficiency of assembling and component management.
In addition, as mentioned above, a plurality of bearing sleeves of alignment arrangements in the axial direction are set on bearing components, be contained on the clutch shaft bearing sleeve in a plurality of bearing sleeves a plurality of radial bearing surface all are set, and the clutch shaft bearing ferrule configuration is in the axial position of centre of gravity side near solid of rotation, thus, a kind of reduction of avoiding the bearing performance that assembly precision causes as much as possible can be provided, the hydrodynamic bearing device of high torque rigidity can be brought into play.
In addition, as mentioned above, the gap width in radial bearing gap is different in the axial direction, in narrow of the little width of wide of the big width of this gap width and gap width, make the narrow portion of width be disposed at the position of centre of gravity side of solid of rotation, make being formed in the electroforming portion that constitutes by precipitating metal, thus towards the zone in radial bearing gap at least of bearing components, can provide the width accuracy height of radial bearing surface at low cost, with the good hydrodynamic bearing device of the bearing performance headed by the torque rigidity.
Description of drawings
Fig. 1 is the sectional drawing of first structure example of the hydrodynamic bearing device of expression first mode of execution of the present invention.
Fig. 2 (A) is a plan view of representing bearing sleeve is fixed in the state of shell, (B) is its sectional drawing of expression, (C) is its worm's eye view of expression.
Fig. 3 (A) is the skeleton diagram of the assembling procedure of expression bearing sleeve, (B) is the amplification profile of the upper section of expression shell.
Fig. 4 is the sectional drawing of second structure example of the hydrodynamic bearing device of expression first mode of execution.
Fig. 5 is a sectional drawing of schematically representing to be incorporated with the spindle drive motor of hydrodynamic bearing device.
Fig. 6 is a sectional drawing of schematically representing to be incorporated with the fan motor of hydrodynamic bearing device.
Fig. 7 is a sectional drawing of schematically representing to be incorporated with the spindle drive motor of hydrodynamic bearing device.
Fig. 8 is the sectional drawing of first structure example of the hydrodynamic bearing device of expression second mode of execution of the present invention.
Fig. 9 (A) is the sectional arrangement drawing of bearing sleeve, (B) is the figure of the upside end face of expression bearing sleeve, (C) is the figure of the downside end face of expression bearing sleeve.
Figure 10 is the sectional drawing of second structure example of the hydrodynamic bearing device of expression second mode of execution.
Figure 11 is the sectional arrangement drawing of other structure example of expression bearing sleeve.
Figure 12 is a sectional drawing of schematically representing to be incorporated with the fan motor of hydrodynamic bearing device.
Figure 13 is a sectional drawing of schematically representing to be incorporated with the spindle drive motor of hydrodynamic bearing device.
Figure 14 is the sectional drawing of first structure example of the hydrodynamic bearing device of expression the 3rd mode of execution of the present invention.
Figure 15 is the sectional drawing of bearing components.
Figure 16 is an end elevation of seeing the bearing components shown in Figure 15 from arrow a direction.
Figure 17 is an end elevation of seeing the bearing components shown in Figure 15 from arrow b direction.
Figure 18 is the sectional drawing of other structures of expression bearing components.
Figure 19 is the sectional drawing of other structures of expression bearing components.
Figure 20 is the sectional drawing of second structure example of the hydrodynamic bearing device of expression the 3rd mode of execution.
Figure 21 be expression the 4th mode of execution of the present invention hydrodynamic bearing device first structure example contain axial section.
Figure 22 represents the sectional drawing of bearing components.
Figure 23 (A) is the stereogram of pattern, and (B) being expression implements to shelter the stereogram of the state of (masking) to pattern, (C) is the stereogram of electroforming member.
Figure 24 is the sectional drawing that inserts the bearing components after being shaped.
Figure 25 is the sectional drawing of second structure example of the hydrodynamic bearing device of expression the 4th mode of execution.
Figure 26 is the sectional drawing of the 3rd structure example of the hydrodynamic bearing device of expression the 4th mode of execution.
Figure 27 is the sectional drawing of the 4th structure example of the hydrodynamic bearing device of expression the 4th mode of execution.
Figure 28 be with many arc bearings constitute radial bearing portion situation contain axial section.
Figure 29 be with many arc bearings constitute radial bearing portion situation contain axial section.
Figure 30 be with many arc bearings constitute radial bearing portion situation contain axial section.
Figure 31 is the axial section that contains with the situation of step bearing formation radial bearing portion.
Among the figure:
1, the 21-hydrodynamic bearing device, the 2-shell, 3-clutch shaft bearing sleeve, 4-second bearing sleeve, 5-shaft component, 6, the 7-sealing component, the 8-spacer member, A, A '-radial bearing surface, the B-protuberance, the axial length of L1-clutch shaft bearing sleeve, the axial length of L2-second bearing sleeve, P-assembles pin, R1, R2-radial bearing portion, T1, the T2-thrust bearing division, S1, the S2-seal space, 101-hydrodynamic bearing device, 102-shaft component, the 104-stator coil, the 105-rotor magnet, 107-shell, 108-bearing components, 109, the 110-sealing component, the 181-bearing sleeve, 182-spacer member, 81a1,81b1,81c1-dynamic pressure groove, R11, R12-radial bearing portion, T11, the T12-thrust bearing division, S11, the S12-seal space, the 201-hydrodynamic bearing device, the 202-solid of rotation, the 203-hub, 206-shaft component, 207, the 208-sealing component, the 209-bearing components, the 210-shell, 211-clutch shaft bearing sleeve, 212-second bearing sleeve, A21, the A22-radial bearing surface, B21, the C21-thrust bearing surface, R21, R22-radial bearing portion, T21, the T22-thrust bearing division, 301,321,331, the 341-hydrodynamic bearing device, the 302-solid of rotation, 303-shaft component, 304-rotor, the 305-bearing components, 306-electroforming portion, 307-shielding part, 308, the 309-radial bearing surface, the 311-pattern, the 312-covered emplacement, Cr1, Cr2, Cr3-radial bearing gap, D1-(the radial bearing gap) the narrow portion of width, D2-(the radial bearing gap) the wide portion of width, the axial length in L-radial bearing gap, R31, R32-radial bearing portion, the T3-thrust bearing division, the S3-seal space, the diameter of axle of d-shaft component.
Embodiment
Below, based on Fig. 1～Fig. 6 the hydrodynamic bearing device of first mode of execution of the present invention and the motor that possesses this device are elaborated.And below " up and down " direction in the explanation is only represented above-below direction among each figure simply, be not limit hydrodynamic bearing device direction and usage mode etc. are set, and too for other mode of executions of the present invention shown in after Fig. 7.
Fig. 1 represents a structure example of the hydrodynamic bearing device of first mode of execution of the present invention.The rotation of hydrodynamic bearing device 1 supporting spindle in being loaded into the motor of HDD shown in this figure.This hydrodynamic bearing device 1 comprises following main structural components: shell 2; With separated in the axial direction position be fixed on the shell 2 a plurality of, be two bearing sleeves (clutch shaft bearing sleeve 3, second bearing sleeves 4) here; Be disposed at the spacer member 8 between this first, second bearing sleeve 3,4; Be inserted into the shaft component 5 in week in first, second bearing sleeve 3,4.
As described later, between the outer peripheral surface 5a of the inner peripheral surface 3a of clutch shaft bearing sleeve 3 and shaft component 5, be provided with first R1 of radial bearing portion, between the outer peripheral surface 5a of the inner peripheral surface 4a of second bearing sleeve 4 and shaft component 5, be provided with second R2 of radial bearing portion.In addition, between the downside end face 6b of the upside end face 3b of clutch shaft bearing sleeve 3 and sealing component 6, be provided with the first thrust bearing division T1, between the upside end face 7b of the downside end face 4b of second bearing sleeve 4 and sealing component 7, be provided with the second thrust bearing division T2.
As the base resin that in the resin material that forms shell 2, uses, so long as energy injection moulding, no matter non-crystalline resin/crystalline resin all can use, for example, polysulfones (PSF), polyether sulfone (PES), polyphenylsulphine (PPSU), Polyetherimide (PEI) etc. can be used as non-crystalline resin, liquid-crystalline polymer (LCP), polyether-ether-ketone (PEEK), polybutylene-terephthalate (PBT), polyphenylene sulfide (PPS) etc. can be used as crystalline resin.Certainly these are nothing but an example, and consideration Environmental Conditions etc. also can be used other base resin.In addition, the kind that is filled into the packing material in the above-mentioned base resin also is not particularly limited, for example can use fibrous packing materials such as glass fibre as packing material, whisker shape packing materials such as potassium titanate, flakey packing materials such as mica, fibrous or pulverous electric conductivity packing materials such as carbon fibre, carbon black, graphite, nanocarbon material, metallic dust.These packing materials can use separately or be use mixing two or more.
In addition, also can use soft metal materials such as brass or aluminum alloy, other metallic material to form shell 7.
Between the second inner peripheral surface 2b of the outer peripheral surface 6a of sealing component 6 and shell 2, be formed with the seal space S1 of specified volume, be formed with the seal space S2 of specified volume between the 3rd inner peripheral surface 2c of the outer peripheral surface 7a of sealing component 7 and shell 2.In the present embodiment, the outer peripheral surface 7a of the outer peripheral surface 6a of sealing component 6 and sealing component 7 forms respectively towards the outer side of shell 2 conical surface shape of undergauge gradually.Therefore, seal space S1, S2 are towards the diminishing cone-shaped of the private side of shell 2.
The porous plastid that first, second bearing sleeve 3,4 constitutes by sintering metal for example, especially with copper to be that the porous plastid of the sintering metal of primary coil forms cylindric, respectively by be pressed into, bonding or be pressed into means such as bonding and be fixed on the first inner peripheral surface 2a of shell 2.And bearing sleeve 3,4 also can be formed by the metallic material of the Cuprum alloy beyond the sintering metal etc.First, second bearing sleeve 3,4 forms each other length difference in the axial direction, in this structure example, forms the axial length L 1 of clutch shaft bearing sleeve 3 greater than the axial length L 2 of second bearing sleeve 4 (L1＞L2).
Shown in Fig. 2 (B), on the inner peripheral surface 3a of clutch shaft bearing sleeve 3, be formed with the zone of the radial bearing surface A that becomes first R1 of radial bearing portion, on this radial bearing surface A, be formed with the dynamic pressure groove 3a1 of herringbone shape.This radial bearing surface A is formed at second bearing sleeve 4 and deviates from the end of a side (upside).In addition, in the inner peripheral surface 3a of clutch shaft bearing sleeve 3, the end face of the opposition side (downside) of isolating in the axial direction with radial bearing surface A is formed with banded protuberance B.This protuberance B forms and divides the roughly the same diameter of peak portion that forms dynamic pressure groove 3a1.
Shown in Fig. 2 (A), on part or all annular section of the upside end face 3b of clutch shaft bearing sleeve 3, be formed with the zone of the thrust bearing surface that becomes the first thrust bearing division T1, on this thrust bearing surface, be formed with the dynamic pressure groove 3b1 of herringbone shape.And, on outer peripheral surface 3d, be formed with a plurality of (illustrated example is 3) the axial groove 3d1 that uniformly-spaced disposes at circumferencial direction.
In addition, shown in Fig. 2 (B), on the inner peripheral surface 4a of second bearing sleeve 4, be formed with the zone of the radial bearing surface A ' that becomes second R2 of radial bearing portion, on this radial bearing surface A ', be formed with the dynamic pressure groove 4a1 of herringbone shape.In addition, shown in Fig. 2 (C), on part or all annular section of the downside end face 4b of second bearing sleeve 4, be formed with the zone of the thrust bearing surface that becomes the second thrust bearing division T2, on this thrust bearing surface, be formed with the dynamic pressure groove 4b1 of herringbone shape.And, on outer peripheral surface 4d, be formed with a plurality of (being illustrated as 3) the axial groove 4d1 that uniformly-spaced disposes at circumferencial direction.
Between first, second bearing sleeve 3,4, the spacer member cylindraceous 8 that is for example formed by soft metals such as brass or aluminium, resin material or sintering metal etc. is installed, spacer member 8 by be pressed into, bonding or be pressed into the first inner peripheral surface 2a that means such as bonding are fixed in shell 2.The inner peripheral surface 8a of spacer member 8 forms bigger slightly than the diameter of inner peripheral surface 3a, the 4a of two bearings sleeve 3,4, and (during bearing operation) not and form the radial bearing gap between the shaft component 5 when shaft component 5 rotation.And, on outer peripheral surface 8d, be formed with a plurality of (for example 3) the axial groove 8d1 that uniformly-spaced disposes at circumferencial direction.
