U.S. patent application number 12/510263 was filed with the patent office on 2011-02-03 for fluid dynamic bearing motor for use with a range of rotational speed rated disc drive memory device products.
Invention is credited to Anthony J. Aiello, Gregor Paco Flores, WelRhem S. Hoon, ChunHong D. Jing, PohLye Lim, Chris M. Woldemar, PowMing Yap.
Application Number | 20110025151 12/510263 |
Document ID | / |
Family ID | 42734634 |
Filed Date | 2011-02-03 |
United States Patent
Application |
20110025151 |
Kind Code |
A1 |
Lim; PohLye ; et
al. |
February 3, 2011 |
Fluid Dynamic Bearing Motor For Use With A Range Of Rotational
Speed Rated Disc Drive Memory Device Products
Abstract
A fluid dynamic bearing motor and method are provided for use
with various disc drive memory device products differently rated by
operational rotational speed. The operational speeds are those
speeds measured during reading and writing memory operations to the
memory device. In an aspect, the present invention meets full
operating requirements, including stiffness and power requirements,
at multiple rated speeds for use with either standard or high-end
performance disc drive products. Costs associated with a dedicated
manufacturing line for high-end products are substantially reduced.
A single manufacturing line can serve both standard and high-end
disc drive memory device products. The present invention is
especially useful in reducing costs of 2.5 inch notebook products
that are typically marketed in two levels of performance, namely,
5400 RPM standard performance products and 7200 RPM high
performance products.
Inventors: |
Lim; PohLye; (Scotts Valley,
CA) ; Yap; PowMing; (Scotts Valley, CA) ;
Jing; ChunHong D.; (Scotts Valley, CA) ; Hoon;
WelRhem S.; (Scotts Valley, CA) ; Woldemar; Chris
M.; (Santa Cruz, CA) ; Flores; Gregor Paco;
(Felton, CA) ; Aiello; Anthony J.; (Santa Cruz,
CA) |
Correspondence
Address: |
SEAGATE TECHNOLOGY LLC;C/O Murabito Hao & Barnes LLP
Two North Market Street, Third Floor
San Jose
CA
95113
US
|
Family ID: |
42734634 |
Appl. No.: |
12/510263 |
Filed: |
July 28, 2009 |
Current U.S.
Class: |
310/90 |
Current CPC
Class: |
H02K 1/187 20130101;
G11B 19/2036 20130101; H02K 7/085 20130101; G11B 5/6005
20130101 |
Class at
Publication: |
310/90 |
International
Class: |
H02K 5/167 20060101
H02K005/167 |
Claims
1. A fluid dynamic bearing motor, for incorporation into a range of
rotational speed rated hard disc drive memory device products,
comprising: a.) a stationary component and a rotatable component,
wherein the stationary component and the rotatable component have
facing surfaces positioned for relative rotation; and b.) a bearing
system: i. defined between the stationary component and the
rotatable component; ii. configured to reduce bearing stiffness
sensitivity and power sensitivity to temperature change; iii.
configured to keep run current below a first predetermined limit
when the rotatable component rotates at a first rotational speed;
and iv. configured to keep run current below a second predetermined
limit without exceeding a voltage supply to the motor when the
rotatable component rotates at a second rotational speed, when: 1.
the first rotational speed is less than the second rotational
speed; and 2. the first rotational speed and the second rotational
speed are rotational speeds during at least one of a reading
operation and a writing operation to the hard disc drive memory
device.
2. The fluid dynamic bearing motor as in claim 1, further
comprising a fluid contained within the bearing system having a
viscosity ratio of less than 3.0, the viscosity ratio calculated by
the fluid viscosity at 0 degrees Celsius (.degree. C.) divided by
the fluid viscosity at 25.degree. C.
3. The fluid dynamic bearing motor as in claim 1, further
comprising a fluid contained within the bearing system having a
viscosity ranging from 70 centipoise (cP) to 4 cP when the bearing
system fluid temperature ranges from -10 degrees Celsius (.degree.
C.) to 70.degree. C.
4. The fluid dynamic bearing motor as in claim 1, further
comprising a fluid contained within the bearing system having a
viscosity index of less than 160.
5. The fluid dynamic bearing motor as in claim 1, wherein the run
current first predetermined specification limit and the run current
second predetermined specification limit are determined when the
bearing system fluid temperature is about -10 degrees Celsius
(.degree. C.) to about 70.degree. C.
6. The fluid dynamic bearing motor as in claim 1, wherein the run
current first predetermined specification limit and the run current
second predetermined specification limit are determined when the
bearing system fluid temperature is one of: about -20.degree. C. to
about 10.degree. C., and about 20.degree. C. to about 40.degree.
C.
7. The fluid dynamic bearing motor as in claim 1, wherein the
stationary component material has a different coefficient of
thermal expansion as compared to the rotational component material,
configured to increase the bearing gap situated therebetween as the
bearing system temperature decreases.
8. The fluid dynamic bearing motor as in claim 7, wherein one of
the facing surfaces comprises one of aluminum, brass, bronze,
plastic, copper-based sintered metals, and polyimide with graphite
filler, and the second facing surface comprises one of stainless
steel, 400 series stainless steel, iron-based sintered metals,
ceramic, carbide, and nitride.
9. The fluid dynamic bearing motor as in claim 1, wherein the
stationary component is structured the same for the first
rotational speed and the second rotational speed, the rotatable
component is structured the same for the first rotational speed and
the second rotational speed, and the bearing system is structured
the same for the first rotational speed and the second rotational
speed.
10. The fluid dynamic bearing motor as in claim 9, wherein the
fluid dynamic bearing motor has a maximized torque constant that is
equal to or less than a maximum torque constant for a motor that
operates at the second rotational speed.
11. The fluid dynamic bearing motor as in claim 1, further
comprising a first base assembly and a first stator assembly
connected to the stationary component when the motor operates at
the first rotational speed, and a second base assembly and a second
stator assembly connected to the stationary component when the
motor operates at the second rotational speed, wherein the
rotatable component is structured the same for the first rotational
speed and the second rotational speed, wherein the bearing system
is structured the same for the first rotational speed and the
second rotational speed, wherein the first base assembly and the
first stator assembly are structured differently than the second
base assembly and the second stator assembly, and wherein the first
stator assembly winding voltage is greater than the second stator
assembly winding voltage.
