WO2005121575A1 - 流体動圧軸受、モータおよび記録媒体駆動装置 - Google Patents
流体動圧軸受、モータおよび記録媒体駆動装置 Download PDFInfo
- Publication number
- WO2005121575A1 WO2005121575A1 PCT/JP2005/010175 JP2005010175W WO2005121575A1 WO 2005121575 A1 WO2005121575 A1 WO 2005121575A1 JP 2005010175 W JP2005010175 W JP 2005010175W WO 2005121575 A1 WO2005121575 A1 WO 2005121575A1
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- WO
- WIPO (PCT)
- Prior art keywords
- dynamic pressure
- thrust
- fluid
- working fluid
- thrust bearing
- Prior art date
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- 239000012530 fluid Substances 0.000 title claims abstract description 116
- 230000002093 peripheral effect Effects 0.000 claims abstract description 34
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- 238000004891 communication Methods 0.000 description 4
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- 238000005461 lubrication Methods 0.000 description 3
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
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- 230000015572 biosynthetic process Effects 0.000 description 2
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Classifications
-
- G—PHYSICS
- G11—INFORMATION STORAGE
- G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
- G11B19/00—Driving, starting, stopping record carriers not specifically of filamentary or web form, or of supports therefor; Control thereof; Control of operating function ; Driving both disc and head
- G11B19/20—Driving; Starting; Stopping; Control thereof
- G11B19/2009—Turntables, hubs and motors for disk drives; Mounting of motors in the drive
- G11B19/2018—Incorporating means for passive damping of vibration, either in the turntable, motor or mounting
-
- 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
- F16C33/72—Sealings
- F16C33/74—Sealings of sliding-contact bearings
- F16C33/741—Sealings of sliding-contact bearings by means of a fluid
- F16C33/743—Sealings of sliding-contact bearings by means of a fluid retained in the sealing gap
- F16C33/745—Sealings of sliding-contact bearings by means of a fluid retained in the sealing gap by capillary action
-
- 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
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/08—Structural association with bearings
- H02K7/085—Structural association with bearings radially supporting the rotary shaft at only one end of the rotor
-
- 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
- F16C2370/00—Apparatus relating to physics, e.g. instruments
- F16C2370/12—Hard disk drives or the like
Definitions
- Fluid dynamic pressure bearing, motor and recording medium driving device
- the present invention relates to a fluid dynamic pressure bearing, a motor, and a recording medium driving device.
- Fluid dynamic pressure bearings are used as bearings for shafts of devices that require high rotational accuracy.
- a working fluid is filled in a gap between a shaft and a housing, and a dynamic pressure generated by rotation is used.
- This dynamic pressure is used to support the shaft rotatably with respect to the housing while maintaining the shaft and the housing so as not to contact each other.
- the fluid dynamic pressure bearing described above is used as a bearing suitable for a spindle motor that drives a recording medium such as a hard disk, which is increasing in speed and accuracy.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2001-65552 (pages 3, 4 and figure) 1st etc.)
- the thrust bearing in the hydrodynamic bearing device of Patent Document 1 described above is formed with a sleeve having a thrust dynamic pressure bearing portion forming projection (thrust plate) and an outer peripheral portion surrounding the projecting portion.
- the shaft member is formed.
- a thrust bearing using oil dynamic pressure generated by rotation of the shaft member is formed by filling a fluid such as oil on the axially opposed surfaces of the protruding portion of the sleeve and the outer peripheral portion of the shaft member.
- a groove for generating a dynamic pressure is formed in the projecting portion so as to form a dynamic pressure of oil by the rotation of the shaft member.
- the hydrodynamic bearing device has an absorption shaft that absorbs oil that has leaked thrust bearing force. Is provided.
- a stop-state force in which the surface of the projecting portion where the dynamic pressure generating groove is formed and the inner surface of the shaft member approach each other while being pressed is generated by the surrounding oil being drawn in by the dynamic pressure generating groove. Due to the negative pressure, bubbles are generated in an area where the absolute amount of oil is not sufficient. If air bubbles are generated, the lubrication performance by the oil will deteriorate, the rotation will become unstable, and inconveniences such as vibration may occur. In the worst case, the bearing may cause metal contact and weld.
- the present invention has been made to solve the above-described problems, and is intended to reduce the thickness of the fluid dynamic pressure bearing capable of stably rotating a shaft and a mode using the fluid dynamic bearing.
- An object of the present invention is to provide a recording medium driving apparatus.
- the present invention provides the following means.
- a fluid dynamic pressure bearing includes a shaft body having a cylindrical portion formed in a substantially cylindrical shape, a disk portion extending radially outward from the cylindrical portion, and a closed end,
- the thrust bearing part is sandwiched between the disk part and a support body having a cylindrical part that rotatably accommodates the columnar part and a bowl-shaped thrust bearing part extending radially outward from the cylindrical part.