For example assemble by the hydrodynamic bearing device 1 that the said structure member constitutes by following operation.
At first, first, second bearing sleeve 3,4 and spacer member 8 are fixed on the first inner peripheral surface 2a of shell 2 by pattern shown in Figure 2.Utilize between the two bearings sleeve 3,4 when for example the assembling pin P shown in Fig. 3 (A) guarantees fixedly coaxial.At this moment, because on the inner peripheral surface 3a of clutch shaft bearing sleeve 3, the underpart side away from radial bearing surface A be provided with radial bearing surface A roughly with the protuberance B in footpath, the posture of clutch shaft bearing sleeve 3 is worsened, and can guarantee coaxial between its two end part reliably.And, by using this assembling pin, can guarantee coaxial between first, second bearing sleeve 3,4 reliably.
In addition, in two bearings sleeve 3,4 and spacer member 8 to shell 2 fixedly the time, shown in the Fig. 3 (B) that amplifies, be in one side or become the mode with the outstanding state of small dimension delta 2 with the upside step surface 2d of the upside end face 3b of clutch shaft bearing sleeve 3 and shell 2, under the state of the axial position of adjusting clutch shaft bearing sleeve 3, be fixed on the inner peripheral surface 2a from step surface 2d.As shown in the drawing, under the situation of the outstanding dimension delta 2 of step surface 2d, the downside end face 6b of sealing component 6 and the axial dimension between the step surface 2f are greater than the width δ 1 in the thrust-bearing gap of the first thrust bearing division T1 at the upside end face 3b that makes clutch shaft bearing sleeve 3.In addition, though not shown second bearing sleeve 4 also is fixed in the first inner peripheral surface 2a of shell 2 under the state that carries out with the same position adjustment of clutch shaft bearing sleeve 3.
The result who adjusts the axial position of two bearings sleeve 3,4 and be fixed in the inner peripheral surface 2a of shell 2 in above-mentioned mode is, as shown in Figures 1 and 2, there is small gap between the upside end face 8b of the downside end face 3c of clutch shaft bearing sleeve 3 and spacer member 8 and between the downside end face 8c of the upside end face 4c of second bearing sleeve 4 and spacer member 8 sometimes.And, also have the only situation about occurring of the side's side in bearing sleeve 3,4 of above-mentioned gap according to the axial dimension of first, second bearing sleeve 3,4 and spacer member 8 and the inner peripheral surface 2a of shell 2.Perhaps, also exist bearing sleeve 3,4 both sides all with the situation of spacer member 8 butts.
Below, shaft component 5 is inserted inner peripheral surface 3a, the 4a of first, second bearing sleeve 3,4 and the inner peripheral surface 8a of spacer member 8, sealing component 6,7 is fixed in the assigned position of shaft component 5.And the either party in the sealing component 6,7 can predetermined fixed can also be integrally formed with shaft component 5 on shaft component 5 before insertion.
After assembling is finished through above-mentioned operation, to the inner space of the shell 2 of sealed member 6,7 sealings, also comprise that for example packing lubrication oil is as lubricating fluid in the internal porosity (internal porosity of porous plastid tissue) of two bearings sleeve 3,4.The filling of lubricant oil for example can be by carrying out as follows: the hydrodynamic bearing device 1 that assembling is finished is impregnated in vacuum tank in the lubricant oil, afterwards, opens to barometric pressure.
In the hydrodynamic bearing device 1 of said structure, when shaft component 5 rotations, the radial bearing surface A of the inner peripheral surface 3a of clutch shaft bearing sleeve 3 and the outer peripheral surface 5a of shaft component 5 are opposed across the radial bearing gap.In radial bearing surface A, the lubricant oil that is filled in the radial bearing gap improves its pressure under the dynamic pressure effect of dynamic pressure groove 3a1, by this pressure shaft component 2 is carried out the non-contact supporting, and it is rotated freely diametrically.In addition, in this structure example, between the outer peripheral surface 5a of protuberance B and shaft component 5, be formed with the radial bearing gap, in this radial bearing gap, form oil film by the oil that oozes out from clutch shaft bearing sleeve 3, utilize this oil film supporting axle member 5 diametrically, make its rotation freely.Thus, constitute by hydraulic bearing and positive circular journal bearing and support and make it to rotate freely first R1 of radial bearing portion diametrically shaft component 5.Also constitute hydraulic bearing at second bearing sleeve 4, and constitute and support and make it to rotate freely second R2 of radial bearing portion diametrically shaft component 5 by radial bearing surface A '.
In addition, when shaft component 5 rotations, the thrust bearing surface of the upside end face 3b of clutch shaft bearing sleeve 3 and the downside end face 6b of sealing component 6 are opposed across the thrust-bearing gap of regulation, and the thrust bearing surface of the downside end face 4b of second bearing sleeve 4 and the upside end face 7b of sealing component 7 are opposed across the thrust-bearing gap of regulation.And, being accompanied by the rotation of shaft component 2, the dynamic pressure effect of lubricant oil by dynamic pressure groove 3b1,4b1 that is filled in each thrust-bearing gap improves its pressure, and upwards shaft component 5 carried out the non-contact supporting at diaxon, and makes its rotation freely.Thus, form shaft component 5 is carried out the non-contact supporting and makes it rotate up freely the first thrust bearing division T1 and the second thrust bearing division T2 at diaxon.
In addition, when shaft component 5 rotations, as mentioned above, because seal space S1, S2 that the outer peripheral surface 6a side of sealing component 6 and the outer peripheral surface 7a side of sealing component 7 form are to the diminishing cone-shaped of the private side of shell 2, the suction effect that centrifugal force caused when therefore the lubricant oil in two seal space S1, the S2 was by the suction effect that causes based on capillary force with based on rotation is inhaled into the direction that narrows down to seal space, is the private side of shell 2.Thus, prevent that effectively lubricant oil from spilling from shell 2 inside.In addition, seal space S1, S2 have pooling feature, promptly absorb the volume-variation amount that is accompanied by the temperature variation of the lubricant oil of filling and brings in the inner space of shell 2, in the range of temperature of imagination, the pasta of lubricant oil is positioned at seal space S1, S2 all the time.
In addition, gap between the inner peripheral surface 8a of the fluid passage that utilization is formed by the axial groove 3d1 of clutch shaft bearing sleeve 3, the fluid passage that is formed by the axial groove 4d1 of second bearing sleeve 4, the fluid passage, each bearing play (the thrust-bearing gap of the radial bearing gap of first R1 of radial bearing portion and second R2 of radial bearing portion, the first thrust bearing division T1 and the second thrust bearing division T2) and the spacer member 8 that are formed by the axial groove 8d1 of spacer member 8 and the outer peripheral surface 5a of shaft component 5 forms continuous peripheral passage in the inside of shell 2.And, be filled in lubricant oil in the inner space of shell 2 by this peripheral passage flow circuit, thus, keep the pressure balance of lubricant oil, prevent from simultaneously to follow locally to produce negative pressure and generate bubble and because of the leakage that generates the lubricant oil that bubble causes or the generation of vibration etc.In addition, an end of an end of the fluid passage that is formed by the axial groove 3d1 of clutch shaft bearing sleeve 3 and the fluid passage that formed by the axial groove 4d1 of second bearing sleeve 4 is communicated with the seal space S1, the S2 that become the atmosphere opening side respectively.Therefore, even,, therefore prevent more effectively because the harmful effect that bubble causes owing to when following lubrication oil circulation, discharge bubble to the extraneous gas open sides because certain reason is sneaked in lubricant oil under the alveolate situation.
In addition, though the not shown axial fluid passage that is formed between two bearings sleeve 3,4 and spacer member 8 and the shell 2 also can form by on the inner peripheral surface 2a of shell 2, axial groove being set.
If the structure shown in more than adopting, then can strengthen axial span between the R1 of radial bearing portion, the R2 and improve load capacity for torque load, on the other hand, owing to can prevent the growing up of each bearing sleeve, therefore can make the bearing sleeve 3,4 of desirable precision easily.In addition, because the axial length of the clutch shaft bearing sleeve 3 and second bearing sleeve 4 differs from one another, therefore obvious difference in appearance can prevent the assembling error reliably, and can realize the simplification of component management.
And, in this structure example, in the inner peripheral surface 3a of the clutch shaft bearing sleeve 3 that axial length is grown up change, owing to be formed with the protuberance B with the footpath with radial bearing surface A in lower axial end portion away from radial bearing surface A, therefore, can between radial bearing surface A, A ', guarantee coaxially during assembling reliably, can prevent to reduce the reduction of the bearing performance that causes because of this precision.And, more than be illustrated at the situation that protuberance B is formed full week of spreading all over inner peripheral surface 3a and continuous band shape, as long as but can guarantee the coaxial of bearing sleeve reliably, also protuberance B for example can be provided with in a circumferential direction intermittently.
Fig. 4 represents other structure example (second structure example) of the hydrodynamic bearing device of first mode of execution of the present invention.Hydrodynamic bearing device 21 shown in this figure is with the main difference point of above-mentioned hydrodynamic bearing device 1: the inner peripheral surface 2a of shell 2 extends to the end face this point of shell 2 and follows in this sealing component 6,7 with the homogeneous diameter and forms smaller diameter this point.In this structure, compare with the hydrodynamic bearing device 1 of first structure example, have the simple shapeization that can make shell 2 and the advantage of pathization.And, in this structure example, the upside end face 2c2 butt of the downside end face 3c of bearing sleeve 3 and spacer portion 2c, the downside end face 2c3 butt of the upside end face 4c of bearing sleeve 4 and spacer portion 2c.Therefore other guide marks common reference marks and omits repeat specification based on first structure example.
In the above description, as the dynamic pressure of the R1 of radial bearing portion, R2 and thrust bearing division T1, the T2 dynamic pressure groove of herringbone shape that produced the means illustration, but also can be the dynamic pressure groove of spiral-shaped or other shapes.Perhaps, produce means as dynamic pressure and can adopt so-called step bearing (stepbearing) or many arc bearings.
Fig. 5 schematically represents to pack into the information equipment of the hydrodynamic bearing device shown in Figure 11 in the hydrodynamic bearing device of first mode of execution of the present invention with a structure example of spindle drive motor.This spindle drive motor for example is used for server HDD, and it comprises: hydrodynamic bearing device 1; Be installed on the shaft component 5 of hydrodynamic bearing device 1 rotor (dish hub) 12 and for example across opposed stator coil 10 in radial direction (radially) gap and rotor magnet 11.Stator coil 10 is installed on the periphery of bearing support 9, and rotor magnet 11 is installed on the interior week of dish hub 12.The shell 2 of hydrodynamic bearing device 1 is installed in the interior week of bearing support 9.On dish hub 12, maintain dish D such as one or more disk.When to stator coil 10 energisings, effect lower rotor part magnet 11 rotations of the electromagnetic force between stator coil 10 and rotor magnet 11, thus, dish hub 12 and the dish D and shaft component 5 one that remain on the dish hub 12 are rotated.
And the hydrodynamic bearing device that more than is illustrated is not limited to the spindle drive motor that dish devices such as HDD are used, and also can preferably use at the motor that requires high speed rotating, high load capacity to torque load, for example in the fan motor.
Fig. 6 schematically represent to pack into example of fan motor of hydrodynamic bearing device 1 of first mode of execution of the present invention wherein makes an example of stator coil 10 and rotor magnet 11 opposed so-called radial gap type fan motors across radial direction (radially) gap.The motor of illustrated example is main, and spindle drive motor structure with shown in Figure 5 is different in the following areas: the stator 13 fixing in the upper end of shaft component 5 periphery has blade this point, bearing support 9 as the housing performance function this point of accommodating each structure member of motor at outer peripheral surface.And therefore other guide marks common reference marks and omits repeat specification based on spindle drive motor shown in Figure 5.
Below, based on Fig. 7～Figure 12 the hydrodynamic bearing device of second mode of execution of the present invention and the motor that possesses this device are elaborated.