12. The fluid dynamic bearing motor as in claim 11, wherein the
fluid dynamic bearing motor has a maximized torque constant that is
equal to or less than a maximum torque constant for a motor that
operates at the first rotational speed.
13. The fluid dynamic bearing motor as in claim 1, wherein the
fluid dynamic bearing is defined between facing surfaces comprising
one of a shaft and a sleeve, a thrustplate and a sleeve, and a
sleeve and a second surface defining a thrust bearing
therebetween.
14. The fluid dynamic bearing motor as in claim 1, wherein the
bearing system contains fluid, the bearing fluid selected from the
group consisting of diesters, polyol esters, polyalphaolefins,
perfluoropolyethers and mineral hydrocarbons.
15. The fluid dynamic bearing motor as in claim 14, wherein the
bearing fluid containing at least one of an anti-oxidant additive
effective to reduce oxidation of the bearing fluid, an anti-wear
additive effective to reduce wear of the facing surfaces, an
anti-corrosion additive effective to reduce corrosion of the facing
surfaces, and a conductivity enhancing additive.
16. The fluid dynamic bearing motor as in claim 1, wherein the
bearing system contains a bearing fluid that is
3-methyl-1,5-pentanediol-di-n-nonanoate.
17. The fluid dynamic bearing motor as in claim 1, wherein the
bearing system contains fluid containing an additive to reduce the
rate of viscosity decrease of the bearing fluid as a function of
increasing temperature.
18. The fluid dynamic bearing motor as in claim 1, wherein the
first rotational speed is 5400 rotations per minute (RPM), and the
second rotational speed is 7200 RPM.
19. The fluid dynamic bearing motor as in claim 1, wherein the
first rotational speed is a speed in the range of 3600 rotations
per minute (RPM) to 15,000 RPM, and the second rotational speed is
a speed in the range of 3600 RPM to 15,000 RPM.
20. A method to enable a fluid dynamic bearing motor to meet
operational requirements for a range of rotational speed rated hard
disc drive memory device products, comprising: i.) minimizing
bearing stiffness sensitivity and bearing power sensitivity to
temperature; ii.) setting bearing dimensions to meet bearing
stiffness required for reading and writing operations to the range
of rotational speed rated hard disc drive memory device products;
iii.) maintaining run current below a first predetermined limit
during motor operation when a rotatable component rotates at a
first rotational speed; and iv.) maintaining run current below a
second predetermined limit without exceeding a voltage supply to
the motor during motor operation when the rotatable component
rotates at a second rotational speed; wherein the bearing is
defined between a stationary component and the rotatable component,
wherein the stationary component and the rotatable component have
facing surfaces positioned for relative rotation, wherein the first
rotational speed is less than the second rotational speed, and
wherein the first rotational speed and the second rotational speed
are rotational speeds during at least one of a reading operation
and a writing operation to the hard disc drive memory device.
21. The method as in claim 20, further comprising maximizing
rotational torque of the motor without exceeding the voltage supply
to the motor.
22. The method as in claim 20, wherein the temperature ranges from
about -10 degrees Celsius (.degree. C.) to about 70.degree. C.
23. The method as in claim 20, wherein minimizing bearing stiffness
sensitivity and bearing power sensitivity to temperature comprises
utilizing a fluid contained within the bearing having a viscosity
ratio of less than 3.0, calculated by the fluid viscosity at 0
degrees Celsius (.degree. C.) divided by the fluid viscosity at
25.degree. C.
24. The method as in claim 20, wherein minimizing bearing stiffness
sensitivity and bearing power sensitivity to temperature comprises
utilizing a material for the stationary component that has a
different coefficient of thermal expansion as compared to the
rotational component material, configured to increase the bearing
gap situated therebetween as the bearing temperature decreases.
25. A fluid dynamic bearing motor, for incorporation into a range
of rotational speed rated hard disc drive memory device products,
comprising: a.) a stationary component and a rotatable component
positioned for relative rotation; and b.) a bearing system: i.
defined between the stationary component and the rotatable
component; ii. configured for generating predetermined drag between
the stationary component and the rotatable component; and iii.
having a drag profile ratio of less than 3.0 at least at both of a
first rotational speed and a second rotational speed of the
rotatable component, when: 1. the bearing system temperature is
between 0 degrees Celsius (.degree. C.) and 25.degree. C.; 2. the
first rotational speed is less than the second rotational speed;
and 3. the first rotational speed and the second rotational speed
are rotational speeds during at least one of a reading operation
and a writing operation to the hard disc drive memory device;
wherein the drag profile ratio is the bearing system drag at
0.degree. C. divided by the bearing system drag at 25.degree.
C.
26. The fluid dynamic bearing motor as in claim 25, further
comprising a fluid contained within the bearing having a viscosity
ratio of less than 3.0, calculated by the fluid viscosity at
0.degree. C. divided by the fluid viscosity at 25.degree. C.
27. The fluid dynamic bearing motor as in claim 25, further
comprising a fluid contained within the bearing that is
3-methyl-1,5-pentanediol-di-n-nonanoate.
28. The fluid dynamic bearing motor as in claim 25, wherein the
stationary component has a different coefficient of thermal
expansion as compared to the rotational component, configured to
increase the bearing gap situated therebetween as the bearing
temperature decreases.
29. The fluid dynamic bearing motor as in claim 25, further
comprising a maximized motor rotational torque that does not exceed
a voltage supply to the motor.
30. The fluid dynamic bearing motor as in claim 25, wherein the
first rotational speed is a speed in the range of 3600 rotations
per minute (RPM) to 15,000 RPM, and the second rotational speed is
a speed in the range of 3600 RPM to 15,000 RPM.
31. The fluid dynamic bearing motor as in claim 25, further
comprising a fluid contained within the bearing having a viscosity
index of less than 160.
32. The fluid dynamic bearing motor as in claim 25, wherein the
stationary component and the rotational component define facing
surfaces, one of the facing surfaces comprising one of aluminum,
brass, bronze, plastic, copper-based sintered metals, and polyimide
with graphite filler, and the second facing surface comprising one
of stainless steel, 400 series stainless steel, iron-based sintered
metals, ceramic, carbide, and nitride.
33. The fluid dynamic bearing motor as in claim 25, wherein the
stationary component is structured the same for the first
rotational speed and the second rotational speed, the rotatable
component is structured the same for the first rotational speed and
the second rotational speed, and the bearing is structured the same
for the first rotational speed and the second rotational speed.
