US20090052817A1 - Methods of Hydraulic Compensation for Magnetically Biased Fluid Dynamic Bearing Motor - Google Patents
Methods of Hydraulic Compensation for Magnetically Biased Fluid Dynamic Bearing Motor Download PDFInfo
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- US20090052817A1 US20090052817A1 US12/195,646 US19564608A US2009052817A1 US 20090052817 A1 US20090052817 A1 US 20090052817A1 US 19564608 A US19564608 A US 19564608A US 2009052817 A1 US2009052817 A1 US 2009052817A1
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- Prior art keywords
- shaft
- sleeve
- grooves
- fluid
- pumping
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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
- 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
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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
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
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- 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
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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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- 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
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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
-
- 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
- H02K7/09—Structural association with bearings with magnetic bearings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
Definitions
- the invention generally relates to fluid dynamic bearing motors and, more particularly, to magnetically biased fluid dynamic bearing motors.
- Disk drives are capable of storing large amounts of digital data in a relatively small area.
- Disk drives store information on one or more recording media, which conventionally take the form of circular storage disks (e.g. media) having a plurality of concentric circular recording tracks.
- a typical disk drive has one or more disks for storing information. This information is written to and read from the disks using read/write heads mounted on actuator arms that are moved from track to track across the surfaces of the disks by an actuator mechanism.
- the disks are mounted on a spindle that is turned by a spindle motor to pass the surfaces of the disks under the read/write heads.
- the spindle motor generally includes a shaft mounted on a base plate and a hub, to which the spindle is attached, having a sleeve into which the shaft is inserted.
- Permanent magnets attached to the hub interact with a stator winding on the base plate to rotate the hub relative to the shaft.
- one or more bearings are usually disposed between the hub and the shaft.
- a lubricating fluid such as air or liquid provides a bearing surface between a fixed member of the housing and a rotating member of the disk hub.
- typical lubricants include gas, oil, or other fluids.
- the relatively rotating members may comprise bearing surfaces such as cones or spheres, or may alternately comprise fluid dynamic grooves formed on the members themselves.
- Fluid dynamic bearings spread the bearing surface over a large surface area, as opposed to a ball bearing assembly, which comprises a series of point interfaces. This bearing surface distribution is desirable because the increased bearing surface reduces wobble or run-out between the rotating and fixed members. Further, the use of fluid in the interface area imparts damping effects to the bearing, which helps to reduce non-repeat run-out.
- fluid dynamic bearings are an advantageous bearing system.
- journal and thrust bearings employ a combination of journal and thrust bearings. Frequently, these designs include a shaft journal bearing design having a thrust plate at an end thereof.
- the journal bearings typically include two grooved surfaces facing the journal (either on the shaft or on the sleeve), the thrust plate bearings typically include two grooved surfaces, one facing each of the gaps defined by the thrust plate and sleeve, and by the thrust plate and counter plate.
- Net hydraulic pressure created by the journal bearings establishes a thrust force on the end of the shaft (i.e., toward the thrust plate bearings) that displaces the shaft axially; an opposing force, generated, for example, by a magnetic bias force, is needed to stabilize the motor.
- the viscosity of the fluid in the bearings changes as well.
- the magnetic bias force remains constant regardless of temperature, the hydraulic pressure (thrust force) generated by the journal bearings varies with the changing fluid viscosity.
- the opposing forces may not be of sufficient magnitudes to offset each other, allowing the rotor to move axially as temperature changes.
- a fluid dynamic bearing motor comprising a stationary sleeve, a rotating shaft axially disposed through the sleeve, a journal gap between the shaft and the sleeve, said gap defined by first and second interfacial surfaces of the shaft and sleeve, at least one set of fluid dynamic grooves formed on the first interfacial surface of the journal gap, and at least one step defined on the second interfacial surface of the journal gap.
- FIG. 1 depicts a plan view of one embodiment of a disk drive that comprises a motor in which the invention is used;
- FIG. 2 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a first embodiment of the invention
- FIG. 2B depicts a groove pattern in accordance with the present invention.
- FIG. 3 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a second embodiment of the invention
- FIG. 4 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a third embodiment of the invention.
- FIG. 5 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a fourth embodiment of the invention.
- FIG. 1 depicts a plan view of one embodiment of a disk drive 10 for use with embodiments of the invention.
- the disk drive 10 includes a housing base 12 and a top cover plate 14 .
