Abstract:
A head gimbal assembly on a suspension for being loaded relative to a disk and a ramp facilitates the loading and unloading of the head relative to the disk. An air bearing effectively regulates the head and gimbal assembly and disk location. Unloading a suction air bearing when the head is unloaded from the disc comprises applying an excitation to the air bearing during unloading to effect a perturbation in the air bearing. The air bearing is a suction bearing, and an excitation pertubates at least one of the modes of the leading edge, trailing edge or roll mode.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     The present invention relates to Provisional Application Serial No. 60/074,766, filed Feb. 17, 1998, by Zine-Eddine Boutaghou, and entitled “DITHER METHOD TO UNLOAD NEGATIVE SUCTION AIR BEARINGS”. Also application Ser. No. 09/081,393, filed May 18, 1998 by James Morgan Murphy and entitled “SUSPENSION-LEVEL PIEZOELECTRIC MICROACTUATOR discloses characteristics of the microactuator. The contents of these applications are incorporated by reference herein. 
    
    
     BACKGROUND OF THE INVENTION 
     The present invention relates generally to disk drives, and particularly to a gimbal-level piezoelectric microactuator for read/write heads for disk drives. 
     One of the major problems of using high suction air bearings in load/unload application shows up during the unloading of the heads. The negative suction forces induces an impulse loading contributing to the excitation of the head-gimbal assembly (“hga”). In addition to the excitation of the head-gimbal assembly, the hga is required to travel up the ramp a considerable distance before the system is able to overcome the suction force. The unload travel distance up the ramp translates into valuable unused real estate at the outside diameter of the disc. 
     Accordingly, there is a need in the art for an actuator for supporting and finely-positioning a read and/or write hga with sufficient accuracy and to operate with a minimum of unused real estate, namely substantially below that possible with typically known systems. 
     SUMMARY OF THE INVENTION 
     A head gimbal assembly on a suspension is loaded relative to a disk. A ramp facilitates the loading and unloading of the head relative to the disk. An air bearing effectively regulates the head and gimbal assembly and disk location. Unloading a suction air bearing when the head is unloaded from the disc comprises applying an excitation to the air bearing during unloading to effect a perturbation in the air bearing. The air bearing is a suction bearing, and an excitation pertubates at least one of the modes of the leading edge, trailing edge or roll mode. 
     A single or multiple air bearing modes can be excited during unload operation of the air bearing. A sweep function containing one or several air bearing modes to perturb the air bearing and cause an instability which eases unloading of the heads. 
     A microactuator can be used to generate the excitation. In case the excitation frequencies are low, the voice coil system can then be used. The amplitude of the excitation may be varied throughout the excitation. In some forms of the invention the gimbal modes, namely either twist and/or bending modes, can be excited to increase the forces acting on the air bearing contributing to overcome the suction forces. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Referring now to the drawings in which like reference numbers represent corresponding parts throughout: 
     FIG. 1 is a top plan view of a disk drive assembly, wherein a top portion of the assembly has been cut-away to expose a head-arm assembly positioned over a platter; 
     FIG. 2 illustrates a piezoelectric monomorph that may be used to implement the second stage positioner; 
     FIG. 3 illustrates a monomorph with pivots at each end; 
     FIG. 4 illustrates a monomorph with one pivot at the end of the monomorph where the lever arm is attached; 
     FIG. 5A illustrates another embodiment, wherein a pivot point is created by having two monomorphs intersect at their deflecting, ends, such that they prevent each other from deflecting translationally, leaving rotation about the pivot point as the only unconstrained degree of freedom; 
     FIG. 5B illustrates the deflection of the lever arm through the arc when voltages are applied to the monomorphs causing them to bend in the manner indicated; 
     FIG. 6 illustrates a microactuator. 
     FIG. 7 shows successive positions of the head-gimbal assembly on the ramp during unload. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     In the following description, reference is made to the accompanying drawings which form a part hereof, and which show, by way of illustration, several embodiments of the present invention. It is understood that other embodiments may be utilized and structural changes may be made without departing from the scope of the present invention. 
     Overview 
     Apparatus is provided for positioning a head adjacent a recording surface of a recording media, said recording surface defining multiple data track locations. The apparatus comprises a movable support arm having a flexure element. The flexure element is for supporting the head adjacent the recording surface and for movably positioning of the head relative to each data track location. 
     There are air bearing means for supporting the support arm relative to the recording surface, and means for exciting the air bearings during an unloading operation of the support arm. The head can be removed from the recording surface in a manner whereby there is a reduced suction force between the head and the recording surface. 
     The present invention preferably discloses a second-stage, fine-positioning, microactuator for use with a read/write head of a disk drive. The microactuator has a much higher bandwidth than VCM actuators, and excludes suspension resonances. The microactuator is a very small, lightweight device that is placed between the head and the suspension of the VCM actuator. The microactuator provides only a very small amount of movement—just enough to allow each head to follow its track. For example, only approximately ±0.5 μm of motion is necessary for a disk drive with a 1 μm track pitch (i.e., 25 k tpi track density). 
     Disk Drive Structure 
     FIG. 1 is a top plan view of a disk drive assembly  10 , wherein a top portion of the assembly  10  has been cut-away to expose a head-arm assembly  12  positioned over a platter  14 . In addition, a top portion of the magnetic structure assembly  16  is removed in order to expose the coil bobbins  18 ,  20  of a voice coil motor (VCM) that controls the movement of the head-arm assembly  12 . The head-arm assembly  12  includes an arm  22 , suspension member  24 , microactuator  26 , and a read/write head  28  positioned over the platter  14 . Generally, a plurality of platters  14  are stacked on a spindle  30  and there are a plurality of head-arm assemblies  12  in an E-block structure to access the platters  14  simultaneously, wherein each head-arm assembly  12  accesses one of two surfaces (top and bottom) of each platter  14 . 
     The head-arm assembly  12  is comprised of both a first stage positioner and a second stage positioner. The first stage positioner comprises the VCM, arm  22 , and suspension member  24  that effect rotational movement of the head-arm assembly  12  about a pivot bearing  32  for coarse positioning. The second stage positioner comprises a suspension level piezoelectric microactuator  30  that effects very small, cross-track, movements of the read/write head  28  for fine positioning. 