- a dynamic pressure generating groove for drawing the working fluid toward a midway portion in the radial direction is formed,
- the inner peripheral edge side force of the annular region of the thrust surface in which the dynamic pressure generating groove is formed At least one through-hole penetrating in the direction of the central axis of the shaft is formed between the inner side and the inner side.
- the shaft body and the support body are relatively rotated. This makes it possible to generate the bowing action of the working fluid on the thrust surface.
- the working fluid moves from the wide thrust side of the thrust bearing to the narrow gap side on the other thrust face side through the through hole.
- the through-hole force S is opened in the annular region of the thrust surface, the working fluid that has moved through the through-hole is supplied to the dynamic pressure generating groove in the annular region.
- the midway portion is a predetermined position between the inner peripheral edge and the outer peripheral edge of the annular region of the thrust surface, and the dynamic pressure generating groove causes the inner peripheral edge side force to be directed outward in the radial direction. It is desirable to be the bending point of the dynamic pressure generating groove that extends in the direction inclined, then bends and inclines in the opposite direction and extends to the outer periphery.
- the through hole is provided at a position connected to any one of the dynamic pressure generating grooves.
- Bubbles generated in the body can be smoothly discharged to the through hole through the dynamic pressure generating groove.
- substantially the entire through hole is disposed in the annular region where the dynamic pressure generating groove is formed.
- the working fluid can be supplied to the annular region.
- a groove portion having a groove force formed in an annular shape over the entire circumference is provided inward in the radial direction of the annular region, and the through-hole is provided with the moving hole. It is desirable that they are arranged at positions connected to the annular region and the relief portion other than the pressure generating groove and the dynamic pressure generating groove.
- the through hole is disposed at a position where the through hole is connected to the dynamic pressure generating groove, bubbles generated in the working fluid can be smoothly discharged to the through hole through the dynamic pressure generating groove. Since the through hole is disposed at a position connecting to the annular region other than the dynamic pressure generating groove, the working fluid can be supplied to the annular region. The through hole is located at the position where it connects to the relief part
- a plurality of the through holes are formed, and the plurality of through holes are arranged at equal intervals in the circumferential direction of the thrust shaft portion with the center axis as a center. Hope you can.
- the dynamic pressure generating groove makes the pressure of the working fluid at the outer peripheral edge higher than the pressure of the working fluid at the inner peripheral edge of the thrust bearing portion.
- a fluid dynamic pressure bearing includes a shaft body having a cylindrical portion formed in a substantially cylindrical shape, a disk portion extending radially outward from the cylindrical portion, and a closed end. And a support having a cylindrical portion that rotatably accommodates the columnar portion, and a bowl-shaped thrust bearing portion that extends radially outward from the cylindrical portion;
- the thrust bearing portion is sandwiched between the disc portion, a retaining portion engaged with the disc portion, a gap between the shaft body and the support body, and the support body and the retaining portion. And a working fluid filled in a gap between the cylindrical portion and the cylindrical portion sealing surface facing the retaining portion of the cylindrical portion, and at least a retaining portion sealing surface facing the cylindrical portion of the retaining portion Partial force
- the thrust bearing part is also inclined in the direction away from the central axis, and is inclined away from each other in the direction away from the thrust bearing part. It is characterized by being formed.
- the shaft body and the support body are relatively Centrifugal force acts on the working fluid.
- the working fluid moves to the outside of the radial direction and toward the thrust bearing along the sealing surface of the retaining portion by centrifugal force.
- the working fluid can be prevented from leaking from the gap between the support and the retaining portion.
- the leakage of the working fluid can be prevented, it is possible to prevent the working fluid from decreasing in the gap between the shaft body and the support body and the gap between the support body and the retaining portion. As a result, the sliding performance between the shaft body and the support is prevented from lowering the lubrication performance due to the working fluid on the thrust surface. In addition, the relative rotation between the shaft body and the support body can be stabilized, and vibration can be prevented.
- the liquid level of the working fluid tends to move in a direction in which the distance between the cylindrical seal surface and the retaining seal surface decreases due to surface tension.
- the direction in which the interval is narrowed is the thrust bearing portion direction.
- the retaining portion seal surface force
- the thrust shaft It is desirable that it is formed longer than the cylindrical part sealing surface in the direction away from the receiving part.
- the working fluid moves the retaining portion seal surface by gravity. It can be prevented from leaking.
- the working fluid is attracted to the thrust bearing by the force and surface tension that causes leakage through the seal surface of the retaining part due to gravity, and the liquid level of the working fluid stops when the gravity and surface tension are balanced.