34. The fluid dynamic bearing motor as in claim 33, wherein the
fluid dynamic bearing motor has a maximized torque constant that is
equal to or less than a maximum torque constant for a motor that
operates at the second rotational speed.
35. The fluid dynamic bearing motor as in claim 25, further
comprising a first base assembly and a first stator assembly
connected to the stationary component when the motor operates at
the first rotational speed, and a second base assembly and a second
stator assembly connected to the stationary component when the
motor operates at the second rotational speed, wherein the
rotatable component is structured the same for the first rotational
speed and the second rotational speed, wherein the bearing is
structured the same for the first rotational speed and the second
rotational speed, wherein the first base assembly and the first
stator assembly are structured differently than the second base
assembly and the second stator assembly, and wherein the first
stator assembly winding voltage is greater than the second stator
assembly winding voltage.
36. The fluid dynamic bearing motor as in claim 35, wherein the
fluid dynamic bearing motor has a maximized torque constant that is
equal to or less than a maximum torque constant for a motor that
operates at the first rotational speed.
37. The fluid dynamic bearing motor as in claim 25, wherein the
bearing contains fluid containing an additive to reduce the rate of
viscosity decrease of the bearing fluid as a function of increasing
temperature.
38. The fluid dynamic bearing motor as in claim 25, wherein the
stationary component and the rotational component are facing
surfaces, the facing surfaces comprising one of a shaft and a
sleeve, a thrustplate and a sleeve, and a sleeve and a second
surface defining a thrust bearing therebetween.
Description
FIELD
[0001] The invention relates generally to a disc drive memory
device, and more particularly to a method and a fluid dynamic
bearing motor for use with a range of different rotationally rated
disc drive memory device products that operate at different
rotational speeds during memory operations.
BACKGROUND
[0002] Disc drive memory systems are utilized in traditional
stationary computing environments and also mobile environments
including portable notebook computers digital cameras, digital
video cameras, video game consoles and personal music players.
These memory systems store digital information that is recorded on
concentric tracks on a magnetic disc medium. At least one disc is
rotatably mounted on a spindle, and the information, which can be
stored in the form of magnetic transitions within the discs, is
accessed using read/write heads or transducers. A drive controller
is typically used for controlling the disc drive system based on
commands received from a host system. The drive controller controls
the disc drive to store and retrieve information from the magnetic
discs. The read/write heads are located on a pivoting arm that
moves radially over the surface of the disc. The discs are rotated
at high speeds during operation using an electric motor located
inside a hub or below the discs. Magnets on the hub interact with a
stator to cause rotation of the hub relative to the stator.
[0003] Many disc drives utilize a spindle motor having a fluid
dynamic bearing (FDB) situated between a shaft and sleeve to
support the hub and the disc for rotation. The bearings permit
rotational movement between the shaft and the sleeve, while
precisely maintaining alignment of the spindle to the shaft. In a
hydrodynamic bearing, a lubricating fluid is provided between a
fixed member bearing surface and a rotating member bearing surface
of the disc drive. These mobile devices are frequently subjected to
various magnitudes of mechanical shock as a result of handling. As
such, performance and design needs have intensified including
improved resistance to shock events including axial and angular
shock resistance, vibration response, and improved robustness. The
read/write heads must be accurately aligned with the storage tracks
on the disc to ensure the proper reading and writing of
information. The stiffness of the fluid dynamic bearing is critical
so that the rotating load is accurately and stably supported on the
spindle without wobble or tilt. Moreover, a demand exists for
increased storage capacity and smaller disc drives, which has led
to the design of higher recording areal density such that the
read/write heads are placed increasingly closer to the disc
surface. Precise alignment of the heads with the storage tracks is
needed to allow discs to be designed with greater track densities,
thereby allowing smaller discs and/or increasing the storage
capacity of the discs.
[0004] As a result of these intensified performance and design
needs, and a need to meet operating requirements (including motor
stiffness and power), motors for disc drive memory devices (i.e.,
2.5 inch notebook motors) are typically marketed at two levels of
performance, namely standard performance and high performance. The
standard performance products commonly operate at about 5400
rotations per minute (RPM) rotational speed, while the higher
performance products require a higher data access rate, which is
typically achieved using a motor that operates at a rotational
speed of about 7200 RPM. The high performance 7200 RPM products
typically have higher manufacturing costs than the standard
performance 5400 RPM products, and the high performance products
typically sell at a lower volume, which results in a higher
production cost due to manufacturing costs being spread over a
smaller number of drives produced. Further, motors for desktop disc
drive memory devices are also marketed at various levels of
performance, namely low (i.e., 5400 RPM), medium (i.e., 7200 RPM)
and high performance (i.e., 10,000 RPM), similarly resulting in
higher production costs.
[0005] A different aspect of current notebook disc drive technology
is the use of a low power mode to extend battery life in laptop
computers. The low power mode, also known as idle mode, involves
parking the read/write head on a ramp that is off a disc surface,
and spinning the motor down to a lower speed while the drive is not
being accessed. This power-saving "idle speed" is significantly
lower than the "rated speed" (5400 or 7200 RPM) of the motor, but
it is sufficiently high to maintain bearing clearances in the fluid
dynamic bearing of the motor. The motor bearing viscous losses and
the resulting run current are reduced by the square of the speed
difference, while the bearing stiffness is reduced proportionally
to the speed. Motor bearing stiffness requirements during the idle
mode operation are not critical since the heads are parked and no
read or write operations are occurring.
SUMMARY
[0006] An apparatus and method are described herein for providing a
fluid dynamic bearing motor for use with an assortment of disc
drive memory device products that operate at a different rotational
speed during memory operations. The fluid dynamic bearing motor
comprises a stationary component, a rotatable component, and a
bearing system. The stationary component and the rotatable
component have facing surfaces positioned for relative rotation.