     The first-stage positioner positions the read/write head  28  in the vicinity of the desired track of the platter  14 . The second stage positioner then precisely aligns the read/write head  28  with the desired track of the platter  14 . 
     The second stage positioner is capable of fine scale movements to define a range of movement in the order of about half the width of the desired track. In addition, the second stage positioner provides a much faster response. 
     Piezoelectric Microactuator 
     FIG. 2 illustrates a piezoelectric monomorph  34  that may be used to implement the second stage positioner . The monomorph  34  is comprised of piezoelectric elements  36 ,  38  bonded to a thin sheet metal structure  40 . Applied voltages cause the piezo elements  36 ,  38  to expand or contract, which makes the structure  34  bend in much the same way a bimetallic strip does with changes in temperature. The piezoelectric monomorph  34  is fixedly mounted at one end while the opposite end produces the required motion by deflection through the arc labeled as  42 . Similarly, the second-stage positioner may also use piezoelectric bimorphs, which are comprised of two piezoelectric crystals bonded together that deform in opposite directions to produce a curvature. 
     There is utilized the displacement or curvature of the monomorphs  34 . This is possible by mounting the monomorph  34  such that its ends can rotate but not move. A monomorph  34  by itself would not be stable; it could buckle if subjected to vertical forces. This is why two intersecting monomorphs  34  are used, i.e., to create a more stable structure. Force or stiffness in the direction of deflection is not actually improved by utilizing the monomorph&#39;s  34  curvature instead of direct deflection. 
     FIG. 3 illustrates a monomorph  34  with pivots  44 ,  46  at each end. Voltages are applied to the piezoelectric elements  36 ,  38  bonded to the thin sheet metal structure  40 , which causes the piezo elements  36 ,  38  to expand or contract. This expansion or contraction causes the structure  34  to bend through the curvature labeled as  48 . The bending motion causes deflection in a lever arm  50  attached to one end of the monomorph  34  as indicated by the arc  52 . 
     For simplicity, however, the microactuator  26  may only use a pivot point at one end, and uses an inactive or counter-bending section at the other end to achieve the same effect. FIG. 4 illustrates a monomorph  34  with one pivot  46  at the end of the monomorph  34  where the lever arm  50  is attached. At the other end, the monomorph  34  is attached to an inactive or counter-bending section  54  that is fixedly mounted to a structure  56 . Voltages are applied to the piezoelectric elements  36 ,  38  bonded to the thin sheet metal structure  40 , which causes the piezo elements  36 ,  38  to expand or contract. This expansion or contraction causes the monomorph  34  to bend through the curvature labeled as  48 . The bending motion causes deflection in a lever arm  50  attached to one end of the monomorph  34  as indicated by the arc  52 . However, the inactive or counter-bending section  54  produces counter-curvature as indicated by the arc at  58 . 
     FIG. 5A illustrates another embodiment, wherein a pivot point  60  is created by having two monomorphs  62 ,  64  intersect at their deflecting ends, such that they prevent each other from deflecting translationally, leaving rotation about the pivot point  60  as the only unconstrained degree of freedom. A lever arm  66 , to which the read/write head  28  is attached, is connected to this pivot point  60  and converts the rotation produced thereby into a translation at the head  28 . FIG. 5B illustrates the deflection of the lever arm  66  through the arc  68  when voltages are applied to the monomorphs  62 ,  64  causing them to bend in the mainer indicated. 
     FIG. 6 illustrates a dual monomorph structure created from an etched sheet of stainless steel  100  by forming side rails  102  and  104  up normal to the sheet  100 , bending their extending tabs  106  and  108  outwards to a specific angle, and bonding piezoelectric elements  110  and  112  to them. Large flat pads  114  and  116  at the end of these monomorph sections allow the microactuator  26  to be spot-welded to a modified load beam  118 . The loadbeam  118  has a formed protrusion  120  which contacts a dimple  122  on the center beam  124  of the microactuator at the ‘virtual pivot’ location, helping to transmit the preload force. 
     A shortened, gimbal or flexure sheet  126  is spot-welded to the flat center section  124  of the resulting U-channel beam. To the end  128  of the gimbal or flexure sheet  126  there is glued the slider or head  130 , which gimbals on a dimple as per current practice. Not shown in FIG. 6 is a flex circuit, which carries the electrical signals to and from the head  130 , and carries the control voltage to the piezo elements  110  and  112 . Only a single wire is attached to each monomorphs, with the suspension acting as the ground return. Opposite-poled regions on the piezo crystals  110  and  112  produces the opposite curvatures necessary at the base of the monomorphs. 
     In a particular version of the design, 70×16×4 mil piezoelectric elements  110  and  112  are bonded to a 3-mil thick stainless steel sheet  100 . This sheet  100  has partially-etched lines etched into it along the fold lines of the forming operations, to improve the locating of these forms, reduce their bend radii, and lower the stresses involved during forming. The sheet  100  also has tooling holes etched into it, for manufacture, and slots in the side rails to allow the flex circuit to pass from the inside to the outside of the channel. 
     FIG. 7 shows a first position  1  and successive positions of the head-gimbal assembly during unload. Position  1  relates to the initial engagement of the head-gimbal with the ramp. Position  2  relates to the position the head is lifted from the disk. Distance A is the required travel of the head to overcome suction force. The head needs to be lifted before it engages the non-glided region. 
     The air bearing has three vibrational modes. The leading edge pitch mode, the trailing edge pitch mode, and the roll mode. These modes can be determined from either modeling or experimentation for each air bearing model. In normal operating conditions, it is suggested not to excite these modes since they may cause fly height modulation. However, during unloading of the head it is desirable to excite one or several of these modes to cause air bearing perturbations which allow unloading of the head. Since the air bearing is governed by Reynolds equations, the response of the system will be a function of the initial conditions of the system, namely a nonlinear system. Both the magnitude of the excitation and the mode of vibration affect the response of the air bearing. 
     As shown in the following table the air bearing modes vary form 40-100 kHz depending on the air bearing type and stiffness. It may be relatively difficult to cause the excitations with the current voice coil system, and the microactuators can perform such operations. The table shows air bearing frequencies, and the paranthetical numbers are predicted numbers. 
     
