CN101410637A - Hydrodynamic bearing device - Google Patents
Hydrodynamic bearing device Download PDFInfo
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- CN101410637A CN101410637A CNA200780011272XA CN200780011272A CN101410637A CN 101410637 A CN101410637 A CN 101410637A CN A200780011272X A CNA200780011272X A CN A200780011272XA CN 200780011272 A CN200780011272 A CN 200780011272A CN 101410637 A CN101410637 A CN 101410637A
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Abstract
A hydrodynamic bearing device which has high loading capability against moment load, and in which manufacture and fixing operation of a bearing sleeve can be easily performed, and a required fixing force can be kept. The bearing sleeve (3) is inserted onto the inner peripheral surface (2a) of a housing, and its lower end face (3c) is secured to the upper end face (2c2) of a spacer part (2c) with an adhesive agent (A1). Also, the bearing sleeve (4) is inserted into the inner peripheral surface (2b) of the housing, and its upper end face (4c) is fixed to the lower end face (2c3) of the spacer part (2c) with an adhesive (A2).
Description
Technical field
The present invention relates to Hydrodynamic bearing apparatus.
Background technique
Usually, Hydrodynamic bearing apparatus non-contact supporting shaft part under the hydrodynamic effect that the bearing play produced.This bearing means possesses features such as high speed rotating, high running accuracy, low noise, being suitable for as being equipped on the information equipment is that the motor of the various electrical equipments of representative uses with bearing means, say with having more, be suitable for the bearing means used as the spindle drive motor of magneto-optical disc apparatus such as optical disk unit such as disk device, CD-ROM, CD-R/RW, DVD-ROM/RAM, MD, MO such as HDD etc., perhaps use with bearing means as motor such as the polygon scanning motor of ultra high speed of laser printer (LBP), color wheel of projecting camera motor, fan motors.
For example, being installed on the Hydrodynamic bearing apparatus of the spindle drive motor of disk drive device such as HDD, is to constitute the radial bearing portion of radial support spindle unit and the thrust bearing division both sides of thrust direction supporting by hydraulic bearing sometimes.As the radial bearing portion in this Hydrodynamic bearing apparatus, be known that, for example the inner peripheral surface of bearing sleeve and therewith the either party of the outer circumferential face of opposed spindle unit form dynamic pressure groove as the dynamic pressure generating unit, and between the two sides, form radial bearing gap (for example with reference to patent documentation 1).
But, in disk drive devices such as the information equipment of the Hydrodynamic bearing apparatus that said structure is installed, for example HDD, more high speed with reading speed turns to purpose, require further high speed rotatingization, but the moment load that acts in this case, the bearing portion of supporting spindle freely of rotating becomes big.Therefore,, radial bearing portion is set at axially-spaced and in many places, simultaneously, must increases the spacing between radial bearing portion in order to adapt to the increase of this moment load.In addition, what adopted is the structure that these a plurality of radial bearing portions is arranged at interior all sides of a bearing sleeve in the past, also require the pathization of the miniaturization of motor, the main shaft that accompanies therewith and bearing sleeve, often be difficult to make the bearing sleeve of the spacing increase that can adapt between radial bearing portion.
As increasing the spacing between radial bearing portion and making the manufacturing of the bearing sleeve easy device that becomes, can consider bearing sleeve is made a plurality of, with it at axially-spaced and be disposed at many places (for example with reference to patent documentation 2).
Patent documentation 1:(Japan) spy opens the 2003-239951 communique
Patent documentation 2:(Japan) No. 3602707 communique of patent
In the occasion that bearing sleeve is disposed at many places, each bearing sleeve is fixed in the inner peripheral surface of shell by bonding or be pressed into etc., but for example under situation about being adhesively fixed, owing to must carry out bonding process carefully, do not stopped up so that be formed at the fluid passage of the lubricating fluid of bearing sleeve outer circumferential face by binder, thereby it is very bothersome in fixed operation, in addition, be pressed into fixing occasion, when increasing the magnitude of interference in interior week of the periphery of bearing sleeve and shell in order to obtain sufficient retention force, then the radial bearing gap since internal diameter of bearing dwindle and radial bearing reduces, torque loss increases etc. might be to the radially bad influence of bearing performance generation.Therefore, from the fixed operation of bearing sleeve and guarantee that the retention force aspect considers that thinking has the necessity of improvement.
In addition, bonding, be pressed into, in any fixing device, when the linear expansion coeffcient of shell is bigger than bearing sleeve, because both thermal shrinkage when temperature reduces is poor, bearing sleeve is from the shell power that suffers oppression, its internal diameter size dwindles, based on producing bad influence to bearing performance radially with above-mentioned same reason.
Summary of the invention
First purpose of the present invention provides a kind of Hydrodynamic bearing apparatus, and it is to the load carrying capacity height of moment load, and the manufacturing and the fixed operation of bearing sleeve are easy, and can guarantee essential retention force.
Second purpose of the present invention provides a kind of Hydrodynamic bearing apparatus, it is to the load carrying capacity height of moment load, the manufacturing and the fixed operation of bearing sleeve are easy, and the internal diameter size that can not cause bearing sleeve dwindles, can guarantee essential retention force, in addition, even the linear expansion coeffcient of shell than the big situation of the linear expansion coeffcient of bearing sleeve under, the reducing of the radial bearing gap that the internal diameter size of the bearing sleeve that both the thermal shrinkage difference in the time of also can preventing or suppress Yin Wendu and reduce causes dwindles, causes thus.
