Abstract:
A system and method for deforming and puncturing magnetic storage media includes one or more pivot arms that support one or more rotationally driven rotatable members bearing multiple deforming members or punch points. The punch points impact the media, producing the deformation, while the rotational forces push the media through the system, and the pivot arms adapt to media characteristics and widths to protect against jams. The puncturing force may be adjustable.

Description:
FIELD OF THE INVENTION 
       [0001]    The invention relates generally to the mechanical arts and more specifically to an apparatus and method for deforming media to mark the media and/or render the media unusable. 
       BACKGROUND 
       [0002]    Destruction of information magnetically encoded onto magnetic storage media is often desired, for example, when the media becomes obsolete but the information is of a sensitive or classified nature. Computer systems provide file delete functions; however, many software products are able to reverse the process and restore the encoded information. Software overwrite methods magnetically alter the information by overwriting the encoded information, but such a process can be slow and reversible. Also, should a computer hard drive crash and stop functioning properly, software overwriting becomes useless. 
         [0003]    It is also known to erase magnetic media through bulk degaussing, which has been employed in different forms to alter the magnetic information on the storage media. Electromagnets and windings that produce strong magnetic fields can erase information from computer hard drives but require high input energy levels or long times to store the energy needed to produce such fields. Permanent magnet structures have also been used for erasing magnetic information, but permanent magnet structures able to produce the strong magnetic fields required to erase information tend to be large and heavy. Bulk degaussing methods also typically leave no outward physical evidence of media erasure. 
         [0004]    Another known method for protecting stored information is to alter the disk that stores the information in configuration or shape, such as by pulverization into fine particles or compaction by a mechanical press. The process of shredding a complete hard drive into many small pieces requires very high contact loads between the cutter teeth and the hard drive. To produce these large forces, the input line energy levels tend to be very high and the overall physical size of the equipment is extremely large. There can also be other hazards associated with the disposal of the small partials produced by the process. 
         [0005]    The deforming of storage media has also been employed in several different forms. It is known, for example, to use a conical shaped crushing head that aligns to a conical-shaped receiving plate. The crushing head moves in a direction that is perpendicular to the surface of the storage media to engage and deform the media. It is also known to use a multi pronged head that moves in a path perpendicular to the surface of the storage media to deform the media. Such approaches require the operator to properly locate the magnetic storage platters inside a hard drive and orient them properly prior to destruction. The use of such physical deforming devices during a security emergency may lead to a greater possibility of operator errors. 
         [0006]    Another approach to physically deforming the media includes using a wedge shaped member that moves in a path perpendicular to the magnetic storage media surface that it contacts. The length of the wedge shaped member is as long as the longest length of the media that it deforms. This approach overcomes the issues associated with the proper orientation of the media but inherently produces a slow cycle time for processing the media. Accordingly, there is a need for a deforming system that eliminates operator errors, is not large in size, is portable, and has a fast cycle time. 
         [0007]    Another concern includes marking media with sensitive information that has been erased or otherwise rendered non-sensitive. Such markings are often applied manually as the sensitive material is erased or damaged. For dealing with destruction of vast quantities of sensitive information, fast and automated methods are preferred. For example, the term “unclassified” might be printed on magnetic storage media automatically as it exits a conveyorized bulk degausser. The marking apparatus could be programmable to include such information as a date, an operator name, and batch information. Such printing is routine in the mass production of goods, and can be accomplished by non-contact means on a variety of materials and surface shapes. In mass production, factors like size, shape, and material can be predetermined precisely and made to remain stable for large batches of product, allowing details like ink type and print head position to be optimized for the process. In contrast, an automated bulk degaussing system suited to information destruction of massive media quantities may treat a mixed stream of such media. Even if limited to a constant form factor such as 3.5 inch (8.89 cm) hard disk drives, the media stream can include a great deal of variation not limited to color, material, shape, and texture that confounds mass printing methods. A system providing flexible marking means for magnetic storage media that contains variable configurations is therefore needed in the destruction of large volumes of sensitive information. 
     
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         [0008]      FIG. 1  is a perspective view of an embodiment of a deforming device. 
           [0009]      FIG. 2  is a plan view of the deforming device of  FIG. 1  together with an example power transmission and driving apparatus. 
           [0010]      FIG. 3  is a partial side cross sectional view of the deforming device of  FIG. 1 . 
           [0011]      FIG. 4  is a partial side cross sectional view of the deforming device of  FIG. 1  with a magnetic medium disposed within the device. 
           [0012]      FIG. 5  is a side view of a portion of a deforming device in accordance with various embodiments. 