       
         
               
               
               
               
             
               
               
               
               
             
           
               
                   
               
               
                   
                 Leading Edge 
                   
                 Trailing Edge 
               
               
                 Air bearings 
                 Pitch (kHz) 
                 Roll Mode (kHz) 
                 Pitch (kHz) 
               
               
                   
               
             
             
               
                   
               
             
          
           
               
                 10 k program 
                 3.75 
                 66.0 
                 77-86.50 
               
               
                   
                 (32.2) 
                 (61.6) 
                 (70.90) 
               
               
                 710.01 
                 27.40 
                 54.0 
                 89.90 
               
               
                   
                 (28.40) 
                 (49.50) 
                 (77.0) 
               
               
                 Enhanced 
                 ? 
                 66.0 
                 74-88 
               
               
                 NPAB 
                 (34.9) 
                 (53.2) 
                 (62.1) 
               
               
                 NPAB 
                 45.52 
                 76.0 
                 ? 
               
               
                   
                 (41.5) 
                 (78.6) 
                 88.4 
               
               
                 Pico 
                 29.0 
                 46.0 
                 87.0 
               
               
                 (highly nonlinear) 
               
               
                   
               
             
          
         
       
     
     The foregoing description of the preferred embodiment of the invention has been presented for the purposes of illustration and description. It is not intended to be exhaustive or to limit the invention to the precise form disclosed. Many modifications and variations arc possible in light of the above teaching. 
     It is intended that the scope of the invention be limited not by this detailed description, but rather by the claims appended hereto.