- the static position of the liquid surface is a position farther from the thrust bearing than when the shaft body is in the vertical position relationship. For this reason, the working fluid can be received by the stopper sealing surface formed longer than the cylindrical sealing surface, and the working fluid can be prevented from flowing out.
- a groove for preventing the working fluid from flowing out through the retaining portion seal surface is formed in the retaining portion seal surface.
- a step portion for preventing the working fluid from flowing out along the retaining portion seal surface is formed on the retaining portion seal surface. desirable.
- step portion it is possible to prevent the liquid surface of the working fluid from moving in a direction in which the thrust bearing portion is separated from the step portion. Therefore, it is possible to prevent the working fluid from flowing out in the gap between the shaft body and the support and the gap force between the support and the retaining portion at the stepped portion.
- a motor according to a third aspect of the present invention includes the fluid dynamic pressure bearing according to the first aspect of the present invention or the fluid dynamic pressure bearing according to the second aspect of the present invention, and the fluid dynamic pressure bearing described above.
- Drive means for relatively rotating the shaft body and the support body is provided.
- the third aspect of the present invention due to the action of the through-hole formed in the thrust bearing portion, at the time of startup, the gap between the thrust bearing portion and the disc portion or the gap between the thrust bearing portion and the retaining portion.
- the working fluid is supplied through the through hole, and the shaft body can be rotated stably.
- bubbles can be prevented from being generated in the working fluid, leakage of the working fluid due to the bubbles can be prevented. For this reason, it is possible to easily reduce the thickness of the motor without having to dispose the leakage working fluid absorbing member.
- a recording medium driving apparatus includes the motor according to the third aspect of the present invention, and is provided with a fixing portion that fixes the recording medium to the shaft body or the support. It is characterized by this.
- the fourth aspect of the present invention it is possible to stably rotate the disc-shaped recording medium fixed to the fixed portion of the shaft body or the support body without vibrating. For this reason, it is possible to prevent the occurrence of an error during writing or reading of information on the recording medium due to unstable rotation of the recording medium.
- the leakage of the working fluid is prevented, it is possible to easily reduce the thickness of the recording medium driving device that does not require the arrangement of an absorbing member that absorbs the leaked working fluid.
- the present invention it is possible to prevent the generation of an excessively negative pressure region in the formation region of the dynamic pressure generating groove due to the action of the through hole formed in the thrust bearing portion. Therefore, it is possible to prevent the generation of bubbles and the generation of vibrations, and the shaft body can be rotated stably. Furthermore, by preventing the generation of air bubbles, it is possible to prevent the working fluid from being expelled and leaking due to the air bubbles. Therefore leaked It is possible to easily reduce the thickness of a fluid dynamic pressure bearing that does not require an absorbing member that absorbs the working fluid, and a motor and a recording medium driving device using the fluid dynamic bearing.
- FIG. 1 is a cross-sectional view showing an embodiment of a recording medium driving device according to the present invention.
- FIG. 2 is a plan view showing the core plate in FIG.
- FIG. 3 is an enlarged cross-sectional view showing the fluid dynamic pressure bearing in FIG. 1.
- FIG. 4 is an enlarged cross-sectional view showing the first seal in FIG.
- FIG. 5 (a) is a plan view for explaining a thrust dynamic pressure generating groove and a through hole formed on the upper end surface of the thrust bearing portion in FIG.
- FIG. 5 (b) is a plan view for explaining a thrust dynamic pressure generating groove and a through hole formed in the lower end face of the thrust bearing portion in FIG.
- FIG. 6 is a view for explaining the action of the first seal in FIG.
- FIG. 7 is a diagram for explaining the action of the first seal in FIG. 4.
- FIG. 8 is an enlarged cross-sectional view showing another embodiment of the seal of the first seal.
- FIG. 9 (a) is a plan view for explaining another embodiment of the thrust dynamic pressure generating groove and the through hole formed on the upper end surface of the thrust bearing portion.
- FIG. 9 (b) is a plan view for explaining another embodiment of the thrust dynamic pressure generating groove and the through hole formed on the lower end face of the thrust bearing portion.
- FIG. 10 (a) is a plan view for explaining still another embodiment of the thrust dynamic pressure generating groove and the through hole formed on the upper end surface of the thrust bearing portion.
- Fig. 10 (b) shows another embodiment of the thrust dynamic pressure generating groove and through hole formed on the lower end face of the thrust bearing section.
- FIG. 11 is an enlarged cross-sectional view showing another embodiment of a sleeve and a boss portion.
- FIG. 12 is an enlarged cross-sectional view showing another embodiment of a permanent magnet.
- FIG. 1 is a cross-sectional view showing the overall configuration of a recording medium driving apparatus according to an embodiment of the present invention.