First device of developing in order to solve above-mentioned first problem possesses: shell; Bearing sleeve, it is accommodated in the inside of shell; Spindle unit, it inserts the interior week of bearing sleeve; Radial bearing portion, under the dynamic pressure effect of the lubricating fluid that it is produced in the radial bearing gap between bearing sleeve inner peripheral surface and the spindle unit outer circumferential face, spindle unit is carried out the non-contact supporting in radial direction, it provides following structure: bearing sleeve is a plurality of in the axially-spaced configuration, between axially spaced bearing sleeve, be provided with cushion part, cushion part fixedly installs with respect to shell, and bearing sleeve is being adhesively fixed in cushion part with the opposed end face of the end face of cushion part.
According to this first device, owing to bearing sleeve is made a plurality of, they at axially-spaced and be disposed at many places, thereby can be increased the spacing between radial bearing portion and can improve load carrying capacity to moment load, simultaneously, can easily make bearing sleeve.In addition, because bearing sleeve is being adhesively fixed in the end face of liner with the opposed end face of the end face of the cushion part that fixedly installs with respect to shell, even thereby form in the outer circumferential face side of bearing sleeve under the situation of fluid passage of lubricating fluid, do not worry that this fluid passage stopped up by binder yet, in addition, also can guarantee the necessary retention force of bearing sleeve.
Second device of developing in order to solve above-mentioned second problem possesses: shell; Bearing sleeve, it is accommodated in the inside of shell; Spindle unit, it inserts the interior week of bearing sleeve; Radial bearing portion, under the dynamic pressure effect of the lubricating fluid that it is produced in the radial bearing gap between bearing sleeve inner peripheral surface and the spindle unit outer circumferential face, spindle unit is carried out the non-contact supporting in radial direction, it provides following structure: bearing sleeve is a plurality of in the axially-spaced configuration, between axially spaced bearing sleeve, be provided with cushion part, cushion part fixedly installs with respect to shell, bearing sleeve keeps the gap to insert the interior week of shell, and the opposed end face of the end face of utilization and described cushion part and being adhesively fixed in described cushion part.
According to this second device, owing to bearing sleeve is made a plurality of, it at axially-spaced and be disposed at many places, thereby can be increased the spacing between radial bearing portion, and can improve load carrying capacity moment load, simultaneously, can easily make bearing sleeve.In addition, owing to keeping the gap, bearing sleeve inserts the inner peripheral surface of shell, and be adhesively fixed in the end face of liner with the opposed end face of the end face of the cushion part that fixedly installs with respect to shell, thereby, even form the situation of the fluid passage of lubricating fluid in the outer circumferential face side of bearing sleeve, do not worry that this fluid passage stopped up by binder yet, and, the internal diameter size that can cause bearing sleeve does not dwindle, and can guarantee the essential retention force of bearing sleeve.In addition, even the linear expansion coeffcient of shell than the big situation of the linear expansion coeffcient of bearing sleeve under, because both the whole amounts or the part amount of contraction difference when temperature reduces absorbed by the gap between the interior week of the periphery of bearing sleeve and shell, thereby also can prevent or suppress reducing of radial bearing gap that the internal diameter size of the bearing sleeve that caused by both thermal shrinkage difference dwindles, causes thus.
At this, any one of no matter above-mentioned first device and second device, in the structure that cushion part is fixedly installed with respect to shell, comprise with cushion part and shell form one structure and by bonding, be pressed into, be pressed into the structure that bonding (be pressed into, bonding and with), welding, proper method such as deposited are fixed in the cushion part of split on shell.
In above-mentioned first device and second device, preferably the binder that concavity is set of at least one side among the end face of the end face of bearing sleeve and cushion part accumulates the place.By utilize the binder place of accumulating to catch filling or be coated on the bearing sleeve end face and the cushion part end face between the part of binder, can prevent that unnecessary binder from spreading to the phenomenon of the inner peripheral surface side (radial bearing gap one side) of bearing sleeve to the internal diameter side flow.
In above-mentioned first device and second device, can fluid passage to its axial both-side opening be set in cushion part.Moreover, the fluid passage of cushion part is communicated with axial fluid passage between inner peripheral surface that is arranged on shell and the bearing sleeve outer circumferential face.These fluid passages become and are used to make the lubricating fluid circulation canal of portion's flow circuit in the enclosure.Lubricating fluid carries out flow circuit via this circulation canal, the pressure balance of filling can be guaranteed thus, the leakage of the lubricating fluid that the generation of generation, the bubble of the bubble that accompanies with the generation of local negative pressure causes and the problems such as generation of vibration can be eliminated simultaneously in the lubricating fluid in the enclosure space that comprises the bearing play.In addition, part by making circulation canal is towards outer gas open sides, even make because of some reason under the situation of sneaking into bubble in the lubricating fluid, bubble also can carry out along with lubricating fluid circulation time be discharged to outside the gas open sides, thereby can more effectively prevent the adverse effect that bubble causes.
In addition, in above-mentioned first device and second device, also can on spindle unit, be provided with to the side-prominent protuberance of external diameter, between the end face of the end face of this protuberance and bearing sleeve, thrust bearing division is set, under the dynamic pressure effect of the lubricating fluid that it is produced in the thrust-bearing gap, spindle unit is carried out the non-contact supporting in thrust direction.Protuberance both can form one with spindle unit, also can be fixed on the spindle unit.In addition, the dynamic pressure generating means of thrust bearing division (dynamic pressure groove etc.) is as long as be formed at a side in the end face of protuberance end face and bearing sleeve.
