WO2011105481A1 - 流体動圧軸受装置 - Google Patents
流体動圧軸受装置 Download PDFInfo
- Publication number
- WO2011105481A1 WO2011105481A1 PCT/JP2011/054124 JP2011054124W WO2011105481A1 WO 2011105481 A1 WO2011105481 A1 WO 2011105481A1 JP 2011054124 W JP2011054124 W JP 2011054124W WO 2011105481 A1 WO2011105481 A1 WO 2011105481A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- housing
- bearing sleeve
- peripheral surface
- bearing
- fluid dynamic
- Prior art date
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Classifications
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- 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
- F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
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- 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
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- 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
- F16C33/72—Sealings
- F16C33/74—Sealings of sliding-contact bearings
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- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
- H02K5/1675—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings radially supporting the rotary shaft at only one end of the rotor
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- 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
- F16C2370/00—Apparatus relating to physics, e.g. instruments
- F16C2370/12—Hard disk drives or the like
Definitions
- the present invention relates to a fluid dynamic bearing device that rotatably supports a shaft member with a fluid dynamic pressure formed in a bearing gap.
- Fluid dynamic pressure bearing devices have characteristics such as high-speed rotation, high rotation accuracy, and low noise.
- bearing devices for motors mounted on various electrical devices such as information devices have been utilized. More specifically, magnetic disk devices such as HDD, optical disk devices such as CD-ROM, CD-R / RW, DVD-ROM / RAM, spindle motors such as magneto-optical disk devices such as MD and MO, lasers, etc. It is suitably used as a motor bearing device such as a polygon scanner motor of a beam printer (LBP), a color wheel motor of a projector, a fan motor, or the like.
- LBP beam printer
- this type of fluid dynamic pressure bearing device includes a bearing sleeve 108 made of sintered metal, a shaft member 102 inserted into the inner periphery of the bearing 108 sleeve, and rotated relative to the bearing sleeve 108. And a housing 107 for housing the bearing sleeve 108.
- the shaft member 102 one having a flange portion 102b at one end of the shaft portion 102a is used.
- a radial bearing gap is formed between the outer peripheral surface of the shaft portion 102a and the inner peripheral surface of the bearing sleeve 108, and the first end surface 102b1 of the flange portion 102b and the end surface 108a of the bearing sleeve 108 facing the first end surface 108a.
- Thrust bearing gap S1 is formed, and a second thrust bearing gap S2 is formed between the other end face 102b2 of the flange portion 102b and the inner bottom face of the housing bottom portion 107c.
- the housing is often a metal machined product or a resin molded product, but the machined product increases the rigidity of the housing, so when the bearing sleeve is press-fitted into the inner periphery of the housing, the circumferential direction of the press-fitting allowance is increased.
- the variation affects the accuracy of the inner peripheral surface of the bearing sleeve. In order to avoid this, it is necessary to increase the accuracy of the inner peripheral surface of the housing and the outer peripheral surface of the bearing sleeve, and the processing cost of these members increases. Further, in press-fitting, it is necessary to accurately align the housing and the bearing sleeve in order to prevent galling and the like.
- the bearing device Since the flange portion is formed at one end of the shaft member, the bearing device is assembled in a state in which another flange-like member (such as a hub) is attached to the other end side of the shaft member (the shaft member is attached to the inner periphery of the bearing sleeve). Can not be inserted). Therefore, it is necessary to remove the flange-shaped member at the time of assembly, and the assembly procedure is restricted.
- another flange-like member such as a hub
- An object of the present invention is to drastically modify the conventional design concept, thereby greatly simplifying the configuration and assembly process of the fluid dynamic pressure bearing device, thereby achieving cost reduction.
- a hydrodynamic bearing device is formed on one of a bearing sleeve, a shaft member inserted in the inner periphery of the bearing sleeve, and an outer peripheral surface of the shaft member and an inner peripheral surface of the bearing sleeve, and the outer periphery of the shaft member.