Fig. 7 schematically represents to be incorporated with the information equipment of hydrodynamic bearing device of second mode of execution of the present invention with a structure example of spindle drive motor.This spindle drive motor is used for disk drive devices such as HDD, and it comprises: hydrodynamic bearing device 101; Be installed on the shaft component 102 rotor (dish hub) 103 and for example across opposed stator coil 104 in radial direction gap and rotor magnet 105.Stator coil 104 is installed on the periphery of bearing support 106, and rotor magnet 105 is installed on the interior week of dish hub 103.The shell 107 of hydrodynamic bearing device 1 is installed in the interior week of bearing support 106.On dish hub 103, maintain dish D11 such as one or more disk.When to stator coil 104 energisings, utilize the electromagnetic force between stator coil 104 and the rotor magnet 105 to make rotor magnet 105 rotations, thus, dish hub 103 and the dish D11 and shaft component 102 one that remain on the dish hub 103 are rotated.
Fig. 8 represents a configuration example of the hydrodynamic bearing device of second mode of execution of the present invention.This hydrodynamic bearing device 101 possesses following main structure member: the bearing components 108 of fixed side and the solid of rotation with the rotary side that is inserted into shaft component 102 all in the bearing components 108.In this structure example, solid of rotation separately is provided with in the axial direction by shaft component 102 and on shaft component 102 that the sealing component 109,110 at two places constitutes.In addition, in this structure example, bearing components 108 comprises: two of separate configuration bearing sleeves 181,181 in the axial direction; Be installed on the spacer member 182 between the two bearings sleeve 181,181; At the shell 107 that is fixed with two bearings sleeve 181,181 and spacer member 182 interior week.
In the hydrodynamic bearing device 101 shown in Figure 8, as described later, between the outer peripheral surface 102a of the inner peripheral surface 181a of upside bearing sleeve 181 and shaft component 102, be provided with first R11 of radial bearing portion, between the outer peripheral surface 102a of the inner peripheral surface 181a of downside bearing sleeve 181 and shaft component 102, be provided with second R12 of radial bearing portion.In addition, between the downside end face 109b of the upside end face 181b of upside bearing sleeve 181 and sealing component 109, be provided with the first thrust bearing division T11, between the upside end face 110b of the downside end face 181c of downside bearing sleeve 181 and sealing component 110, be provided with the second thrust bearing division T12.
The porous plastid that two bearing sleeves 181,181 constitute by sintering metal, especially be that the porous plastid of the sintering metal of primary coil forms cylindric with copper.Two bearings sleeve 181,181 can also be formed by soft metals such as brass.On the outer peripheral surface 181d of bearing sleeve 181, go up uniformly-spaced to be provided with axial groove 181d1 at a plurality of positions of circumferencial direction (illustrated example is 3 positions).
On the inner peripheral surface 181a of two bearings sleeve 181,181, be respectively equipped with the zone of the radial bearing surface A11 that constitutes the R11 of first, second radial bearing portion, R12, shown in Fig. 9 (A), a plurality of dynamic pressure groove 181a1 with herringbone shape alignment arrangements on the zone that constitutes radial bearing surface A11 form symmetric shape in the axial direction.Dynamic pressure groove 181a1 also can be arranged as known other shapes, and is for example spiral-shaped etc.
Shown in Fig. 9 (B), be formed with the first dynamic pressure groove zone that constitutes by the helically shaped a plurality of dynamic pressure groove 181b1 of alignment arrangements on part or all annular section of the upside end face 181b of two bearings sleeve 181,181.In addition, shown in Fig. 9 (C), on part or all annular section of downside end face 181c, be formed with the second dynamic pressure groove zone of a plurality of dynamic pressure groove 181c1 formations of alignment arrangements adult word shape.In the present embodiment, the first dynamic pressure groove zone of the bearing sleeve 181 of upside constitutes the thrust bearing surface B11 of the first thrust bearing division T11, and the second dynamic pressure groove zone of the bearing sleeve 181 of downside constitutes the thrust bearing surface C11 of the second thrust bearing division T12.Above-mentioned dynamic pressure groove 181a1,181b1 and 181c1 can both form simultaneously with the shaping of bearing sleeve 181.
Sealing component 109,110 forms ring-type by soft metal materials such as brass, other metallic material or resin material, and for example be adhesively fixed on the outer peripheral surface 102a of shaft component 102, when being adhesively fixed, being coated to binder on the shaft component 102 is filled into as the circumferential groove 102c of binder reservoir and solidifies, thus, sealing component 109,110 improves with respect to the bonding strength of shaft component 102.
Be formed with the first seal space S11 of specified volume between the inner peripheral surface 107a of the upper end open portion side of the outer peripheral surface 109a of sealing component 109 and shell 107, in addition, be formed with the second seal space S12 of specified volume between the inner peripheral surface 107a of the lower ending opening portion side of the outer peripheral surface 110a of sealing component 110 and shell 107.In this structure example, the outer peripheral surface 109a of sealing component 109 and the outer peripheral surface 110a of sealing component 110 form respectively towards the outer side of the bearing means conical surface shape of undergauge gradually.Therefore, two seal space S11, S12 constitute to direction near each other (internal direction of the shell 107) cone-shaped of undergauge gradually.When shaft component 102 rotation, the suction effect that centrifugal force causes when suction effect that the lubricant oil in two seal space S11, the S12 causes by capillary force and rotation is inhaled into the direction (internal direction of shell 107) that narrows down to seal space.Thus, prevent that effectively lubricant oil from spilling from the inside of shell 107.For preventing leakage of oil reliably, can form the tunicle (not shown) that forms by oil-proofing agent respectively at the upper and lower end face of shell 107, the upside end face 109c of sealing component 109 and the downside end face 110c of sealing component 110.
First and second seal space S11, S12 have pooling feature, and this pooling feature absorbs the volume-variation amount that is accompanied by the temperature variation of the lubricant oil in the inner space that is filled into shell 107 and causes.In the range of temperature of imagination, pasta is positioned at two seal space S1, S2 all the time.For achieving the above object, the summation with the volume of two seal space S11, S12 is set at the volume-variation amount that causes greater than the temperature variation that is accompanied by the lubricant oil that is filled in the inner space at least.
The assembling of the hydrodynamic bearing device 101 of said structure is undertaken by following operation.
With bearing sleeve 181,181 and spacer member 182 utilize bonding, be pressed into, suitably means such as deposited are fixed on the inner peripheral surface 107a of shell 107.Then, after interior week with shaft component 102 insertion bearing sleeves 181,181 and spacer member 182, with sealing component 109,110 clipping the mode of bearing sleeve 181,181 and spacer member 182, and the periphery of the circumferential groove 102c of the shaft component 102 that under the state of the axial clearance of guaranteeing to stipulate, is adhesively fixed.When finishing the assembling of hydrodynamic bearing device 101 like this, in by the inner space of two sealing components, 109,110 hermetically sealed shells 107, the internal porosity that also comprises two bearings sleeve 181,181 is for example filled lubricant oil as lubricating fluid.Under atmospheric pressure open carrying out after the filling of lubricant oil can be impregnated in the lubricant oil by the hydrodynamic bearing device of for example assembling being finished 101 in vacuum tank.
In the hydrodynamic bearing device 101 of said structure, when shaft component 102 rotations, the radial bearing surface A11 of the inner peripheral surface 181a of two bearings sleeve 181 is opposed across the radial bearing gap with the outer peripheral surface 102a of shaft component 102 respectively.And, follow the rotation of shaft component 102, in each radial bearing gap, produce the dynamic pressure of lubricant oil, by this pressure non-contact supporting axle member 102 diametrically, make its rotation freely.Thus, form non-contact supporting axle member 102 diametrically and make its rotation first R1 of radial bearing portion and second R2 of radial bearing portion freely.
In addition, when shaft component 102 rotations, the downside end face 109b of zone (the first dynamic pressure groove zone) and sealing component 109 of thrust bearing surface B11 of upside end face 181b of bearing sleeve 181 that constitutes upside is opposed across the first thrust-bearing gap of regulation, in addition, it is opposed across the second thrust-bearing gap of regulation to constitute the upside end face 110b of zone (the second dynamic pressure groove zone) and sealing component 110 of thrust bearing surface C11 of downside end face 181c of downside bearing sleeve 181.And, follow the rotation of shaft component 102, in each thrust-bearing gap, produce the lubricant oil dynamic pressure, at the diaxon non-contact supporting axle member 102 that makes progress, make its rotation freely according to this pressure.Thus, be formed on make progress non-contact supporting axle member 102 and make freely the first thrust bearing division T11 and the second thrust bearing division T12 of its rotation of diaxon.
But, in the running of hydrodynamic bearing device 101, exist and follow part generation negative pressure and generate bubble, produce the situations such as generation of the leakage or the vibration of lubricant oil owing to generating bubble.To this, in the present embodiment, axial groove 181d1, the axial groove 182d1 of spacer member 182, each axial clearance (radial bearing gap of the R11 of first, second radial bearing portion, R12 by two bearings sleeve 181,181, the thrust-bearing gap of first, second thrust bearing division T11, T12) and the gap between the outer peripheral surface 102a of the inner peripheral surface 182a of spacer member 182 and shaft component 102, form continuous circulation stream in the inside of hydrodynamic bearing device 101, therefore in bearing operation, lubricant oil circulates by this circulation stream.Prevent above-mentioned unfavorable condition thus effectively.In addition, the end of the axial groove 181d1 of two bearings sleeve 181 is communicated with the seal space S11, the S12 that become the atmosphere opening side respectively.Therefore,, be discharged to the extraneous gas open sides when following lubrication oil circulation, therefore prevent more effectively because the harmful effect that bubble causes owing to bubble even in lubricant oil, sneaking under the alveolate situation owing to certain reason.
In the structure shown in above, use and have the first dynamic pressure groove zone that constitutes by dynamic pressure groove 181b1, the bearing sleeve 181,181 that on downside end face 181c, has the second dynamic pressure groove zone that constitutes by dynamic pressure groove 181c1 at upside end face 181b respectively, in other words, use two identical bearing sleeves to form bearing components 108.Therefore, bearing sleeve 181,181 can be installed on the shell 107 under the situation of not considering the upper-lower position relation, can avoid the hydrodynamic bearing device 101 out of use unfavorable conditions that cause because of assembly defect, both end sides at bearing components 108 is provided with thrust bearing division T11, T12 simultaneously, can obtain the good hydrodynamic bearing device of torque rigidity easily and with low cost.Especially in this structure example, because with the dynamic pressure groove 181b1 alignment arrangements of upside end face 181b is spiral-shapedly to form the first dynamic pressure groove zone, the dynamic pressure groove 181c1 alignment arrangements adult word shape of downside end face 181c is formed the second dynamic pressure groove zone, therefore can improve the identity of both ends of the surface, prevent mistaken up and down situation of installing reliably each bearing sleeve 181.
In addition, with two kinds of bearing sleeves intensive be a kind of bearing sleeve, correspondingly except can reducing the parts unit price, can also reduce the component management cost.
And, in this structure example, on the thrust bearing surface B11 towards the first thrust-bearing gap (the first dynamic pressure groove zone) of the first thrust bearing division T11, be formed with the helically shaped dynamic pressure groove of alignment arrangements, on the thrust bearing surface C11 towards the second thrust-bearing gap (the second dynamic pressure groove zone) of the second thrust bearing division T12, be formed with the dynamic pressure groove of alignment arrangements adult word shape, but, as long as can guarantee identity, then for example can be by the groove number, the different alignment arrangements in tilt angle becomes the dynamic pressure groove of same shape to constitute the first dynamic pressure groove zone and the second dynamic pressure groove zone.
In addition, below only consider from the identity angle, determine the alignment arrangements shape of the dynamic pressure groove in the first dynamic pressure groove zone and the second dynamic pressure groove zone, but, also can make the alignment arrangements shape of dynamic pressure groove different according to for example first thrust bearing division T11, the needed pressure of the second thrust bearing division T12 with groove number etc.
Owing in this structure example, the spacer member 182 of non-porous plastid is installed between bearing sleeve 181,181, therefore can reduces the lubricants capacity that should be filled in bearing inside.Thus, can also shorten the axial dimension of sealing component 109,110, enlarge the bearing span of the radial bearing R11 of portion, R12.
In addition, though the diagram of omission, in the hydrodynamic bearing device 101 of said structure, the either party in the sealing component 109,110 can be integrally formed with shaft component 102, according to this structure, the assembling of hydrodynamic bearing device 101 oversimplified more.
In addition, be illustrated at the situation that dynamic pressure that the radial bearing gap produces hydrodynamic produces means (dynamic pressure groove) that is arranged in interior week in the above description, but the dynamic pressure groove also can be arranged on the outer peripheral surface 102a of the opposed shaft component 102 in radial bearing gap at bearing sleeve 181.At this moment, because the upper-lower position of two bearings sleeve relation can not brought influence to verticity, therefore, the dynamic pressure groove that is used to form first R1 of radial bearing portion and its shape of dynamic pressure groove that is used to form second R2 of radial bearing portion etc. can differ from one another.