This situation also can be the protuberance outer circumferential side formation seal space at above-mentioned spindle unit.The sealing space has function, the so-called pooling feature of the volume-variation (expansion) that absorption causes in the temperature variation of the lubricating fluid in enclosure space because of filling.
In above-mentioned first device and second device, shell can be made the contour forming product of melted material.The material of shell can be any one of resin, metal.Shell is being made under the resinous situation, for example can adopted the injection moulding of thermoplastic resin etc.In addition, shell is being made under the metal situation, for example can adopted mold casting formings such as aluminum alloy, magnesium alloy, stainless steel, injection moulding (so-called MIM method, melt the sex change injection molding).
The Hydrodynamic bearing apparatus of relevant above-mentioned first device is applicable to HDD, particularly is applicable to the motor of server with disk drive devices such as HDD of packing into.
The Hydrodynamic bearing apparatus of relevant above-mentioned second device is applicable to the motor of disk drive device such as the HDD that packs into.
According to above-mentioned first device, a kind of Hydrodynamic bearing apparatus can be provided, it is to the load carrying capacity height of moment load, and the manufacturing and the fixed operation of bearing sleeve are easy, and can guarantee essential retention force.
In addition, according to above-mentioned second device, can provide a kind of Hydrodynamic bearing apparatus, it is to the load carrying capacity height of moment load, and the manufacturing and the fixed operation of bearing sleeve are easy, and the internal diameter that can not cause bearing sleeve dwindles and can guarantee essential retention force.In addition, even the situation that the linear expansion coeffcient of shell is bigger than the linear expansion coeffcient of bearing sleeve, the minimizing in the radial bearing gap that the internal diameter size of the bearing sleeve that both the thermal shrinkage difference in the time of also can preventing or suppress temperature and reduce causes dwindles, causes thus.
Description of drawings
Fig. 1 is the sectional drawing of the Hydrodynamic bearing apparatus of first mode of execution;
Fig. 2 is top figure (Fig. 2 (a)), sectional drawing (Fig. 2 (b)), the following figure (Fig. 2 (c)) that the state on the shell is fixed in bearing sleeve in expression;
Fig. 3 is the amplification profile of the upper section of expression shell;
Fig. 4 is the amplification profile of periphery at the position that is adhesively fixed of expression bearing sleeve and cushion part;
Fig. 5 is the sectional drawing of the Hydrodynamic bearing apparatus of second mode of execution;
Fig. 6 is the sectional drawing of the Hydrodynamic bearing apparatus of the 3rd mode of execution;
Fig. 7 is the sectional drawing of the Hydrodynamic bearing apparatus of the 4th mode of execution;
Fig. 8 is top figure (Fig. 8 (a)), sectional drawing (Fig. 8 (b)), the following figure (Fig. 8 (c)) that the state on the shell is fixed in bearing sleeve in expression;
Fig. 9 is the amplification profile of the upper section of expression shell;
Figure 10 is the amplification profile of periphery at the position that is adhesively fixed of expression bearing sleeve and cushion part;
Figure 11 is the sectional drawing of the Hydrodynamic bearing apparatus of the 5th mode of execution;
Figure 12 is the sectional drawing of the Hydrodynamic bearing apparatus of the 6th mode of execution.
Symbol description
1: Hydrodynamic bearing apparatus
11: Hydrodynamic bearing apparatus
21: Hydrodynamic bearing apparatus
2: shell
2c: cushion part
2c1: fluid passage
3: bearing sleeve
4: bearing sleeve
5: spindle unit
6: sealed member
7: sealed member
A1: binder
A2: binder
C1: radial direction gap
C2: radial direction gap
R1: the first radial bearing portion
R2: the second radial bearing portion
T1: first thrust bearing division
T2: second thrust bearing division
S1: seal space
S2: seal space
Embodiment
Below, with reference to the description of drawings embodiments of the present invention.
Fig. 1 represents Hydrodynamic bearing apparatus of the present invention (fluid dynamic-pressure bearing device) 1.This Hydrodynamic bearing apparatus 1 is for example in the rotation with supporting spindle in the motor of HDD of the HDD that packs into, particularly server.A plurality of for example two bearing sleeves 3,4 that this Hydrodynamic bearing apparatus 1 is accommodated in the inside of shell 2 with shell 2, in axial spaced positions from each other, the spindle unit 5 that inserts the inner peripheral surface of bearing sleeve 3,4 are that the main composition part constitutes.
As described below, between the outer circumferential face 5a of the inner peripheral surface 3a of bearing sleeve 3 and spindle unit 5, be provided with first R1 of radial bearing portion, between the outer circumferential face 5a of the inner peripheral surface 4a of bearing sleeve 4 and spindle unit 5, be provided with second R2 of radial bearing portion.In addition, in this embodiment, between the downside end face 6b of the upside end face 3b of bearing sleeve 3 and sealed member 6, be provided with the first thrust bearing division T1, between the upside end face 7b of the downside end face 4b of bearing sleeve 4 and sealed member 7, be provided with the second thrust bearing division T2.For convenience of explanation, sides (paper upside) of giving prominence to from shell 2 with the end of spindle unit 5 are upside, are that downside describes with its opposition side.