- the hydrodynamic pressure generating part generates fluid dynamic pressure in the radial bearing gap between the surface and the inner peripheral surface of the bearing sleeve, and is formed by press working.
- the housing has an engaging portion that engages with the end surface of the bearing sleeve, and a thrust receiver that contacts and supports one end of the shaft member.
- the axial relative position between the housing and the bearing sleeve is determined simply by pressing the bearing sleeve into the housing and pushing the bearing sleeve until the end surface of the bearing sleeve engages with the engaging portion of the housing.
- the basic configuration of the bearing device is completed simply by inserting the shaft member into the inner periphery of the bearing sleeve.
- the thrust bearing is formed of a so-called pivot bearing, it is not necessary to provide a clearance for the thrust bearing gap, and the allowable dimensional error in the axial relative position between the bearing sleeve and the housing is alleviated.
- the press housing has low rigidity, and the pressing force in the inner diameter direction after press-fitting becomes small. Therefore, even if there is a slight misalignment between the housing and the bearing sleeve, the press-fitting operation can be performed smoothly. From the above, the assembly workability is remarkably improved and the configuration becomes simple.
- the processing cost will be significantly lower than the machining, so the part cost can be reduced.
- the rigidity of the press-made housing is low, the pressing force in the inner diameter direction that the bearing sleeve receives from the housing after press-fitting is also smaller than the machined product. Therefore, the deformation of the inner peripheral surface of the bearing sleeve due to the press-fitting can be suppressed, and a decrease in accuracy due to the deformation of the radial dynamic pressure generating region facing the radial bearing gap can be avoided. Further, since it is not necessary to attach a flange portion to one end of the shaft member, there is also a merit that the bearing device can be assembled even with another flange-like member such as a rotor attached to the other end of the shaft member.
- the housing can be provided with a large-diameter portion, a small-diameter portion, and a step portion connecting the large-diameter portion and the small-diameter portion, and the engaging portion can be constituted by the step portion.
- the bottom portion can be provided integrally or separately in the housing, and a separate thrust receiver can be disposed on the bottom portion.
- a rotation stopper for the thrust receiver it is preferable to provide a rotation stopper for the thrust receiver at the bottom of the housing.
- the bottom portion can be provided integrally or separately in the housing, and the thrust receiver can be integrated with the bottom portion.
- the press-fitting portion between the outer periphery of the bearing sleeve and the inner periphery of the housing can be intermittently provided in the circumferential direction.
- at least a portion of the housing inner peripheral surface facing the outer peripheral surface of the bearing sleeve is formed in a polygonal cross section, or at least a portion of the housing inner peripheral surface facing at least the outer peripheral surface of the bearing sleeve in the circumferential direction.
- protrusions In the former configuration, at least a portion of the housing that faces the outer peripheral surface of the bearing sleeve may be formed with a uniform thickness. You may form the outer peripheral surface of a housing in cross-sectional perfect circle shape.
- the present invention provides a new design concept that is different from the conventional design concept and that simplifies the configuration and assembly process of the bearing device.
- the configuration of the bearing device and the assembly process can be greatly simplified.
- FIG. 3 is a transverse sectional view of the fluid dynamic pressure bearing device shown in FIG. 2 and a partially enlarged view thereof. It is a figure which shows embodiment which provided the rotation stopper in the thrust receiver, and is a cross-sectional view of a fluid dynamic pressure bearing apparatus.
- FIG. 4B is a cross-sectional view taken along line AA in FIG. 4A, showing an embodiment in which a thrust stopper is provided on the thrust receiver. It is a figure which shows embodiment which provided the rotation stopper in the thrust receiver, and is a cross-sectional view of a fluid dynamic pressure bearing apparatus.