           [0013]      FIG. 6  is a partial side cross sectional view of the deforming device of  FIG. 1  with an object disposed within the device. 
           [0014]      FIG. 7  is a partial side cross sectional view of the deforming device of  FIG. 1  with an object disposed within the device. 
           [0015]      FIG. 8  is a side view of a portion of a deforming device in accordance with various embodiments. 
           [0016]      FIG. 9  is a side view of a portion of a deforming device in accordance with various embodiments. 
           [0017]      FIG. 10  is a side view of two example rotatable members spaced in accordance with various embodiments. 
           [0018]      FIG. 11  is a side view of two example rotatable members spaced in accordance with various embodiments. 
           [0019]      FIG. 12  comprises side and cross-sectional views of an example deforming member. 
           [0020]      FIG. 13  comprises side and cross-sectional views of an example deforming member. 
           [0021]      FIG. 14  comprises side and cross-sectional views of an example deforming member. 
           [0022]      FIG. 15  a partial side cross-sectional view of an embodiment of a deforming device. 
           [0023]      FIG. 16  a partial side cross-sectional view of an embodiment of a deforming device. 
       
    
    
       [0024]    Skilled artisans will appreciate that elements in the figures are illustrated for simplicity and clarity and have not necessarily been drawn to scale. For example, the dimensions and/or relative positioning of some of the elements in the figures may be exaggerated relative to other elements to help to improve understanding of various embodiments of the invention. Also, common but well-understood elements that are useful or necessary in a commercially feasible embodiment are often not depicted in order to facilitate a less obstructed view of these various embodiments of the invention. It will further be appreciated that certain actions and/or steps may be described or depicted in a particular order of occurrence while those skilled in the art will understand that such specificity with respect to sequence is not actually required. It will also be understood that the terms and expressions used herein have the ordinary meaning as is accorded to such terms and expressions with respect to their corresponding respective areas of inquiry and study except where specific meanings have otherwise been set forth herein. 
       DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0025]    Generally speaking, pursuant to these various embodiments, an apparatus for deforming media includes a media conveyance path, a pivot arm, and a biasing system operatively connected to the pivot arm to bias the pivot arm toward the media conveyance path. At least one rotatable member is rotatably secured to the pivot arm, and at least one deforming member is secured to the rotatable member. Accordingly, a medium may be accepted into the media conveyance path wherein the medium is engaged by a plurality of deforming members rotating on the rotatable member. A deforming force is thereby applied to the medium through the deforming members via the biasing system. The rotating members may be moved away from the medium when the deforming members encounter a force from the medium that is larger than the deforming force. 
         [0026]    So configured, a magnetic medium may be punctured or otherwise deformed, thereby rending the information stored thereon at least partially unreadable. The punctured or deformed nature of the medium may also serve as an indication that the medium has been at least partially erased or otherwise rendered unreadable. Moreover, the biasing member in certain embodiments allows for retraction of the deforming and rotating members to reduce jamming. 
         [0027]    These and other benefits may become clearer upon making a thorough review and study of the following detailed description. Referring now to the drawings, and in particular to  FIGS. 1-4 , an example apparatus for deforming media includes a media conveyance path  9 , a pivot arm  66 , and a biasing system  10  operatively connected to the pivot arm  66  that biases the pivot arm  66  toward the media conveyance path  9 . At least one rotatable member  70  is rotatably secured to the pivot arm  66 , and at least one deforming member, such as punch point  78 , is secured to the rotatable members  70  such that the deforming members are biased toward the media conveyance path  9  to at least partially deform a medium  1  passing through the media conveyance path  9 . A driving apparatus such as electric motor  20  can be operatively connected to the rotatable member  70 . 
         [0028]    With reference to  FIG. 1 , an opening or aperture  4  allows access of the magnetic storage medium  1  to the media conveyance path  9 . The aperture  4  is defined by a media restrictor plate  3  through which a medium  1  to be deformed is passed. The aperture  4  of the media restrictor plate  3  defines the allowable cross-sectional area of the magnetic storage media  1  that can pass through the media conveyance path  9 . The height and width of the aperture  4  of the media restrictor plate  3  is preferably slightly larger than the size of the magnetic storage medium  1 . The media passageway top surface  5 , media passageway bottom surface  7 , and media passageway side surfaces  6  and  11  define the media conveyance path  9  through the apparatus and are spaced to be slightly larger that the medium  1  to be deformed. The height and width of the media conveyance path  9  is preferably slightly larger than the height and width of the aperture  4 . 
