WO2004038240A1 - 動圧軸受装置 - Google Patents
動圧軸受装置 Download PDFInfo
- Publication number
- WO2004038240A1 WO2004038240A1 PCT/JP2003/012944 JP0312944W WO2004038240A1 WO 2004038240 A1 WO2004038240 A1 WO 2004038240A1 JP 0312944 W JP0312944 W JP 0312944W WO 2004038240 A1 WO2004038240 A1 WO 2004038240A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- dynamic pressure
- thrust
- bearing
- pressure groove
- groove region
- Prior art date
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 22
- 239000000463 material Substances 0.000 claims description 16
- 239000002966 varnish Substances 0.000 claims description 13
- 230000003746 surface roughness Effects 0.000 claims description 10
- 230000009471 action Effects 0.000 claims description 7
- 239000012530 fluid Substances 0.000 claims description 2
- 239000000314 lubricant Substances 0.000 abstract description 3
- 230000000694 effects Effects 0.000 abstract description 2
- 239000010687 lubricating oil Substances 0.000 description 5
- 239000003921 oil Substances 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000011148 porous material Substances 0.000 description 3
- 229910000906 Bronze Inorganic materials 0.000 description 2
- 229910000881 Cu alloy Inorganic materials 0.000 description 2
- 239000010974 bronze Substances 0.000 description 2
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 238000005498 polishing Methods 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910001369 Brass Inorganic materials 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- OAICVXFJPJFONN-UHFFFAOYSA-N Phosphorus Chemical compound [P] OAICVXFJPJFONN-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- CUZMQPZYCDIHQL-VCTVXEGHSA-L calcium;(2s)-1-[(2s)-3-[(2r)-2-(cyclohexanecarbonylamino)propanoyl]sulfanyl-2-methylpropanoyl]pyrrolidine-2-carboxylate Chemical compound [Ca+2].N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1.N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1 CUZMQPZYCDIHQL-VCTVXEGHSA-L 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005530 etching Methods 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000003672 processing method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
- B21K1/00—Making machine elements
- B21K1/04—Making machine elements ball-races or sliding bearing races
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/02—Stamping using rigid devices or tools
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J5/00—Methods for forging, hammering, or pressing; Special equipment or accessories therefor
- B21J5/02—Die forging; Trimming by making use of special dies ; Punching during forging
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J5/00—Methods for forging, hammering, or pressing; Special equipment or accessories therefor
- B21J5/06—Methods for forging, hammering, or pressing; Special equipment or accessories therefor for performing particular operations
- B21J5/12—Forming profiles on internal or external surfaces
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
- B21K23/00—Making other articles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
- F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
- F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/14—Special methods of manufacture; Running-in
Definitions
- the present invention relates to a dynamic pressure bearing device.
- This bearing device is used for information equipment, for example, HDDs, magnetic disk drives for FDD, optical disk devices such as CD-ROM and DVD-ROM, magneto-optical disk devices such as MD and MO, and laser beams. It is suitable for use in polygon scanners of printers (LBP) or for small appliances such as electrical equipment, such as axial fans.
- LBP printers
- electrical equipment such as axial fans.
- Japanese Patent Application Laid-Open No. 2002-61641 discloses an example of such a dynamic pressure bearing device.
- the disclosed bearing includes a cylindrical housing having a bottom, a bearing sleeve fixed to the inner periphery of the housing, and a shaft inserted into the inner peripheral surface of the bearing sleeve.
- a member including a member, a radial bearing portion and a thrust bearing portion which rotatably support the shaft member in a non-contact manner by a dynamic pressure action generated when the shaft member and the bearing sleeve rotate relative to each other.
- the thrust bearing portion is formed in a thrust bearing gap between the both end surfaces of the flange portion of the shaft member, the housing bottom surface and the end surface of the bearing sleeve facing each other. It generates pressure by the action of dynamic pressure, and supports the shaft member in a non-contact manner in the thrust direction.
- grooves for generating dynamic pressure (dynamic pressure grooves) must be formed on any of the surfaces (both ends of the flange, the bottom of the housing, and the end of the bearing sleeve) facing the thrust bearing gap.