The fluid passage 2c1 of cushion part 2c also can be after with outer casing forming processes and forms by implementing the hole, still, for the reduction of the manufacture cost of subduing, bringing thus of seeking machining period, preferably carries out moulding simultaneously with the moulding of shell 2.This can implement by being provided with on the forming die that shell 2 is carried out moulding with the corresponding shaping pin of shape of fluid passage 2c1.In addition, the shape of cross section of fluid passage 2c1 is not limited to circle, also can be non-circular shape (elliptical shape and polygonal etc.).In addition, the cross sectional area of fluid passage 2c1 is axially not necessarily constant, and for example its cross sectional area also can have relatively large part and relative less part.
The resin that forms shell 2 mainly is a thermoplastic resin, for example polysulfones (PSU), polyether sulfone (PES), Polyphenylene Sulfone (PPSU), Polyetherimide (PEI) can be used, liquid-crystalline polymer (LCP), polyether-ether-ketone (PEEK), polybutylene terephthalate (PBT), polyphenylene sulfide (PPS) etc. can be used as crystalline resin as non-crystalline resin.In addition, the kind of the packing material that above-mentioned resin is filled is not particularly limited yet, for example, can use fibrous or Powdered electric conductivity packing materials such as flakey packing materials such as whisker shape packing material, mica, carbon fiber, carbon black, graphite, carbon nanometer materials, metallic dust such as fibrous packing material, potassium titanate such as glass fibre as packing material.These packing materials can use separately or also can mix two or more uses.In this embodiment, as the material that forms shell 2, the resin material of use is to have cooperated carbon fiber or the carbon nano-tube as the electric conductivity packing material of 2～8wt% in the liquid-crystalline polymer (LCP) as crystalline resin.
Spindle unit 5 is formed by stainless steel and other metal materials, makes roughly the axle shape with the footpath on the whole.In addition, in this embodiment, utilize suitable fixing device for example bonding or be pressed into bonding (and be pressed into) sealing material 6,7 of ring-type is fixed in spindle unit with bonding.These sealing materials 6,7 become outer circumferential face 5a from spindle unit 5 to the side-prominent form of external diameter, are accommodated in large-diameter portion 2d, the 2e of shell 2 respectively.In addition, in order to improve the bonding strength of binder, be provided with circumferential groove 5a1, the 5a2 that accumulates the place as binder as the outer circumferential face 5a of the spindle unit 5 of the fixed position of sealing material 6,7.Moreover sealed member 6,7 both can also can form with resin material with soft metal material and the formation of other metallic material such as brass.In addition, the side among the sealed member 6,7 also can be integrally formed with spindle unit 5.Under this situation, by the assembly that a spindle unit 5 and a side's sealed member constitutes, also the compound body of available metal and resin constitutes.As an example, can consider to make spindle unit 5 with metal, with resin one side's sealing material is carried out insert moulding simultaneously.
The outer circumferential face 6a of sealing material 6 forms the space S 1 of the volume with regulation between the large-diameter portion 2d of itself and shell 2, the outer circumferential face 7a of sealing material 7 its with the large-diameter portion 2d of shell 2 between formation have the space S 2 of the volume of regulation.In this embodiment, the outer circumferential face 7a of the outer circumferential face 6a of sealing material 6 and sealing material 7 forms the diminishing conical surface-shaped of diameter to the outer side of shell 2 respectively.Therefore, seal space S1, S2 are to the diminishing cone shape of the private side of shell 2.
The porous plastid that bearing sleeve 3,4 for example constitutes with sintering metal, the porous plastid that particularly with copper is the sintering metal of primary coil forms cylindric, insert inner peripheral surface 2a, the 2b of shell 2 respectively, perhaps defeat into (gently being pressed into) inner peripheral surface 3a, 4a with being unlikely being pressed into of size that produces distortion.
And, amplifying shown in the back as Fig. 4, the downside end face 3c of bearing sleeve 3 utilizes adhesive A 1 to be fixed in the upside end face 2c2 of cushion part 2c.The binder that the downside end face 3c of bearing sleeve 3 is provided with the circumferential groove shape accumulates the 3c1 of place, the part of adhesive A 1 enters binder and accumulates the 3c1 of place, can prevent unnecessary adhesive A 1 thus to the internal diameter side flow, and spread to the phenomenon of inner peripheral surface 3a one side (radial bearing gap one side) of bearing sleeve 3.The binder that a plurality of circumferential groove shapes are set on also can downside end face 3c accumulates the 3c1 of place.In addition, interior all sides of downside end face 3c have chamfering 3c2, and this chamfering 3c2 helps also to prevent that adhesive A 1 from spreading to internal side diameter.In addition, the surface opening rate of the downside end face 3c of preferred bearing sleeve 3 is littler than the surface opening rate of outer circumferential face 3d, so that adhesive A 1 is difficult to invade from the surface opening of downside end face 3c the inside of bearing sleeve 3.Moreover, also the binder place of accumulating of concavity can be arranged at the upside end face 2c2 of cushion part 2c, perhaps the binder place of accumulating with concavity is arranged at the downside end face 3c of bearing sleeve 3 and the upside end face 2c2 both sides of cushion part 2c.