         [0029]    The magnetic storage medium  1  contacts the media passageway bottom surface  7 , which can be oriented at any angle from horizontal to vertical. Preferably, the media passageway bottom surface  7  slants at an angle of 30° downward from a point where the magnetic storage medium  1  passes through the media restrictor plate  3  to a point where the magnetic storage medium  1  exits the media conveyance path  9  at the opposing end, thus allowing for gravity feed of the medium  1 . The media passageway side surface  6  is attached to the chassis side  2 . The chassis side  2  is a rigid frame member that provides a common ground reference and support for many components of the apparatus. 
         [0030]      FIG. 2  illustrates parts associated with an example power transmission and driving apparatus to produce the rotational motion of the rotatable members  70 . By one approach, an electric motor  20  converts electrical power into rotational motion. The electric motor  20  is rigidly attached to a speed reducer  22 . The input energy to electrical motor  20  produces rotational motion and torque that is transmitted to the speed reducer  22 . Depending upon the horsepower, shaft rotations per minute (“RPM”) speed of the electric motor  20 , and the size of the rotatable members  70  necessary for a given application, the speed reducer  22  is preferably configured to produce an output shaft speed greater than 10 RPM and a torque greater than 10 ft-lbs (1.38 kg-m), although other configurations are possible depending on the application of the device. The resulting rotational motion of the speed reducer  22  is transmitted to the speed reducer output shaft  24 . Any appropriate attachment means such as bolts or shaft keys are used to firmly secure speed reducer output shaft  24  to a shaft coupling  26 . Keys, bolts, or other suitable means are used to rigidly attach the shaft coupling  26  to a gear box input shaft  30 . The input shaft  30  receives energy approximately equal to the amount present in the speed reducer output shaft  24 . 
         [0031]    By another approach, the driving apparatus may include a crank handle (not shown). The crank handle, for example, may include a lever arm, or crank handle offset, that attaches to a hand grip member. The lever arm length, or crank handle offset, could be changed by one skilled in the art to match the input torque requirements to the speed reducer  22  or other coupling to the rotatable members  70  to operate the mechanism. Such an approach may be useful in an emergency situation where power to the apparatus is lost. Other example approaches to the driving apparatus for providing input energy to the rotatable members  70  could be in the form of a pneumatic or hydraulic driven motor or an internal combustion engine, although other approaches may be envisioned. 
         [0032]    With reference to  FIGS. 2 and 3 , the gear box housing  8  is a rigid frame support member that contains components of the power transmission drive between input shaft  30  (connected to the driving apparatus, here electric motor  20 ) and rotatable members  70 . The gear box housing  8  is securely attached to the media passageway side surface  11  and to the chassis side  2 . Bearings  32  and  34  support the gear box input shaft  30  at two points along its length and constrain it to rotational motion about its axis. Input shaft bearings  32  and  34  are securely seated in gear box housing  8 . The input shaft  30  has a counterclockwise direction of rotation when viewed from the right hand side of  FIG. 2 . Bolts, keys, or other suitable attaching methods are used to firmly affix drive gear  36  to the input shaft  30  at a location that is between the input shaft bearings  32  and  34 . The rotational motion and energy that the drive gear  36  receives is approximately equal to that of the input shaft  30 . The drive gear  36  is in mesh contact with an idler gear  38 , drawn partially cut away to reveal drive gear  36  behind it, and second stage gear  47 . The energy from drive gear  36  is approximately evenly split between the idler gear  38  and second stage gear  47 . The idler gear  38  takes on a clockwise direction of rotation. Any appropriate means such as bolts or keys may be used to rigidly attach the idler gear  38 , shown partially cut away, to the idler gear shaft  40 , which is also drawn partially cut away. Shaft bearings  42  and  44  support the idler gear shaft  40  at each end and constrain it to rotational motion about its axis. Shaft bearings  42  and  44  are firmly mounted in gear box housing  8 . 
         [0033]    A second stage gear  46  is in mesh contact with the idler gear  38 . The rotational direction of the second stage gear  46  is reversed to counterclockwise, and the amount of rotational torque increases as according to the ratio of the second stage gear  46  to the idler gear  38 . Keys, bolts, or other suitable holding means may be used to soundly affix the second stage gear  46  to an arm pivot shaft  48 . Three shaft bearings  50 ,  52 , and  54  limit the arm pivot shaft  48  to rotational motion about its axis. One shaft bearing  50  is firmly seated in the chassis side  2 , and the other shaft bearings  52  and  54  are firmly held in the gear box housing  8 . The smaller second stage gear  56  is positioned and firmly attached with any suitable means to the arm pivot shaft  48  that is coaxial with the larger second stage gear  46 . The smaller second stage gear  56  receives energy approximately equal to that contained in the larger second stage gear  46  and moves in the same rotational direction. Second stage gears  46  and  56  are in a position on arm pivot shaft  48  that places their location between shaft bearings  52  and  54 . The second stage gear  56  is located towards the inside of the mechanism relative to the larger second stage gear  46 . Under certain geometry limiting constraints, the reverse positioning could be applied. 