Figure 10 represents other structure example (second structure example) of the hydrodynamic bearing device of second mode of execution of the present invention.Hydrodynamic bearing device 121 shown in this figure is mainly different in the structure that is made of two bearing sleeves 181,181 and shell 7 on bearing components 108 this point with hydrodynamic bearing device 101 shown in Figure 8.At this moment, on the inner peripheral surface 181a of bearing sleeve 181, be provided with under the situation of dynamic pressure groove, if this dynamic pressure groove 181a2 shape is adopted as shown in figure 11 a plurality of axial groove shapes that uniformly-spaced are provided with at circumferencial direction, then can with structure shown in Figure 8 similarly, under the situation of the upper-lower position of not considering two bearings sleeve 181,181, install.The R11 of radial bearing portion, the R12 that are made of the dynamic pressure groove 181a2 of this mode are so-called step bearings.Certainly, be located at the dynamic pressure groove that will be used to form the R11 of radial bearing portion, R12 under the situation on the outer peripheral surface 102a of shaft component 102, with similarly above-mentioned, its shape can freely be set.And above-mentioned structure in addition is owing to based on first structure example shown in Figure 8, therefore be marked with common reference marks and omit repeat specification.
And in the above hydrodynamic bearing device that is illustrated 101,121, the R11 of radial bearing portion, R12 can be by constituting becoming so-called many arc bearings that a plurality of arc surfaces are set on the zone of radial bearing surface.In addition, as thrust bearing division T11, T12, except that produce the dynamic pressure effect of lubricant oil by above-mentioned herringbone shape or spiral-shaped etc. dynamic pressure groove, can also adopt is becoming on the zone of thrust bearing surface so-called step bearing that a plurality of radial direction grooves are provided with predetermined distance in a circumferential direction or so-called wave mode bearing (stepped ramp type becomes wave mode) etc.
In addition, in the above description, as the fluid of the inside that is filled in hydrodynamic bearing device 101,102, illustration lubricant oil, can produce the fluid of dynamic pressure in each bearing play but can also use in addition, for example gas such as air or magnetic fluid etc.
More than, situation about using in the spindle drive motor used of dish device that the hydrodynamic bearing device 101 of present embodiment is packed into is illustrated, but the hydrodynamic bearing device 101 of present embodiment is except that being used for spindle drive motor that information equipment uses, also can preferably use at the motor that requires high speed rotating, high torque rigidity, for example in the fan motor.
Figure 12 schematically represent to pack into second mode of execution of the present invention hydrodynamic bearing device 101 fan motor an example, wherein make an example of stator coil 104 and rotor magnet 105 opposed so-called radial gap type fan motors across radial direction (radially) gap.The motor of illustrated example is main, and spindle drive motor structure with shown in Figure 7 is different in the following areas: have blade this point and bearing support 136 as the housing performance function this point of accommodating each structure member of motor at the fixing rotor 133 of the upper end of shaft component 102 periphery at outer peripheral surface.And therefore other guide marks common reference marks and omits repeat specification based on spindle drive motor shown in Figure 7.
Below, based on Figure 13～Figure 20 the hydrodynamic bearing device of the 3rd mode of execution of the present invention and the motor that possesses this device are elaborated.
Figure 13 schematically represents to be incorporated with the information equipment of hydrodynamic bearing device of the 3rd mode of execution of the present invention with a structure example of spindle drive motor.This spindle drive motor is used for disk drive devices such as HDD, and it comprises: drive portion 204 and the bearing support 205 that the solid of rotation 202 with shaft component 206 is carried out the hydrodynamic bearing device 201 of non-contact supporting, for example constitutes across the opposed stator coil 204a in radial direction gap and rotor magnet 204b diametrically.Hub 203 is installed on shaft component 206, on hub 203, is fixed with rotor magnet 204b.In addition, on bearing support 205, be fixed with stator coil 204a.The shell 210 of hydrodynamic bearing device 201 is fixed in the interior week of bearing support 205.In addition, as shown in the drawing, on hub 203, maintain one or more (Figure 13 is 2) dish D21.In the disk drive device that so constitutes, when when stator coil 204a switches on, the electromagnetic force that utilization produces between stator coil 204a and rotor magnet 204b makes rotor magnet 204b rotation, follows therewith, is fixed in dish D21 and the rotation of shaft component 206 one on the hub 203.
Figure 14 represents an example (first structure example) of the hydrodynamic bearing device 201 of the 3rd mode of execution of the present invention.Hydrodynamic bearing device 201 shown in this figure possesses following main composition member: have the bearing components 209 of a plurality of bearing sleeves and the solid of rotation 202 of the shaft component 206 with the interior week of inserting bearing components 209.
Sealing component 207,208 forms from outer peripheral surface 206a to the side-prominent form of external diameter under the state that is fixed in shaft component 206, and is accommodated in the inside (the interior week of big diametral plane 210b, 210c) of shell 210 respectively.Can use bonding or be pressed into, be pressed into and various means such as bonding and use to the fixing fixing means of shaft component 206 as sealing component 207,208.Being fixed with to be provided with on the position of sealing component 207,208 in the outer peripheral surface 206a of shaft component 206 becomes the circumferential groove of binder reservoir 206a1,206a2, realizes the raising of sealing component 207,208 with respect to the bonding strength of shaft component 206 thus.And sealing component 207,208 can be formed by soft metal materials such as brass or other metallic material, also can form with resin material.In addition, in the sealing component 207,208 can be integrally formed at shaft component 206.Like this, make under the integrally formed situation of a sealing component and shaft component, for example can also be with metal shaft component 206 as insertion parts, utilize resin injection to be shaped in the sealing component any.
Form the seal space S21 of specified volume between the outer peripheral surface 207a of sealing component 207 and the big diametral plane 210b of shell 210, form the seal space S22 of specified volume between the outer peripheral surface 208a of sealing component 208 and the big diametral plane 210c of shell 210.In this structure example, the outer peripheral surface 207a of sealing component 207 and the outer peripheral surface 208a of sealing component 208 constitute respectively towards the outer side of shell 210 cone-shaped of undergauge gradually.Therefore, seal space S21, S22 have the diminishing cone-shaped of private side (clutch shaft bearing sleeve 211 sides) towards shell 210.
Constitute in a plurality of bearing sleeves of bearing components 209, the porous plastid that clutch shaft bearing sleeve 211 for example is made of sintering metal forms cylindric.In this embodiment, clutch shaft bearing sleeve 211 is formed cylindric by the porous plastid that with copper is the sintering metal of primary coil, and by be pressed into, bonding or be pressed into means such as bonding and be fixed on the inner peripheral surface (path face 210a) of shell 210.And, clutch shaft bearing sleeve 211 also can be formed by the porous plastid that nonmetallic material such as resin or pottery constitute, in addition, except that porous plastids such as sintering metal, also can form by the material of structure of emptying aperture that inside does not have emptying aperture or only has a size of the degree that lubricant oil can not come in and go out.Second bearing sleeve 212 described later also can be selected same material.
A plurality of radial bearing surface A21, A22 separately are formed on the inner peripheral surface 211a of clutch shaft bearing sleeve 211 in the axial direction.In this embodiment, as shown in figure 15, the zone (dynamic pressure generating section) of a plurality of dynamic pressure groove 211a1 alignment arrangements behaviour word shapes is set at the radial bearing surface A21 of upside, and the zone (dynamic pressure generating section) of a plurality of dynamic pressure groove 211a2 alignment arrangements behaviour word shapes is formed on the radial bearing surface A22 of downside.The outer peripheral surface 206a of these radial bearing surface A21, A22 and shaft component 206 is opposed, when shaft component 206 rotation, and outer peripheral surface 206a between form the radial bearing gap (with reference to Figure 14) of the R21 of first, second radial bearing portion described later, R22 respectively.
In a plurality of bearing sleeves that constitute bearing components 209, the porous plastid that second bearing sleeve 212 for example is made of sintering metal forms cylindric, and is disposed at axial side's side (being downside here) of clutch shaft bearing sleeve 211.In this embodiment, second bearing sleeve 212 is formed cylindric by the porous plastid that with copper is the sintering metal of primary coil, and by be pressed into, bonding or be pressed into means such as bonding and be fixed on the path face 210a of shell 210.Therefore, in this embodiment, clutch shaft bearing sleeve 211 is configured in shell 210 with respect to the zone of second bearing sleeve 212 by upside in week.Particularly, the axial neutral position of the R21 of radial bearing portion, the R22 that forms respectively between the outer peripheral surface 206a of the radial bearing surface A21 of clutch shaft bearing sleeve 211, A22 and opposed with it shaft component 206 is positioned at the upside (near hub 203 sides) in the axial neutral position of bearing components 209.
On whole of the lower end surface 212b of second bearing sleeve 212 or a part of zone, be formed with thrust bearing surface B21.As shown in figure 16, in this structure example, be formed with (in other words, along the circumferential direction alignment arrangements has a plurality of dynamic pressure groove 212b1 of joggling part) zone with a plurality of dynamic pressure groove 212b1 alignment arrangements adult word shapes.This thrust bearing surface B21 is opposed with the upper-end surface 207b that is fixed in the sealing component 207 on the shaft component 206, and when shaft component 206 rotation, and the upper-end surface 207b of sealing component 207 between form the thrust-bearing gap (with reference to Figure 14) of the first thrust bearing division T21 described later.
In addition, on whole of the upper-end surface of clutch shaft bearing sleeve 211 211b or a part of zone, form thrust bearing surface C21.As shown in figure 17, in this structure example, form zone with a plurality of dynamic pressure groove 211b1 alignment arrangements adult word shapes.This thrust bearing surface C21 is opposed with the lower end surface 208b that is fixed in the sealing component 208 on the shaft component 206, when shaft component 206 rotation, and the lower end surface 208b of sealing component 208 between form the thrust-bearing gap (with reference to Figure 14) of the second thrust bearing division T22 described later.
Here, the internal diameter size of second bearing sleeve 212 (diameter dimension of inner peripheral surface 212a) is greater than the internal diameter size of clutch shaft bearing sleeve 211.Therefore, under the state in the interior week of shaft component 206 being inserted the clutch shaft bearing sleeve 211 and second bearing sleeve 212, only the inner peripheral surface 211a of clutch shaft bearing sleeve 211 can become radial bearing surface A21, A22.
On outer peripheral surface 211d, the 212d of each bearing sleeve 211,212, a plurality of (illustrated example is 3) axial groove 211d1,212d1 is respectively in a circumferential direction uniformly-spaced to form.Thus, formation can be communicated with the fluid flowing path between thrust bearing division T21, the T22 that separately forms in the axial direction.
For example assemble by the hydrodynamic bearing device 201 that said structure constitutes by following operation.
At first, clutch shaft bearing sleeve 211 is adhesively fixed on the path face 210a of shell 210.At this moment, in the same plane or than the mode of step surface 210e with the upper-end surface 211b of clutch shaft bearing sleeve 211 by axial upside (near the lower end surface 208b side of sealing component 208) with the step surface 210e of the shell 210 that is positioned at its outside diameter, under the state that has carried out axially locating, be fixed on the path face 210a.Thus, only be located between the lower end surface 208b of thrust bearing surface C21 on the upper-end surface 211b of clutch shaft bearing sleeve 211 and sealing component 208 and can form the second thrust bearing division T22.
Then, with lower end side (an axial side of clutch shaft bearing sleeve 211) importing to path face 210a in the week of second bearing sleeve 212 from shell 210.And, determine the axial position of second bearing sleeve 212 with respect to shell 210, axially spaced-apart distance till making from the lower end surface 212b of second bearing sleeve 212 that is provided with thrust bearing surface B21 to the upper-end surface 211b of the clutch shaft bearing sleeve 211 that is provided with thrust bearing surface C21 becomes specified value, in this position second bearing sleeve 212 is fixed on the path face 210a of shell 210.Thus, the combination of bearing components 209 finishes.
Like this, by using with the intensive structure to a bearing sleeve (clutch shaft bearing sleeve 211) of both sides' radial bearing surface A21, A22, therefore, for example the forming accuracy during radial bearing surface A21, the A22 by improving shaping both sides on clutch shaft bearing sleeve 211 in advance only can be finished both sides' radial bearing surface A21, the coaxality between the A22 accurately.Therefore, existing technology is that both sides' radial bearing surface A21, A22 are arranged on the respectively different bearing sleeves, and the positioning parts that will so obtain is fixed on the shell 210, compares more manageable coaxality with the situation of such prior art.In addition, and compare, realize the raising of operating efficiency, can cut down finished cost thus in the situation of carrying out the same axial adjustment between the inner peripheral surface (radial bearing surface) between a plurality of sleeves.