Similarly, utilize adhesive A 2 the upside end face 4c of bearing sleeve 4 to be fixed in the downside end face 2c3 of cushion part 2c.The binder that the upside end face 4c of bearing sleeve 4 is provided with the circumferential groove shape accumulates the 4c1 of place, part by adhesive A 2 enters binder and accumulates the 4c1 of portion, prevent unnecessary adhesive A 2 to the internal diameter side flow, and spread to the phenomenon of inner peripheral surface 4a one side (radial bearing gap one side) of bearing sleeve 4.The binder of circumferential groove shape accumulates the 4c1 of place and also can be provided with a plurality of on upside end face 4c.In addition, interior all sides of upside end face 4c have chamfering 4c2, and this chamfering 4c2 helps also to prevent that adhesive A 2 from spreading to internal side diameter.In addition, the surface opening rate of the upside end face 4c of preferred bearing sleeve 4 is littler than the surface opening rate of outer circumferential face 4d, so that adhesive A 2 is difficult to invade from the surface opening of downside end face 4c the inside of bearing sleeve 4.Moreover, also the binder place of accumulating of concavity can be arranged at the downside end face 2c3 of cushion part 2c, perhaps the binder place of accumulating with concavity is arranged at the upside end face 4c of bearing sleeve 4 and the downside end face 2c3 both sides of cushion part 2c.
As shown in Figure 2, bearing sleeve 3 is formed with lambdoid dynamic pressure groove 3a1 at the inner peripheral surface 3a as the radial bearing surface of first R1 of radial bearing portion, be formed with lambdoid dynamic pressure groove 3b1 at upside end face 3b, also be formed with axial groove 3d1 at outer circumferential face 3d as the thrust bearing surface of the first thrust bearing division T1.Axial groove 3d1 can form a plurality of for example three, and uniformly-spaced arranges along circumference.Utilize this axial groove 3d1, between the inner peripheral surface 2a of itself and shell 2, form axial fluid passage.Similarly, bearing sleeve 4 is formed with lambdoid dynamic pressure groove 4a1 at the inner peripheral surface 4a as the radial bearing surface of second R2 of radial bearing portion, be formed with lambdoid dynamic pressure groove 4b1 at downside end face 4b, also be formed with axial groove 4d1 at outer circumferential face 4d as the thrust bearing surface of the second thrust bearing division T2.Axial groove 4d1 can be provided with a plurality of for example three, and uniformly-spaced arranges along circumference.Utilize this axial groove 4d1, between the inner peripheral surface 2b of itself and shell 2, form axial fluid passage.
Shown in Fig. 3 amplifies, utilizing adhesive A 1 bearing sleeve 3 to be fixed under the state of upside end face 2c2 of cushion part 2c, the upside step surface 2f of its upside end face 3b and shell 2 forms with one side, perhaps becomes the state that only protrudes in step surface 2f dimension delta 2.This state can manage by the axial dimension (the perhaps axial dimension of cushion part 2c) to the inner peripheral surface 2a of the axial dimension of bearing sleeve 3 and shell 2 and be achieved.Shown in figure, only protrude under the situation of step surface 2f dimension delta 2 at the upside end face 3b that makes bearing sleeve 3, the downside end face 6b and the axial dimension between the step surface 2f of sealed member 6 are bigger than the thrust-bearing gap delta 1 of the first thrust bearing division T1.In addition, having omitted diagram, also is same about bearing sleeve 4.
This Hydrodynamic bearing apparatus 1 for example can be assembled according to following operation.
At first, after the upside end face 2c2 that adhesive A 1 is coated on the downside end face 3c of bearing sleeve 3 or cushion part 2c goes up, with the inner peripheral surface 2a of bearing sleeve 3 insertion shells 2, the downside end face 3c that makes bearing sleeve 3 is via the upside end face 2c2 butt of adhesive A 1 with cushion part 2c.At this moment, make the position of axial groove 3d1 of bearing sleeve 3 consistent with the position of the fluid passage 2c1 of cushion part 2c.Thus, the fluid passage 2c1 of fluid passage that is formed by axial groove 3d1 and cushion part 2c is communicated with.
Then, adhesive A 2 is coated on after the downside end face 2c3 of the upside end face 4c of bearing sleeve 4 or cushion part 2c, with the inner peripheral surface 2b of bearing sleeve 4 insertion shells 2, the upside end face 4c that makes bearing sleeve 4 is via the downside end face 2c3 butt of adhesive A 2 with cushion part 2c.At this moment, make the position of axial groove 4d1 of bearing sleeve 4 consistent with the position of the fluid passage 2c1 of cushion part 2c.Thus, the fluid passage 2c1 of fluid passage that is formed by axial groove 4d1 and cushion part 2c is communicated with.
Then, adhesive A 1, A2 are solidified, form as shown in Figure 2 shell 2 and the assembly of bearing sleeve 3,4.
Afterwards, spindle unit 5 is inserted inner peripheral surface 3a, the 4a of bearing 3,4 and the inner peripheral surface 2c4 of cushion part 2c, sealed member 6,7 is fixed in the assigned position of spindle unit 5.Moreover a side of sealed member 6,7 both can predetermined fixed also can be integrally formed with spindle unit 5 on spindle unit 5 before insertion.
Finished after the assembling through above-mentioned operation,, also comprised the internal porosity (internal porosity of porous plastid tissue) of bearing sleeve 4,5, for example filled filling lubricant oil as lubricating fluid in the inner space of the shell 2 of sealed parts 6,7 sealings.The filling of lubricant oil be in vacuum tank, impregnated in the lubricant oil by the Hydrodynamic bearing apparatus 1 that for example will finish assembling after, open to barometric pressure and to carry out.