- FIG. 5a It is a figure which shows embodiment which provided the rotation stopper in the thrust receiver, and is the sectional view on the AA line in FIG. 5a. It is a figure which shows the other example of a housing shape, and is a cross-sectional view of the fluid dynamic pressure bearing device and a partially enlarged view thereof. It is a figure which shows other embodiment of the hydrodynamic bearing apparatus, and is sectional drawing which shows embodiment which made the bottom part separate from the housing small diameter part. It is a figure which shows other embodiment of the hydrodynamic bearing apparatus, and is sectional drawing which shows embodiment which sealed the opening of the housing with the seal part. It is a figure which shows other embodiment of the hydrodynamic bearing apparatus, and is sectional drawing which shows embodiment which sealed the opening of the housing with the seal part.
- FIG. 1 shows a main part of a polygon mirror spindle motor equipped in a laser beam printer (LBP) as an example of a spindle motor for information equipment.
- This motor includes a fluid dynamic bearing device 1, a rotor 3 fixed to the upper end of a shaft member 2 of the fluid dynamic bearing device 1, a polygon mirror 4 attached to the rotor 3, and a circuit board 5 as a base.
- the rotor magnet is rotated by an electromagnetic force between a rotor magnet (not shown) attached to the rotor 3 and a stator coil (not shown) attached to the circuit board 5, whereby the rotor 3 and the polygon mirror 4 are axial members. 2 and rotate together.
- an axial magnetic bias between the rotor magnet and the stator coil an axial pressing force acts on the shaft member 2 downward.
- the hydrodynamic bearing device 1 includes a housing 7, a bearing sleeve 8 fixed to the inner periphery of the housing 7, a shaft member 2 inserted into the inner periphery of the bearing sleeve 8, and a thrust receiver 9 disposed inside the housing. Prepare.
- the housing 7 is formed by pressing a steel plate (for example, a stainless steel plate such as SUS305), for example, deep drawing.
- the illustrated housing 7 is formed in a bottomed, generally cylindrical shape integrally having an upper large-diameter portion 7a and a lower small-diameter portion 7b, and has a substantially uniform wall thickness as a whole.
- the small-diameter portion 7b integrally has a bottom portion 7c that closes one end of the housing, and the step portion 7d that connects the large-diameter portion 7a and the small-diameter portion 7b has an S-shaped cross section.
- the step portion 7d functions as an engaging portion that engages with an end surface (lower end surface) located on the press-fitting direction side of the bearing sleeve 8 as described later.
- the large-diameter portion 7a of the housing 7 is formed in a polygonal cross-section (regular decagonal shape in the drawing) in which both the inner peripheral surface and the outer peripheral surface have corners at equal intervals in the circumferential direction (multiple shapes in the drawing). Square part).
- the small-diameter portion 7b is formed in a cylindrical shape having a perfectly circular cross section on both the inner and outer peripheral surfaces.
- the polygonal portion of the large-diameter portion 7a only needs to be formed at least in the region a facing the outer peripheral surface of the bearing sleeve 8.
- the large-diameter portion 7a excluding the region a has an inner / outer peripheral surface with a circular cross section. You may form in a cylindrical shape.
- the opening end of the housing 7 (the opening end of the large-diameter portion 7a) is located at a position protruding toward the housing opening side from the end surface of the bearing sleeve 8 on the housing opening side.
- any material can be selected as long as it can be pressed with high accuracy, and a metal plate other than stainless steel, such as brass, can also be used.
- the circuit board 5 is fixed to the outer peripheral surface of the small diameter portion 7b by means such as adhesion.
- the stepped portion 7d may be a flat surface, and the surface of the circuit board 5 may be fixed in contact with the flat stepped portion 7d (not shown).
- the circuit board 5 is annularly brought into line contact with the stepped portion 7d at the curved point on the outer diameter side of the stepped portion 7d, the influence of backlash between both surfaces can be avoided and good between the housing 7 and the circuit board 5 can be obtained. The perpendicularity can be easily obtained.
- the bearing sleeve 8 is a porous body of sintered metal mainly composed of copper or iron, for example, and is formed in a cylindrical shape through the steps of compacting, sintering, and sizing.