- the housing base 12 is combined with cover plate 14 to form a sealed environment to protect the internal components from contamination by elements outside the sealed environment.
- the base and cover plate arrangement shown in FIG. 1 is well known in the industry; however, other arrangements of the housing components have frequently been used, and aspects of the invention are not limited by the particular configuration of the disk drive housing.
- Disk drive 10 further includes a disk pack 16 that is mounted on a hub 202 (see FIG. 2 ) for rotation on a spindle motor (not shown) by a disk clamp 18 .
- Disk pack 16 includes one or more of individual disks that are mounted for co-rotation about a central axis. Each disk surface has an associated read/write head 20 that is mounted to the disk drive 10 for communicating with the disk surface.
- read/write heads 20 are supported by flexures 22 that are in turn attached to head mounting arms 24 of an actuator 26 .
- the actuator shown in FIG. 1 is of the type known as a rotary moving coil actuator and includes a voice coil motor (VCM), shown generally at 28 .
- Voice coil motor 28 rotates actuator 26 with its attached read/write heads 20 about a pivot shaft 30 to position read/write heads 20 over a desired data track along a path 32 .
- VCM voice coil motor
- FIG. 2 is a sectional side view of a fluid dynamic bearing motor 200 according to one embodiment of the present invention.
- the motor 200 comprises a rotating assembly 205 , a stationary assembly 203 , and a bearing assembly 207 .
- the rotating assembly 205 comprises a shaft 202 affixed at a first end 221 to a hub 204 that supports at least one disk (not shown) for rotation.
- a second end 223 of the shaft 202 is distal from the first end 221 .
- the hub 204 additionally supports a magnet assembly 252 comprising a back iron 211 with a magnet 209 affixed thereon.
- the magnet assembly 252 is positioned on the inside circumferential surface 254 of the hub 204 .
- the stationary assembly 203 comprises a sleeve 208 mounted on the base 12 .
- the sleeve 208 further comprises a bore 231 through which the shaft 202 is disposed axially.
- a stator 210 mounted on the base 12 cooperates with the magnet 209 in the hub 204 to induce rotation of the shaft 202 and hub 204 relative to the sleeve 208 .
- the stator 210 comprises a plurality of “teeth” 235 formed of a magnetic material such as steel, where each of the teeth 235 is wound with a winding or wire 237 .
- the bearing assembly 207 is formed in a journal (or gap) 217 defined between the facing surfaces of the inner diameter 215 of the sleeve 208 and the outer diameter 219 of the shaft 202 .
- a fluid 214 such as air, oil or gas is disposed between the shaft 202 and the sleeve 208 .
- the journal 217 further comprises fluid dynamic grooves 300 ; an example is formed on one or both of the interfacial surfaces 215 , 219 (in FIG. 2 , the fluid dynamic grooves 300 are formed on the outer surface 219 of the shaft 202 ).
- the fluid dynamic grooves 300 form a circumferential ring around an interfacial journal surface 215 , 219 and may comprise a V-shaped pattern or a chevron, spiral or sinusoidal pattern or other pattern (not shown).
- the pattern generates a pressure distribution across the bearing surface that provides improved bearing rocking stiffness.
- the fluid dynamic grooves 300 may be formed asymmetrically, where the length of one leg of the pattern leading to the pattern's pressure apex is greater than the length of the leg on the other side of the pattern's apex.
- a net flow of fluid 214 is pumped toward the leg with the shorter length.
- a net hydraulic pressure is generated by the journal bearing grooves 300 toward the second end 223 of the shaft 202 .
- Pressure is also generated as a function of the size of the gap between the shaft 202 and sleeve 208 in the areas of the grooves 300 (and depending on the size of the gap, symmetric grooves 300 may also be used, and the same effect achieved). This pressure exerts a positive thrust force on the second end 223 of the shaft 202 that displaces the shaft 202 axially.
- One way to balance the asymmetry pressure acting on the shaft 202 is to offset the magnet 209 and stator 210 relative to each other to create a magnetic bias force that biases the hub 204 downward and stabilizes the motor 200 .
- the center lines of the magnet 209 and stator 210 are separate by a vertical distance of d.
- This method has generally proven to be effective; however, temperature changes in the motor may limit or hinder the ability of the magnetic force to bias the hub 204 . This is because the viscosity of the fluid 214 varies with changes in temperature, which means that the journal asymmetry pressure is not constant, but rather may be a function of temperature. Therefore, because the magnetic force can not be varied accordingly to address and counter the changes in journal asymmetry pressure, temperature variations will cause the shaft 202 and hub 204 to move axially.