- a dynamic pressure groove is formed on the end face of the thrust plate separate from the housing body, and this is attached to one end opening of the bowing body to form the bottom of the housing.
- the present invention aims at providing a dynamic pressure bearing device capable of forming a dynamic pressure groove of a thrust bearing portion with high accuracy and low cost and having an excellent durability life.
- the present invention includes a shaft member having a first thrust surface, and a first varnish thrust surface facing the first thrust surface of the shaft member in the thrust direction.
- a dynamic pressure groove region having a plurality of dynamic pressure grooves is formed, and a pressure is generated by a dynamic pressure action of fluid in a thrust bearing gap between the first thrust surface and the varnish thrust surface,
- the dynamic pressure groove region is formed by pressing, and the height difference obtained by subtracting the outer peripheral edge from the inner peripheral edge of the surface is 0 m or more and 2 m.
- the dynamic pressure groove region facing the thrust bearing gap is formed by pressing, so that the dynamic pressure groove processing can be performed at low cost.
- the height difference between the inner and outer diameter portions of the dynamic pressure groove region is regulated as described above, so that contact with the shaft member at the time of start / stop of the motor or the like is performed on the inner diameter side where the peripheral speed is low. Swell. Therefore, it is possible to suppress the progress of wear at the contact portion between the two, and it is possible to improve the durability life of the bearing device.
- the height difference in the dynamic pressure groove region is, for example, formed by forming a portion corresponding to the dynamic pressure groove region of the material into a tapered surface having a lower inner diameter side, and pressing the material in this state. Can be.
- the first and second varnish surfaces are formed in a direction orthogonal to the thrust direction.
- the first thrust surface can be formed, for example, by providing a flange portion on the shaft member and forming an end surface of the flange portion facing the first varnish last surface.
- the thrust surface may be formed on an end surface of a shaft member having a shaft shape. If the surface roughness of the dynamic pressure groove area P is rough, it is difficult to satisfy the above-mentioned height difference, even if pressing is performed accurately, but the dynamic pressure groove area has a surface roughness of 0.6 Ra or less. If there is, it will be possible to satisfy this. 'In addition, Ra means the center line average roughness specified in Japanese Industrial Standards (JIS B 0601).
- Surface roughness of 0.6 Ra or less can be achieved by finishing at least the back of the dynamic pressure groove area.
- the "back" of the dynamic pressure groove region means a convex portion between adjacent dynamic pressure grooves.
- a processing method capable of removing microscopic projections, for example, lapping or chemical polishing is preferable.
- the same surface roughness can be obtained even if re-pressing is performed as finishing after the first press (press twice).
- the dynamic pressure bearing device may further include a housing provided with an opening at one end and the other end sealed with a thrust plate.
- the dynamic pressure groove region can be formed on the end face of the thrust plate.
- the above-mentioned dynamic pressure groove region may be formed on the first thrust surface of the flange portion.
- FIG. 1 is a sectional view of a hydrodynamic bearing device according to an embodiment of the present invention.
- '' Fig. 2 is a plan view of the varnish last surface (upper surface of the thrust plate).
- FIG. 3 is an enlarged cross-sectional view of the varnish last surface (the upper end surface of the thrust plate) according to the present invention.
- FIG. 4 is a cross-sectional view showing a schematic structure of a press device for forming the varnish last surface.
- FIG. 5 is a cross-sectional view showing the shape of the material of the thrust plate before pressing.
- FIG. 6 is a view showing the measurement results of the relative change of the thrust bearing gap in the comparative product.
- FIG. 7 is a diagram showing a measurement result of a relative change amount of a thrust bearing gap in the product of the present invention.
- FIG. 8 is a sectional view showing another embodiment of the present invention.
- FIG. 9 is a cross-sectional view showing the state of the thin-walled material before press working (FIG. A) and after press working (FIG. B). Description of the preferred embodiment
- FIG. 1 shows a hydrodynamic bearing device 1 according to the present invention.
- the hydrodynamic bearing device 1 includes a cylindrical housing 7 having a bottom having an opening ⁇ a at one end, a cylindrical bearing sleeve 8 fixed to an inner peripheral surface of a housing 7, a shaft member 2,
- the sealing member 10 fixed to the opening 7a of 7 is a main component.