         [0034]    A punch drive gear  58  is in mesh contact with the smaller second stage gear  56 . The punch drive gear  58  is reversed to clockwise and the amount of rotational torque increases according to the ratio of the punch drive gear  58  to the second stage gear  56 . A suitable means such as shaft keys or bolts is used to firmly secure the punch drive gear  58  to a rotatable member shaft  60 . Shaft bearings  62  and  64  restrict the rotatable member shaft  60  to rotational motion about its axis. The shaft bearings  62  and  64  are firmly constrained in the pivot arm  66 . Shaft keys, bolts, or other appropriate holding means may be used to rigidly hold a rotatable member mount  68  to the rotatable member shaft  60 . The rotatable member mount  68  has approximately the same torque and rotational direction as the punch drive gear  58 . Bolts, rivets, or other suitable means may be used to affix one rotatable member  70  to each side of the rotatable member mount  68 . 
         [0035]    The number of rotatable members and spacing between them can be changed to meet the challenges associated with different magnetic storage media sizes. For example, if 1.8 inch (4.57 cm) hard drives or smaller micro drives are to be deformed, then three or more rotatable members  70  may be mounted along the rotatable member shaft  60  to ensure contact with the small 1.8 inch (4.57 cm) media traversing the pathway. If 5.25 inch (13.336 cm) hard drives are to be deformed, then only one rotatable member  70  is necessary per rotatable member shaft  60 . Similarly, the internal construction of all magnetic storage media hard drives is not the same; for instance, the spindle motors that rotate the magnetic storage platters inside a hard drive are generally centered from side to side. Accordingly, two rotatable members  70  may cover the width of a 3.5 inch (8.89 cm) hard drive and still avoid the relatively dense hard drive spindle motor. The spacing of the rotatable members  70  may be configured as necessary. It is also realized that if large quantities of hard drives with steel covers is deformed, the rotatable member  70  can experience excess wear and need replacement periodically. Accordingly, a reusable type of holding device such as bolts for mounting rotatable member  70  may be used, although more permanent mounting means can be used as well. 
         [0036]    With continuing reference to  FIG. 3 , the gear train of the input drive gear  36 , the second stage gear  47 , the arm pivot shaft  49 , the second stage gear  57 , the punch drive gear  59 , and the rotatable member shaft  61  are nearly mirror images of the structures opposite a plane  72 , including the power transmission aspects of the idler gear  38 , the second stage gear  46 , the arm pivot shaft  48 , the second stage gear  56 , the punch drive gear  58 , and the rotatable member shaft  60 . Only the shafts  30  and  40  and respective mounting bearings differ in this example embodiment. The mirror image extends to the reverse direction of rotation of respective gears and to the rotatable members  70  and  71 , which are driven through the gear train. 
         [0037]    By one approach, with reference to  FIG. 4 , a rotatable member  71  may be split along a parting line  74  into two semicircular portions. A rotatable member  70 , shown as a one piece circular member, or rotatable member  71  can be sectioned into one or more equal or unequal portions depending on design and maintenance requirements. The rotatable member  70  extends through a slot in the media passageway top surface  5  and into the media conveyance path  9 . Likewise, the bottom rotatable member  71  extends through media passageway bottom surface  7  and into the media conveyance path  9 . As the magnetic storage medium  1  travels in the direction of arrow  76 , it will come into contact with the rotatable members  70  and  71 . The clockwise rotational torque on the top rotatable member  70  and counterclockwise rotational torque on the bottom rotatable member  71  will cause the magnetic storage medium  1  to be pulled into and past the rotatable members  70  and  71 . As the medium  1  passes between the rotatable members  70  and  71 , the punch points  78  located on the outside periphery of rotatable member  70  and  71  will puncture the medium  1 . 