During spindle unit 5 rotations, the inner peripheral surface 3a of bearing sleeve 3 and the inner peripheral surface 4a of bearing sleeve 4 are opposed via the radial bearing gap with the inner peripheral surface 5a of spindle unit 5 respectively.Gap between the inner peripheral surface 2c4 of cushion part 2c and the outer circumferential face 5a of spindle unit 5 is bigger than above-mentioned radial bearing gap.In addition, and opposed with the downside end face 6b of sealed member 6, the downside end face 4b of bearing sleeve 4 is opposed via the upside end face 7b of thrust-bearing gap and sealed member 7 via the thrust-bearing gap for the upside end face 3b of bearing sleeve 3.And along with the rotation of spindle unit 5, lubricant oil produces dynamic pressure in above-mentioned radial bearing gap, and spindle unit 5 is rotated the supporting of non-contact freely by the lubricating oil oil film radial direction that is formed in the above-mentioned radial bearing gap.Thus, be formed in radial direction and rotate first R1 of radial bearing portion and second R2 of radial bearing portion of non-contact supporting shaft part 5 freely.Simultaneously, lubricant oil produces dynamic pressure in above-mentioned radial bearing gap, and the sealed member 6,7 that is fixed in spindle unit 5 is rotated the supporting of non-contact freely by the lubricating oil oil film thrust direction that is formed in the above-mentioned thrust-bearing gap.Thus, be formed in and rotate the first thrust bearing division T1 and the second thrust bearing division T2 of non-contact supporting shaft part 5 freely on the thrust direction.
In addition, as mentioned above, owing to be formed at seal space S1, the S2 of the outer circumferential face 7a side of the outer circumferential face 6a side of sealed member 6 and sealed member 7, be diminishing coniform to the private side of shell 2, thereby the draw that produces by capillary force of the lubricant oil utilization in two space S 1, S2, and the draw that produces of the centrifugal force during rotation, being drawn towards the direction that seal space narrows down is the private side of shell 2.Thus, can prevent oil leak effectively from the inside of shell 2.In addition, seal space S1, S2 have the pooling feature that the lubricant oil that absorbs the inner space that is filled in shell 2 varies with temperature the volume-variation amount of generation, and in the scope of imaginary temperature variation, the pasta of lubricant oil is usually located in seal space S1, the S2.
In addition, utilization by the formed fluid passage of axial groove 3d1 of bearing sleeve 3, by the formed fluid passage of axial groove 4d1 of bearing sleeve 4, cushion part 2c fluid passage 2c1, 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 second T2 of radial bearing portion), and the outer circumferential face 5a of the inner peripheral surface 2c4 of cushion part 2c and spindle unit 5 between the gap, form continuous circulation canal in the inside of shell 2.And, the lubricant oil of the inner space by being filled in shell 2 circulates via this circulation canal, can guarantee the pressure balance of lubricant oil, the leakage of the lubricant oil that simultaneously, can prevent the generation of the bubble that accompanies with the generation of local negative pressure, causes because of the generation of bubble and generation of vibration etc.In addition, communicate with seal space S1, S2 respectively by an end of the formed fluid passage of axial groove 3d1 of bearing sleeve 3 with by an end of the formed fluid passage of axial groove 4d1 of bearing sleeve 4 as the atmosphere opening side.Therefore, no matter bubble is sneaked under the situation in the lubricant oil owing to why plant reason, bubble all can carry out along with lubricant oil circulation time be discharged to outside the gas open sides, thereby can more effectively prevent the adverse effect that causes by bubble.
Fig. 5 represents the Hydrodynamic bearing apparatus 11 of second mode of execution.The difference of the Hydrodynamic bearing apparatus 1 of this Hydrodynamic bearing apparatus 11 and above-mentioned first mode of execution is, with constituting cushion part 2c with the sleeve-like part of shell 2 splits, utilize bonding, be pressed into, be pressed into the inner peripheral surface 2a that the method that is fit to such as bonding is fixed in this cushion part 2c on shell 2.Fluid passage 2c1 forms the axial groove shape at the outer circumferential face of cushion part 2c.This cushion part 2c can perhaps form with metallic material with resin identical with shell 2 or different resins.In addition, the inner peripheral surface 2a of shell 2 begins to run through bearing sleeve 4 from the installation position of bearing sleeve 3 installation position is compared with the Hydrodynamic bearing apparatus 1 of first mode of execution in that axially to be light planar, and the shape of shell 2 is by simplification.Because other item is benchmark with first mode of execution all, thereby identical in fact parts and position then add identical symbolic representation, and the repetitive description thereof will be omitted.
Fig. 6 represents the Hydrodynamic bearing apparatus 21 of the 3rd mode of execution.The difference of the Hydrodynamic bearing apparatus 1 of this Hydrodynamic bearing apparatus 21 and above-mentioned first mode of execution is that inner peripheral surface 2a, the 2b of shell 2 extends to the end face of shell 2 respectively with homogeneous diameter, and correspondingly, sealed member 6,7 becomes smaller diameter.Compare with the Hydrodynamic bearing apparatus 1 of first mode of execution, its advantage is to make the shape of shell 2 to simplify, and can pathization.Because other item is a benchmark with first mode of execution all, thereby identical in fact parts and the identical symbolic representation of position interpolation, and the repetitive description thereof will be omitted.
In the explanation of first～the 3rd above mode of execution, as the dynamic pressure generating means of the R1 of radial bearing portion, R2 and thrust bearing division T1, T2, represented lambdoid dynamic pressure groove for example, but also can be the dynamic pressure groove of helical and other shape.Perhaps, also can adopt so-called stepped bearing and oily blade profile bearing as the dynamic pressure generating means.