In addition, in this structure example, the clutch shaft bearing sleeve 211 that will have a plurality of radial bearing surface A21, A22 is disposed at the axial position of centre of gravity side of comparing relative close solid of rotation 202 with second bearing sleeve 212 that does not have radial bearing surface.According to this structure, as described later, reduce the axial centre of the R21 of radial bearing portion, the R22 that between the outer peripheral surface 206a of each radial bearing surface A21, A22 and opposed with it shaft component 206, form and the axially spaced-apart distance of solid of rotation 202 centers of gravity, can improve the torque rigidity of hydrodynamic bearing device 201.
And, in this structure example,, therefore compare with the situation that described thrust bearing surface B21, C21 are located on the single bearing sleeve because the second thrust bearing surface B21, C21 are located at respectively on the different bearing sleeves, can increase axial span.Therefore, according to this structure, can realize the raising of torque rigidity.Particularly, as this structure example, by in the end face of a plurality of bearing sleeves 211,212, be presented axially in conduct first end face of at last distolateral (for example lower end side) lower end surface 212b, with on the upper-end surface 211b away from conduct second end face of lower end surface 212b thrust bearing surface B21, C21 are set respectively in the axial direction, can increase the axially spaced-apart distance of thrust bearing surface B21, C21 thus to greatest extent, thus, can further realize the raising of torque rigidity.
And, in this structure example, at the upper-end surface 212c butt of lower end surface 211c that makes clutch shaft bearing sleeve 211 and opposed with it second bearing sleeve 212 state under, with second bearing sleeve 212 with respect to shell 210 location and fixing, but also can be with above-mentioned mode positioning and fixing second bearing sleeve 212 in addition.For example, can be with the extent of deviation of the axial dimension of imagination clutch shaft bearing sleeve 211 and second bearing sleeve 212, form the mode in gap slightly at (between lower end surface 211c and the upper-end surface 212c) between the two bearings sleeve 211,212, preestablish the axial dimension of the path face 210a of the axial dimension of two bearings sleeve 211,212 and shell 210.Certainly, also can be earlier with second bearing sleeve 212 with respect to shell 210 position fixing after, clutch shaft bearing sleeve 211 is fixed on the shell 210.
Carried out as described above after the combination of bearing components 209, shaft component 206 has been inserted the interior week of each bearing sleeve 211,212, and sealing component 207,208 has been fixed in the assigned position of shaft component 206.At this moment, by the axially spaced-apart till will be from the upper-end surface 207b of side's sealing component 207 to the lower end surface 208b of the opposing party's sealing component 208 apart from management under the state of specified value, each sealing component 207,208 is fixed in shaft component 206, and the summation in the thrust-bearing gap of each thrust bearing division T21, T22 described later thus is set within the limits prescribed.And any in the sealing component 207,208 can predetermined fixed also can be integrally formed with shaft component 206 on shaft component 206 before insertion.
After assembling is finished through above-mentioned operation, in the inner space of the shell 210 of sealed member 207,208 sealings, for example inject lubricant oil as lubricating fluid.Thus, the lubricated oil in inner space of bearing components 209 that comprises the inside emptying aperture (the inside emptying aperture of porous plastid tissue) of each bearing sleeve 211,212 is full of.The filling of lubricant oil for example can be impregnated in the lubricant oil in vacuum tank by the hydrodynamic bearing device 201 that assembling is finished after, under atmospheric pressure open carrying out.
In the hydrodynamic bearing device 201 of said structure, when shaft component 206 (solid of rotation 202) rotated, the outer peripheral surface 206a that is formed at two radial bearing surface A21, A22 on the inner peripheral surface 211a of clutch shaft bearing sleeve 211 and shaft component 206 was opposed across the radial bearing gap.And, follow the rotation of shaft component 206, the lubricant oil in above-mentioned radial bearing gap is pressed into the axial centre side of being located at the dynamic pressure groove on each radial bearing surface A21, A22 respectively, and its pressure improves.Constitute dynamic pressure effect first R21 of radial bearing portion and second R22 of radial bearing portion (with reference to Figure 14) of non-contact supporting axle member 206 (solid of rotation 202) diametrically by this dynamic pressure groove 211a1,211a2 respectively.
Meanwhile, the thrust-bearing gap between the upper-end surface 207b of thrust bearing surface B21 on the lower end surface 212b that is formed at second bearing sleeve 212 and opposed with it sealing component 207 and be formed at thrust bearing surface C21 on the upper-end surface 211b of clutch shaft bearing sleeve 211 and the lower end surface 208b of opposed with it sealing component 208 between the thrust-bearing gap, form the oil film of lubricant oil respectively by the dynamic pressure effect that is arranged at dynamic pressure groove 212b1,211b1 on each thrust bearing surface B21, C21.And, constitute the pressure utilize these oil films respectively at diaxon the make progress first thrust bearing division T21 and the second thrust bearing division T22 (with reference to Figure 14) of non-contact supporting axle member 206 (solid of rotation 202).
In addition, as mentioned above, because seal space S21, the S22 with the outer peripheral surface 208a side formation of sealing component 208 is towards the diminishing cone-shaped of the private side of shell 210 in the outer peripheral surface 207a side of sealing component 207, therefore, under the suction effect that centrifugal force causes when suction effect that is caused by capillary force and rotation of lubricant oil in two seal space S21, the S22, be inhaled into the direction that narrows down to seal space, be the private side of shell 210.Thus, prevent that effectively lubricant oil from spilling from shell 210 inside.In addition, seal space S21, S22 have the pooling feature that absorbs the volume-variation amount that is accompanied by the temperature variation of the lubricant oil in the inner space that is filled into shell 210 and causes, in the range of temperature of imagination, the pasta of lubricant oil is positioned at seal space S21, S22 all the time.
In addition, owing to there is fluid flowing path by axial groove 211d1, the 212d1 formation of each bearing sleeve 211,212, therefore, even under the situation of the imbalance of pressure of lubricant oil, also can promptly remove its pressure difference, can prevent to follow locally to produce negative pressure and generate bubble and produce the leakage of the lubricant oil that causes or the generation of vibration etc. by bubble.In addition, an end of the fluid flowing path that forms of an end of the fluid flowing path that forms of the axial groove 211d1 by clutch shaft bearing sleeve 211 and the axial groove 212d1 by second bearing sleeve 212 is communicated with the seal space S21, the S22 that become the atmosphere opening side respectively.Therefore, even, be discharged to the extraneous gas open sides when being accompanied by lubrication oil circulation, therefore can prevent the generation of the above-mentioned unfavorable condition that sneaking into of bubble causes more reliably in lubricant oil owing to bubble because certain reason is sneaked under the alveolate situation.
More than, have been described in detail at a structure example of the hydrodynamic bearing device of the 3rd mode of execution of the present invention, but the present invention is not limited to the said structure example, also can be suitable for to form above-mentioned hydrodynamic bearing device with external structure.
More than, to week in shell 210 situation that clutch shaft bearing sleeve 211 is configured on the upper-side area (zones of sealing component 208 sides) with respect to the outer relatively shell 210 of second bearing sleeve 212 being illustrated, but also can be configured in side (sealing component 207 sides) in contrast according to the axial position of centre of gravity of solid of rotation 202.That is, can consider the kind of the equipment that uses according to the hydrodynamic bearing device 201 of packing into, make the position of centre of gravity of solid of rotation 202 be positioned at the situation of the downside (away from a side of hub 203) in the axial neutral position of bearing components 209.In this case, by clutch shaft bearing sleeve 211 being disposed at underside area (zones of sealing component 207 sides) than the outer relatively shell 210 of second bearing sleeve 212, reduce the axial centre of the R21 of radial bearing portion, R22 and the axially spaced-apart distance of solid of rotation 202 centers of gravity, can obtain the high torque rigidity thus.
In addition, more than internally do not have radial bearing surface a week second bearing sleeve 212 describe with the situation that shell 210 splits form, but also they can be formed as one.Figure 18 represents the one example, forms as one to the protuberance 210f and the shell 210 of the side-prominent sleeve shape of internal diameter from the path face 210a of shell 210.At this moment, the internal diameter size of protuberance 210f (diameter dimension of inner peripheral surface 210f1) is greater than the internal diameter size of clutch shaft bearing sleeve 211.Therefore, under the state in interior week of the protuberance 210f that shaft component 206 (with reference to Figure 14) is inserted clutch shaft bearing sleeve 211 and shell 210, same with the said structure example, only the inner peripheral surface 211a of clutch shaft bearing sleeve 211 can become radial bearing surface A21, A22.In addition, on the 210f2 of the lower end surface of protuberance 210f, for example be formed with the radial bearing surface B21 of shape as shown in figure 16.In this embodiment, by this lower end surface 210f2, the inner peripheral surface 210f1 of protuberance 210f links to each other with the big diametral plane 210b of shell 210.In addition, in this illustrated example, on protuberance 210f, be provided with axial through hole 210f4, constitute fluid flowing path by this through hole 210f4 and axial groove 211d1.
According to this structure, can further realize the reduction of part number, simultaneously since the clustered operation of bearing components 209 only positioning and fixing clutch shaft bearing sleeve 211 get final product, can realize the simplification of flow chart thus.
In addition, bearing components 209 can also be included and do not had the 3rd bearing sleeve of radial bearing surface A21, A22 week.Figure 19 represents a wherein example, and bearing components 209 constitutes possesses clutch shaft bearing sleeve 211 and the shell 210 that has as the protuberance 210f of second bearing sleeve, and also possesses the 3rd bearing sleeve 213 in the lower end side of protuberance 210f (second bearing sleeve).In the figure, the internal diameter size of the internal diameter size of protuberance 210f and the 3rd bearing sleeve 213 is all greater than the internal diameter size of clutch shaft bearing sleeve 211.Therefore, same with the said structure example, only the inner peripheral surface 211a of clutch shaft bearing sleeve 211 can become radial bearing surface A21, A22.In addition, thrust bearing surface B21 is located on the lower end surface 213b of the 3rd bearing sleeve 213.On the outer peripheral surface 213d of the 3rd bearing sleeve 213, be formed with axial groove 213d1, constitute above-mentioned fluid flowing path by the through hole 210f4 of this axial groove 213d1 and protuberance 210f and the axial groove 211d1 of clutch shaft bearing sleeve 211.
According to this structure, can easily carry out each bearing sleeve 211,213 location, and, therefore can stably supply with sufficient lubricating oil to each bearing play because any thrust bearing surface B21, C21 are formed by sintering metal with respect to shell 210.Therefore, can prevent oil-break as much as possible, can stablize the higher oil film of performance and form ability in the bearing play.In addition,, form as one, also play the effect of the oil mass of adjusting the lubricant oil that is filled into bearing interior space by a part and shell 210 with bearing sleeve as above-mentioned.
In addition, above illustration to make the inner peripheral surface of shell 210 be the situation of the different shape of diameter (for example path face 210a and big diametral plane 210b, 210c), can certainly use constitute above-mentioned beyond the shell 210 of shape and bearing components 209 with this shell 210.Figure 20 represents the one example, and the structure with hydrodynamic bearing device 201 shown in Figure 14 aspect following is different: the inner peripheral surface of shell 210 is homogeneous diameter (having the certain inner peripheral surface 210g of a diameter) this point; Follow the smaller this point of sealing component 207,208 diameters therewith.At this moment, by the shell 210 that uses this shape, has the advantage of shell 210 simple shapeization and pathization.
In addition, more than at the inner peripheral surface 211a that the alignment arrangements zone (dynamic pressure generating section) of dynamic pressure groove 211a1,211a2 is formed at clutch shaft bearing sleeve 211 with radial bearing surface A21, A22, have the upper-end surface 211b of thrust bearing surface C21 or situation about having on the lower end surface 212b of second bearing sleeve 212 of thrust bearing surface B21 is illustrated, but not necessarily be defined in this mode.For example, the dynamic pressure generating section that dynamic pressure groove 211a1,211a2 constitute can also be formed at outer peripheral surface 206a with the opposed shaft component 206 of each radial bearing surface A21, A22, and also the dynamic pressure generating section that dynamic pressure groove 212b1,211b1 can be constituted be formed on the lower end surface 208b with the upper-end surface 207b of the opposed sealing component 207 of each thrust bearing surface B21, C21, sealing component 208.For the dynamic pressure generating section of mode shown below too, be not limited to bearing components 209 sides, can be formed at opposed with it shaft component 206, each sealing component 207,208 side.