         [0038]    A biasing system  10  generates the force needed for the punch points  78  to puncture the medium  1 , and  FIG. 5  shows a simplified sketch of the example biasing system  10  illustrated in  FIGS. 1-4 . The biasing system  10  includes a compressed spring  110  having a first spring end  101  and a second spring end  102 , wherein the compressed spring  110  is disposed on a spring guide assembly  107 . The spring guide assembly  107  includes a spring guide  108  having a spring guide first end  103  disposed toward the first spring end  101  and a spring guide second end  105  disposed toward the second spring end  102 . The spring guide assembly  107  also includes an adjustable spring retainer  112  secured to the spring guide first end  103  and a center pivot block  100  slidably engaging the spring guide  108  toward the spring guide second end  105  and the second spring end  102 . A pivot pin  82  is rigidly fixed to the chassis side  2  and supports and restricts the motion of a spring guide mount  86  to pure rotational motion about the axis of the pivot pin  82 . The spring guide  108  is rigidly attached to the spring guide mount  86  with a center pivot block  100  constraining it to limited rotational motion about the axis of the pivot pin  82 . 
         [0039]    The compression spring  110  slides over the spring guide  108 , and the adjustable spring retainer  112  is adjustable along the length of the spring guide  108 . The adjustable spring retainer  112  constrains the compression spring  110  in a compressed state and from sliding off the spring guide  108 . Pivot pins  88  and  104  support the ground link  92 . The first pivot pin  88  is firmly attached to the chassis side  2 , and the second pivot pin  104  is rigidly attached to the center pivot block  100 . The ground link  92  is restricted to rotational motion about the axes of the pivot pin  88 . Pivot pins  94  and  104  support the pivot arm link  98 . The first pivot pin  94  is soundly attached to the pivot arm  66 . The pivot arm link  98  moves in with both linear and rotational motion when the linkage assembly moves. The configuration of the linkage assembly determines the motion of pivot arm link  98  and may be adjusted for a particular application. The arm pivot shaft  48  and media passageway top surface  5  both support and restrict the motion of the pivot arm  66  to pure rotational motion about the axis of the arm pivot shaft  48 . Bearings in the pivot arm  66  support the rotatable member shaft  60 , thereby allowing it to rotate about its axial centerline. The rotatable member  70  is firmly attached to the rotatable member shaft  60  and rotates in unison with it. So configured, the pivot arm  66  is rotatably secured to the first pivot arm link  98  and the chassis  2 , which at least partially supports the apparatus; the first pivot arm link  98  is rotatably secured to the center pivot block  100  and a second pivot arm link  92 ; and the spring guide assembly  107  and the second pivot arm link  92  are rotatably secured to the chassis  2  such that the compressed spring  110  biases the pivot arm  66  toward the media conveyance path  9 . 
         [0040]    Accordingly, when compressed, the spring  110  exerts a force on the center pivot block  100  in the direction of the spring axial centerline. The center pivot block  100  transfers this force to the pivot pin  104 , which in turn transfers the force to the pivot arm links  92  and  98 . The first pivot arm link  98  transfers the force of the spring  110  to the pivot pin  94 , which in turn creates a rotational moment on the pivot arm  66  about the centerline of the arm pivot shaft  48 . The rotational force moment of the pivot arm  66  applies a vector summed force in the general direction of force arrow  120 . This vector summed force  120  is transferred from the pivot arm  66  to the rotatable member shaft  60 , which applies this same force to the rotatable member  70 . The ground link  92  provides the required opposing force on the pivot pin  104  to keep the mechanism in a stable condition. 
         [0041]    Other configurations of this mechanism are possible to meet other conditions. For example, if one were to reduce the spring rate of the spring  110 , then the pivot pin  94  may be moved farther away from the arm pivot shaft  48  to a location that would provide a larger moment arm to provide an equivalent rotational force moment on the pivot arm  66 . In another example, the pivot pin  82  may be moved away from the arm pivot shaft  48 . In this condition, the ground link  92  and/or the pivot arm link  98  may be made longer, and the location of the pivot pin  88  may be moved (or some combination of all three) to obtain a necessary rotational torque on the pivot arm  66  for a given application. One could also keep the location of the arm pivot shaft  48  fixed and change the relative locations or lengths of the rotatable member shaft  60 , pivot pin  82 , pivot pin  88 , pivot pin  94 , pivot pin  104 , ground link  92 , or pivot arm link  98  to produce a wide variety of mechanism operating conditions. Accordingly, the mechanism can be configured to optimize its performance for the media to be deformed. 