Fig. 7, Fig. 8, Fig. 9 and Figure 10 represent the Hydrodynamic bearing apparatus (fluid dynamic-pressure bearing device) 31 of the 4th mode of execution, and be corresponding with Fig. 1, Fig. 2, Fig. 3 and Fig. 4 of above-mentioned first mode of execution respectively.And, for example rotation of supporting spindle in the motor of HDD of packing into of this Hydrodynamic bearing apparatus 31.The difference of the Hydrodynamic bearing apparatus 31 of the 4th mode of execution and the Hydrodynamic bearing apparatus 1 of above-mentioned first mode of execution is, for example use the porous plastid that constitutes by sintering metal, be that the porous plastid of the sintering metal of primary coil forms bearing sleeve 3,4 cylindraceous particularly, keep minimum radial direction clearance C 1, inner peripheral surface 2a, the 2b that C2 inserts shell 2 respectively in order to copper.And, the size of these radial direction clearance C 1, C2 is set at, for example in imaginary range of temperature, can absorb whole amounts because of the different thermal shrinkage differences that cause of linear expansion coeffcient of the bearing sleeve 3,4 of resin system shell 2 and sintering metal system.In addition, radial direction clearance C 1 and C2 both can set mutually the same size for, also can be set at different sizes.Because other item is a benchmark with first mode of execution all, thereby identical symbolic representation is then added at identical in fact parts and position, and the repetitive description thereof will be omitted.
Figure 11 represents the Hydrodynamic bearing apparatus 41 of the 5th mode of execution.The difference of the Hydrodynamic bearing apparatus 31 of this Hydrodynamic bearing apparatus 41 and above-mentioned the 4th mode of execution is, with constituting cushion part 2c with the sleeve-like part of shell 2 splits, utilize bonding, be pressed into, be pressed into the inner peripheral surface 2a that the method that is fit to such as bonding is fixed in this cushion part 2c on shell 2.Fluid passage 2c1 forms the axial groove shape at the outer circumferential face of cushion part 2c.This cushion part 2c can use resin identical with shell 2 or different resin or metallic material to constitute.In addition, the inner peripheral surface 2a of shell 2 begins to run through bearing sleeve 4 from the installation position of bearing sleeve 3 installation position is compared with the Hydrodynamic bearing apparatus 31 of the 4th mode of execution in that axially to be light planar, and the shape of shell 2 is by simplification.Because other item is a benchmark with the 4th mode of execution all, thereby identical symbolic representation is then added at identical in fact parts and position, and the repetitive description thereof will be omitted.
Figure 12 represents the Hydrodynamic bearing apparatus 51 of the 6th mode of execution.The difference of the Hydrodynamic bearing apparatus 31 of this Hydrodynamic bearing apparatus 41 and above-mentioned the 4th mode of execution is that inner peripheral surface 2a, the 2b of shell 2 extends to the end face of shell 2 respectively with homogeneous diameter, and correspondingly, sealed member 6,7 becomes smaller diameter.Compare with the Hydrodynamic bearing apparatus 31 of the 4th mode of execution, its advantage is to make the shape of shell 2 to simplify, but and pathization.Because other item is a benchmark with the 4th mode of execution all, thereby identical symbolic representation is then added at identical in fact parts and position, and the repetitive description thereof will be omitted.
In the explanation of the 4th～the 6th above mode of execution,, represented the dynamic pressure groove of reading shape for example, but also can be the dynamic pressure groove of helical and other shape as the dynamic pressure generating means of the R1 of radial bearing portion, R2 and thrust bearing division T1, T2.Perhaps also can adopt so-called stepped bearing and oily blade profile bearing as the dynamic pressure generating means.
Claims (14)
1, a kind of Hydrodynamic bearing apparatus, it possesses: shell; Bearing sleeve, it is accommodated in the inside of this shell; Spindle unit, it inserts the interior week of this bearing sleeve; Described spindle unit under the dynamic pressure effect of the lubricating fluid that it is produced in the radial bearing gap between described bearing sleeve inner peripheral surface and the described spindle unit outer circumferential face, supports in non-contact in the radial direction in radial bearing portion, and described Hydrodynamic bearing apparatus is characterised in that,
It is a plurality of that described bearing sleeve separates configuration in the axial direction;
Between described axially spaced bearing sleeve, be provided with cushion part;
Described cushion part fixedly installs with respect to described shell;
Described bearing sleeve is being adhesively fixed in described cushion part with the opposed end face of the end face of described cushion part.
2, Hydrodynamic bearing apparatus as claimed in claim 1 is characterized in that, the binder that at least one side is provided with concavity among the end face of the end face of described bearing sleeve and described cushion part accumulates the place.
3, Hydrodynamic bearing apparatus as claimed in claim 2 is characterized in that, is provided with fluid passage to its axial both-side opening in described cushion part.
4, Hydrodynamic bearing apparatus as claimed in claim 3 is characterized in that, the fluid passage of described cushion part is communicated with axial fluid passage between inner peripheral surface that is arranged on described shell and the described bearing sleeve outer circumferential face.
5, Hydrodynamic bearing apparatus as claimed in claim 1, it is characterized in that, described spindle unit has to the side-prominent protuberance of external diameter, and between the end face of the end face of this protuberance and described bearing sleeve, be provided with thrust bearing division, under the dynamic pressure effect of the lubricating fluid that this thrust bearing division is produced in described thrust-bearing gap, described spindle unit is supported in non-contact on thrust direction.
6, the described Hydrodynamic bearing apparatus of claim 5 is characterized in that, is formed with seal space at the outer circumferential side of the protuberance of described spindle unit.
7, Hydrodynamic bearing apparatus as claimed in claim 1 or 2 is characterized in that, described shell is that melted material is carried out contour forming and the shell that forms.