In addition, more than as the R21 of radial bearing portion, R22 and thrust bearing division T21, T22, illustration utilize a plurality of dynamic pressure grooves of alignment arrangements behaviour word shape to produce the structure of the dynamic pressure effect of lubricating fluids, but the present invention is not limited thereto.
For example, as the R21 of radial bearing portion, R22, though it is not shown, but can adopt a plurality of positions, the so-called step-like dynamic pressure generating section of axial groove alignment arrangements in circumferencial direction, or a plurality of arc surfaces of alignment arrangements in a circumferential direction, and and the outer peripheral surface 206a of opposed shaft component 206 between be formed with radial clearance (bearing play), so-called many arc bearings of wedge-like.
In addition, the side of thrust bearing division T21, T22 or both sides can utilize and omit illustrated that on the zone that becomes thrust bearing surface B21, C21 the dynamic pressure groove of a plurality of radial direction groove shape along the circumferential direction is provided with predetermined distance, so-called step bearing or wave mode bearing formations such as (stepped ramp type become wave mode).Certainly, can also adopt the dynamic pressure groove 212b1 of each thrust bearing surface B21, C21, the alignment arrangements shape of 211b1 are made as spiral helicine bearing.
In addition, more than to shaft component 206 rotation and utilize the structure of bearing components 209 these shaft components 206 of supporting to be illustrated, but in contrast, the present invention also can be applicable to bearing components 209 sideway swivels and utilize the structure of shaft component 206 side bearing bearing components 209.
In addition, above illustration lubricant oil be used in the radial bearing gap as being filled in the inside of hydrodynamic bearing device 201 or the thrust-bearing gap produces the fluid of the dynamic pressure effect of fluid, but, in addition, also can use to produce the fluid of dynamic pressure effect in each bearing play, for example gas, magnetic fluid etc. such as air have mobile oiling agent or lubricating grease etc.
Below, based on Figure 21～Figure 31 the hydrodynamic bearing device of the 4th mode of execution of the present invention is described.
Figure 21 be expression the 4th mode of execution of the present invention hydrodynamic bearing device 301 an example (first structure example) contain axial section.Hydrodynamic bearing device 301 shown in this figure is for example packed into and is used in the spindle drive motors such as HDD, and it comprises following main structure member: bearing components 305; Has the solid of rotation 302 that is inserted into the shaft component 303 in week in the bearing components 305.In addition, the details aftermentioned, but the hydrodynamic bearing device 301 shown in this figure constitutes: make radial bearing gap separate configuration on two axial positions, and and two radial bearing clearance C r1, Cr2 between the zone, each gap width is successively decreased towards axial top.
Solid of rotation 302 is by constituting as the bottom: shaft component 303, and it is for example formed by stainless steel and other metal materials, and spreading all over entire axial length, to form diameter certain; Hub (dish hub) 304, it is located at the upper end periphery of shaft component 303; Also have not shown dish, rotor magnet and be used for dish is fixed on pincers on the hub 304.The center of gravity of the solid of rotation 302 of this structure (axially center of gravity) G is positioned at the upside (near hub 304 sides) of the axial centre of bearing components 305.The outer peripheral surface 303a of shaft component 303 forms even surface, and lower end surface 303b forms protruding spherical.
The upper end open portion in week forms above axially the conical surface 305c of hole enlargement gradually in bearing components 305, is formed with annular seal space S 3 between the outer peripheral surface 303a of this conical surface 305c and shaft component 303.
In the inner peripheral surface 305a zone below the above-mentioned conical surface 305c of ratio in bearing components 305 leans on, separately be provided with the zone (zone of blacking among the figure) of the radial bearing surface 308,309 that becomes the R31 of radial bearing portion, R32 at two positions up and down.As shown in figure 22, on radial bearing surface 308,309, be respectively arranged with a plurality of dynamic pressure groove 308a, the 309a of alignment arrangements adult word shape as dynamic pressure generating section.The dynamic pressure groove 308a of upside forms axially asymmetric with respect to axial centre m regional between tipper up and down, the axial dimension X1 of the upper-side area of axial centre m is greater than the axial dimension X2 of underside area.On the other hand, the dynamic pressure groove 309a of downside forms axial symmetry, and its regional up and down axial dimension equates with above-mentioned axial dimension X2 respectively.At this moment, when shaft component 303 rotation, for the inhalation power (pump suction) of the lubricant oil that causes by the dynamic pressure groove, the inhalation power that the inhalation power that the dynamic pressure groove 308a of upside causes causes greater than the dynamic pressure groove 9a of the symmetric figure of downside relatively.Under the situation that does not need pump suction, can make the dynamic pressure groove 308a of upside and the axial symmetric shape of the same employing of dynamic pressure groove 309a of downside.The dynamic pressure groove is beyond also can alignment arrangements behaviour word shape, for example spiral-shaped or other known shapes.In addition, for simplifying drawing, omitted the dynamic pressure groove among Figure 21.
Part or all annular section of the inner bottom surface 305b of bearing components 305 becomes the thrust bearing surface of thrust bearing division T3, and in this structure example, this zone forms smooth surfaces.
The inner peripheral surface 305a that comprises the bearing components 305 of radial bearing surface 308,309 forms the taper that successively decreases towards axial top internal diameter.Just, in this structure example, be formed among radial bearing clearance C r1, the Cr2 between the outer peripheral surface 303a of radial bearing surface 308,309 and shaft component 303, each upper end portion becomes narrow D1 of the little width of gap width, and each underpart becomes wide D2 of the big width of gap width.And, be easy understanding, in the illustrated example with the exaggerative expression of the inclined degree of inner peripheral surface 305a, the axially spaced-apart between the reduction ε of the radius clearance between narrow D1 of the width of radial bearing clearance C r1 (or Cr2) and wide D2 of width and two ones apart from the ratio of (axial length in radial bearing gap) L, be the atomic little value of the inclination ε/L shaped ε of becoming/L≤1/500 (if with for the tilt angle of axis then be below 0.11 °).The conical surface that in batches becomes to produce this small tilt angle at low cost with common machining is difficulty relatively, if but with electroforming processing, then because reason described later, this conical surface also can be produced in batches low-cost and accurately.
Below, the manufacturing process to the bearing components 305 of said structure describes based on accompanying drawing.
(Z1) pattern production process
In the pattern production process shown in Figure 23 (A), form and to utilize conductive material, for example implemented the stainless steel, nickel chrome steel of Quenching Treatment, other nickel alloy or the pattern 311 of the solid shaft shape that forms such as evanohm.Pattern 311 also can be formed by the nonmetallic material such as pottery of having implemented conductive processing (for example, forming the tunicle of electric conductivity from the teeth outwards) except these metallic material.
Be provided with the forming section N of shaping electroforming portion 306 in a part of zone of end face of pattern 311 and the outer peripheral surface that is attached thereto.Forming section N is the shape of the relief pattern counter-rotating that makes electroforming portion 306 inboards, on its outer peripheral surface, two positions that separate in the axial direction are formed with the 311a1 of mould portion that the peak portion between dynamic pressure groove 308a, the 309a is formed, the row of 311a2 in a circumferential direction.Certainly, the shape of the 311a1 of mould portion, 311a2 also can be corresponding to the dynamic pressure groove shape, forms spiral-shaped etc.And, comprise that the surface accuracy of the forming section N of the 311a1 of mould portion, 311a2 directly influences the precision of electroforming portion 306.Therefore, forming section N processes as far as possible accurately in advance preferably according to electroforming portion 306 desired various precision.
(Z2) shelter operation
Shown in Figure 23 (B), in sheltering operation, implementing except that forming section N in the outer surface of pattern 311 sheltered, form covered emplacement 312.As the lining material that forms covered emplacement 312, considering that electroforming described later adds man-hour, can preferably use insulating properties and have corrosion proof material with respect to electrolyte solution.
(Z3) electroforming manufacturing procedure
Electroforming processing is by carrying out as follows: after pattern 311 being impregnated in the electrolyte solution of metal ions such as comprising Ni or Cu, to pattern 311 energisings, separate out (electrolysis is separated out) metal target at the forming section N of pattern 311.Also can contain carbon or fluorine in the electrolyte solution as required and be sliding material such as particle or asccharin iso-stress and relax material.The kind of electrodeposit metals is suitably selected according to physical propertys such as the desired hardness of bearing surface, fatigue strength or chemical property.
After the electroforming process finishing, shown in Figure 23 (C), on the forming section N of pattern 311, form the electroforming member 313 that has hidden electroforming portion 306.At this moment, describe the shape of the 311a1 of mould portion, 311a2 at the inner peripheral surface of electroforming portion 306, a plurality of dynamic pressure groove 308a, 309a shown in Figure 22 separately forms in the axial direction.And, thickness for electroforming portion 306, the stripping property of peeling off from pattern 311 when it is blocked up descends, opposite cross the durability decline of electroforming portion 306 when thin when it, therefore, form optimum thickness, for example thickness about 10 μ m～200 μ m according to desired bearing performance or bearing size and then according to purposes etc.
And electroforming portion 306 also can form based on the method for electroless plating (chemical plating) except that the method based on above-mentioned electrolysis plating (plating).Under the situation of employing based on the method for electroless plating, replacing does not need the electric conductivity of pattern 311 or the insulating properties of covered emplacement 312, and covered emplacement 312 preferred utilizations have corrosion proof material formation.
(Z4) insert forming process
Though the diagram of omission in inserting forming process, after electroforming member 313 is disposed at the mould of regulation as insertion parts, uses melted material, for example melting resin to insert shaping.Behind injecting resin, when making resin solidification and carrying out die sinking, as shown in figure 24, can obtain the drip molding that the electroforming member 313 that is made of pattern 311 and electroforming portion 306 and shielding part 307 become one.
Forming with resin under the situation of shielding part 307, as its base resin no matter be that crystalline resin/non-crystalline resin all can use.Can use liquid-crystalline polymer (LCP), polyphenylene sulfide (PPS), polyether-ether-ketone (PEEK), polyoxymethylene (POM), polyamide (PA) etc. as crystalline resin, in addition, can use polyphenylsulphine (PPSU), polyether sulfone (PES), Polyetherimide (PEI), polyamide-(acyl) imines (PAI) etc. as non-crystalline resin.The reinforcing material (no matter fibrous, Powdered etc. form) or the various packing materials such as oiling agent, conductive material that also can be as required in illustrative above-mentioned base resin, add one or more.
And shielding part 307 can use the low melting metals such as melted material, for example magnesium alloy or aluminum alloy beyond the resin.In addition, also can after utilizing the mixture injection moulding of metal powder and binder, adopt degreasing sintered so-called MIM to be shaped, and, also can use the so-called CIM of the mixture of pottery and binder to be shaped.
Here, aspect the characteristic of electroforming processing, to the beginning face of separating out of pattern 311, be that the internal surface of electroforming portion 306 becomes by the dense face of the surface accuracy of transfer printing pattern 311 (forming section N) accurately, on the other hand, separate out the face that finishes side, be that the outer surface of electroforming portion 306 forms roughened surface.Therefore, when the shaping of shielding part 307, melting resin enters among electroforming portion 306 surfaces small concavo-convex, and by so-called anchoring effect, electroforming portion 306 becomes firmly with the combination force of shielding part 307.
(Z5) separation circuit
The electroforming member 313 that forms as described above is transplanted on separation circuit, it is separated into the bearing components 305 and pattern 311 of electroforming portion 306 and shielding part 307 formation one.In this separation circuit, for example by pattern 311 or bearing components 305 are applied impact, make the inner peripheral surface hole enlargement a little of electroforming portion 306, from the surface lifting electroforming portion 306 of pattern 311.Thus, pattern 311 can separate from bearing components 305, after extracting pattern 311, obtains as the bearing components 305 of finishing part.And, as the means of peeling off of electroforming portion 306, except that above-mentioned means, can also use for example by heating (or cooling) electroforming portion 306 and pattern 311, between produces the method for thermal expansion amount difference, or and with the method for two means (impact and heat) etc.