The bearing system is defined between the stationary component and
the rotatable component; configured to reduce bearing stiffness
sensitivity and power sensitivity to temperature change; configured
to keep run current below a first predetermined limit when the
rotatable component rotates at a first rotational speed; and
configured to keep run current below a second predetermined limit
without exceeding a voltage supply to the motor when the rotatable
component rotates at a second rotational speed. The first
rotational speed is less than the second rotational speed, and the
first rotational speed and the second rotational speed are
rotational speeds during at least one of a reading operation and a
writing operation to the hard disc drive memory device. These and
various other features and advantages will be apparent from a
reading of the following detailed description.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] The foregoing aspects and many of the attendant advantages
of this invention will become more readily appreciated by reference
to the following detailed description, when taken in conjunction
with the accompanying drawings, wherein:
[0008] FIG. 1 is a top plan view of a disc drive data storage
system in which the present invention is useful, in accordance with
an embodiment of the present invention;
[0009] FIG. 2 is a sectional side view of a contemporary spindle
motor used in a disc drive data storage system, in which an
embodiment of the present invention is useful;
[0010] FIG. 3A is a representative table illustrating differences
in component features and oils for two separate contemporary motor
designs that operate at differently rated rotational speeds;
[0011] FIG. 3B is a representative table illustrating the present
invention component features and oils that are optimized to meet
performance requirements for two separate motors that operate at
differently rated rotational speeds, in accordance with an
embodiment of the present invention;
[0012] FIG. 4 is a representative table illustrating oil viscosity
versus temperature behavior for three contemporary oils used with
typical fluid dynamic bearing motor disc drive memory devices, and
a low-viscosity oil 3-methyl-1,5-pentanediol-di-n-nonanoate as used
in accordance with an embodiment of the present invention; and
[0013] FIG. 5 is representative table illustrating run currents
sampled at 0.degree. C. for contemporary separate motor-base
assembly products rated at 5400 RPM and 7200 RPM rotational speeds,
in comparison to present invention embodiment common rotor products
and common motor products at 5400 RPM and 7200 RPM rotational
speeds.
DETAILED DESCRIPTION
[0014] Exemplary embodiments are described with reference to
specific configurations. Those of ordinary skill in the art will
appreciate that various changes and modifications can be made while
remaining within the scope of the appended claims. Additionally,
well-known elements, devices, components, methods, process steps
and the like may not be set forth in detail in order to avoid
obscuring the invention.
[0015] In order to lower production costs of disc drive motors for
high-end disc drive products that typically sell at lower volumes,
it is desirable to use a single motor design for a range of
different rotationally rated disc drive memory device products that
operate at different rotational speeds (i.e., 5400 RPM and 7200 RPM
speed products). Thus, overall manufacturing volume is increased,
and the added costs associated with a dedicated manufacturing line
for high-end 7200 RPM products can be avoided. However, a motor
designed for 7200 RPM operation conventionally includes a motor
torque constant (Kt) that is lower than a motor torque constant
typically used with a 5400 RPM motor so that the driver electronics
can spin the motor up to the rated speed at low temperatures (i.e.,
0 degrees Celsius) without exceeding the source voltage. By
employing a motor designed for 7200 RPM operation, and instead
spinning it at 5400 RPM, a lower torque constant results in
significantly higher running current, which is detrimental to
battery life in a 5400 RPM notebook motor. Therefore, it is
desirable to have a single motor design for both products (i.e.,
5400 RPM and 7200 RPM products), which meets stiffness, run current
and voltage performance requirements of current state of the art
motors that employ separate designs for two different rated speed
products.
[0016] An apparatus and method are described herein for a fluid
dynamic bearing motor for use with an assortment of differently
rated disc drive memory devices that operate at a different
rotational speed during reading and writing memory operations.
Reading and writing speeds are motor rotational speeds in which the
memory device performs reading and writing operations, as
contrasted to a non-memory operation idle speed in which for
example, the read/write head is off a disc surface. In an
embodiment, the present invention meets full operating
requirements, including stiffness and power requirements, at
multiple rated speeds for use with either standard or high-end
performance disc drives. The present invention substantially
reduces added costs associated with a dedicated manufacturing line
for high-end products, thus allowing a single manufacturing line to
serve both standard and high-end products. The present invention is
especially useful in reducing costs of 2.5 inch notebook products
that are typically marketed at two levels of performance, namely
5400 RPM standard performance products and 7200 RPM high
performance products.
[0017] It will be apparent that features of the discussion and
claims may be utilized with disc drive memory systems, low profile
disc drive memory systems, spindle motors, brushless DC motors,
ball bearing assemblies, various fluid dynamic bearing designs
including hydrodynamic and hydrostatic bearings, and other motors
employing a stationary and a rotatable component, including motors
employing conical bearings. Further, embodiments of the present
invention may be employed with a fixed shaft or a rotating shaft.
Also, as used herein, the terms "axially" or "axial direction"
refers to a direction along a centerline axis length of the shaft
(i.e., along axis 260 of shaft 202 shown in FIG. 2), and "radially"
or "radial direction" refers to a direction perpendicular to the
centerline axis 260, and passing through centerline axis 260. Also,
as used herein, the expressions indicating orientation such as
"upper", "lower", "top", "bottom", "height" and the like, are
applied in a sense related to normal viewing of the figures rather
than in any sense of orientation during particular operation, etc.
These orientation labels are provided simply to facilitate and aid
understanding of the figures as described in this description and
should not be construed as limiting.
[0018] Referring to the drawings wherein identical reference
numerals denote the same elements throughout the various views,
FIG. 1 illustrates a top plan view of a typical disc drive data
storage system 110 in which the present invention is useful.
Features of the discussion and claims are not limited to this
particular design, which is shown only for purposes of the example.
Disc drive 110 includes base plate 112 that is combined with cover
114 (shown with a broken--exposing view) forming a sealed
environment to protect the internal components from contamination
by elements outside the sealed environment. Disc drive 110 further
includes disc pack 116, which is mounted for rotation on a spindle
motor (described in FIG. 2) by disc clamp 118. Disc pack 116
includes a plurality of individual discs, which are mounted for
co-rotation about a central axis. Each disc surface has an
associated head 120 (read head and write head), which is mounted to
disc drive 110 for communicating with the disc surface. In the
example shown in FIG. 1, heads 120 are supported by flexures 122,
which are in turn attached to head mounting arms 124 of actuator
body 126. The actuator shown in FIG. 1 is a rotary moving coil
actuator and includes a voice coil motor, shown generally at 128.
Voice coil motor 128 rotates actuator body 126 with its attached
heads 120 about pivot shaft 130 to position heads 120 over a
desired data track along arc path 132. This allows heads 120 to
read and write magnetically encoded information on the surfaces of
discs 116 at selected locations.