- a fluid dynamic pressure bearing 10 is applied to a recording medium driving apparatus 1 as shown in FIG.
- the recording medium driving apparatus 1 includes a stator 11 including electromagnets 13 arranged in an annular shape, and a rotor (shaft body) 16 including permanent magnets 14 disposed opposite to the electromagnets 13 disposed inside the stator 11.
- the motor 17 includes a fluid dynamic pressure bearing 10 that rotatably supports the rotor 16 with respect to the stator 11.
- the electromagnet 13 provided in the stator 11 and the permanent magnet 14 provided in the rotor 16 constitute driving means 15 that rotationally drives the rotor 16 relative to the stator 11.
- the rotor 16 is provided with a fitting portion (fixing portion) 18 for fitting the ring plate-shaped recording medium HD, and a screw hole for a screw 20 for attaching the pressing member 19 for fixing the recording medium HD. 21 is formed.
- the pressing member 19 is made of an annular plate material having a convex cross-sectional shape, and is attached to the rotor 16 with screws 20.
- the recording medium HD is fitted into the fitting portion 18 of the rotor 16 and is pressed against the fitting portion 18 by the pressing member 19, so that the rotor 16 and the recording medium HD are configured integrally.
- the stator 11 includes a boss portion 12 disposed at the center of the electromagnet 13.
- a permanent magnet 14 provided in the rotor 16 is disposed opposite to the electromagnet 13 by fitting a sleeve (support) 22 of the fluid dynamic pressure bearing portion 10 described later to the boss portion 12.
- a shield plate 23 is disposed between the electromagnet 13 and the recording medium HD to block the magnetic field formed by the electromagnet 13 and the permanent magnet 14. By arranging the shield plate 23, the influence of the magnetic field of the electromagnet 13 and the permanent magnet 14 in the region near the recording medium HD is weakened, and an error in reading the recording medium HD force information can be prevented.
- the stator 11 is formed with a stator opening 24 that accommodates a coil 25 of an electromagnet 13 described later. By housing the coil 25 in the stator opening 24 in this manner, the arrangement position of the electromagnet 13 can be made closer to the stator 11 side (lower in the figure), and the recording medium driving device 1 can be made thinner. it can.
- FIG. 2 is a plan view for explaining the core plate 26 of the recording medium driving apparatus 1 of FIG.
- the electromagnet 13 includes a coil 25 that generates an alternating magnetic field when supplied with a three-phase alternating current, and a core plate 26 that also has two metal plate forces around which the coil 25 is wound. It is configured.
- the core plate 26 includes an annular core back 27, a plurality of teeth 28 extending radially inward from the core back 27, and a force. The tip portion of the inner side in the radial direction of the tooth 28 is formed so that the circumferential length is longer than the outer side.
- the coil 25 is wound around the tooth 28.
- the core plate 26 also has a force with the first plate 29 on the recording medium HD side and the second plate 30 on the state 11 side, so that the first plate 29 and the second plate 30 Are superimposed on each other.
- the tip of the tooth 28 of the first plate 29 is bent toward the recording medium HD, and a facing portion 31 that faces the permanent magnet 14 substantially in parallel is formed.
- the core back 27 of the first plate 29 is formed with a locking portion 32 that locks the jumper wire between the coils 25.
- the locking portion 32 is formed by cutting the core back 27 and raising the member of the core knock 27.
- the facing portion 31 by forming the facing portion 31, the area of the facing surface between the electromagnet 13 and the permanent magnet 14 can be increased, and the driving force of the driving means 15 can be improved.
- the core plate 26 is disposed so that the lower end of the second plate 30 is positioned substantially on the same plane as the lower end of the permanent magnet 14, and the upper end force of the opposing portion 31 of the first plate 29 is permanent.
- the magnet 14 is disposed so as to be substantially flush with the upper end of the magnet 14.
- the arrangement position of the core plate 26 can be moved closer to the stator 11 side, and the recording medium driving device 1 can be easily thinned.
- the rotor 16 can be rotated with respect to the stator 11 by applying an alternating magnetic field generated by the electromagnet 13 configured as described above to the permanent magnet 14.
- FIG. 3 is a cross-sectional view showing a configuration of a fluid dynamic pressure bearing in the recording medium driving apparatus of FIG.
- the fluid dynamic pressure bearing 10 includes the rotor 16 described above, a sleeve (support body) 22 that rotatably supports the port 16, and the rotor 16 removed from the sleeve 22. It is roughly composed of a retaining part 33 for preventing slipping!