8, a kind of Hydrodynamic bearing apparatus possesses: shell; Bearing sleeve, it is accommodated in the inside of this shell; Spindle unit, it is inserted into the interior week of this bearing sleeve; Described spindle unit under the dynamic pressure effect of the lubricating fluid that it is produced in the radial bearing gap between described bearing sleeve inner peripheral surface and the described spindle unit outer circumferential face, supports in non-contact in the radial direction in radial bearing portion, and described Hydrodynamic bearing apparatus is characterised in that,
It is a plurality of that described bearing sleeve separates configuration in the axial direction;
Between the described bearing sleeve that separates on axially, be provided with cushion part;
Described cushion part fixedly installs with respect to described shell;
Described bearing sleeve keeps interior week of inserting described shell with gap, and the opposed end face of the end face of utilization and described cushion part and being adhesively fixed in described cushion part.
9, Hydrodynamic bearing apparatus as claimed in claim 8 is characterized in that, the binder that at least one side among described bearing sleeve end face and described cushion part end face is provided with concavity accumulates the place.
10, Hydrodynamic bearing apparatus as claimed in claim 9 is characterized in that, is provided with fluid passage to its axial both-side opening in described cushion part.
11, Hydrodynamic bearing apparatus as claimed in claim 10 is characterized in that, the axial fluid passage between the outer circumferential face of the fluid passage of described cushion part and inner peripheral surface that is arranged on described shell and described bearing sleeve is communicated with.
12, Hydrodynamic bearing apparatus as claimed in claim 8, it is characterized in that, described spindle unit has to the side-prominent protuberance of external diameter, and between the end face of the end face of this protuberance and described bearing sleeve, be provided with thrust bearing division, under the dynamic pressure effect of the lubricating fluid that this thrust bearing division is produced in described thrust-bearing gap, described spindle unit is supported in non-contact on thrust direction.
13, Hydrodynamic bearing apparatus as claimed in claim 12 is characterized in that, is formed with seal space at the outer circumferential side of the protuberance of described spindle unit.
14, Hydrodynamic bearing apparatus as claimed in claim 8 or 9 is characterized in that, described shell is that melted material is carried out contour forming and the shell that forms.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006086359A JP4855117B2 (en) | 2006-03-27 | 2006-03-27 | Hydrodynamic bearing device |
| JP086371/2006 | 2006-03-27 | ||
| JP2006086371A JP2007263176A (en) | 2006-03-27 | 2006-03-27 | Hydrodynamic bearing device |
| JP086359/2006 | 2006-03-27 | ||
| PCT/JP2007/055559 WO2007119428A1 (en) | 2006-03-27 | 2007-03-19 | Hydrodynamic bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101410637A true CN101410637A (en) | 2009-04-15 |
| CN101410637B CN101410637B (en) | 2011-01-26 |
Family
ID=38636374
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780011272XA Expired - Fee Related CN101410637B (en) | 2006-03-27 | 2007-03-19 | Hydrodynamic bearing device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4855117B2 (en) |
| CN (1) | CN101410637B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102694435A (en) * | 2011-03-25 | 2012-09-26 | 日本电产株式会社 | Spindle motor and storage disk drive |
| CN103261624A (en) * | 2011-03-29 | 2013-08-21 | 三菱重工业株式会社 | Turbocharger and method for manufacturing floating bush |
| CN108026968A (en) * | 2015-08-19 | 2018-05-11 | 大同金属工业株式会社 | Vertical bearing device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10318250A (en) * | 1997-05-22 | 1998-12-02 | Sony Corp | Fluid bearing and manufacture thereof |
| JP3602707B2 (en) * | 1997-11-21 | 2004-12-15 | 東京パーツ工業株式会社 | Hydrodynamic bearing motor |
| JP2002070849A (en) * | 2000-08-28 | 2002-03-08 | Matsushita Electric Ind Co Ltd | Dynamic pressure type fluid bearing device and method for manufacturing the same |
| JP2005163903A (en) * | 2003-12-02 | 2005-06-23 | Ntn Corp | Dynamic bearing device |
-
2006
- 2006-03-27 JP JP2006086359A patent/JP4855117B2/en not_active Expired - Fee Related
-
2007
- 2007-03-19 CN CN200780011272XA patent/CN101410637B/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102694435A (en) * | 2011-03-25 | 2012-09-26 | 日本电产株式会社 | Spindle motor and storage disk drive |
| CN102694435B (en) * | 2011-03-25 | 2014-12-10 | 日本电产株式会社 | Spindle motor and storage disk drive |
| CN103261624A (en) * | 2011-03-29 | 2013-08-21 | 三菱重工业株式会社 | Turbocharger and method for manufacturing floating bush |
| CN103261624B (en) * | 2011-03-29 | 2016-03-23 | 三菱重工业株式会社 | Turbosupercharger and floating bush manufacture method |
| US9726189B2 (en) | 2011-03-29 | 2017-08-08 | Mitsubishi Heavy Industries, Ltd. | Turbocharger and method of manufacturing floating bush |
| CN108026968A (en) * | 2015-08-19 | 2018-05-11 | 大同金属工业株式会社 | Vertical bearing device |
| CN108026968B (en) * | 2015-08-19 | 2019-08-30 | 大同金属工业株式会社 | Vertical bearing device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101410637B (en) | 2011-01-26 |
| JP4855117B2 (en) | 2012-01-18 |
| JP2007263173A (en) | 2007-10-11 |
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