- journal asymmetry pressure fluctuations are countered by changing the gap width between the shaft 202 and sleeve 208 in the asymmetric portions of the journal bearings 300 A. This is accomplished by creating a step 260 on the journal surface 215 , 219 that is opposite the asymmetric grooves 300 .
- the step 260 is located on the inner diameter 215 of the sleeve 208 , opposite the journal bearing grooves 300 on the shaft 202 .
- the step 260 is also offset axially from the grooves 300 , so that when the motor 200 is at rest, the gap separating the grooved portion of the shaft 202 from the sleeve 208 is a standard width w 1 .
- the apex 304 of the grooves 300 is generally adjacent a gap of standard width w 1 .
- the grooves 300 move closer axially to the step 260 , and the width of the gap separating the upper portion of the grooved area (i.e., mostly the upper leg of the groove pattern) of the shaft 202 from the sleeve 208 shrinks to a gap w 2 .
- this design provides additional stiffness (pressure change vs. axial movement of shaft) to the motor, reducing or eliminating the need for either a thrust plate with grooves or for a tight thrust gap, which draws constant power.
- Steps 260 may be created either by removing material from the shaft 202 or sleeve 208 (e.g., by processes including, but not limited to, turning, grinding, electrochemical machining, or electrical discharge machining), or by adding material to the surfaces 202 , 208 (e.g., by processes including, but not limited to, plating, coating, or sputtering). For example, Diamond Like Coating (DLC) may be sputtered onto the appropriate area.
- DLC Diamond Like Coating
- FIG. 3 illustrates a second embodiment of the present invention.
- the motor 400 is configured similarly to the motor 200 in FIG. 2 .
- the step 460 is formed on the outer diameter 419 of the shaft 402 , rather than on the inner diameter 415 of the sleeve 408 .
- the step 460 operates in the same manner as the step 260 in FIG. 2 , to narrow the bearing gap and thus counter hydraulic pressure variations.
- FIG. 4 A third embodiment of the invention is illustrated in FIG. 4 .
- the motor 500 is similar to the motors 200 and 400 illustrated in FIGS. 2 and 3 .
- the journal 517 comprises two steps 560 A, 560 B located across the journal from each set of asymmetry grooves 300 .
- the steps 560 A, 560 B are depicted as formed on the outer diameter 519 of the shaft 502 , it will be appreciated that the steps 560 A, 560 B may also be formed on the inner diameter 515 of the sleeve 508 , as the step 260 is located in FIG. 2 .
- FIG. 5 illustrates a fourth embodiment of the invention.
- the motor 600 is similar to the motor 500 in FIG. 4 and uses the same principle of a double step.
- the journal steps 660 A, 660 B are made larger than in the previous embodiments so that they interact with larger areas of the bearing grooves 300 .
- the grooves 300 comprise two legs: L 1 that pumps upward toward the apex, and L 2 that pumps downward toward the apex.
- L 1 that pumps upward toward the apex
- L 2 that pumps downward toward the apex.
- each individual set of bearing grooves 300 is affected to a larger degree over both legs L 1 , L 2 , unlike the previous embodiments that affected the gaps adjacent smaller portions of the bearing grooves, and more particularly narrowed the gaps mostly adjacent the upper legs of the grooves.
- a magnetically biased fluid dynamic bearing motor is provided in which axial movement of the shaft and hub is limited despite temperature-induced pressure fluctuations in the journal.
- the design also provides improved stiffness to the motor, reducing or eliminating the need for thrust plate bearing grooves or tight thrust gaps.
- the motor doesn't need a thrust bearing as the thrust is created by the journal asymmetry. This asymmetry is created by asymmetric bearing grooves in the journal bearing (as described above) and/or by the proper location of the step or steps 260 relative to the groove pattern in the journal bearing.
- Positioning of the step or steps 260 alters the pressure profile in the journal bearing and thus the pressure on the bottom of the shaft to support the shaft for rotation over the base.
- the effect is asymmetry whether or not the groove pattern itself being asymmetric.
- either the end surface of the shaft (e.g. 280 , FIG. 2 ) or the facing surface of the base 12 or counterplate 282 may be grooved to provide a quicker take-off when the motor shaft 202 spins up.
- the groove pattern would typically be designed to pump toward the center of the shaft.
