BACKGROUND OF THE INVENTION

This invention relates generally to hydrodynamic bearings, and more particularly to hydrodynamic bearings having a conical design and reduced temperature sensitivity. As part ofthe continuing advances in computer technology, greater and greater amounts of data are sought to be stored in higher and higher densities on constantly rotating magnetic discs. Magnetic disc drives typically include one or more spinning magnetic discs supported on a common precision spindle bearing assembly for constant high speed rotation. At least one magnetic read/write head which flies in close proximity to each disc is provided at a selected location relative to each one ofthe discs. The head reads or writes streams of data from or to tracks which are in prescribed locations on the surface ofthe disc. The width ofthe tracks determines the number of tracks that can be defined on a given disc. The greater the number of given tracks, the greater the storage density. A magnetic disc drive assembly whose spindle bearing has low run out can accommodate higher track densities, and this results in in¬ creased storage density per disc.

A magnetic disc drive assembly whose spindle bearing has low run out can accommodate higher track densities, and this results in increased storage density per disc.

Hydrodynamic spindle bearings are known in which the shaft part and the housing part have respective, facing bearing surfaces which support relative rotary motion between the surfaces. By means of these bearing surfaces, one bearing part rides on film of liquid lubricant (e.g. oil) against the other part Such bearings are well

known in the technology and generally are characterized by low run-out, among other advantages. However, such bearings require a continuously circulating lubrication supply. It is this lubrication issue which is of great importance in the design of a successful hydrodynamic bearing, whether it be for use in a disc drive or in any other environment.

With the development ofthe self-contained lubrication type hydrodynamic spindle bearing, the main problem to be solved is preventing lubricant leakage out of the bearing. In any environment, the loss of such lubricant would degrade the performance ofthe bearing, shortening its life and reducing the stiffness or resistance to tilting ofthe bearing. The problems are especially acute in magnetic disc drives incorporating such hydrodynamic bearings, as these losses can degrade bearing performance and cause read/write errors. Further, leakage of lubricant can lead to contamination in the magnetic disc surface, causing malfunction ofthe read/write process or even catastrophic failure ofthe flying head assembly. Such disc drives are subjected to wide variations in operating conditions, especially in operating tempera¬ tures. Without careful design, such changes in temperatures or changes in pressures can result in substantial fluid losses from the bearings.

Despite other efforts to solve this problem such as the capillary trap and restrictive valve combinations shown in U.S. Patent 5,246,294, the need for a hydrodynamic bearing having a reliable level of stiffness over a range of operating environments remains to be satisfied.

SUMMARY OF THE INVENTION

Therefore it is a general object ofthe invention to provide an improved hydrodynamic bearing which is relatively insensitive to temperatures. It is a further objective of this invention to provide a hydrodynamic bearing which maintains its stiffness even across wide ranges of operating temperature environment.

Another objective ofthe invention is to provide hydrodynamic bearing which does not consume undue power even under stringent or difficult to operate conditions.

A further objective ofthe invention is to provide a hydrodynamic bearing which is highly stable and stabilized against tilting or wobble so that it is especially useful in disc drives or the like.

These and other objectives ofthe present invention are achieved in a hydrodynamic bearing of a conical design having a fixed shaft and a conical sleeve whose surface facing the shaft flairs inwardly toward a center region, the flared conical sections facing inwardly tapered regions ofthe shaft. The sleeve and shaft define at the axial center thereof a connection region which is concave in shape and preferably faces a flapped surface ofthe shaft to define a concave connection region. A collapsible tube is provided in the concave region which collapses under increased pressures as the operating environment changes. Collapse ofthe tube causes withdrawal of some ofthe lubricating fluid from between the facing surfaces ofthe conical bearing, reducing the wetted surface region between the bearings. As a result, even with changes in operating temperatures, the stiffness ofthe bearing remains stable while the consumption of power in the bearing does not vary excessively. As a result, a highly efficient bearing which is highly useful in disc drives and other similar operating environments is achieved.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other features and advantages ofthe present invention will be more fully understood by reference to the following detailed description in conjunction with the attached drawings in which like reference numerals refer to like elements and in which :

Figure 1 A is a top plan view of a disc drive with which the present invention is useful; Figure IB is a cut-away side view of a magnetic disc drive assembly with which the present invention is useful; and

Figure 2 is a partial side cross section of an embodiment ofthe present invention.

DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT

An illustrative disc drive assembly 10 is shown in Figure 1 where a shaft 11 is fixedly mounted in a housing 13 for the disc drive assembly. A hub 18 supports at least one and typically a plurality of magnetic discs 14 which are mounted concentrically to the spindle shaft and supported by a rotating spindle housing or sleeve 15. A motor 16, the details of which are not relevant to this invention, is also mounted to the frame 13 to drive the rotating housing 15 and cause the discs 14 to rotate. The means for accessing the data were shown schematically in Figure IB which also shows the shaft 11 mounting one ofthe discs 14. As seen in this figure, as the discs rotate, access to the data is obtained by servo placement of a transducer 23 supported on an actuator arm 27, and positioned by a voice coil motor 30 of a type well known in this technolo¬ gy. It is well known that the long life and usefulness of this design depends directly on the ability ofthe spindle motor to support the discs for constant speed, rotation and a uniform speed without tilt or wobble; the spindle motor must operate over widely varying environmental conditions because ofthe many heat sources which may be present nearby changing the environmental temperature over the period of operation, and must further have the ability to withstand significant shocks.

It is to achieve these benefits that a conical bearing ofthe type to be described below has been designed. Generally speaking, an embodiment ofthe bearing assembly 19 shown in Figure 1 A has housing or hub 15 surrounding shaft 11, and forming a pair of conical bearings 30, 32 with their apexes directed toward each other. Specifically, shaft 11 includes conical portions 34, 36 which mate with inclined wall portions 38, 40 but are separated therefrom by bearing gaps 42, 44 respectively. One side ofthe housing walls that define the bearing gaps, preferably the outer walls 38, 40 are grooved such as with inward pumping spiral grooves (not shown, but of a type well known in this technology) substantially over their bearing surfaces.

Referring further to Figure 1 A and to the more detailed drawing of a preferred embodiment of Figure 2, it can be seen that the housing wall portions 38, 40 flare radially inwardly from transverse end walls 50, 52. As previously described, these surfaces face inwardly tapering wall sections 36, 34 to define the gaps ofthe bearing. The inwardly tapering surfaces 34, 36 are a part ofthe fixed shaft of this design The wall portions 38 and 40, which flair outwardly toward the center ofthe bearing, end in

short substantially vertical wall sections 60, 62 shaft which cooperate with a vertical surface 64 ofthe shaft to define a connection or transition zone 66.

The short vertical faces 40, 42 at the ends ofthe flared cones ofthe sleeve define the openings 68 and 70 which lead to the connection zone 64; the major region ofthe connection zone 70 is defined by concave recess 72 in sleeve 15. This sleeve 15 encircles and rotates around the stationary shaft 11 and the tapered cones which are a part thereof.

A hollow tube 80 is placed in the concave region and surrounds the stationary shaft 11. This tube 80 is made of a plastic material which is not permeable to oil or air. The tube is filled preferably with air at ambient pressure, although other gasses and pressures are possible. The tube 80 is collapsible when sufficient pressure is applied to the outside ofthe tube. That is, the tube is designed to flex and even collapse under sufficient pressure; this increases the available volume ofthe concave region 70 surrounding the shaft, modifying the amount of lubricating fluid found between the bearing surfaces. The hydrodynamic bearing is primarily defined between the facing conical surfaces. The use ofthe conical surfaces to define the gap provides a wedged type design which provides substantial overall stability for the system along all axes against rocking or tilting. At least one ofthe two facing conical surfaces above and below the connecting regions have patterns of grooves to distribute the lubricating fluid through the bearing.