[0019] A flex assembly provides the requisite electrical connection
paths for the actuator assembly while allowing pivotal movement of
the actuator body 126 during operation. The flex assembly (not
shown) terminates at a flex bracket for communication to a printed
circuit board mounted to the bottom side of disc drive 110 to which
head wires are connected; the head wires being routed along the
actuator arms 124 and the flexures 122 to the heads 120. The
printed circuit board typically includes circuitry for controlling
the write currents applied to the heads 120 during a write
operation and a preamplifier for amplifying read signals generated
by the heads 120 during a read operation.
[0020] Referring to FIG. 2, a sectional side view is illustrated of
a contemporary spindle motor for use in a disc drive data storage
system 110. This fluid dynamic bearing motor includes a rotatable
component that is relatively rotatable about a stationary
component, defining a journal bearing 206 therebetween. In this
example, the rotatable components include shaft 202 and hub 210. In
an alternative design, the shaft 202 is a stationary component, and
the sleeve 204 is a rotatable component. Hub 210 includes a disc
flange, which supports disc pack 116 (like that shown in FIG. 1)
for rotation about axis 260 of shaft 202. Shaft 202 and hub 210 are
integral with backiron 215. One or more magnets 216 are attached to
a periphery of backiron 215. The magnets 216 interact with a
lamination stack 214 attached to the base 220 to cause the hub 210
to rotate. Magnet 216 can be formed as a unitary, annular ring or
can be formed of a plurality of individual magnets that are spaced
about the periphery of hub 210. Magnet 216 is magnetized to form
two or more magnetic poles. The stator lamination stack 214
includes teeth about which stator windings 211 are wound. A circuit
board applies and controls a voltage across the stator windings 211
to control rotational speed of the motor. The interaction of magnet
216 with the stator windings 211 creates a back-EMF voltage that
must remain within a source voltage (as described below). The
voltage generated by the motor (back-EMF voltage) plus the voltage
measured across the motor and drive circuit resistors must not
exceed the source voltage (i.e., the battery or power supply to the
motor). The stationary components include sleeve 204 and stator
windings 211, which are affixed to base 220. Bearing 206 is
established between the sleeve 204 and the rotating shaft 202. A
thrust bearing 207 is established between hub 210 and sleeve 204.
Thrust bearing 207 provides an upward force on hub 210 to
counterbalance the downward forces including the weight of hub 210,
axial forces between magnet 216 and attractive plate 230, and axial
forces between stator lamination stack 214 and magnet 216. In the
case of a fluid dynamic bearing spindle motor, a fluid, such as
lubricating oil fills the interfacial regions between shaft 202 and
sleeve 204, and between hub 210 and sleeve 204, as well as between
other stationary and rotatable components. While the present figure
is described herein with a lubricating fluid, those skilled in the
art will appreciate that useable fluids include a liquid, a gas, or
a combination of a liquid and gas.
[0021] FIG. 3A is a representative table illustrating differences
in component features and oils for two separate contemporary motor
design products that operate at differently rated rotational
speeds. In contemporary motor designs it is a typical approach to
maximize commonality between motors used for 7200 RPM products and
those used for 5400 RPM products in order to optimize component and
assembly tooling costs. This results in different fluid dynamic
bearing designs (i.e., bearing size and bearing gap) for the two
products, since bearing stiffness increases with speed, and the
amount of viscous loss in the bearing must be reduced to maintain a
reasonable run current. Additionally, the motor torque constant is
separately optimized for the specific rated speed of each product,
which typically results in a different number of stator winding
turns and a different winding resistance value for the different
speed products.
[0022] As described, the contemporary 5400 RPM motor uses a greater
number of stator winding turns as compared to the contemporary 7200
RPM motor. The 5400 RPM motor uses a predetermined optimized fluid
bearing size, while the 7200 RPM motor uses the same or smaller
bearing size as the 5400 RPM motor. The 5400 RPM motor uses a
predetermined optimized fluid bearing gap, while the 7200 RPM motor
uses a larger bearing gap as compared to the 5400 RPM motor. Both
the 5400 RPM and 7200 RPM motors use either a low viscosity or
medium viscosity oil for the fluid dynamic bearings. These design
differences are used to independently optimize the stiffness
performance and viscous losses for each different speed.
[0023] FIG. 3B is a representative table illustrating the present
invention component features and oils that are optimized to meet
performance requirements for two separate motors that operate at
differently rated rotational speeds, in accordance with an
embodiment of the present invention. In designing a motor for use
in multiple products with different rated speeds, it is ideal to
maximize the commonality, or have complete commonality for all
components, for use with a range of different rotationally rated
disc drive memory device products that operate at different
rotational speeds during memory operations, in order to achieve the
full potential cost benefits as previously described.
[0024] A comparison of FIG. 3A with FIG. 3B illustrates the
differences between the present invention motor components that are
the same for the different speed products, and the contemporary
designs that use different motor components for different speed
products. As illustrated, the contemporary 7200 RPM motor typically
uses less stator winding turns as compared to the contemporary 5400
RPM motor. The present invention 5400 RPM motor uses the same
number of stator winding turns as the present invention 7200 RPM
motor. Additionally, the present invention motor that operates at
either 5400 RPM or 7200 RPM uses a fluid bearing size and a fluid
bearing gap that is optimized to best meet both rotational speed
requirements. Further, the present invention motor that operates at
either 5400 RPM or 7200 RPM uses a low viscosity bearing fluid
allowing tradeoffs between voltage margin at 0.degree. C./7200 RPM
and stiffness at 25.degree. C./5400 RPM to be optimized to best
meet both rotational speed requirements.
[0025] Greater or lesser cost benefits may be realized by varying
degrees of commonality between two different rated speed products.
When the present invention design is used along with other common
disc drive systems, (i.e., heads, head stack assembly, voice-coil
motor, discs, etc.) a firmware code change can be used to instruct
the driver electronics to access a particular motor (i.e. a 5400
RPM standard drive or a 7200 RPM high-end drive), providing a
manufacturing flexibility and cost benefit.
[0026] Turning now to FIG. 4, a table is shown illustrating oil
viscosity versus oil temperature behavior for three oils used with
contemporary fluid dynamic bearing motor disc drive memory devices,
and a low-viscosity oil 3-methyl-1,5-pentanediol-di-n-nonanoate as
used in accordance with an embodiment of the present invention.