- the thrust stiffness is primarily created by journal bearing asymmetry, established in whole or in part by the step facing the journal groove pattern.
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- Mechanical Engineering (AREA)
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- Fluid Mechanics (AREA)
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- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
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Abstract
Description
- This application is a divisional of U.S. application Ser. No. 10/602,471, filed Jun. 23, 2003, now U.S. Pat. No. 7,422,370, which claims the priority of U.S. Provisional Application No. 60/401,797, filed Aug. 6, 2002 by LeBlanc et al. (entitled “Hydraulic Compensation For Magnetic Bias FDB Motor”), which is herein incorporated by reference.
- The invention generally relates to fluid dynamic bearing motors and, more particularly, to magnetically biased fluid dynamic bearing motors.
- Disk drives are capable of storing large amounts of digital data in a relatively small area. Disk drives store information on one or more recording media, which conventionally take the form of circular storage disks (e.g. media) having a plurality of concentric circular recording tracks. A typical disk drive has one or more disks for storing information. This information is written to and read from the disks using read/write heads mounted on actuator arms that are moved from track to track across the surfaces of the disks by an actuator mechanism.
- Generally, the disks are mounted on a spindle that is turned by a spindle motor to pass the surfaces of the disks under the read/write heads. The spindle motor generally includes a shaft mounted on a base plate and a hub, to which the spindle is attached, having a sleeve into which the shaft is inserted. Permanent magnets attached to the hub interact with a stator winding on the base plate to rotate the hub relative to the shaft. In order to facilitate rotation, one or more bearings are usually disposed between the hub and the shaft.
- Over the years, storage density has tended to increase, and the size of the storage system has tended to decrease. This trend has lead to greater precision and lower tolerance in the manufacturing and operating of magnetic storage disks.
- From the foregoing discussion, it can be seen that the bearing assembly that supports the storage disk is of critical importance. One bearing design is a fluid dynamic bearing. In a fluid dynamic bearing, a lubricating fluid such as air or liquid provides a bearing surface between a fixed member of the housing and a rotating member of the disk hub. In addition to air, typical lubricants include gas, oil, or other fluids. The relatively rotating members may comprise bearing surfaces such as cones or spheres, or may alternately comprise fluid dynamic grooves formed on the members themselves. Fluid dynamic bearings spread the bearing surface over a large surface area, as opposed to a ball bearing assembly, which comprises a series of point interfaces. This bearing surface distribution is desirable because the increased bearing surface reduces wobble or run-out between the rotating and fixed members. Further, the use of fluid in the interface area imparts damping effects to the bearing, which helps to reduce non-repeat run-out. Thus, fluid dynamic bearings are an advantageous bearing system.
- Many current fluid dynamic bearing designs employ a combination of journal and thrust bearings. Frequently, these designs include a shaft journal bearing design having a thrust plate at an end thereof. The journal bearings typically include two grooved surfaces facing the journal (either on the shaft or on the sleeve), the thrust plate bearings typically include two grooved surfaces, one facing each of the gaps defined by the thrust plate and sleeve, and by the thrust plate and counter plate. Net hydraulic pressure created by the journal bearings establishes a thrust force on the end of the shaft (i.e., toward the thrust plate bearings) that displaces the shaft axially; an opposing force, generated, for example, by a magnetic bias force, is needed to stabilize the motor.
- However, as the temperature fluctuates in the motor, the viscosity of the fluid in the bearings changes as well. While the magnetic bias force remains constant regardless of temperature, the hydraulic pressure (thrust force) generated by the journal bearings varies with the changing fluid viscosity. Thus, the opposing forces (thrust force vs. magnetic bias force) may not be of sufficient magnitudes to offset each other, allowing the rotor to move axially as temperature changes.
- Therefore, a need exists for a magnetically biased fluid dynamic bearing design that can compensate for changing temperature and fluid viscosity in the motor.
- A fluid dynamic bearing motor comprising a stationary sleeve, a rotating shaft axially disposed through the sleeve, a journal gap between the shaft and the sleeve, said gap defined by first and second interfacial surfaces of the shaft and sleeve, at least one set of fluid dynamic grooves formed on the first interfacial surface of the journal gap, and at least one step defined on the second interfacial surface of the journal gap.
- So that the manner in which the above recited embodiments of the invention are attained and can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to the embodiments thereof which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.