         [0042]    With reference to  FIG. 6 , two biasing systems are shown that in all aspects are identical in size and configuration and are mirrored about line  72 . The biasing systems&#39; configurations and sizes can be different to tailor the mechanism to a specific operating condition. Compression springs  110  are axially aligned with and freely slide over the spring guides  108 . Spring retainers  112  in part provide a means for both preloading and constraining the compression springs  110  in place. Each spring retainer  112  contains an internal clearance hole slightly larger in diameter than the threaded portions  114  at the end of the spring guides  108 . Adjustment nuts  116  thread onto the threaded portions  114  and contact the sides of spring retainers  112  to compress and preload the compression springs  110 . The distance that the adjustment nut  116  is threaded onto the threaded portion  114  directly affects to the amount of force that the rotatable members  70  and  71  apply to the magnetic storage medium  1 . In the illustrated example, a 5 inch (12.7 cm) long free length spring is compressed ¾ inch (1.9 cm) through the adjustment of the adjustment nut  116  to reach a predetermined preload force. Other spring diameters and lengths may be used. After the adjustment nuts  116  preload the compression springs  110  to the desired condition, lock nuts  118  are threaded onto the threaded portions  114  and tightened against the adjustment nuts  116 . 
         [0043]    The forces generated by the compression springs  110  are transferred through the linkages and produce counter rotational moments of the pivot arms  66  and  67  about the pivot arm shafts  48  and  49  respectively. The bearings  80  are pressed into the pivot arms  66  and  67 , and slide over the pivot arm shafts  48  and  49 , which constrain the pivot arms  66  and  67  to rotation only. The media passageway top surface  5  and media passageway bottom surface  7  limit the rotational motion in the pivot arms  66  and  67  respectfully. Accordingly, the compression springs  110  are compressed to a predetermined preload value to ensure that an ordinary hard drive or other magnetic storage media will be punctured as a result of the force with which the punch points  78  engage the media. 
         [0044]    So configured, the deforming apparatus may operate according to the following example method. A medium  1  is accepted into the media conveyance path  9  wherein the medium  9  is engaged by a plurality of deforming members, such as punch points  98 , rotating on at least one rotating member  70 . The apparatus applies a deforming force to the medium  1  through the deforming members via the biasing system  10 . The apparatus allows movement of at least one of the rotating members  70  away from the medium  1  when the deforming members engage the medium and encounter an engaging force higher than the deforming force. By one approach, the biasing system  10  includes an adjustable compressed spring guide assembly  107  such that the deforming force is adjustable for a user. 
         [0045]    Referring to  FIG. 7 , the ability to move the rotating member  70  away from the medium  1  will be described. For example, a dense and incompressible object  122  may be placed into the media conveyance path  9  and brought into contact with the punch points  78  of the rotatable members  70  and  71 . When the object  122  provides an opposing reaction force greater than the puncturing force of the punch points  78 , the pivot arms  66  and  67  will rotate to positions where compression springs  110  produce a higher net reaction force and the opposing reaction forces between the object  122  and the rotatable members  70  and  71  reach a state of equilibrium. In practice, the springs  110  can be differentially preloaded to approximately compensate for the weight of the mechanism plus that expected for the medium  1 , for example, through an extra partial turn tightening the lower of adjustment nuts  116 . In practice, the frictional force of the punch points  78  acting on a typical abusive object  122  combined with the torque imparted to either of the rotatable members  70  or  71  through the drive train will overcome the friction between the object  122  and the top surface  5  or the bottom surface  7  to eject the object  122  and avoid a jam. 
         [0046]    So configured, jam conditions that may occur should the pivot arms  66  and  67  be fixed and not able to move away from the object  122 , thereby potentially overloading the electric motor  20 , may be avoided. A motor stall caused by a component failure is still possible, and therefore, conventional overload protection may still be provided for the motor. 
         [0047]    By another approach, the biasing system  10  may utilize other types of springs to bias the pivot arm  66 . For example, and with reference to  FIG. 8 , an extension spring  150  may be operatively connected to the pivot arm  66  at a first point  152  and to the chassis  2  and/or the media passageway top surface  5  at a second point  154 . If the distance between the connection points  152  and  154  is longer than the natural free length of the spring  150 , then the spring  150  can be elongated to attach it and create a spring preload condition to produce a counterclockwise moment in pivot arm  66 . This rotational torque in pivot arm  66  causes the rotatable member  70  to produce a force in the direction of arrow  120  that will puncture a hard drive beneath it. Other spring types such as torsion springs or leaf springs could also be used. 
         [0048]    By yet another approach, the biasing system may use mechanical energy storage devices other than springs such as a hydraulic system. With reference to  FIG. 9 , an example hydraulic system will be described. The example hydraulic system includes a tank  126  containing a fluid in a volume  134  such that the pressure of the fluid is adjustable, and wherein the tank  126  is in fluid communication with a piston  139  operatively secured to a pivot block  100 . The pivot block  100  is rotatably secured to a first pivot arm link  98  and a second pivot arm link  92 . The second pivot arm link  92  is rotatably secured to the chassis  2 , and the first pivot arm link  98  is rotatably connected to the pivot arm  66  such that the hydraulic system biases the pivot arm  66  toward the media conveyance path  9 . 