- the rotor 16 has a substantially cylindrical shaft (cylindrical portion) 34 and a bowl-shaped disc portion 35 that extends radially outward at the outer periphery of the shaft 34 at one end of the shaft 34. It is made. On the surface of the disc portion 35 facing the sleeve 22, a recess 36 for accommodating a thrust bearing portion 39, which will be described later, and a yoke 52 for holding the retaining portion 33 and the permanent magnet 14 are formed. Further, on the upper surface of the disc portion 35 (upward surface in FIG. 3), a fitting portion 18 that fits the recording medium HD is formed.
- radial dynamic pressure generating grooves 37 called herringbone grooves are formed in two rows in the axial direction of the shaft 34.
- These radial dynamic pressure generating grooves 37 include grooves extending in one direction with respect to the generatrix of the cylindrical surface constituting the outer peripheral surface of the shaft 34 from one end side of the shaft 34, and the disk portion 35 side force is also inclined in the opposite direction. It is configured by combining with the extending groove. In other words, the pair of grooves are configured to have a wide force by directing in the rotational direction of the shaft 34.
- the radial dynamic pressure generating groove 37 is a force that does not intersect with each other but a space is formed between the grooves. It will be formed.
- the sleeve 22 includes a cylindrical portion 38 that rotatably supports the shaft 34, a flange-like thrust bearing portion 39 that extends radially outward on the entire outer peripheral surface at one end of the cylindrical portion 38, It is composed of
- a bottom plate 40 that forms the bottom surface of the cylindrical portion 38 is disposed at the lower end of the cylindrical portion 38 (downward in FIG. 3).
- FIG. 4 is an enlarged cross-sectional view for explaining the first seal 42 of the fluid dynamic pressure bearing 10 of FIG.
- a sleeve fitting portion 41 that is fitted to the boss portion 12 of the stator 11 is formed below the cylindrical portion 38, and the thrust bearing portion 39 and the sleeve fitting portion 41 are connected. In between, there is a slot that forms a slippery seal 42 together with a retaining portion seal surface 53 described later.
- a single seal surface (cylindrical seal surface) 43 is formed.
- the sleeve seal surface 43 is formed as an inclined surface inclined inward in the radial direction toward the sleeve fitting portion 41. Further, an oil cut surface 44 formed in a chamfered shape is provided at a step at the boundary between the sleeve seal surface 43 and the sleeve fitting portion 41.
- FIG. 5 (a) is a plan view for explaining a thrust dynamic pressure generating groove formed on the upper end surface of the thrust bearing portion of the fluid dynamic pressure bearing in the present embodiment
- FIG. FIG. 3 is a plan view for explaining a thrust dynamic pressure generating groove formed on the lower end face of the thrust bearing portion in the present embodiment.
- FIGS. 5 (a) and 5 (b) the upper end surface 39a and the lower end surface 39b in the thickness direction of the thrust bearing portion 39 shown in FIG.
- An annular ring-shaped portion 45 formed, and an annular thrust surface 46 disposed adjacent to the radially outer side of the groove portion 45 are provided.
- a large number of thrust dynamic pressure generating grooves (dynamic pressure generating grooves) 47 called herringbone grooves are formed on the thrust surface 46.
- Each of these thrust dynamic pressure generating grooves 47 is directed radially outward from the side of the convex portion 45, and inclines in one direction with respect to the radial direction and extends in an arc shape, and then bends at an intermediate position (midway portion). Then it tilts in the opposite direction and extends to the outer periphery.
- the thrust bearing portion 39 is provided with two through holes 48 that penetrate the thrust bearing portion 39 in the thickness direction.
- These through holes 48 are formed at the same radial position with an angular interval of 180 ° around the central axis of the shaft 34.
- Each through-hole 48 is formed on the thrust surface 46 adjacent to the gap portion 45, and is a tapered chamfered portion that gradually spreads in the opening direction toward the opening in the thrust surface. 49.
- the chamfered portion 49 is formed on the opening end side so as to overlap with the ridge portion 45. As a result, a part of the groove wall of the gap portion 45 is cut away to form a communication recess that connects the through hole 48 and the gap portion 45.
- the retaining portion 33 includes a retaining disc 50 that prevents the rotor 16 from slipping out of the sleeve 22, and a sealed cylinder that, together with the sleeve 22, forms a chiral seal 42. 51, the force is roughly configured.
- the retaining disk 50 is fixed to the yoke 52 of the rotor 16 so that It is formed to hold the thrust bearing 39.
- the retaining disk 50 and the yoke 52 may be fixed by an adhesive G, and it is preferable that the retaining disk 50 and the yoke 52 are fixed by welding and fixed without gaps. By fixing without gaps in this way, oil, which will be described later, does not leak from the gap between the retaining disc 50 and the yoke 52.
- the seal cylinder 51 is disposed on the inner peripheral surface of the retaining disc 50 so as to extend toward the stator 11 side.
- a retaining portion seal surface 53 that forms the first seal 42 together with the sleeve seal surface 43 is formed in the region facing the sleeve seal surface 43 described above.