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FIG. 1 depicts a plan view of one embodiment of a disk drive that comprises a motor in which the invention is used; -
FIG. 2 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a first embodiment of the invention; -
FIG. 2B depicts a groove pattern in accordance with the present invention. -
FIG. 3 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a second embodiment of the invention; -
FIG. 4 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a third embodiment of the invention; and -
FIG. 5 depicts a side sectional view of a magnetically biased fluid dynamic bearing motor according to a fourth embodiment of the invention. - To facilitate understanding, identical reference numerals have been used, where possible, to designate identical elements that are common to the figures.
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FIG. 1 depicts a plan view of one embodiment of adisk drive 10 for use with embodiments of the invention. Referring toFIG. 1 , thedisk drive 10 includes ahousing base 12 and atop cover plate 14. Thehousing base 12 is combined withcover plate 14 to form a sealed environment to protect the internal components from contamination by elements outside the sealed environment. The base and cover plate arrangement shown inFIG. 1 is well known in the industry; however, other arrangements of the housing components have frequently been used, and aspects of the invention are not limited by the particular configuration of the disk drive housing. -
Disk drive 10 further includes adisk pack 16 that is mounted on a hub 202 (seeFIG. 2 ) for rotation on a spindle motor (not shown) by adisk clamp 18.Disk pack 16 includes one or more of individual disks that are mounted for co-rotation about a central axis. Each disk surface has an associated read/writehead 20 that is mounted to thedisk drive 10 for communicating with the disk surface. In the example shown inFIG. 1 , read/writeheads 20 are supported byflexures 22 that are in turn attached tohead mounting arms 24 of anactuator 26. The actuator shown inFIG. 1 is of the type known as a rotary moving coil actuator and includes a voice coil motor (VCM), shown generally at 28.Voice coil motor 28 rotatesactuator 26 with its attached read/writeheads 20 about apivot shaft 30 to position read/writeheads 20 over a desired data track along apath 32. -
FIG. 2 is a sectional side view of a fluid dynamic bearingmotor 200 according to one embodiment of the present invention. Themotor 200 comprises arotating assembly 205, astationary assembly 203, and abearing assembly 207. - The rotating
assembly 205 comprises ashaft 202 affixed at afirst end 221 to ahub 204 that supports at least one disk (not shown) for rotation. Asecond end 223 of theshaft 202 is distal from thefirst end 221. Thehub 204 additionally supports amagnet assembly 252 comprising aback iron 211 with amagnet 209 affixed thereon. In one embodiment of the invention, themagnet assembly 252 is positioned on the insidecircumferential surface 254 of thehub 204. - The
stationary assembly 203 comprises asleeve 208 mounted on thebase 12. Thesleeve 208 further comprises abore 231 through which theshaft 202 is disposed axially. Astator 210 mounted on thebase 12 cooperates with themagnet 209 in thehub 204 to induce rotation of theshaft 202 andhub 204 relative to thesleeve 208. Thestator 210 comprises a plurality of “teeth” 235 formed of a magnetic material such as steel, where each of theteeth 235 is wound with a winding orwire 237. - The bearing
assembly 207 is formed in a journal (or gap) 217 defined between the facing surfaces of theinner diameter 215 of thesleeve 208 and theouter diameter 219 of theshaft 202. A fluid 214 such as air, oil or gas is disposed between theshaft 202 and thesleeve 208. Thejournal 217 further comprises fluiddynamic grooves 300; an example is formed on one or both of theinterfacial surfaces 215, 219 (inFIG. 2 , the fluiddynamic grooves 300 are formed on theouter surface 219 of the shaft 202). - The fluid
dynamic grooves 300 form a circumferential ring around aninterfacial journal surface - The fluid
dynamic grooves 300 may be formed asymmetrically, where the length of one leg of the pattern leading to the pattern's pressure apex is greater than the length of the leg on the other side of the pattern's apex. When asymmetry of the pattern is created by legs with different lengths, a net flow offluid 214 is pumped toward the leg with the shorter length. As thehub 204 andshaft 202 rotate, a net hydraulic pressure is generated by thejournal bearing grooves 300 toward thesecond end 223 of theshaft 202. Pressure is also generated as a function of the size of the gap between theshaft 202 andsleeve 208 in the areas of the grooves 300 (and depending on the size of the gap,symmetric grooves 300 may also be used, and the same effect achieved). This pressure exerts a positive thrust force on thesecond end 223 of theshaft 202 that displaces theshaft 202 axially. - One way to balance the asymmetry pressure acting on the