- the bearing sleeve 8 after sizing is impregnated with lubricating oil, and the internal holes are filled with lubricating oil.
- the bearing sleeve can be formed of a soft metal material such as brass or another porous body (for example, a porous resin) that is not a sintered metal.
- two radial dynamic pressure generating regions N1 and N2 in which a plurality of dynamic pressure grooves 8a1 as dynamic pressure generating portions are arranged in a herringbone shape are vertically arranged on the inner peripheral surface 8a of the bearing sleeve 8. Formed apart.
- a back portion 8a2 for partitioning the dynamic pressure groove 8a1 in the circumferential direction and an annular smooth portion 8a3 are formed.
- a dynamic pressure groove 8a1 and a back portion 8a2 are symmetrically formed on both sides in the axial direction with the smooth portion 8a3 as a center.
- the back portion 8a2 and the smooth portion 8a3 have the same level of convex shape, and the other region (including the dynamic pressure groove 8a1) of the inner peripheral surface 8a of the bearing sleeve 8 is formed in a concave shape of the same level.
- the lengths of the upper and lower radial dynamic pressure generation regions N1 and N2 are equal.
- the radial dynamic pressure generation regions N1 and N2 are formed by forming a core rod having a forming die corresponding to the shape of the radial dynamic pressure generation regions N1 and N2 on the outer peripheral surface in the sizing process of the bearing sleeve 8 made of sintered metal.
- the bearing sleeve 8 is press-fitted into the die while both end faces are constrained by punches, the inner peripheral surface of the bearing sleeve 8 is pressed against the outer peripheral surface of the core rod, and the shape of the mold is changed to the inner periphery of the bearing sleeve 8. Molded by transferring to the surface.
- the shaft member 2 has a shaft shape having a spherical portion 2a at the tip, and is made of, for example, stainless steel.
- a thrust bearing portion S that functions as a pivot bearing is configured by bringing the spherical surface portion 2a of the shaft member 2 into contact with a thrust receiver 9 disposed on the inner bottom surface of the housing bottom portion 7c.
- the thrust receiver 9 is made of a material having low friction and excellent wear resistance, such as a resin, and is disposed on the inner bottom surface of the housing bottom 7c.
- the thrust receiver 9 may be omitted by forming a coating (for example, a resin coating or a hard coating) having low friction and high wear resistance on a sliding portion with the shaft member 2 in the surface of the housing bottom 7c. .
- the bottom portion 7 c functions as the thrust receiver 9.
- the thrust receiver 9 is disposed on the bottom 7 c of the housing 7.
- the bearing sleeve 8 is press-fitted into the inner periphery of the large-diameter portion 7 a of the housing 7, and the bearing sleeve 8 is moved until the end surface (lower end surface) of the bearing sleeve 8 on the press-fitting direction side comes into contact with the stepped portion 7 d (engagement portion). Push forward.
- the press-fit operation is performed after applying an adhesive to the inner peripheral surface of the housing large-diameter portion 7a or the outer peripheral surface of the bearing sleeve 8 as necessary, the housing 7 and the bearing sleeve 8 are more firmly fixed.
- the shaft member 2 is inserted into the inner periphery of the bearing sleeve 8, and lubricating oil is injected into the annular gap between the inner peripheral surface 8 a of the bearing sleeve 8 and the outer peripheral surface of the shaft member 2.
- the hydrodynamic bearing device 1 shown in FIG. 1 is completed.
- the air pushed into the bottom 7c side of the housing 7 with the insertion of the shaft member 2 mainly passes through the gap P between the inner peripheral surface of the housing large-diameter portion 7a and the outer peripheral surface of the bearing sleeve 8. Released outside.
- the radial dynamic pressure generation regions N1 and N2 on the inner peripheral surface of the bearing sleeve 8 and the outer peripheral surface of the shaft member 2 have a radial bearing gap.