- the retaining portion seal surface 53 is formed as an inclined surface that inclines radially inwardly in the direction away from the retaining disc 50.
- An annular groove 55 is formed in the cylindrical inner peripheral surface 54 adjacent to the retaining portion sealing surface 53 and the retaining disc 50 in a direction away from the retaining portion sealing surface 53.
- the cylindrical inner peripheral surface 54 may be formed in a cylindrical shape, and an inclined surface force may be formed in the same manner as the retaining portion seal surface 53.
- the capillary seal 42 formed with a gap force between the sleeve seal surface 43 and the retaining portion seal surface 53 is configured so that the gap is widened by directing in a direction away from the retaining disc 50.
- the radially outer space of the seal cylinder 51 may be used as a space for embedding the permanent magnet 14 and the like.
- gaps C1 to C4 are provided between the shaft 34 and the sleeve 22 and between the sleeve 22 and the retaining portion 33, respectively. That is, between the thrust surface 46 of one end surface 45 of the thrust bearing portion 39 in which the thrust dynamic pressure generating groove 47 is formed, and the inner surface of the recess 36 of the rotor 16 facing this, and between the other end surface 45 Clearances CI and C2 are formed between the thrust surface 46 and the surface of the retaining portion opposite to the thrust surface 46, respectively.
- a uniform gap C3 is provided between the outer peripheral surface of the shaft 34 in which the radial dynamic pressure generating groove 37 is formed and the inner peripheral surface of the cylindrical portion 38 with the shaft 34 being disposed in the center of the cylindrical portion 38. Is to be formed. Further, a gap C4 is formed between the end face of the shaft 34 and the bottom plate 40 of the sleeve 22.
- gaps CI, C2, C3 are filled with oil (working fluid) F, and the level of oil F Filled so that it is located at the seal 42 on the carrier. Therefore, the canary seal 42 can hold the oil F so as not to leak to the outside due to its surface tension.
- the oil F is drawn into the gap C1 and the gap C2 from the outer peripheral edge side of the thrust surface 46 and the negative portion 45 side along the thrust dynamic pressure generating groove 47.
- an annular dynamic pressure generation region A in which dynamic pressure is generated is formed over the entire circumference. Due to this dynamic pressure, the thrust bearing portion 39 can be rotated while being held at a substantially central position in the axial direction between the inner surface of the recess 36 and the surface of the retaining portion 33.
- an alternating magnetic field is generated in the coil 25 by supplying a three-phase alternating current to the coil 25 of the stator 11 constituting the motor 17.
- this alternating magnetic field acts on the permanent magnet 14, the rotor 16 is rotated. Since the recording medium HD is fixed to the rotor 16, when the rotor 16 is rotated, the recording medium HD is rotated together with the rotor 16.
- the dynamic pressure generated on the thrust surface 46 of the thrust bearing portion 39 presses the thrust bearing portion 39 in the thickness direction with the same dynamic pressure, so that the thrust bearing portion 39 is in the recess 3 of the rotor 16.
- the space between the inner surface of 6 and the surface of the retaining portion 33 is balanced and held at a substantially central position in the axial direction.
- the rotor 16 since the dynamic pressure is not generated when the motor 17 is stopped, the rotor 16 is lowered in the direction of gravity in the sleeve 22. Therefore, for example, when the recording medium driving device 1 is installed in a vertical relationship as shown in FIG. 1, the rotor 16 is lowered in the axial direction with respect to the sleeve 22, and the upper gap C1 is It becomes smaller than the lower gap C2.
- the motor 17 is started in this state, in each of the gaps CI and C2, the oil F is drawn radially outward from the negative portion 45 side by the thrust dynamic pressure generating groove 47.
- the through hole 48 opened in the thrust surface 46 is provided, so the upper narrow !, the gap C1 has the lower wide, and the gap C2. Oil F is supplied from through the through hole 48.
- the chamfered portion 49 is provided at the opening of the through hole 48 so that the oil supplied from the through hole 48 to the dynamic pressure generating region A spreads to the dynamic pressure generating portion A. Since it is supplied smoothly, it is more effective.
- the body drive device 1 can be easily reduced in thickness.
- the rotor 16 rotates and the bubbles are drawn into the through hole 48. Since the drawn bubbles remain in the through-hole 48, the bubbles stay in the dynamic pressure generation region A, and the above-described various problems can be prevented.
- the through hole 48 is provided at two positions in the axial target position with respect to the central axis, the oil F is distributed and supplied to the dynamic pressure generation region A. Can do. Also, the weight balance and rotation balance of the rotor 16 can be achieved.