- the housing 7 is formed in a bottomed cylindrical shape having a cylindrical side portion 7b and a bottom portion 7c.
- the bottom portion 7c is formed of a thin disk-shaped thrust plate having a substantially uniform thickness, which is separate from the side portion 7b.
- the housing 7 having one end sealed is formed by bonding to the lower opening of 7b by press-fitting or by using both of them and attaching them to the side 7b.
- the upper end face 7c1 (third varnish face) of the thrust plate 7c has A region P (dynamic pressure groove region), which becomes one thrust bearing surface of the shaft bearing portion T, is formed in an annular shape. In this region, as shown in FIG. A back portion P 2 which is a convex portion between the pressure grooves P 1 is formed in a spiral shape.
- the dynamic pressure groove region P is formed by pressing as described later, and in order to improve workability at that time, the thrust plate 7c is made of a soft metal material having a small yield stress, for example, It is desirable to use a copper alloy (Machiyu, gunmetal, lead bronze, phosphor bronze, etc.) or an aluminum alloy (JIS A class 2-7).
- the shape of the dynamic pressure groove in the dynamic pressure groove region P is arbitrary, and may be a herringbone shape.
- the dynamic pressure groove region P is formed in a rectangular shape in a part of the upper end face 7 c 1 in the radial direction, but is formed in another region other than the illustrated one (for example, the inner diameter side than the illustrated one).
- the shaft member 2 is formed of, for example, a metal material such as stainless steel (for example, SUS420J2 specified in JIS), and is integrally or separately provided at the lower end of the shaft portion 2a and the shaft portion 2a. Flange portion 2b.
- the upper end surface 2 b 1 of the flange portion 2 b faces the lower end surface 8 c of the bearing sleeve 8 via a thrust bearing gap
- the lower end surface 2 b 2 (first thrust surface) is a thrust plate 7 c. It faces the upper end face 7c1 (the varnish thrust face) of the thrust bearing via a thrust bearing gap.
- the bearing sleeve 8 is formed in a cylindrical shape from, for example, an oil-impregnated sintered metal obtained by impregnating a porous material, particularly a sintered metal mainly composed of copper, with lubricating oil or lubricating grease.
- a porous material particularly a sintered metal mainly composed of copper
- lubricating oil or lubricating grease On the inner peripheral surface 8a of the bearing slip 8, two upper and lower regions serving as radial bearing surfaces of the first radial bearing portion R1 and the second radial bearing portion R2 are provided axially separated from each other.
- a herringbone-shaped dynamic pressure groove is formed in each of the two regions.
- the shape of the dynamic pressure groove may be a spiral shape, an axial groove shape, or the like.
- the dynamic pressure groove is formed through the radial bearing gap with the inner peripheral surface 8 a of the bearing slip 8. It may be formed on the outer peripheral surface of the shaft portion 2a of the facing shaft member 2. Further, the bearing sleeve 8 can be formed of a soft metal such as brass or a copper alloy other than the porous material.
- the other end of the thrust bearing T is provided on the lower end surface 8c of the bearing sleeve 8.
- a region (dynamic pressure groove region) serving as a last bearing surface is formed in an annular shape, and a spiral dynamic pressure groove (not shown) is formed in this region.
- the shape of the dynamic pressure groove is arbitrary, and a herringbone shape may be adopted.
- the seal member 10 is annular, and is fixed to the inner peripheral surface of the opening 7a of the housing 7 by means of press-fitting, bonding or the like.
- the inner peripheral surface 10a of the seal member 10 is formed in a cylindrical shape, and the lower end surface of the seal member 10 is in contact with the upper end surface 8b of the bearing sleeve 8.
- the shaft portion 2a of the shaft member 2 is inserted into the inner peripheral surface 8a of the bearing sleeve 8, and the flange portion 2b is connected to the lower end surface 8c of the bearing sleeve 8 and the upper end surface 7c1 of the thrust plate 7c. Is housed in the space between the two.