[0027] The oils used with contemporary motor designs include a
high-viscosity desktop disc drive oil and two medium-viscosity
notebook disc drive oils. The contemporary desktop oil 1 has a
higher viscosity than the present invention oils and is typically
used in larger 3.5'' desktop disc drives that carry a larger load
and operate with a 12V power supply. The contemporary notebook oils
2 and 3 have a medium level of viscosity and less viscosity change
between cold temperature (i.e. 0.degree. C.) and ambient
temperature (i.e. 25.degree. C.), which makes them more suitable to
notebook disc drive motors that support a lighter load with fewer
and smaller discs, which operate on a 5V battery.
[0028] Oil characteristics including overall viscosity level (high,
medium, low, etc.) and viscosity versus temperature "flatness" are
utilized by the present invention. These characteristics are
typically represented in industry by a parameter known as viscosity
index (VI).
[0029] The viscosity index characterizes the flatness of oil
viscosity versus temperature by a calculation related to the oil
viscosity at two specific temperatures: 40.degree. C. and
100.degree. C. While this may be useful in many industries, in the
case of hard disc drives and the present invention, the
temperatures of interest also ranges from about -10.degree. C. to
70.degree. C. For optimizing the bearing and electromagnetic design
of a disc drive motor, significant design considerations include
the back-EMF voltage generated and run current at about -10.degree.
C. to 0.degree. C., and the run current and bearing stiffness at
about 25.degree. C. to 35.degree. C. For this reason, the viscosity
index of an oil is less useful because it is related to a different
temperature range. The relative flatness of an oil viscosity in a
cold region does not always correlate to its relative flatness in a
hot region. In an embodiment of the present invention, a bearing
fluid is used having a viscosity index of less than 160.
[0030] As illustrated, the present invention motor design for
multiple operating speeds utilizes a bearing oil that has both low
viscosity and a relatively flatter viscosity vs. temperature curve
as compared to the contemporary bearing oils. In an embodiment, the
present invention utilizes 3-methyl-1,5-pentanediol-di-n-nonanoate
base oil, which is sufficiently flat for the present invention
motor to meet performance requirements of contemporary separate
motor designs. As shown in FIG. 4, the bearing fluid has a
viscosity in the range of 60 centipoise (cP) to 4 cP when the fluid
temperature is in the range of -10.degree. C. to 70.degree. C.
Viscosity as described herein is described in terms of absolute
viscosity (cP), in contrast to kinematic viscosity in centistokes
(cSt). In an embodiment, a bearing fluid is utilized with a
viscosity ranging from 70 cP to 4 cP when the bearing fluid
temperature ranges from -10.degree. C. to 70.degree. C.
Alternatively, a bearing fluid may be utilized having a viscosity
ratio of less than 3.0, which is calculated by the fluid viscosity
at 0.degree. C. divided by the fluid viscosity at 25.degree. C. In
an embodiment, the oil 3-methyl-1,5-pentanediol-di-n-nonanoate base
oil is used with a viscosity ratio of 2.79.
[0031] In another embodiment, the present invention utilizes an oil
that is a specific base oil from the polyol ester group of oils, as
described in U.S. Pat. No. 5,907,456, the disclosure of which is
incorporated herein in its entirety by reference, which has a low
viscosity and is sufficiently flat in the 0.degree. C. to
25.degree. C. temperature range for the present invention motor to
meet performance requirements of contemporary separate motor
designs. Specifically, the present invention oil enables the
bearing stiffness and viscous loss trade-offs between 0.degree. C.
and 25.degree. C., and between 5400 RPM and 7200 RPM, to be
optimized such that run current and stiffness requirements of
contemporary separate motors can be met by the present invention
motor design for multiple speed products.
[0032] Other oils of low and relatively flat viscosity are also
used by the present invention motor, including blended oils as
described in U.S. Pat. No. 5,930,075, the disclosure of which is
incorporated herein in its entirety by reference. In an embodiment,
the bearing fluid is selected from the group consisting of
diesters, polyol esters, polyalphaolefins, perfluoropolyethers and
mineral hydrocarbons. Moreover, the
3-methyl-1,5-pentanediol-n-nonanoate base oil as shown can be
formulated with a combination of additives including antioxidant,
anti-wear, and conductivity-enhancing additives. In an embodiment,
the present invention bearing fluid includes an anti-oxidant
additive being effective to reduce oxidation of the lubricating
fluid, an anti-wear additive being effective to reduce wear of the
bearing facing surfaces, an anti-corrosion additive being effective
to reduce corrosion of the facing surfaces, and a conductivity
enhancing additive. In an embodiment, the bearing fluid
anti-oxidant additive is selected from the group consisting of
amines, phenols, and mixtures thereof. Bearing fluids and additives
are further referred to in U.S. Pat. No. 5,907,456, the disclosure
of which is incorporated herein in its entirety by reference.
[0033] In an embodiment, the present invention bearing fluid
further includes at least one additive that reduces the rate of
viscosity decrease of the bearing fluid as a function of increasing
temperature. Bearing fluids additives are further referred to in
U.S. Pat. No. 6,952,324, the disclosure of which is incorporated
herein in its entirety by reference. In an embodiment, the bearing
fluid additive is a polymer selected from the group consisting of
polymethylacrylates, polyisobutene, olefin copolymer and styrene
copolymer. Alternatively, the bearing fluid additive is a short
chain alcohol ester, has a concentration of about 1-50% by volume
of the lubricating fluid, or has a molecular weight within a range
of about 1,000 Daltons to about 1,000,000 Daltons.
[0034] The table illustrated in FIG. 5 represents run currents
sampled at 0.degree. C. for contemporary separate motor-base
assembly (MBA) products rated at 5400 RPM and 7200 RPM (bars 1, 2,
3 for 5400 RPM motor, and bars 1, 2, 3 for 7200 RPM motor), in
comparison to present invention embodiment common rotor products
and common motor products at 5400 RPM and 7200 RPM (bars 4, 5 for
5400 RPM motor, and bars 4, 5 for 7200 RPM motor). By "common
rotor" it is meant herein that one rotor design may be utilized
with a range of different rotationally rated disc drive memory
device products that operate at different rotational speeds during
memory operations. By "common motor" it is meant herein that one
motor design may be utilized with a range of different rotationally
rated disc drive memory device products that operate at different
rotational speeds during memory operations.