- the recording medium driving apparatus 1 including the fluid dynamic pressure bearing 10 and the motor 17 according to the present embodiment configured as described above, the recording medium HD can be stably rotated without vibrating. . Therefore, it is possible to accurately write information to the recording medium HD and read information from the recording medium HD.
- the thrust dynamic pressure generating groove 47 is formed by, for example, positioning the bending point of the thrust dynamic pressure generating groove 47 radially outward, or by setting the height of the thrust dynamic pressure generating groove 47 to the radially inward and outward directions.
- the generated dynamic pressure is higher in the periphery of the outer peripheral edge than in the periphery of the inner peripheral edge of the thrust bearing portion 47. Therefore, the force for supporting the rotor 16 and the sleeve 22 at the outer peripheral edge of the thrust bearing portion 47 is increased.
- NRRO Non—Repeatable Runout
- the oil F in the first seal 42 has a direction in which the liquid surface area decreases due to surface tension, that is, a direction in which the interval between the sleeve seal surface 43 and the retaining portion seal surface 53 decreases. The force pushed into As a result, the seal 42 can keep the oil F from leaking outside.
- the oil F when the rotor 16 rotates, the oil F also rotates due to friction with the retaining portion seal surface 53, and centrifugal force acts on the oil F. Oil F is pressed against the retaining portion seal surface 53 by centrifugal force, and is pushed along the retaining portion seal surface 53 toward the thrust bearing 39. For this reason, the first seal 42 can further improve the retention of the oil F when the rotor 16 rotates. Further, since the occurrence of oil leakage can be prevented, it is not necessary to provide an absorbing member that absorbs the leaked oil, and the recording medium driving device 1 can be easily made thinner.
- the oil F extends to the right in FIG. 6 along the sleeve seal surface 43 due to gravity as shown in FIG. Since the oil F is prevented from moving in the right direction by the groove 55, the oil F can be held so as not to leak to the outside.
- the oil F extends to the left in FIG. 7 along the retaining portion seal surface 53 due to gravity, as shown in FIG. Since the oil F is prevented from moving leftward by the oil cut surface 44, the oil F can be held so as not to leak to the outside.
- the groove 55 may be formed in the retaining portion 33 to prevent the oil F from leaking, or the step portion 61 may be formed as shown in FIG.
- the stepped portion 61 may be formed on the inner circumferential surface 54 of the cylinder, and is formed so as to expand radially outward. Since the movement of the oil F is prevented by the step of the stepped portion 61, the oil F can be held so as not to leak to the outside.
- FIGS. 4 and 5 a configuration is shown in which the chamfered portion 45 and the through-hole 48 are connected by a chamfered portion 44 formed in the opening of the through-hole 48.
- a straight groove-like communication recess 71 for directly connecting the through hole 48 and the negative portion 45 may be provided.
- the depth of the communication recess 71 and the depth of the ring groove 16 are substantially the same. -This is because, when air bubbles escape from the gap 45 to the through-hole 48, they can be smoothly discharged without pulling the step.
- a slope may be provided in which the depth gradually decreases toward the through hole 48 from the ridge portion 45. According to the slope without depending on the step, it is a force that can smoothly discharge the bubbles to the through hole 48.
- the through hole 48 is provided with one of the thrust dynamic pressure generating grooves 47.
- the thrust dynamic pressure generating groove 47 itself may be used as a communication recess for connecting the through hole 48 and the negative portion 45.
- the boss 12a may not be abutted against the end face of the sleeve (support) 22a.
- annular oil cut groove 44a is provided on the side surface of the sleeve 22a in place of the oil cut surface 44 (see FIG. 4) provided by chamfering at the corner of the abutting portion of the sleeve 22. It has been.
- the oil kerf 44a has the same effect as the oil kerf 44 that prevents the oil F from leaking.
- a stepped portion 6 la that avoids interference with the boss portion 12a is provided at the lower end portion (lower end portion in FIG. 11) of the retaining portion seal surface 53a in the retaining portion 33a.
- the stepped portion 61a has the same effect as the stepped portion 61 of preventing the oil F from leaking.
- boss portion 12a is formed as a separate member from the stator 11, and a sleeve 22a is disposed inside the boss portion 12a. Since the relative positional relationship between the boss portion 12a and the sleeve 22a is determined by the jig used when assembling the two, the same relative positional relationship can always be maintained.
- a magnetic material layer 14a may be provided on the opposite surface.
- the direction of the magnetic flux entering and exiting the surface of each magnetic pole of the permanent magnet 14 is restricted by the magnetic material layer 14a, so that the magnetic pole does not reach the stator 11. Therefore, even if the stator 11 is also formed of a magnetic material force such as iron, when the permanent magnet rotates relative to the stator 11 in a state of approaching the stator 11, it becomes a loss of power of the motor 17 There is no iron loss that causes current loss or magnetic hysteresis loss. Further, since the permanent magnet 14 can be disposed close to the surface of the stator 11, the motor 17 can be made thinner.