shaft 202 is to offset themagnet 209 andstator 210 relative to each other to create a magnetic bias force that biases thehub 204 downward and stabilizes themotor 200. As illustrated inFIG. 2 , the center lines of themagnet 209 andstator 210 are separate by a vertical distance of d. This method has generally proven to be effective; however, temperature changes in the motor may limit or hinder the ability of the magnetic force to bias thehub 204. This is because the viscosity of the fluid 214 varies with changes in temperature, which means that the journal asymmetry pressure is not constant, but rather may be a function of temperature. Therefore, because the magnetic force can not be varied accordingly to address and counter the changes in journal asymmetry pressure, temperature variations will cause theshaft 202 andhub 204 to move axially. - One solution to this problem would be to use the axial shaft displacement to change the length of the asymmetry created by the
journal bearings 300. However, the axial displacement required to effectively counter the pressure changes would likely be too great to be practically incorporated. In the embodiment illustrated inFIG. 2 , journal asymmetry pressure fluctuations are countered by changing the gap width between theshaft 202 andsleeve 208 in the asymmetric portions of the journal bearings 300A. This is accomplished by creating astep 260 on thejournal surface asymmetric grooves 300. InFIG. 2 , thestep 260 is located on theinner diameter 215 of thesleeve 208, opposite thejournal bearing grooves 300 on theshaft 202. Thestep 260 is also offset axially from thegrooves 300, so that when themotor 200 is at rest, the gap separating the grooved portion of theshaft 202 from thesleeve 208 is a standard width w1. Although there is a small axial overlap of the step and grooves, theapex 304 of thegrooves 300 is generally adjacent a gap of standard width w1. Thus, as theshaft 202 moves downward, thegrooves 300 move closer axially to thestep 260, and the width of the gap separating the upper portion of the grooved area (i.e., mostly the upper leg of the groove pattern) of theshaft 202 from thesleeve 208 shrinks to a gap w2. As the gap in this region tightens, more pressure is built up at the bottom of theshaft 202, and the pressure pushes the shaft back up. Furthermore, this design provides additional stiffness (pressure change vs. axial movement of shaft) to the motor, reducing or eliminating the need for either a thrust plate with grooves or for a tight thrust gap, which draws constant power. - Typical fluid dynamic bearing motors have journal bearing gaps on the order of five microns or less, and changes to the gap must be controlled to a fraction of that number. Therefore, processes used to create the
steps 260 and must be very precise.Steps 260 may be created either by removing material from theshaft 202 or sleeve 208 (e.g., by processes including, but not limited to, turning, grinding, electrochemical machining, or electrical discharge machining), or by adding material to thesurfaces 202, 208 (e.g., by processes including, but not limited to, plating, coating, or sputtering). For example, Diamond Like Coating (DLC) may be sputtered onto the appropriate area. -
FIG. 3 illustrates a second embodiment of the present invention. Themotor 400 is configured similarly to themotor 200 inFIG. 2 . However, inFIG. 3 , thestep 460 is formed on theouter diameter 419 of theshaft 402, rather than on theinner diameter 415 of thesleeve 408. Thestep 460 operates in the same manner as thestep 260 inFIG. 2 , to narrow the bearing gap and thus counter hydraulic pressure variations. - A third embodiment of the invention is illustrated in
FIG. 4 . Themotor 500 is similar to themotors FIGS. 2 and 3 . However, thejournal 517 comprises twosteps asymmetry grooves 300. Although thesteps outer diameter 519 of theshaft 502, it will be appreciated that thesteps inner diameter 515 of thesleeve 508, as thestep 260 is located inFIG. 2 . -