In addition, because bearing components 305 formed bottom tube-like, and inner peripheral surface 305a forms towards the opening side taper of undergauge gradually, therefore, separates patterns 311 from bearing components 305 and becomes and so-calledly extract reluctantly.But, as this structure example, on the inner peripheral surface 305a of bearing components 305, be provided with under the situation of dynamic pressure groove 308a, 309a unreasonablely when extracting pattern 311, the dynamic pressure of causing groove 308a, 309a damage is arranged, and then the possibility that causes bearing performance to descend.Relative with it, in this structure example, as mentioned above, be set at the small value about ε/L≤1/500 owing to will comprise the inclination ε/L of inner peripheral surface 305a of the radial bearing surface 308,309 of bearing components 305, therefore the degree of extracting reluctantly is also small.And, form as thin as a wafer thickness owing to constitute the electroforming portion 306 of bearing components 305, and electroforming portion 306 firmly fixes with shielding part 307, therefore, when extracting pattern 311, electroforming portion 306 follow excellent spring resinous shielding part 307 distortion and be out of shape.For these reasons, can prevent the dynamic pressure groove 308a that the separation owing to pattern 311 causes, the damage of 309a effectively.
The shaft component 303 (solid of rotation 302) that the pattern 311 that is independent of drawing to inserting in interior week of the bearing components 305 that forms is as described above prepared respectively, be full of lubricant oil as fluid in the inner space of bearing components 305, thus, finish hydrodynamic bearing device shown in Figure 21 301.On the other hand, because the pattern 311 that separates can use in the electroforming processing repeatedly, therefore can stablize and produce high-precision bearing components 305 at low cost in batches.Be full of under the state of lubricant oil, the lubricant oil of seal space S3 is subjected to the effect of the inhalation power that caused by capillary force.Thus, lubricant oil maintains in the scope of seal space S3 all the time.
In the hydrodynamic bearing device 301 of said structure, when shaft component 303 (solid of rotation 302) rotated, the radial bearing surface 308,309 that separately forms on two positions up and down of the inner peripheral surface 305a of bearing components 305 was opposed across the outer peripheral surface 303a of radial bearing clearance C r1, Cr2 and shaft component 303 respectively.And, be accompanied by the rotation of shaft component 303,, improve the oil film rigidity of the lubricant film that forms at radial bearing clearance C r1, Cr2 by this pressure in the dynamic pressure that radial bearing clearance C r1, Cr2 produce lubricant oil, and diametrically shaft component 303 is carried out the non-contact supporting, make its rotation freely.Thus, form first R31 of radial bearing portion and second R32 of radial bearing portion, they carry out the non-contact supporting and make its rotation freely the solid of rotation 302 with shaft component 303 diametrically.In addition, meanwhile, form thrust bearing division T3 between the inner bottom surface 305b of the lower end surface of shaft component 303 303b and bearing components 305, it supports the solid of rotation 302 with shaft component 303 in the axial direction, and makes its rotation freely.
Usually, the rigidity (bearing rigidity) that is formed at the oil film in radial bearing gap diminishes along with this gap width and uprises.Therefore, in the said structure that the gap width that makes the radial bearing gap reduces gradually, be higher than the oil film rigidity of wide D2 of the big width of gap width in the oil film rigidity of little narrow the D1 of width of intermediate gap, radial bearing gap width above axially.In this structure example, the center of gravity G of solid of rotation 302 is positioned at the upside of the axial centre of bearing components 305, therefore, can improve bearing rigidity in the zone near the center of gravity G of solid of rotation 302, on the other hand, can reduce bearing rigidity in the zone away from center of gravity G.Thus, necessary bearing rigidity and low moment of torsionization in the time of can realizing guaranteeing having the solid of rotation 302 highi degree of accuracy rotation of shaft component 303 simultaneously.In addition, in this structure example, because two positions that separate in the axial direction are located in above-mentioned radial bearing gap, therefore, the bearing centre of the R31 of radial bearing portion, R32 is positioned at the position of upside of the axial centre of bearing components 305.Thereby, can shorten the span of the center of gravity G of the bearing centre of radial bearing portion and solid of rotation 302, become the good structure of load capacity (torque rigidity) with respect to torque load.
And, ratio (inclination) ε/L of axial distance of separation (axial length in radial bearing gap) L between the reduction ε of narrow the D1 of width of above-mentioned radial bearing clearance C r1 (or Cr2) and the radius clearance between wide D2 of width and two ones preferably adopts 1/1000≤ε/L≤1/500.Its reason is, when the value of inclination ε/L less than 1/1000 the time, be difficult to fully obtain the raising effect and the low effect of torque drop of bearing rigidity.On the other hand, when greater than 1/500 the time, the value of wide D2 of width is excessive, the possibility that has the bearing rigidity deficiency to make that running accuracy worsens.In addition, when above-mentioned bearing components 305 was shaped, it is big that the degree of extracting reluctantly becomes, and the possibility that causes radial bearing surface 308,309 damages is arranged.
In addition, be preferably formed each member and make minimum diameter gap (internal diameter size of narrow D1 of the width) δ of radial bearing clearance C r1 become 1/1000≤δ/d≤1/250 with respect to ratio δ/d of the diameter of axle d of shaft component 303, it the reasons are as follows described.At first, can be than the lower limit 1/1000 of δ/d according to derivation such as the circularity of the outer peripheral surface of pattern 311, shaft component 303 and electroforming portion 306 inner peripheral surfaces, cylindricities.That is, when diametric clearance δ becomes less than the circularity of the inner peripheral surface 305a of the outer peripheral surface 303a of shaft component 303, bearing components 305, cylindricity, between shaft component 303 and bearing components 305, produce and contact, be difficult to guarantee the performance of stipulating.Though can further improve above-mentioned various precision, be accompanied by high precision int, can cause that unavoidably cost improves.Therefore, during balance aspect considering function aspects and cost, than δ/d preferably more than 1/1000.On the other hand, the CLV ceiling limit value 1/250 than δ/d can derive according to the viewpoint of running accuracy, torque rigidity.That is, big if the minimum diameter gap delta in radial bearing gap becomes, then can not guarantee desirable bearing rigidity, torque rigidity, produce running accuracy deterioration, shaft component 303 and bad phenomenon such as bearing components 305 contacts.Therefore, preferably adopt below 1/250 than δ/d.
In addition, in this structure example, the zone of the radial bearing surface that becomes inner peripheral surface 305a 308,309 of bearing components 305 and be formed in the electroforming portion 306 that constitutes by precipitating metal with the inner bottom surface 305b (thrust bearing surface) of the lower end surface 303b sliding contact of shaft component 303.Aspect the electroforming processing characteristics, in electroforming portion 306, for becoming for the inner surface accuracy of the beginning face of separating out of pattern 311, the surface configuration that forms pattern 311 by transfer printing accurately dense face.Thereby, in the outer surface of pattern 311, especially when the forming section N that will form electroforming portion 306 forms accurately, do not need to implement extra fine finishing etc., can improve the precision of the inner peripheral surface 305a and the inner bottom surface 305b of the bearing components 305 that comprises dynamic pressure groove 308a, 309a easily, can highi degree of accuracy the width accuracy of management radial bearing clearance C r1, Cr2.In addition, because radial bearing surface 308,309 and thrust bearing surface form metal covering, therefore in the R31 of radial bearing portion, R32, can suppress the characteristic variations that causes by temperature variation or wearing and tearing etc., in addition, can improve wearability at thrust bearing division T3.According to more than, can be suppressed on the hydrodynamic bearing device 301 that load has vibration or the situation of impacting under solid of rotation 302 oscillating quantity increase, be accompanied by the reduction of the verticity of resonance, and can keep high runnability.
More than, structure example at the hydrodynamic bearing device of the 4th mode of execution of the present invention is illustrated, but above-mentioned structure of the present invention is not limited to the hydrodynamic bearing device 301 of aforesaid way, also can preferably use in the hydrodynamic bearing device of other modes.Below, based on accompanying drawing its structure example is described, still,, be marked with same reference marks, and omit repeat specification at member and position based on aforesaid way for the simplification that illustrates.
Figure 25 represents second structure example of the hydrodynamic bearing device of the 4th mode of execution of the present invention.Hydrodynamic bearing device 321 shown in this figure mainly contains following 2 points with the different aspect of hydrodynamic bearing device 301 shown in Figure 21: the hub 304 that constitutes solid of rotation 302 is arranged on the below of bearing components 305, and the center of gravity G of solid of rotation 302 is positioned at the below this point of bearing components 305; And corresponding with it, the internal diameter size of bearing components 305 forms this point in the mode of successively decreasing to axial below.And, though not shown, can be same in the both ends open portion of bearing components 305 with mode shown in Figure 21, form seal space.
Figure 26 represents the 3rd structure example of the hydrodynamic bearing device of the 4th mode of execution of the present invention.In the hydrodynamic bearing device 331 shown in this figure, the inner peripheral surface of bearing components 305 is not as Figure 21 and the taper that internal diameter size is successively decreased to axial a certain side shown in Figure 25, but is diameter is relatively little in the axial direction the first inner peripheral surface 305d and the diameter second inner peripheral surface 305e greater than this first inner peripheral surface 305d by zoning.Part or all axial region at the first inner peripheral surface 305d is provided with radial bearing surface 308, in part or all axial region of the second inner peripheral surface 305e radial bearing surface 309 is set.Just, in this structure example, the integral body of the radial bearing clearance C r1 that forms between the outer peripheral surface 303a of the radial bearing surface 308 of upside and shaft component 303 becomes narrow D1 of width, and the integral body of the radial bearing clearance C r2 that forms between the outer peripheral surface 303a of the radial bearing surface 309 of downside and shaft component 303 becomes wide D2 of width.
Figure 27 represents the 4th structure example of the hydrodynamic bearing device of the 4th mode of execution of the present invention.Hydrodynamic bearing device 341 shown in this figure mainly aspect following structure with hydrodynamic bearing device 301 shown in Figure 21 different, bearing components 345 is main part 345a and the roughly hemispheric protuberance 345b with radial bearing surface 308,309 by zoning, protuberance 345b is provided with to the top of main part 345a is outstanding, and the outer peripheral surface 303a of shaft component 303 between form seal space S3 and lubricant oil reservoir 346.The integral body that constitutes the sidepiece of main part 345a successively decreases internal diameter size towards axial top.
Though not shown, but this bearing components 345 for example can form as follows.At first, according to the shaping order of above-mentioned bearing components 305, the sidepiece of main part 345a and protuberance 345b are mold formed with the state with respect to parallel axes, and separate with pattern.Then, to copying as finishing the main part 345a of part and the mould of 3 protuberance 45b shapes has carried out under the heated state, apply compressing power from the outside diameter of this bearing components 345, the sidepiece of main part 345a and protuberance 345b are out of shape to internal diameter direction, become a kind of state of plastic deformation.Then, open this mould and can obtain the bearing components 345 shown in this figure.
More than, at certain by shaft component 303 being formed on whole entire axial length diameter, and the internal diameter size that makes bearing components 305 diameter difference in the axial direction, the different in the axial direction structure of gap width in radial bearing gap is illustrated, but in the arbitrary structure example shown in above, it is certain also can to form on whole entire axial length diameter by the inner peripheral surface 305a that makes bearing components 305, and make shaft component 303 diameter difference in the axial direction, make the gap width in radial bearing gap different in the axial direction thus.
Above as the R31 of radial bearing portion, R32, illustration utilize herringbone shape or spiral-shaped dynamic pressure groove to produce the structure of hydrodynamic, but the present invention is not limited thereto.For example, also can constitute a side or the both sides of the R31 of radial bearing portion, R32 by so-called many arc bearings or step bearing.These bearings can be by obtaining as a plurality of arc surfaces of dynamic pressure generating section, the radial bearing surface 308,309 that axial groove for example is formed at bearing components 305.The formation method of these dynamic pressure generating sections is owing to be as the criterion with each operation under the situation that forms dynamic pressure groove 308a, 309a, so detailed.
Figure 28 represents the example with the side of many arc bearings formation radial bearing R31 of portion, R32 or both sides' situation.In this embodiment, the zone that becomes radial bearing surface 308,309 of the inner peripheral surface of bearing components 305 constitutes (so-called three-arc bearing) by three arc surfaces 351.The centre of curvature of three arc surfaces 351 respectively from the axle center O of bearing components 305 (shaft component 303) with equidistant biasing.In each zone with three arc surface 351 zonings, the radial bearing gap is that the both direction with respect to circumferencial direction is the diminishing wedge-like clearance C r3 of wedge-like respectively.Therefore, when bearing components 305 during with shaft component 303 relative rotations, according to its counterrotating direction, the lubricant oil in the radial bearing gap is pressed into the minimum clearance side of wedge-like clearance C r3, and its pressure rises.By the dynamic pressure effect of this lubricant oil, bearing components 305 and shaft component 303 are carried out the non-contact supporting.And, can also form the one section dark axial groove that is known as separating vessel in three arc surfaces 351 boundary portion each other.