         [0049]    One way to control the fluid pressure is through use of an inlet valve  128  allows a compressible pneumatic gas such as air, nitrogen, or other suitable gas to be pumped under pressure into a volume  130  and held there without escaping from the tank  126 . A second volume  134  is filled with the non-compressible hydraulic fluid that extends through a pipe  136  and into a cylinder  138  enclosing the piston  139 . The cylinder  138  is rotatably connected to a secure structure such as the chassis  2  via a pivot pin  140 . The piston  139  is confined to linear travel within a volume defined by cylinder  138  at one end and at the other end to the center pivot block  100  via pivot pin  142 . The tank  126  can take on many different forms. The compressible gas in the volume  130 , when placed under pressure, will transfer that same pressure through a flexible bladder  132  and to the non-compressible fluid in volume  134 . The fluid in the volume  134  will then be pushed through the pipe  136  into the cylinder  138  and against the piston  139  causing a force on the center pivot block  100  in the direction of the arrow  120 . Alternatively, the pressure of the fluid in volume  134  may be controlled by any known means. This same force will be transmitted through the pivot pin  104 , pivot arm link  98 , and pivot pin  94  to the pivot arm  66 . This force will cause a counterclockwise moment on the pivot arm  66  about the pivot arm shaft  48  thereby rotating the pivot arm  66  until it comes into contact with media passageway top surface  5 . The moment on the pivot arm  66  will induce a force on the rotatable member shaft  60  in the direction of the arrow  120 . The rotatable member  70  is soundly attached to rotatable member shaft  60  and receives this same force and transmits it to the magnetic storage medium  1  during operation. 
         [0050]    By another approach, a pneumatic system may be used as a biasing system whereby the pneumatic gas in the volume  130  works directly against the cylinder  138  to bias the pivot arm  66 . Other hydraulic and pneumatic components that one skilled in the art would include in such a commercial system are not illustrated or described here. It is also possible to use some combination of springs, hydraulic fluids, or pneumatic gases for the biasing systems. Other example means of energy storage or potential that may be incorporated into the biasing systems include heavy weights, lever arms, and various types of motors or other apparatuses that are able to store mechanical or electrical energy. 
         [0051]    Movement of the pivot arm  66  away from and then quickly toward the media passageway top surface  5  during the passage of material through the media conveyance path may cause undesired vibration and noise. The vibration and noise, however, can be reduced with the implementation of a shock absorbing device. For example, a shock absorber  144  of a common hydraulic shock absorbing type is operatively connected to the pivot arm  66  at a first point  146  and to the chassis  2  through the media passageway top surface  5  at a second point  148 . During an overload operating condition, the pivot arm  66  will move away from the media passageway top surface  5 . After the overload operating condition has passed, the pivot arm  66  will begin to rotate in a counterclockwise direction. If the size and load ratings of the shock absorber  144  are matched to the biasing system, the shock absorber  144  can reduce the angular velocity of the pivot arm  66  to a desired value. The shock absorber  144  can come in many different forms such as hydraulic, hydraulic/spring combinations, metal spring, air spring, open and closed cell foam, rubber, or any other form of a semi-elastic material. 
         [0052]    Various configurations of deforming members or punch points will be described with reference to  FIGS. 10-14 .  FIG. 10  illustrates an example configuration where the distance between the rotatable members  70  and  71  is such that the punch points  78  will produce a clearance spacing  160  between opposing punch points of about 1/16 inch (0.159 cm).  FIG. 11  illustrates another example configuration of an overlapping condition of intentionally misaligned punch points  79 . The punch points  79  on the circumferences of rotatable members  70  and  71  in  FIG. 11  are elongated to produce a punch point overlap  162 . Embodiments with rotatable members intentionally staggered transversely across the media conveyance path are possible whether or not the points overlap. 
         [0053]      FIG. 12  illustrates an example punch point configuration. The deforming members typically have a generally tapering tip. In this example, a rotatable member body  164  has a pyramid shaped punch point  78  securely attached to it. This pyramid shaped region may be machined into the body of the rotatable member  164 . The cross-section line  166  indicates the view plane of the section view of punch point punch sides  168  and  170 . The punch point sides  168  and  170  can form a square cross-section at all cutting planes along the height of the pyramid shape region, creating edges that concentrate the punch forces and promote deeper punctures. This configuration of the deforming members can provide a good operational lifetime when composed of heat treated, mildly hard steel. By other approaches, the punch point cross-section need not be square with sides parallel and orthogonal to the media direction. For example, the cross-section may be rhomboidal to promote cutting with two acute edges and spreading with two obtuse edges parallel and orthogonal to the media direction. 