FIG. 5 illustrates a fourth embodiment of the invention. Themotor 600 is similar to themotor 500 inFIG. 4 and uses the same principle of a double step. However, the journal steps 660A, 660B are made larger than in the previous embodiments so that they interact with larger areas of the bearinggrooves 300. Thegrooves 300 comprise two legs: L1 that pumps upward toward the apex, and L2 that pumps downward toward the apex. When themotor 600 is at rest, a majority of each set ofgrooves 300 is adjacent a gap of standard width w1, while the edges of the grooves are just bordered by a narrower gap w2 created by thesteps shaft 602 moves downward axially, the gap narrows over a larger portion of thegrooves 300, and narrows completely over the upper legs L2, to a width of w2. The narrower gap over the upper legs L2 takes away the downward pumping of these legs, and also diminishes the upward pumping of the lower legs L1. Thus each individual set of bearinggrooves 300 is affected to a larger degree over both legs L1, L2, unlike the previous embodiments that affected the gaps adjacent smaller portions of the bearing grooves, and more particularly narrowed the gaps mostly adjacent the upper legs of the grooves. - Thus the present invention represents a significant advancement in the filed of fluid dynamic bearing motor design. A magnetically biased fluid dynamic bearing motor is provided in which axial movement of the shaft and hub is limited despite temperature-induced pressure fluctuations in the journal. The design also provides improved stiffness to the motor, reducing or eliminating the need for thrust plate bearing grooves or tight thrust gaps. In addition to the thermal compensation effects, the motor doesn't need a thrust bearing as the thrust is created by the journal asymmetry. This asymmetry is created by asymmetric bearing grooves in the journal bearing (as described above) and/or by the proper location of the step or
steps 260 relative to the groove pattern in the journal bearing. Positioning of the step or steps 260 alters the pressure profile in the journal bearing and thus the pressure on the bottom of the shaft to support the shaft for rotation over the base. In other words, when the reduced gap width provided by thestep 260 is over the grooves, the effect is asymmetry whether or not the groove pattern itself being asymmetric. Also, either the end surface of the shaft (e.g. 280,FIG. 2 ) or the facing surface of the base 12 orcounterplate 282 may be grooved to provide a quicker take-off when themotor shaft 202 spins up. The groove pattern would typically be designed to pump toward the center of the shaft. However, even in this instance the thrust stiffness is primarily created by journal bearing asymmetry, established in whole or in part by the step facing the journal groove pattern. - While the foregoing is directed to embodiments of the invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.
Claims (20)
Priority Applications (1)
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US12/195,646 US20090052817A1 (en) | 2002-08-06 | 2008-08-21 | Methods of Hydraulic Compensation for Magnetically Biased Fluid Dynamic Bearing Motor |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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US40179702P | 2002-08-06 | 2002-08-06 | |
US10/602,471 US7422370B2 (en) | 2002-08-06 | 2003-06-23 | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
US12/195,646 US20090052817A1 (en) | 2002-08-06 | 2008-08-21 | Methods of Hydraulic Compensation for Magnetically Biased Fluid Dynamic Bearing Motor |
Related Parent Applications (1)
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US10/602,471 Division US7422370B2 (en) | 2002-08-06 | 2003-06-23 | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
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US20090052817A1 true US20090052817A1 (en) | 2009-02-26 |
Family
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US10/602,471 Expired - Fee Related US7422370B2 (en) | 2002-08-06 | 2003-06-23 | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
US12/195,646 Abandoned US20090052817A1 (en) | 2002-08-06 | 2008-08-21 | Methods of Hydraulic Compensation for Magnetically Biased Fluid Dynamic Bearing Motor |
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US10/602,471 Expired - Fee Related US7422370B2 (en) | 2002-08-06 | 2003-06-23 | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
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Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3934950A (en) * | 1972-10-04 | 1976-01-27 | Skf Industrial Trading And Development Company, B.V. | Bearing for high speed rotary shafts |
US4141603A (en) * | 1976-09-03 | 1979-02-27 | U.S. Philips Corporation | Rotation-insensitive spiral groove bearing |
US4547081A (en) * | 1981-08-26 | 1985-10-15 | Nippon Seiko Kabushiki Kaisha | Dynamic pressure type fluid bearing |