- a coating for preventing rusting may be provided around the permanent magnet 14.
- the coating include a layer made of electrodeposited epoxy resin and a layer having nickel plating strength.
- the film thickness is generally about 30 m.
- the coating is not limited to the above as long as it has the function of preventing squeezing.
- the coating may be applied to the permanent magnet 14 before the above-described magnetic material layer 14a is provided on the permanent magnet 14.
- the coating may be applied to the permanent magnet 14 and the magnetic material after the magnetic material layer 14a is provided on the permanent magnet 14. It can be applied to layer 14a.
- the force described by applying the fluid dynamic pressure bearing to the inner rotor type motor is not limited to this inner rotor type motor, and other various motors such as an outer rotor type motor. It can be applied to.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Rotational Drive Of Disk (AREA)
- Sealing Of Bearings (AREA)
- Motor Or Generator Frames (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/629,013 US7736061B2 (en) | 2004-06-11 | 2005-06-02 | Fluid dynamic bearing motor, and recording-medium driving apparatus |
JP2006514475A JPWO2005121575A1 (ja) | 2004-06-11 | 2005-06-02 | 流体動圧軸受、モータおよび記録媒体駆動装置 |
US12/926,457 US20110068650A1 (en) | 2004-06-11 | 2010-11-18 | Fluid dynamic bearing motor, and recording-medium driving apparatus |
US13/614,360 US8777488B2 (en) | 2004-06-11 | 2012-09-13 | Fluid dynamic bearing motor, and recording medium driving apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004174712 | 2004-06-11 | ||
JP2004-174712 | 2004-11-06 |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/629,013 A-371-Of-International US7736061B2 (en) | 2004-06-11 | 2005-06-02 | Fluid dynamic bearing motor, and recording-medium driving apparatus |
US12/800,891 Continuation US8292506B2 (en) | 2004-06-11 | 2010-05-25 | Fluid dynamic bearing, motor, and recording-medium driving apparatus |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005121575A1 true WO2005121575A1 (ja) | 2005-12-22 |
Family
ID=35503133
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/010175 WO2005121575A1 (ja) | 2004-06-11 | 2005-06-02 | 流体動圧軸受、モータおよび記録媒体駆動装置 |
Country Status (3)
Country | Link |
---|---|
US (4) | US7736061B2 (ja) |
JP (4) | JPWO2005121575A1 (ja) |
WO (1) | WO2005121575A1 (ja) |
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JP2015039292A (ja) * | 2006-09-07 | 2015-02-26 | サムスン電機ジャパンアドバンスドテクノロジー株式会社 | ディスク駆動装置 |
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KR20140087292A (ko) * | 2012-12-28 | 2014-07-09 | 삼성전기주식회사 | 스핀들 모터 |
US8773816B1 (en) * | 2013-03-13 | 2014-07-08 | Nidec Corporation | Spindle motor with hydrodynamic bearing structure having capillary seal and disk drive apparatus including same |
WO2014136198A1 (ja) * | 2013-03-05 | 2014-09-12 | 有限会社中▲野▼製作所 | 回転駆動装置 |
JP2018061408A (ja) * | 2016-10-07 | 2018-04-12 | 日本電産株式会社 | ファンモータ |
JP6827331B2 (ja) | 2017-01-30 | 2021-02-10 | シナノケンシ株式会社 | アウターロータ型モータ |
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2005
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- 2005-06-02 US US11/629,013 patent/US7736061B2/en not_active Expired - Fee Related
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2010
- 2010-05-25 US US12/800,891 patent/US8292506B2/en not_active Expired - Fee Related
- 2010-10-13 JP JP2010230946A patent/JP2011052828A/ja not_active Withdrawn
- 2010-10-13 JP JP2010230844A patent/JP2011080597A/ja not_active Withdrawn
- 2010-11-18 US US12/926,457 patent/US20110068650A1/en not_active Abandoned
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2012
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Also Published As
Publication number | Publication date |
---|---|
US8292506B2 (en) | 2012-10-23 |
US20130020894A1 (en) | 2013-01-24 |
JP2011080597A (ja) | 2011-04-21 |
JP2011052828A (ja) | 2011-03-17 |
JP2013127316A (ja) | 2013-06-27 |
US20110068650A1 (en) | 2011-03-24 |
US20080089626A1 (en) | 2008-04-17 |
US8777488B2 (en) | 2014-07-15 |
US7736061B2 (en) | 2010-06-15 |
JPWO2005121575A1 (ja) | 2008-04-10 |
US20100239195A1 (en) | 2010-09-23 |
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