         [0054]      FIG. 13  illustrates an example punch point configuration with unequal side lengths. The rotatable member body  172  in this example contains punch points  173  that have sides of unequal length. The punch point  173  may be machined into the rotatable member body  172  to provide a firm connection between them. The cross-section line  174  indicates the view plane of the section view of punch point sides  175 ,  177 ,  178 , and  179 . The punch point sides  177  and  179  may be of approximately equal lengths, and differ from sides  175  and  178  that are themselves of approximately equal lengths, thereby providing a rectangular cross-sectional shape. By another approach, a reduced cross-sectional area may be used with sides  175 ,  177 ,  178 , and  179  all of unequal lengths. Preferably, the dimension encountering a stronger load in pushing the medium  1  through the media conveyance path  9  is the longer dimension. So configured, the unequal sides can provide an increased bending strength to the punch points in a desired direction and increase punch point life. In certain approaches, certain sides  176  of the punch points  173  can have the form of a concave (as shown in  FIG. 13 ), convex, planar, or other predetermined surface shape that can alter the profile to affect cutting action or strength as desired. The cross-sectional profile may alternatively be a three sided wedge shape or a five or more sided object. 
         [0055]      FIG. 14  illustrates an example punch point configuration with a circular cross-section  188  that can be replaced if wear or damage has occurred. For example, carbide punch points that are resistant to wear are also subject to breakage when encountering certain shape and hardness features as may occasionally occur in magnetic storage media. In this example, the rotatable member  180  contains threaded holes  183  that extend from the outer circumference into the rotatable member body  180 . The punch point  182  has a male threaded base  184  that extends from the punch body, for example a stud bonded to carbide. The threaded base  184  may then threadingly engage the rotatable member  180  at the threaded holes  183 . The cross-section line  186  indicates the view plane of the punch point  182  with a circular cross-sectional shape and conical profile. The base of the conical punch point  182  can be provided with flats to facilitate the loosening and tightening of the punch point  182  in the rotatable number  180 . Accordingly, the deforming members can be removably secured to the rotatable member. 
         [0056]    By another approach, deforming apparatuses may include only one biasing system and set of rotatable members as illustrated in  FIGS. 15 and 16 .  FIG. 15  illustrates a one-sided configuration with a solid bottom surface  190 . The embodiment requires only one rotatable member assembly and its related mechanical energy storage components, power transmission drive assembly and related support members. In that configuration, the torque imparted to the rotatable member  70  must overcome the frictional force between the medium  1  and bottom surface  190  as a result of the punch force exerted on medium  1 . 
         [0057]      FIG. 16  illustrates a one-sided configuration wherein the media conveyance path  9  includes at least one roller  198  to reduce the friction of the media passing through the device. The media passage bottom surface  194  in one such configuration is attached to the media passageway side surface  6 . A series of low friction rollers  198  are placed in the media passageway bottom surface  194 . The roller axels  196  are secured at each end to media passageway side surfaces  6  and  11 . The roller axels  196  support the rollers  198  in a manner that allows them to freely rotate about their center axes. The bottom surface  194  may be contoured to facilitate the transfer of media onto rollers  198 . The total number of rollers  198  required for each assembly and outside diameter of the roller is dependent on the size and type of magnetic storage media desired to be processed. If, for example, the mechanism were designed to process 1.8 inch (4.57 cm) format hard drive or smaller, then the total number of rollers  198  could be reduced and the outside diameter of the rollers may be ½ inch (1.27 cm) or less. It may also be desired when processing small media sizes to elongate the punch points  78  on the outer periphery of rotatable member  70  to produce a minimal clearance  192  between the tips of punch points  78  and the roller  198 . 
         [0058]    So configured, the deforming apparatus may be tailored to rapidly mark and/or destroy magnetic storage media of various sizes. The retractable pivot arm lessens the probability of jams, and the deforming members can mark a variety of media form factors. 
         [0059]    Those skilled in the art will recognize that a wide variety of modifications, alterations, and combinations can be made with respect to the above described embodiments without departing from the spirit and scope of the invention, and that such modifications, alterations, and combinations are to be viewed as being within the ambit of the inventive concept.