- An oil film whose pressure is increased by the dynamic pressure action of the dynamic pressure groove 8a1 is formed.
- Radial bearing portions R1 and R2 for supporting the shaft member 2 in a non-contact manner in the radial direction are formed at two locations in the axial direction by the oil film. A downward thrust load applied to the shaft member 2 is contact-supported by the thrust bearing portion S.
- the bearing sleeve 8 in the assembly process of the bearing device, the bearing sleeve 8 is press-fitted into the inner periphery of the housing 7, and the bearing sleeve 8 is simply pushed forward until the end surface of the bearing sleeve 8 engages with the stepped portion 7d of the housing 7.
- the relative position in the axial direction between the housing 7 and the bearing sleeve 8 is determined.
- the pivot bearing is adopted as the thrust bearing portion S, it is not necessary to create a gap in the thrust bearing gap, and the shaft member 2 is simply inserted into the inner periphery of the bearing sleeve 8 after the bearing sleeve 8 is press-fitted.
- the basic configuration of the bearing device is completed.
- the press housing 7 has low rigidity, and even if there is a slight misalignment between the housing 7 and the bearing sleeve 8, the press-fitting operation can be performed smoothly. Therefore, the centering of the housing 7 and the bearing sleeve 8 at the time of press-fitting is rough. Is enough. Therefore, according to the present invention, the configuration and assembly process of the hydrodynamic bearing device can be simplified.
- the housing 7 is formed by press working, the processing cost can be significantly reduced compared to the machined product. Therefore, not only the configuration of the hydrodynamic bearing device and the assembly process can be simplified, but also the cost of the entire bearing device can be reduced by reducing the component cost.
- the flange portion at one end of the shaft member 2 which is essential in the bearing device shown in FIG. 13 is not required, and therefore the bearing device is assembled even with the rotor 3 attached to the upper end of the shaft member 2. be able to.
- another flange-like member (hub or the like) must be attached to the upper end of the shaft member.
- the thrust bearing surface of the thrust bearing portion S2 is loaded, and the thrust bearing surface may be deformed.
- the shaft member 2 can be assembled to the bearing device even after the rotor 3 is press-fitted and fixed to the upper end, and this type of problem can be avoided.
- the rigidity of the housing is reduced by making the housing into a press-processed product, the compression force in the inner diameter direction received by the bearing sleeve 8 after press-fitting into the housing 7 is compared with the machined product.
- the large-diameter portion 7a of the housing 7 is formed in a polygonal shape, so that press-fitting portions between the outer periphery of the bearing sleeve 8 and the inner periphery of the housing 8 are provided intermittently in the circumferential direction. Therefore, the compression force in the inner diameter direction that acts on the bearing sleeve 8 after being press-fitted into the inner periphery of the housing 7 can be further reduced, and deformation of the inner peripheral surface of the bearing sleeve 8 can be further prevented. As shown in FIG.
- this effect is achieved by providing protrusions 11 at a plurality of locations in the circumferential direction of the inner peripheral surface of the large-diameter portion 7 a of the housing 7 that faces the outer peripheral surface of the bearing sleeve 8. It can also be obtained by press-fitting the bearing sleeve 8 into the housing large-diameter portion 7a while elastically deforming.
- FIG. 3 illustrates a case where both the inner peripheral surface and the outer peripheral surface of the housing large-diameter portion 7a are polygonal in cross section and the thickness in the circumferential direction is uniform.
- the inner peripheral surface of the housing large-diameter portion 7 a may have a polygonal cross section, while the outer peripheral surface may be formed in a perfect circular shape to form a polygonal portion.
- the entire outer peripheral surface of the housing 7 becomes a perfect circle. Therefore, when the housing 7 is fitted and fixed to the inner periphery of the cylindrical bracket of the motor, the mounting accuracy is improved and the rotation of the motor is increased. Accuracy can be increased.
- the opening side of the housing 7 is not sealed with a sealing member (reference numeral 110 in FIG. 13), and the end surface of the bearing sleeve 8 is exposed to the opening side of the housing 7. Yes.