- the tapered surface 2a1 of the shaft portion 2a is opposed to the inner peripheral surface 10a of the seal member 10 via a predetermined gap.
- a tapered seal space S is formed which gradually expands toward (upward). When the shaft member 2 rotates, the tapered surface 2a1 of the shaft portion 2a also functions as a so-called centrifugal force seal.
- the interior space of the housing 7 (including the pores inside the bearing sleeve 8) sealed with the sealing member 10 is filled with a lubricant (lubricating oil), and the oil level of the lubricant is in the sealing space S. is there.
- the sealing space S may be a tapered space or a cylindrical space having the same diameter in the axial direction.
- a pressure is generated in the radial bearing gap by the dynamic pressure action of the lubricating oil, and the shaft portion 2a of the shaft member 2 is radially moved by an oil film formed in the upper and lower radial bearing gaps. Rotatably supported in a non-contact manner.
- a first radial bearing portion Rl and a second radial bearing portion R2 that rotatably support the shaft member 2 in the radial direction in a non-contact manner are configured.
- a pressure is generated in the upper and lower thrust bearing gaps by the dynamic pressure action of the lubricating oil, and the flange portion 2b of the shaft member 2 is rotatable in both thrust directions by the oil film formed in the thrust bearing gap. Is supported in a non-contact manner.
- a thrust bearing portion T that rotatably supports the shaft member 2 in the thrust direction in a non-contact manner is configured.
- the dynamic pressure groove region P of the upper end face 7 c 1 of the thrust plate 7 c is a plastic deformation by press forming, that is, as shown in FIG. 4, the material 7 c of the thrust plate 7 c arranged on the die 25. , Are formed by pressing with upper and lower punches 21 and 23. A die 23 having a groove portion corresponding to the shape of the dynamic pressure groove region P is attached to one of the punches, for example, the upper punch 21. Material 7 c at the inner periphery of the die 2 5 plastic deformation occurs on the end face of the 'while restraining the outer diameter, material 7 c by pressing the mold 2 3 the material 7 c 5', the dynamic pressure generating groove area P is transferred It is formed.
- the thrust plate 7c is formed of the above-described material 7c, which is soft and has a low yield stress, a highly accurate dynamic pressure groove can be formed even with a low press pressure.
- the dynamic pressure groove region P of the thrust plate 7c has a height difference H1 obtained by subtracting the outer peripheral edge from the inner peripheral edge of the surface thereof within a range of 0 or more +2 m or less. Formed.
- the surface of the dynamic pressure groove region P is a plane in a direction orthogonal to the axis.
- the surface of the dynamic pressure groove region P becomes an inclined surface having a higher inner diameter side.
- the slope ⁇ here is not limited to the case where the contour of the surface exists on the slope straight line as shown in the figure, but also includes the case where these contours exist on the curve.
- the degree of inclination of the surface of the dynamic pressure groove region P is exaggerated for ease of understanding.
- the dynamic pressure groove area P of the shaft member immediately after the start and stop of the motor Contact the lower end surface 2b1 of the part 2b on the entire surface or the inner peripheral part.
- contact is suppressed only at the outer peripheral portion where the peripheral speed is high, so that uneven wear due to contact between the flange portion 2b and the thrust plate 7c immediately after starting or immediately before stopping can be prevented, and the bearing life can be reduced. Can be improved.
- the surface of the dynamic pressure groove region P has an inclined shape with the outer diameter side being higher, and the dynamic pressure groove region P is formed as described above. There is an inconvenience of contacting the flange portion 2b on the outer diameter side where the peripheral speed is fast. Also, if the height difference H 1 exceeds 2 ⁇ , the wear of the contact portion is accelerated.
- this thrust plate 7c forms a portion Q corresponding to the dynamic pressure groove region P of the material 7c 'into a tapered surface shape in which the inner diameter side is lowered by H2.
- ' Can be formed by pressing with a press device shown in FIG. With the press, the material 7c warps in the manner shown in Figs. 9 (a) and 9 (b), but the deformation at this time occurs so as to negate the taper direction of the Q section.
- the dynamic pressure groove region P of the thrust plate 7c can be finished within the range of the height difference (0 ⁇ H1 ⁇ 2 ⁇ m).