US4795275A (en) * | 1987-08-12 | 1989-01-03 | Digital Equipment Corporation | Hydrodynamic bearing |
US4797009A (en) * | 1986-09-30 | 1989-01-10 | Kabushiki Kaisha Toshiba | Dynamic pressure air bearing |
US4918678A (en) * | 1977-12-12 | 1990-04-17 | Dolby Ray Milton | Disc reproducing system for compensating mechanical imperfections |
US4998033A (en) * | 1989-04-12 | 1991-03-05 | Ebara Corporation | Gas dynamic bearing for spindle motor |
US5046863A (en) * | 1989-11-07 | 1991-09-10 | Nippon Seiko Kabushiki Kaisha | Dynamic pressure bearing device |
US5524985A (en) * | 1995-03-21 | 1996-06-11 | Seagate Technology, Inc. | Fluid thermal compensation and containment for hydrodynamic bearings |
US5715116A (en) * | 1993-03-15 | 1998-02-03 | Matsushita Electric Industrial Co., Ltd. | Spindle motor for driving memory disk |
US5988887A (en) * | 1996-10-29 | 1999-11-23 | Samsung Electronics Co., Ltd. | Journal bearing apparatus |
US6191510B1 (en) * | 1997-12-19 | 2001-02-20 | 3M Innovative Properties Company | Internally damped stator, rotor, and transformer and a method of making |
US20010022869A1 (en) * | 2000-02-24 | 2001-09-20 | Nsk Ltd | Fluid bearing device |
US6398414B1 (en) * | 2000-08-22 | 2002-06-04 | Yen Sun Technology Corp. | Structure of a bearing |
US7422370B2 (en) * | 2002-08-06 | 2008-09-09 | Seagate Technology Llc | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
-
2003
- 2003-06-23 US US10/602,471 patent/US7422370B2/en not_active Expired - Fee Related
-
2008
- 2008-08-21 US US12/195,646 patent/US20090052817A1/en not_active Abandoned
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3934950A (en) * | 1972-10-04 | 1976-01-27 | Skf Industrial Trading And Development Company, B.V. | Bearing for high speed rotary shafts |
US4141603A (en) * | 1976-09-03 | 1979-02-27 | U.S. Philips Corporation | Rotation-insensitive spiral groove bearing |
US4918678A (en) * | 1977-12-12 | 1990-04-17 | Dolby Ray Milton | Disc reproducing system for compensating mechanical imperfections |
US4547081A (en) * | 1981-08-26 | 1985-10-15 | Nippon Seiko Kabushiki Kaisha | Dynamic pressure type fluid bearing |
US4797009A (en) * | 1986-09-30 | 1989-01-10 | Kabushiki Kaisha Toshiba | Dynamic pressure air bearing |
US4795275A (en) * | 1987-08-12 | 1989-01-03 | Digital Equipment Corporation | Hydrodynamic bearing |
US4998033A (en) * | 1989-04-12 | 1991-03-05 | Ebara Corporation | Gas dynamic bearing for spindle motor |
US5046863A (en) * | 1989-11-07 | 1991-09-10 | Nippon Seiko Kabushiki Kaisha | Dynamic pressure bearing device |
US5822846A (en) * | 1993-03-15 | 1998-10-20 | Matsushita Electric Industrial Co., Ltd. | Method of manufacturing a disk drive spindle motor |
US5715116A (en) * | 1993-03-15 | 1998-02-03 | Matsushita Electric Industrial Co., Ltd. | Spindle motor for driving memory disk |
US5524985A (en) * | 1995-03-21 | 1996-06-11 | Seagate Technology, Inc. | Fluid thermal compensation and containment for hydrodynamic bearings |
US5988887A (en) * | 1996-10-29 | 1999-11-23 | Samsung Electronics Co., Ltd. | Journal bearing apparatus |
US6191510B1 (en) * | 1997-12-19 | 2001-02-20 | 3M Innovative Properties Company | Internally damped stator, rotor, and transformer and a method of making |
US20010022869A1 (en) * | 2000-02-24 | 2001-09-20 | Nsk Ltd | Fluid bearing device |
US6398414B1 (en) * | 2000-08-22 | 2002-06-04 | Yen Sun Technology Corp. | Structure of a bearing |
US7422370B2 (en) * | 2002-08-06 | 2008-09-09 | Seagate Technology Llc | Hydraulic compensation for magnetically biased fluid dynamic bearing motor |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009022305B3 (en) * | 2009-05-22 | 2010-11-25 | Minebea Co., Ltd. | Spindle motor for use in hard disk drive for driving storage disk, has rotor magnet comprising magnetic material whose magnetic density has negative temperature coefficient so that magnetic force reduces with increasing temperature |
WO2012154410A3 (en) * | 2011-05-11 | 2013-01-24 | Seagate Technology Llc | Adjustable gap for a fluid dynamic bearing |
GB2508519A (en) * | 2011-05-11 | 2014-06-04 | Seagate Technology Llc | Adjustable gap for a fluid dynamic bearing |
US9470261B2 (en) | 2011-05-11 | 2016-10-18 | Seagate Techonology Llc | Adjustable gap for a fluid dynamic bearing |
CN107255117A (en) * | 2017-05-27 | 2017-10-17 | 西安交通大学 | A kind of gap adjustable sliding bearing based on hydraulic pressure |
Also Published As
Publication number | Publication date |
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US7422370B2 (en) | 2008-09-09 |
US20040027018A1 (en) | 2004-02-12 |
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