- the entire internal space of the housing 7 is not filled with the lubricating oil, but only the annular gap between the inner peripheral surface 8a of the bearing sleeve 8 and the outer peripheral surface of the shaft member 2 is filled with the lubricating oil. Therefore, the management process of a sealing member and an oil surface position can be omitted, and further cost reduction can be achieved.
- an oil-repellent coating 12 on the outer peripheral surface of the shaft member 2 outside the bearing sleeve 8 as shown by a broken line in FIG. .
- the axial position of the oil repellent coating 12 is, for example, near the opening end of the housing 7.
- FIGS. 4 and 5 show an example of the rotation stopper.
- a part of the disk-shaped thrust receiver 9 is cut away to form a flat surface 9a, and when the housing 7 is pressed, the thrust receiver is placed on the bottom 7c of the small diameter portion 7b.
- a concave portion 7c1 that conforms to the shape of 9 is provided, and the thrust receiver 9 is accommodated in the concave portion 7c1.
- the flat surface 9a of the thrust receiver 9 and the linear peripheral surface of the recess 7c1 are engaged in the circumferential direction, so that the thrust receiver is prevented from rotating.
- FIG. 4 shows an example in which the flat surface 9a is provided at one location
- FIG. 5 shows an example in which the flat surface 9a is provided at two opposing locations.
- FIG. 1 illustrates the case where the housing bottom portion 7c is integrated with the small diameter portion 7b. However, as shown in FIG. 7, both may be configured separately.
- the bottom portion 7 c functions as the thrust receiver 9.
- the bottom portion 7c is fixed to the housing 7 by caulking the lower end of the small diameter portion 7b, for example.
- the bottom portion 7c itself may be formed of a material (for example, resin) having low friction and high wear resistance, or the bottom portion 7c is made of metal, and the sliding portion with the shaft member 2 on the surface has low friction and wear resistance.
- a rich film for example, a resin film or a hard film may be formed.
- the seal member 10 is formed in an annular shape from, for example, a soft metal material such as brass, another metal material, or a resin material, and the end surface of the seal member 10 is separated from the upper end surface of the bearing sleeve 8. It is fixed to the upper end of 7a.
- the inner peripheral surface of the seal member 10 is close to the outer peripheral surface of the shaft member 2 to form a non-contact seal (labyrinth seal).
- the shape and configuration of the seal member 10 are arbitrary. For example, as shown in FIG.
- a cylindrical leg portion 10a that abuts against the end surface of the bearing sleeve 8, and a protruding portion 10b that protrudes from the upper end of the leg portion 10a toward the inner diameter side. It can also be formed in an L-shaped cross section that is integrally formed.
- the lubricating oil is interposed only in the annular gap between the inner circumferential surface 8a of the bearing sleeve 8 and the outer circumferential surface of the shaft member 2, and in addition to the gap, a thrust bearing portion is provided.
- a so-called fully oil-impregnated configuration in which all the internal space of the housing 7 including the peripheral space of S and the gap P is filled with lubricating oil can also be adopted. In this fully oil-impregnated configuration, the oil level usually exists on the inner peripheral surface of the seal member 10.
- anneal the heat-treated housing 7 as a heat treatment. Specifically, the housing 7 is heated to 1050 ° C., held for a certain time (about 20 minutes), and then slowly cooled. Thereby, since the pressing force in the inner diameter direction from the housing 7 after the press-fitting of the bearing sleeve 8 is reduced, the deformation of the inner peripheral surface of the bearing sleeve 8 can be further suppressed.
- FIG. 10 shows the measurement results of the amount of contraction of the inner peripheral surface of the bearing sleeve 8 depending on whether the housing 7 is annealed or not.
- the size of the bearing sleeve 8 is ⁇ 4 (inner diameter) ⁇ ⁇ 7.5 (outer diameter) ⁇ 7.3 (length), and the housing 7 is made of SUS305 with a wall thickness of 0.2 mm.