These grooves are in a spiral rather than a herringbone pattern (typically found in hydrodynamic bearings), and are designed so that all the pumping action is toward the center or connector region 70. The result is to build up a considerable amount of pressure in this center connection region where the collapsible tube 80 is located. As this pressure builds up in the connector region, the tube which is filled with air at ambient pressure progressively collapses, drawing more ofthe fluid out from between the two relatively rotating conical surfaces into the connection region 70. The more region 70 draws fluid the less fluid is found at the bearing opening, until the fluid recedes such that the effective bearing surface begins to shrink. When the pressure does not increase anymore, an equilibrium is reached between the pressure in the system and the pump defined by the active, still wetted bearing area.

The bearing is now able to operate efficiently under a variety of environmental conditions. If the bearing is operating at a low temperature environment, the lubricat¬ ing fluid has a high viscosity and the bearing is operating or pumping with a high efficiency level. As a result, the pressures will increase in the connection zone 70, causing the tube 80 to collapse, thereby depleting much ofthe bearing of its fluid and thereby diminishing the effective surface area ofthe bearing.

In contrast, in a high temperature, low viscosity environment, little or nothing ofthe bearing is depleted. This maintains the stiffness and diminishes the power consumption ofthe bearing. Overall, the power and stiffness vs. temperature balance ofthe overall system will be equalized so that the stiffness ofthe system necessary to support the disc mounted on the hub without tilt or wobble will be maintained while the power consumption will not be excessive. That is, as the operating temperature goes up, viscosity goes down, the bearing is less efficient and the power consumption is increased. So for a given level of fluid in the bearing, there is now less pressure with higher temperatures, and the tube 80 will collapse less than at lower temperatures. At higher temperatures, where the bearing is filled with fluid, more ofthe bearing surface is covered with oil, and there is more stiffness. This design thus balances out the fact that typically as the temperature increases, the stiffness decreases.

It is further well known that in a hydrodynamic bearing, as the operating temperature goes up, the viscosity goes down. Therefore, for a given level of fluid in the bearing, there is less pressure, and the tube 80 will collapse less than at a lower operating temperature so that more ofthe bearing remains filled with fluid. This will result in more ofthe bearing surface being covered with oil, and as a result more stiffness in the bearing. Thus, this design improvement balances out the fact that stiffness goes up in a hydrodynamic bearing as temperature decreases, but so does power consumption, which is a bad thing for maintaining the operability ofthe bearing cartridge especially as used in a spindle motor which has limited power available. This present design provides the benefit of establishing a bearing wherein the power is not excessive even at the lowest probably operating temperatures and at that temperature there will still be the required stiffness. The design, by providing a balancing effect which plays off against operating pressure, will also provide a hydrodynamic bearing which is in the

proper power consumption range even at lower temperatures, even while maintaining the necessary stiffness in the system at higher temperature. The primary benefit of this design is to have less power consumption at the lowest temperatures which is where excessive power consumption is most likely to occur, while maintaining sufficient stiffness even at the highest operating temperatures where the stiffness is the most likely to fall below the desired minimum level. Although the design disclosed herein will work across a wide range of angles for the taper ofthe conical bearing, it has been found that the largest apex angle would be about 60 degrees.

A further feature ofthe present invention which should also be noted is the presence ofthe sealing stopper 100 located near the bottom ofthe central, fixed shaft. It can be seen that the desired conical form ofthe fixed shaft includes a sleeve 102 incorporating on its outer surface a conical section 104 and having a flat axial inner surface 106. Substantial pressures are created during the operation ofthe bearing which could potentially cause oil to leak out from the connecting region 70 through the recess 108 which is provided to implement fitting the sleeve over the outer surface of the shaft, and between the shaft and sleeve and out into the outer atmosphere. It is to prevent this phenomenon from occurring that the stopper 100 is provided which is crushed between the end ofthe major portion ofthe shaft and a plug 112 which is inserted loosely into the bottom ofthe hydrodynamic bearing cartridge. The stopper or gasket 100 is pressed between these two pieces in piecing the density ofthe gasket and providing a tight seal against any lubricant leakage along the gap between the surfaces 106, 107.