[0035] In an embodiment, the present invention provides a single
fluid dynamic motor design that can be incorporated into either a
disc drive memory device product with a rotational speed of, for
example, 5400 RPM, or a disc drive memory device product with a
rotational speed of 7200 RPM. Although the 5400 RPM and 7200 RPM
motors are referred to throughout this description, in an
embodiment, the present invention motor design can also be
effectively incorporated into other rotational speed disc drive
memory device products such as 3600 RPM, 4200 RPM, 5400 RPM, 5800
RPM, 5900 RPM, 7200 RPM, 10,000 RPM and 15,000 RPM, or other
rotational speed disc drive memory device products including speeds
between 3600 RPM and 15,000 RPM. Also, while the present invention
is described with reference to a fluid dynamic bearing motor, other
motors as described above may utilize embodiments of the present
invention. These various rotational speeds are speeds of the disc
drive memory device during reading or writing memory operations.
The present invention substantially reduces added costs associated
with a dedicated manufacturing line for high-end products, thus
allowing a single manufacturing line to serve both standard and
high-end products. The present invention is especially useful in
reducing costs of 2.5 inch notebook products that are typically
marketed in two levels of performance, namely 5400 RPM standard
performance products and 7200 RPM high performance products. In an
embodiment, the present invention meets full operating requirements
of both products, including stiffness and power requirements, at
multiple rated speeds for use with either standard or high-end
performance disc drives.
[0036] As shown in FIG. 5, the present invention provides different
levels of motor commonality for a motor design that can be used
with either a 5400 RPM product or a 7200 RPM product, thus
achieving varying levels of costs and benefits. The common rotor
and common motor are designs of the present invention. The 5400 RPM
motors are numbered as 1-5. The 5400 RPM motors 1-3 represent
products with a separate motor-base assembly (MBA), the base being
the disc drive base upon which the disc drive is mounted.
"Separate" means that the 5400 RPM design is different as compared
with the 7200 RPM design.
[0037] Motor 2 bar graph (5400 RPM) represents a conventional motor
with a gap and winding Kt conventionally used for a 5400 RPM motor.
Likewise, motor 2 bar graph (7200 RPM) represents a conventional
motor with a gap and winding Kt conventionally used for a 7200 RPM
motor. Motor 3 bar graph (5400 RPM) represents a motor with a gap
and winding Kt conventionally used for a 5400 RPM motor, but with a
low-viscosity oil. Likewise, motor 3 bar graph (7200 RPM)
represents a motor with a gap and winding Kt conventionally used
for a 7200 RPM motor, but with a low-viscosity oil.
[0038] Next, the 5400 RPM motor 4 represents a product with a
common Rotor, the rotor being the rotational components, including
the magnet. In the case of a "common Rotor," all rotating and
bearing-related parts of the motor are common (i.e., including a
rotating sleeve and cap mounted to the sleeve enclosing the
bearing), but the base and stator assembly are unique for each
speed product. This allows a single manufacturing line for the
rotor assembly (a complicated portion of a motor-base assembly) to
serve two different product lines, resulting in a cost benefit.
Next, the 5400 RPM motor 5 represents a product with a common Motor
(common motor being the highest level of commonality). In the case
of the "common motor," the stationary component is structured the
same for the 5400 RPM rotational speed and the 7200 RPM rotational
speed, the rotatable component is structured the same for the 5400
RPM rotational speed and the 7200 RPM rotational speed, and the
bearing is structured the same for the 5400 RPM rotational speed
and the 7200 RPM rotational speed.
[0039] Similarly, the 7200 RPM motors are numbered as 1-5. The 7200
RPM motors 1-3 represent products with a separate motor-base
assembly (MBA), the base being the disc drive base upon which the
disc drive is mounted. "Separate" means that the 7200 RPM design is
different as compared with the 5400 RPM design. Next, the 7200 RPM
motor 4 represents a product with a common Rotor, the rotor being
the rotational components, including the magnet. As described
above, in the case of a "common Rotor," all rotating and
bearing-related parts of the motor are common, but the base and
stator assembly are unique for each speed product. This allows a
single manufacturing line for the rotor assembly (a complicated
portion of a motor-base assembly) to serve two different product
lines, resulting in a cost benefit. Next, the 7200 RPM motor 5
represents a product with a common Motor (common motor being the
highest level of commonality). In the case of the "common motor,"
the stationary component is structured the same for the 5400 RPM
rotational speed and the 7200 RPM rotational speed, the rotatable
component is structured the same for the 5400 RPM rotational speed
and the 7200 RPM rotational speed, and the bearing is structured
the same for the 5400 RPM rotational speed and the 7200 RPM
rotational speed.
[0040] The bar graphs of motors 1 and 2 (prior art) illustrate some
advantages of the present invention motors 4 and 5. Motor 2 bar
graphs for the 5400 RPM and 7200 RPM motors (prior art) are motors
used for their separate rotational speed products. The bar graph
for motor 1 (7200 RPM) has the same run current as motor 2 (7200
RPM), since these motors 1 and 2 (7200 RPM) are the same. However,
when motor 2 (7200 RPM) is used as-is for the 5400 RPM motor, motor
bar 1 (5400 RPM) results in a run current that can exceed the run
current specification limit (due to the Kt being optimized for the
7200 RPM). Further, FIG. 5 illustrates the lower run currents for
the present invention motors 4 and 5 as compared to the
conventional motors 1 and 2.
[0041] The present invention fluid dynamic bearing motor design can
serve more than one operational rotational speed while meeting
operational requirements of a conventional separate motor that is
designed for a single operational rotational speed. Optimization of
the fluid dynamic bearing is performed to determine the desired
trade-off between power and stiffness. Design considerations
include minimized run current resulting from minimization of
bearing viscous losses and maximization of the motor torque
constant. In an embodiment, with regard to a fluid dynamic bearing
motor that meets operational requirements for a 5400 RPM motor and
a 7200 RPM motor, the present invention employs the following
design methods. Bearing sensitivity to temperature change is
reduced.
[0042] At ambient temperature (i.e., 25.degree. C.) bearing gap and
bearing size are structured to meet a required operational
stiffness under operating vibration conditions for the 5400 RPM
motor, since stiffness is lower with lower rotational speed. The
bearing stiffness is optimized to minimize the motor response to
vibration of the base, caused by a shock event or other vibration
causing source. The response motion causes the read/write head to
shift, potentially "off track." If the motion is large, the head
will be unable to follow the disc data track and could fail at
reading or writing to the disc. The sensitivity of this "off track"
motion is increased at high frequency since the servo system that
moves the head can more easily respond to low frequency vibrations.