- the difference between the circular diameter and the outer diameter of the bearing sleeve 8) was 12 ⁇ m.
- the measurement result of FIG. 10 represents a housing whose inner peripheral surface is a decagon and the housing outer peripheral surface is a perfect circle (FIG. 6).
- the measurement result of FIG. The measurement result of what was done (FIG. 3) is represented.
- “Top” represents the amount of deformation in the upper radial dynamic pressure generation region N1
- “Bottom” represents the amount of deformation in the lower radial dynamic pressure generation region N2.
- the plot point of “no annealing” represents an average value.
- the amount of inner diameter shrinkage in the radial dynamic pressure generation regions N1 and N2 is smaller in “with annealing” than in “without annealing”. Therefore, it can be understood that by performing the annealing process on the housing, the deformation of the radial dynamic pressure generation regions N1 and N2 can be prevented more reliably and higher bearing performance can be obtained.
- the radial dynamic pressure generation regions N1 and N2 can be formed not only on the outer peripheral surface of the bearing sleeve 8, but also on the outer peripheral surface of the shaft member 2. Further, as the shapes of the radial dynamic pressure generation regions N1 and N2, a known shape such as a spiral shape can be used in addition to the herringbone shape. Furthermore, although the case where the shaft member 2 is rotated is illustrated as an embodiment, the configuration of the present invention is similarly applied to the case where the shaft member 2 is a fixed shaft and the housing 7 and the bearing sleeve 8 are the rotation side. be able to.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
Description
・ハウジングの内周に軸受スリーブを圧入し、軸受スリーブの端面がハウジングの係合部と係合するまで軸受スリーブを押し進めるだけで、ハウジングと軸受スリーブの軸方向相対位置が定まる:
・スラスト軸受隙間の隙間出し作業が不要であり、軸受スリーブの圧入後、軸受スリーブの内周に軸部材を挿入するだけで、軸受装置の基本構成が完成する:
・ハウジングと軸受スリーブに多少の芯ずれがあっても圧入作業をスムーズに行えるため、圧入時におけるハウジングと軸受スリーブの芯合わせもラフなもので足りる:
といった作用効果を得ることができ、これにより軸受装置の構成や組立工程の大幅な簡略化を達成することができる。
2 軸部材
3 ロータ
4 ポリゴンミラー
5 回路基板
7 ハウジング
7a 大径部
7b 小径部
7c 底部
7d 段差部
8 軸受スリーブ
8a1 動圧溝(動圧発生部)
9 スラスト受け
10 シール部材
N1 ラジアル動圧発生領域(上側)
N2 ラジアル動圧発生領域(下側)
P 隙間
S スラスト軸受部
Claims (12)
- 軸受スリーブと、
軸受スリーブの内周に挿入された軸部材と、
軸部材の外周面と軸受スリーブの内周面のどちらか一方に形成され、軸部材の外周面と軸受スリーブの内周面との間のラジアル軸受隙間に流体動圧を発生させる動圧発生部と、
プレス加工で形成され、内周に軸受スリーブが圧入され、軸受スリーブの圧入方向前方に、軸受スリーブの端面と係合する係合部が形成されたハウジングと、
軸部材の一端を接触支持するスラスト受けと
を有する流体動圧軸受装置。 - ハウジングに、大径部と、小径部と、大径部と小径部を接続する段差部とを設け、段差部で前記係合部を構成した請求項1記載の流体動圧軸受装置。
- ハウジングに底部を一体又は別体に設け、かつ底部に別体のスラスト受けを配置した請求項1または2記載の流体動圧軸受装置。
- ハウジングの底部に、スラスト受けの回り止めを設けた請求項3記載の流体動圧軸受装置。