Figure 29 represents to be made of many arc bearings other examples of the side of the R31 of radial bearing portion, R32 or both sides' situation.In this embodiment, the zone that becomes radial bearing surface 308,309 of the inner peripheral surface of bearing components 305 constitutes (so-called three-arc bearing) by three arc surfaces 351, but in each zone of being divided by three arc surfaces 351, the radial bearing gap is that a direction with respect to circumferencial direction is the diminishing wedge-like clearance C of wedge-like r3 respectively.Many arc bearings of this structure also can be described as cone bearing.In addition, be formed with the one section dark axial groove that is known as separating vessel 352 in three arc surfaces 351 boundary portion to each other.Therefore, when bearing components 305 and shaft component 303 to prescribed direction is relative when rotating, the lubricant oil in the radial bearing gap is pressed into the minimum clearance side of wedge-like clearance C r3, its pressure rises.By the dynamic pressure effect of this lubricant oil, bearing components 305 and shaft component 303 are supported by non-contact.
Figure 30 represents to be made of many arc bearings other examples of the side of the R31 of radial bearing portion, R32 or both sides' situation.In this example, in structure shown in Figure 29, the regulation of the minimum clearance side of three arc surfaces 351 zone θ is respectively the concentric arc surface formation of centre of curvature by the axle center O with bearing components 305 (shaft component 303).Therefore, stipulate among the regional θ that radial bearing gap (minimum clearance) is certain at each.Many arc bearings of this structure are also referred to as flat awl (tape flat) bearing.
Figure 31 represents to be made of step bearing an example of the side of the R31 of radial bearing portion, R32 or both sides' situation.In this embodiment, on the zone that becomes radial bearing surface 308,309 of the inner peripheral surface of bearing components 305 (electroforming portion 306), be provided with the dynamic pressure groove 353 of a plurality of axial groove shapes with predetermined distance at circumferencial direction.
More than, as the R31 of radial bearing portion, R32, be formed on axial two positions and divide the structure of radial bearing portion that is arranged, but also can adopt the zone up and down of the inner peripheral surface that spreads all over bearing components 305 that the structure of the above radial bearing portion in three positions is set.In addition, Figure 28～many arc bearings shown in Figure 30 are so-called three-arc bearing, but are not limited to this, many arc bearings that also can adopt so-called four arc bearings, five arc bearings and then be made of the arc surface of the above quantity of six circular arcs.
In addition, above illustration on the radial bearing surface 308,309 of the electroforming portion 306 that constitutes bearing components 305, form the situation of dynamic pressure generating section, but also can with the outer peripheral surface 303a of these radial bearing surface 308,309 opposed shaft components 303 on dynamic pressure generating section is set.At this moment, the zone that becomes radial bearing surface 308,309 of electroforming portion 306 forms and does not have concavo-convex cylinder planar.
In addition, more than at radial bearing surface 308 in the electroforming portion 306 that constitutes bearing components 305,309 or the outer peripheral surface 303a of shaft component 303 on dynamic pressure generating section is set, utilize this dynamic pressure generating section to produce hydrodynamic in the radial bearing gap, constitute the radial bearing R31 of portion with hydraulic bearing, the situation of R32 is illustrated, but, by the radial bearing surface 308 that makes electroforming portion 306,309 form and do not have concavo-convex cylinder planar, and the outer peripheral surface 303a of shaft component 303 formed do not have concavo-convex cross section round type, can constitute the radial bearing R31 of portion by enough positive circular journal bearings thus, R32 (omitting diagram).
In addition, above illustration constitute the mode of thrust bearing division T3 with trunnion bearing, but the lower end that for example also can make shaft component 303 is a tabular surface, this tabular surface or with it the end face of opposed bearing components a plurality of dynamic pressure grooves etc. of the helically shaped or herringbone shape of alignment arrangements are set, utilize hydraulic bearing to constitute thrust bearing division (not shown) thus.
In addition, more than use lubricant oil as the lubricating fluid in the inner space that is filled into hydrodynamic bearing device, but also can use other fluids that can form fluid film, for example lubricating grease or magnetic fluid and then can also use gas such as air etc.
Because above-mentioned hydrodynamic bearing device has high running accuracy, therefore, can be preferably used as the bearing that the fan motor of the spindle drive motor of dish devices such as the various motor that require high verticity, for example HDD or personal computer is used.
Claims (8)
1. hydrodynamic bearing device, it comprises:
Bearing sleeve, it has radial bearing surface;
Shaft component, it is inserted into the interior week of this bearing components;
Radial bearing portion, it passes through the dynamic pressure effect of the fluid of the radial bearing gap generation between the outer peripheral surface of the radial bearing surface of described bearing components and described shaft component, diametrically described shaft component is carried out the non-contact supporting,
Described hydrodynamic bearing device is characterised in that,
Dispose a plurality of described bearing sleeves in the axial direction,
And each bearing sleeve forms axial length difference each other.
2. hydrodynamic bearing device according to claim 1, wherein,
Be provided with on any inner peripheral surface at least in two adjacent bearing sleeves and described radial bearing surface with the protuberance in footpath, this protuberance is positioned at than described radial bearing surface more by the position of another bearing sleeve side.
3. hydrodynamic bearing device according to claim 1, wherein,
Described shaft component has to the side-prominent protuberance of external diameter, be provided with thrust bearing division between the end face of the end face of this protuberance and described bearing sleeve, this thrust bearing division carries out the non-contact supporting to described shaft component in the axial direction by the dynamic pressure effect of the fluid that produces in the thrust-bearing gap.
4. hydrodynamic bearing device according to claim 3, wherein,
Outer circumferential side at described protuberance is formed with seal space.
5. hydrodynamic bearing device, it comprises:
Bearing components;
Solid of rotation, it has the shaft component that is inserted into week in this bearing components;
First and second thrust-bearing gap, it is formed between described bearing components and the described solid of rotation;
The first dynamic pressure groove zone, it produces hydrodynamic in the described first thrust-bearing gap;
The second dynamic pressure groove zone, it produces hydrodynamic in the described second thrust-bearing gap,
Described hydrodynamic bearing device is characterised in that,
Described bearing components has two bearing sleeves of alignment arrangements in the axial direction,
These two bearing sleeves all have described first dynamic pressure groove zone and the described second dynamic pressure groove zone in both ends of the surface, and the described first dynamic pressure groove area surface that makes a bearing sleeve is to the described first thrust-bearing gap, and the described second dynamic pressure groove area surface that makes another bearing sleeve is to the described second thrust-bearing gap.
6. hydrodynamic bearing device according to claim 5, wherein,
Described first dynamic pressure groove zone forms difformity with the described second dynamic pressure groove zone.
7. hydrodynamic bearing device according to claim 5, wherein,
Between described two bearing sleeves, spacer member is housed.
8. motor, it comprises: the described hydrodynamic bearing device of each in the claim 1 to 7, rotor magnet and stator coil.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006083470A JP2007255654A (en) | 2006-03-24 | 2006-03-24 | Dynamic pressure bearing device |
| JP2006083457A JP4937619B2 (en) | 2006-03-24 | 2006-03-24 | Hydrodynamic bearing device |
| JP083470/2006 | 2006-03-24 | ||
| JP083457/2006 | 2006-03-24 | ||
| JP2006102265A JP2007278326A (en) | 2006-04-03 | 2006-04-03 | Dynamic pressure bearing device |
| JP102265/2006 | 2006-04-03 | ||
| JP2006156309A JP5058516B2 (en) | 2006-06-05 | 2006-06-05 | Hydrodynamic bearing device |
| JP156309/2006 | 2006-06-05 | ||
| PCT/JP2007/055859 WO2007111218A1 (en) | 2006-03-24 | 2007-03-22 | Fluid bearing device |
Related Child Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210023188.2A Division CN102537031B (en) | 2006-03-24 | 2007-03-22 | Fluid dynamic bearing device |
| CN2010101303198A Division CN101852245B (en) | 2006-03-24 | 2007-03-22 | Fluid bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101405513A true CN101405513A (en) | 2009-04-08 |
| CN101405513B CN101405513B (en) | 2010-11-10 |
Family
ID=38630094
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800100900A Expired - Fee Related CN101405513B (en) | 2006-03-24 | 2007-03-22 | Fluid bearing device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4937619B2 (en) |
| CN (1) | CN101405513B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106321523A (en) * | 2015-06-17 | 2017-01-11 | 奇鋐科技股份有限公司 | Fan vibration reducing structure and fan with vibration reducing structure |
| CN108561536A (en) * | 2018-05-10 | 2018-09-21 | 上海理工大学 | A kind of high-precision motor device and precision equipment |
| CN108591274A (en) * | 2018-05-10 | 2018-09-28 | 上海理工大学 | A kind of sealing device and precision equipment |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5398132B2 (en) | 2007-09-28 | 2014-01-29 | 豊田バンモップス株式会社 | Grinding wheel |
| KR101434020B1 (en) * | 2012-07-04 | 2014-08-25 | 삼성전기주식회사 | Spindle motor |
| US11221039B2 (en) | 2017-01-09 | 2022-01-11 | Hamilton Sundstrand Corporation | Bearing assembly with surface layer |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2608708B2 (en) * | 1986-09-27 | 1997-05-14 | セイレイ工業株式会社 | Threshing machine horizontal feeder for threshing machine |
| US5407281A (en) * | 1994-07-22 | 1995-04-18 | Quantum Corp. | Self-replenishing hydrodynamic bearing |
| JP2005003042A (en) * | 2003-06-10 | 2005-01-06 | Ntn Corp | Hydrodynamic bearing device |
| JP2005321089A (en) * | 2004-04-09 | 2005-11-17 | Ntn Corp | Dynamic pressure bearing device |
-
2006
- 2006-03-24 JP JP2006083457A patent/JP4937619B2/en not_active Expired - Fee Related
-
2007
- 2007-03-22 CN CN2007800100900A patent/CN101405513B/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106321523A (en) * | 2015-06-17 | 2017-01-11 | 奇鋐科技股份有限公司 | Fan vibration reducing structure and fan with vibration reducing structure |
| CN108561536A (en) * | 2018-05-10 | 2018-09-21 | 上海理工大学 | A kind of high-precision motor device and precision equipment |
| CN108591274A (en) * | 2018-05-10 | 2018-09-28 | 上海理工大学 | A kind of sealing device and precision equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101405513B (en) | 2010-11-10 |
| JP2007255651A (en) | 2007-10-04 |
| JP4937619B2 (en) | 2012-05-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101852245B (en) | Fluid bearing device | |
| CN101405513B (en) | Fluid bearing device | |
| US8782901B2 (en) | Dynamic bearing device | |
| CN102738942B (en) | Motor and disk drive device | |
| CN101400904B (en) | Fluid dynamic pressure bearing device and method of producing the same | |
| CN101868636B (en) | Fluid dynamic-pressure bearing device | |
| CN101952610B (en) | Sintered bearing | |
| US7687951B2 (en) | Fluid dynamic bearing device and motor equipped with the same | |
| CN101438068B (en) | Fluid bearing device and its manufacturing method | |
| CN103415716A (en) | Fluid dynamic pressure bearing device | |
| US20090148084A1 (en) | Fluid Dynamic Bearing Device | |
| CN101395393A (en) | Fluid bearing device | |
| KR101405075B1 (en) | Fluid bearing device and its manufacturing method | |
| CN106662143A (en) | Fluid dynamic bearing device, and bearing member and shaft member for use in same | |
| CN101184929A (en) | Fluid bearing device | |
| CN101018955B (en) | Fluid bearing device and motor having the same | |
| US20070014496A1 (en) | Fluid dynamic bearing system | |
| JP5058516B2 (en) | Hydrodynamic bearing device | |
| CN206988281U (en) | Fluid dynamic-pressure bearing device and the motor for possessing the fluid dynamic-pressure bearing device | |
| CN100480522C (en) | Dynamic pressure bearing device | |
| CN101443563A (en) | Fluid bearing device | |
| JP5901979B2 (en) | Method for manufacturing fluid dynamic bearing device | |
| CN101144499A (en) | Dynamic pressure bearing device, method of manufacturing the same, and motor using the same | |
| JP4846470B2 (en) | DYNAMIC PRESSURE BEARING DEVICE AND MOTOR HAVING THE SAME | |
| JP2021001629A (en) | Bearing member and fluid dynamic pressure bearing device including the same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20101110 Termination date: 20200322 |