- the surface roughness of the dynamic pressure groove region P of the thrust plate 7c is rough, it is difficult to satisfy H 1 ⁇ 2 m even if the processing is accurately performed by the press device shown in FIG. Therefore, it is desirable that the surface roughness of the dynamic pressure groove region P be as smooth as possible.
- the surface roughness of the dynamic pressure groove region P (particularly, the surface roughness of the back portion P2) is desirably in the range of 0 to 0.6 Ra. This surface roughness can be obtained by performing finishing on the back portion P 2 of the dynamic pressure groove region P (or both the dynamic pressure groove P 1 and the back portion P 2) after pressing.
- lapping chemical polishing, re-pressing (double pressing), or the like.
- FIGS. 6 and 7 show a bearing device having the thrust plate 7c provided with the above countermeasures (the device of the present invention) and a bearing device having a thrust plate pressed without taking the above countermeasures (comparative product). The operation was repeated starting and stopping, and the relative change in the thrust bearing clearance was measured.
- the horizontal axis represents the number of tests (cycles) and the vertical axis represents the amount of wear (m).
- the product of the present invention can significantly reduce the amount of wear as compared with the comparative product, and has a remarkable effect on the improvement of the durability life of the bearing device.
- the thrust plate 7c is separate from the housing 7.
- the present invention provides a structure in which the thrust plate is integrated with the housing, that is, the housing 7 is formed into a bottomed cylindrical shape having a bottom portion integrally. The same applies to the case where the dynamic pressure groove region P is formed on the inner bottom surface of the bottom.
- the dynamic pressure groove region P can be formed on either end face 2b1, 2b2 of the flange portion 2b as shown in FIG. It can be formed on one or both sides (the drawing shows the case where the dynamic pressure groove regions P are formed on both end faces).
- This structure is particularly suitable when the shaft portion 2a and the flange portion 2b of the shaft member 2 are formed separately as shown in the figure.
- one end opening of the bearing sleeve 8 is sealed with a thrust member 11, and the upper end surface thereof is opposed to the lower end surface 2b2 of the flange portion 2b.
- a varnish last surface 7c1 is formed on the upper end surface of a thrust plate 7c constituting the bottom of the housing 7, as in the embodiment shown in FIG. You can also.
- the case where a dynamic pressure bearing having a dynamic pressure groove is used as the radial bearing portions R l and R 2 has been described.
- a radial bearing Any material can be used as long as it supports the shaft member 2 in the radial direction without contact with an oil film of lubricating oil formed in the gap.
- the area to be the radial bearing surface has a perfect circular cross section without dynamic pressure grooves. Certain bearings (round bearings) can also be used.
- region of a thrust bearing part can be shape
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/531,519 US7946770B2 (en) | 2002-10-24 | 2003-10-09 | Hydrodynamic bearing device |
AU2003271137A AU2003271137A1 (en) | 2002-10-24 | 2003-10-09 | Hydrodynamic bearing device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002/310003 | 2002-10-24 | ||