Thus, bearing stiffness can be tuned for a number of different
frequency zones of concern (i.e., around structural resonances). In
an example, bearing stiffness is tuned at bearing oil temperatures
of about 25.degree. C. to about 70.degree. C. The bearing gap is
the radial gap of the journal between the two relatively rotatable
facing surfaces. Bearing gaps typically range from about 1.5 to 6
.mu.m, and also about 2.1 to 3.5 .mu.m. Bearing size is dependent
on the shaft diameter (i.e., 1.8 mm to 5 mm) and the axial height
of the motor. The disc drive height of 5 mm to 25 mm can have a
wide range of bearing lengths depending on a disc pack size.
Notebook motors typically have a shaft diameter of about 2.5 to 3.0
mm and a bearing length of about 1.5 to 3 mm (sum of upper and
lower journals). A thrust bearing size can also affect
stiffness.
[0043] Bearing stiffness typically decreases as temperature
increases, while bearing stiffness typically increases as
temperature decreases. At lower temperatures, the bearing oil
viscosity is higher and the bearing is stiffer. Therefore, a
bearing fluid is selected that has a flat viscosity versus
temperature behavior ("flat oil"), such as the present invention
oil described in FIG. 4. This results in a smaller increase of
viscous losses between ambient temperatures (about 25.degree. C.)
and cold conditions (typically about 0.degree. C.). In an
embodiment, headroom voltage is calculated at 0.degree. C. At this
temperature, the 3-methyl-1,5-pentanediol-di-n-nonanoate bearing
oil shows lowest viscosity, providing an improved motor design,
considering factors such as Kt, voltage, and run current.
[0044] Alternatively, or in addition to utilizing a "flat oil," the
present invention compensates for bearing temperature change with
thermally compensating materials that face the bearing. The
thermally compensating materials are provided by materials having
different coefficients of thermal expansion. The bearing gap
situated between the materials increases as the bearing temperature
decreases. Example materials of one surface (i.e., shaft) include
aluminum, brass, bronze, plastic, copper-based sintered metals, and
polyimide with graphite filler, and example materials of the facing
surface (i.e., sleeve) include stainless steel, 400 series
stainless steel, iron-based sintered metals, ceramic, carbide, and
nitride.
[0045] The viscous torque losses in relation to temperature are
represented by the bearing system drag profile. The bearing drag
profile can be affected by various means, including those described
herein including a "flat oil" and thermally compensating material
components with different coefficients of thermal expansion. Power
is determined when viscous torque losses are multiplied by speed.
The drag is a rotational torque, and can be a result of factors
including bearing fluid viscosity, the rotational speed of the
drive, bearing diameter, etc. Both torque and power are directly
proportional to fluid viscosity.
[0046] Once the bearing dimensions and viscous losses are
optimized, the stator winding for 7200 RPM operation is designed to
ensure a voltage margin is adequate to allow the motor to rotate at
the higher rated 7200 RPM rotational speed (vs. 5400 RPM). Voltage
margin is also known in industries as "headroom voltage." The
voltage generated by the motor (back-EMF voltage) plus the voltage
measured across the motor and drive circuit resistors must not
exceed the source voltage (i.e., the battery or power supply to the
motor). This can be expressed by the equation Vsource>Vemf+I
multiplied by R. "Vsource" represents the source voltage, "Vemf"
represents the back-EMF voltage, "I" represents the run current
(amps), and "R" represents the motor and drive circuit resistance
(ohms). Run current is current supplied by the driver electronics
to the winding coil, in order to rotate the motor. Run currents are
minimized to reduce power loss, and are typically greater in the
7200 RPM motor as compared with the 5400 RPM motor. In an example,
run current is minimized at bearing oil temperatures of about
-10.degree. C. to about 0.degree. C. and about 25.degree. C. to
about 35.degree. C. Disc drive source voltages are typically 3.3V
for thin disc drives, 5V for notebook drives or 12V for 3.5 inch
disc drives, although any source voltage is possible. In an
example, the back-EMF voltage is adjusted for bearing oil
temperatures of about -10.degree. C. to about 0.degree. C.
[0047] The motor torque constant (Kt) for the 7200 RPM motor ranges
from about 0.45 oz-in/A to 0.75 oz-in/A. The motor torque constant
(Kt) for the 5400 RPM motor ranges higher from about 0.7 oz-in/A to
1.0 oz-in/A. Kt can also be expressed as motor voltage constant
(Ke), depending on units. In an embodiment (i.e., common rotor
design), the Kt is maximized to reduce run current. Kt may be
maximized for other reasons, such as a higher torque produced by
the motor, which results in a faster spin-up of the motor, shorter
time-to-ready, quicker electrical breaking to spin down, or more
current generated on spin-down for use in parking the heads (such
as in the case where the disc drive electrical supply is suddenly
interrupted). There are numerous methods to adjust the Kt,
including varying the magnet material, magnetization strength,
number of stator laminations, stator diameter, and number of stator
winding turns.
[0048] Once the specification requirements are met for the 7200 RPM
motor, the common motor utilizes the above-described methods to
next meet the specification requirements (i.e., run current limit)
for the 5400 RPM motor. In an embodiment, the headroom voltage
margin is minimized at 7200 RPM for cold starting conditions
(typically 0.degree. C.). Therefore the Kt can be maximized, which
lowers the run current at 5400 RPM operation. In the case of the
common rotor, the 5400 RPM fluid dynamic bearing motor has a
maximized torque constant that is equal to or less than a maximum
torque constant for a motor that operates at the 5400 RPM
rotational speed. In the case of the common motor, the 5400 RPM
fluid dynamic bearing motor has a maximized torque constant that is
equal to or less than a maximum torque constant for a motor that
operates at the 7200 RPM rotational speed. With the ability to
increase the motor Kt and the added viscous loss margin related to
desensitizing the bearing to temperature change, the resulting
motor run current is lowered for operational temperatures and a
range disc drive memory device products that operate at different
rotational speeds during memory operations.
[0049] Modifications and variations may be made to the disclosed
embodiments while remaining within the spirit and scope of the
invention. The implementations described above and other
implementations are within the scope of the following claims.
* * * * *