The invention can be further understood by considering the sequence of assembly ofthe subject design. The assembly sequence begins with the sleeve 120, to which is attached the magnet 122 and the hub 124. The magnet is glued onto the outer part ofthe sleeve 120; the hub would typically be a shrink fit onto the outer surface of the sleeve. The o-rings 126, 128 are then placed in the channels on the upper and lower end surfaces ofthe sleeve. Next the collapsible hollow plastic tube 80 is placed in the concave recess 72 and the major portion 130 ofthe axil is passed through the top opening ofthe sleeve, extending through the connection region 70 and out the bottom ofthe sleeve. As this is done, the cortical sleeve 104 which bears the lower cone which will mate with the lower conical bearing surface 40 is pressed into place over the

surface ofthe sleeve. This is facilitated by typically holding the shaft portion 130 in a fixture, and pressing the sleeve 102 over the outer portion ofthe shaft until it butts up against the shoulder 134, the joinder of these two parts being facilitated by the recess 108 in the outer surface of shaft 130. At this point the bottom counter plate 90B is installed, this counterplate being pressed against the bottom surface 52 ofthe sleeve and capturing the o-ring 126 in its recess. The counterplate is held in place by the shoulder 150. A removable o-ring is also slipped into place adjacent the tapered end 160 ofthe counterplate 90B and the outer surface ofthe sleeve 104 which is now a part ofthe fixed shaft. This o-ring 158 shown in dotted lines in Figure 2 is to seal a potential opening from one end ofthe hydrodynamic bearing against the outside atmosphere while the bearing is filled, the o-ring being removed after the filling process is complete.

The assembly which exists to this point is put into a vacuum oven, with a measured amount of oil placed on the top surface 50 where the top counterplate 90A will rest when final assembly is completed. Obviously, in this partially assembled cartridge for a motor, the top counterplate 90A is not in place until after the filling. Although altemative approaches to filling the bearing are sufficiently possible, this is believed to be the most efficient and the least likely to leave an oil residue outside of the tapered hydrodynamic bearing surfaces. The partially assembled bearing cartridge is now placed in a heated vacuum chamber and all air is evacuated from the chamber resulting in all being withdrawn from between the bearing surfaces and the connection region 70. When normal pressure is restored, the oil which is resting on the surface 50 is drawn into the region of between the bearing surfaces 36, 38 and 34, 40 as well as the connection region 70 since no air is present. Now any remaining oil on the surface 50 is cleaned off, and the top counter¬ plate 90A is squeezed into place inside the shoulder 151 to be held firmly in place with its taping end over the outwardly extending surface 153 ofthe fixed shaft. The assembly is now complete with the exception ofthe gasket or crushed rubber ball 100 on the bottom together with the cap 112, and the rivet 170 on the top. At this point, the rubber ball 100 or gasket may be put in place and glued into place and the cartridge type assembly can now be either tested or stored for later use.

In order to incoφorate this cartridge assembly into a disc drive, the assembly to this point has its lower region as defined by sleeve 102 inserted into an appropriate opening in the base 180, and the cap 112 is then pressed into place below the plug or gasket 100. It should be noted that the cap 112 should not fit too tightly as such might cause air to be trapped above the cap and forced back up into the hydrodynamic bearing. After a disc or discs are loaded on the hub 124, then the top cover 182 is placed over the spindle motor, and held in place by a rivet or screw 170 inserted into the top ofthe fixed shaft. The remaining pieces ofthe motor represented by the lamination and windings 190 in Figure 2 are supported in the interior ofthe housing now established in accordance with the technology well known in this field.

By virtue of this design approach, a hydrodynamic bearing assembly ofthe conical type is defined wherein the power and stiffness are both controlled relative to the operating or environmental temperature. Where the temperature is lower in the operating environment than during the filling process, the added pressure build up between the cones compresses the cones and lowers the fluid level in the bearing, reducing the bearing surface from the outer diameter in the direction ofthe inner diameter ofthe conical bearing. When the pressure is greater, the opposite result occurs.

Other features and advantages ofthe present invention will become apparent to a person of skill in the art who studies the above disclosure.