- ハウジングに底部を一体又は別体に設け、かつ前記スラスト受けを底部と一体にした請求項1または2記載の流体動圧軸受装置。
- 前記底部の軸部材との接触部分に表面処理を施した請求項5記載の流体動圧軸受装置。
- 軸受スリーブの外周とハウジングの内周との間の圧入部を、円周方向で間欠的に設けた請求項1~6何れか1項に記載の流体動圧軸受装置。
- ハウジング内周面の少なくとも軸受スリーブの外周面と対向する部分を、断面多角形に形成した請求項7記載の流体動圧軸受装置。
- ハウジングの少なくとも軸受スリーブの外周面と対向する部分を均一肉厚に形成した請求項8記載の流体動圧軸受装置。
- ハウジングの外周面を断面真円状に形成した請求項7または8記載の流体動圧軸受装置。
- ハウジング内周面の少なくとも軸受スリーブの外周面と対向する部分の円周方向複数箇所に、突起を設けた請求項7記載の流体動圧軸受装置。
- プレス加工したハウジングに焼なましを施した請求項1~11何れか1項に記載の流体動圧軸受装置。
Priority Applications (3)
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CN201180010531.3A CN102762879B (zh) | 2010-02-26 | 2011-02-24 | 流体动压轴承装置 |
US13/575,495 US8864380B2 (en) | 2010-02-26 | 2011-02-24 | Fluid dynamic bearing device |
EP11747441.1A EP2541084B1 (en) | 2010-02-26 | 2011-02-24 | Fluid dynamic bearing device |
Applications Claiming Priority (4)
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JP2010042194 | 2010-02-26 | ||
JP2010-042194 | 2010-02-26 | ||
JP2011-036958 | 2011-02-23 | ||
JP2011036958A JP5752437B2 (ja) | 2010-02-26 | 2011-02-23 | 流体動圧軸受装置 |
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WO2011105481A1 true WO2011105481A1 (ja) | 2011-09-01 |
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PCT/JP2011/054124 WO2011105481A1 (ja) | 2010-02-26 | 2011-02-24 | 流体動圧軸受装置 |
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US (1) | US8864380B2 (ja) |
EP (1) | EP2541084B1 (ja) |
JP (1) | JP5752437B2 (ja) |
CN (1) | CN102762879B (ja) |
WO (1) | WO2011105481A1 (ja) |
Cited By (1)
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CN104731421B (zh) | 2013-12-24 | 2018-02-13 | 昆山维信诺显示技术有限公司 | 一种电容式触摸屏的fpc及其安装方法 |
WO2016084354A1 (ja) * | 2014-11-27 | 2016-06-02 | パナソニックIpマネジメント株式会社 | 電動機と電動機を備える冷凍機器 |
DE102016123297B4 (de) * | 2016-12-02 | 2019-03-28 | Lohr Technologies Gmbh | Gelenk |
JP7023754B2 (ja) | 2017-12-08 | 2022-02-22 | Ntn株式会社 | 流体動圧軸受装置 |
WO2019112057A1 (ja) * | 2017-12-08 | 2019-06-13 | Ntn株式会社 | 流体動圧軸受装置 |
CN208656558U (zh) * | 2018-10-08 | 2019-03-26 | 广东肇庆爱龙威机电有限公司 | 用于马达的轴承室结构 |
US11959513B2 (en) | 2019-03-26 | 2024-04-16 | Ntn Corporation | Fluid dynamic bearing device |
US11371520B2 (en) * | 2020-07-21 | 2022-06-28 | John Wun-Chang Shih | Fluid dynamic-pressure bearing set for a fan |
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US20120294556A1 (en) | 2012-11-22 |
JP2011196544A (ja) | 2011-10-06 |
JP5752437B2 (ja) | 2015-07-22 |
CN102762879A (zh) | 2012-10-31 |
EP2541084A4 (en) | 2013-12-04 |
EP2541084B1 (en) | 2016-02-24 |
EP2541084A1 (en) | 2013-01-02 |
US8864380B2 (en) | 2014-10-21 |
CN102762879B (zh) | 2016-04-27 |
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