JP2002310003A JP4245897B2 (ja) | 2002-10-24 | 2002-10-24 | 動圧軸受装置の製造方法 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004038240A1 true WO2004038240A1 (ja) | 2004-05-06 |
Family
ID=32171029
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/012944 WO2004038240A1 (ja) | 2002-10-24 | 2003-10-09 | 動圧軸受装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7946770B2 (ja) |
JP (1) | JP4245897B2 (ja) |
KR (1) | KR100955664B1 (ja) |
CN (1) | CN100360818C (ja) |
AU (1) | AU2003271137A1 (ja) |
WO (1) | WO2004038240A1 (ja) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100597073B1 (ko) | 2004-07-07 | 2006-07-04 | 한국과학기술원 | 요철 내면이 형성된 복합재료 저널베어링 및 그 제조방법 |
JP4554324B2 (ja) * | 2004-10-07 | 2010-09-29 | Ntn株式会社 | 動圧軸受装置 |
JP2006194385A (ja) * | 2005-01-14 | 2006-07-27 | Ntn Corp | 動圧軸受装置 |
JP2006283971A (ja) * | 2005-03-11 | 2006-10-19 | Nippon Densan Corp | 流体動圧軸受およびこの流体動圧軸受を備えたスピンドルモータ |
US8618706B2 (en) | 2008-12-04 | 2013-12-31 | Seagate Technology Llc | Fluid pumping capillary seal for a fluid dynamic bearing |
JP5314517B2 (ja) * | 2009-07-06 | 2013-10-16 | 三菱重工業株式会社 | 軸受装置、軸受ユニットおよび回転機械 |
US8764307B2 (en) | 2010-10-29 | 2014-07-01 | Koyo Bearings Usa Llc | Roller thrust bearing vibration isolator |
KR101145873B1 (ko) * | 2011-01-05 | 2012-05-17 | 주식회사 삼홍사 | 스핀들 모터 |
EP2549059A1 (de) * | 2011-07-21 | 2013-01-23 | Siemens Aktiengesellschaft | Verfahren zum Betrieb einer Rotationsmaschine |
JP5619937B2 (ja) * | 2013-01-15 | 2014-11-05 | キヤノンマシナリー株式会社 | 摺動面構造 |
US9790990B2 (en) * | 2013-06-17 | 2017-10-17 | Seagate Technology Llc | Bearing gap determined depth and width |
TWI599150B (zh) * | 2016-09-01 | 2017-09-11 | 昆山廣興電子有限公司 | 馬達及其動壓板 |
WO2020171021A1 (ja) * | 2019-02-22 | 2020-08-27 | 株式会社Ihi | スラストフォイル軸受、スラストフォイル軸受のベースプレートの製造方法 |
CN111120390A (zh) * | 2019-12-16 | 2020-05-08 | 苏州柯琳艾尔智能科技有限公司 | 风扇芯轴防倾斜结构 |
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US6435721B1 (en) * | 1999-10-29 | 2002-08-20 | Matsushita Electric Industrial Co., Ltd. | Spindle motor unit having hydrodynamic bearing |
JP2002025089A (ja) * | 2000-07-10 | 2002-01-25 | Ricoh Co Ltd | 傾き検出装置および光ディスク装置 |
JP2002061641A (ja) | 2000-08-23 | 2002-02-28 | Ntn Corp | 動圧型軸受装置 |
-
2002
- 2002-10-24 JP JP2002310003A patent/JP4245897B2/ja not_active Expired - Lifetime
-
2003
- 2003-10-09 US US10/531,519 patent/US7946770B2/en not_active Expired - Fee Related
- 2003-10-09 CN CNB2003801032654A patent/CN100360818C/zh not_active Expired - Fee Related
- 2003-10-09 WO PCT/JP2003/012944 patent/WO2004038240A1/ja active Application Filing
- 2003-10-09 KR KR1020057006960A patent/KR100955664B1/ko active IP Right Grant
- 2003-10-09 AU AU2003271137A patent/AU2003271137A1/en not_active Abandoned
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JPH0560127A (ja) * | 1991-08-30 | 1993-03-09 | Mitsubishi Electric Corp | 動圧軸受のコイニング加工法 |
JP2000120664A (ja) * | 1998-10-16 | 2000-04-25 | Ngk Spark Plug Co Ltd | セラミックス製動圧軸受 |
US20020025089A1 (en) * | 2000-08-23 | 2002-02-28 | Natsuhiko Mori | Hydrodynamic bearing unit |
JP2002195265A (ja) * | 2000-12-26 | 2002-07-10 | Nsk Ltd | 流体軸受装置用スラストプレートの製造方法 |
Also Published As
Publication number | Publication date |
---|---|
US7946770B2 (en) | 2011-05-24 |
KR20050083798A (ko) | 2005-08-26 |
KR100955664B1 (ko) | 2010-05-06 |
JP4245897B2 (ja) | 2009-04-02 |
AU2003271137A1 (en) | 2004-05-13 |
JP2004144205A (ja) | 2004-05-20 |
CN1711429A (zh) | 2005-12-21 |
CN100360818C (zh) | 2008-01-09 |
US20060098907A1 (en) | 2006-05-11 |
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