PATENT DOCUMENT

Publication Number: US-7349203-B2
Application Number: US-52393106-A
Country: US
Kind Code: B2

Title: Computer controlled display device

Abstract:
The present invention is a computer controlled display device. In one embodiment, the display device includes a flat panel display having an input for receiving display data. Additionally, a moveable assembly may be coupled to the display. The moveable assembly may provide at least three degrees of freedom of movement for the flat panel display device. Additionally, the moveable assembly may have a cross-sectional area, which is substantially less than a cross-sectional area of a display structure of the flat panel display. Additionally, the moveable assembly may include a plurality of stacked ball-and-socket assemblies.

Claims:
1. A computer controlled display system, comprising:
 a flat panel display having a display surface and an input for receiving display data to be displayed on said display surface; 
 a moveable assembly coupled mechanically to said flat panel display, said moveable assembly having a cross-sectional area which is substantially less than an area of said display surface, said moveable assembly being moveable to allow said flat panel display to be selectively positioned in space relative to a user of said computer controlled display system; and 
 a base coupled mechanically to said moveable assembly and to said flat panel display through said moveable assembly, said base housing computer components comprising a microprocessor, a memory, a bus, an I/O (input/output) controller, and an I/O port, wherein said microprocessor is coupled to said input of said flat panel display said base houses computer components further comprising an optical drive and a network interface and wherein said cross-sectional area is defined by a cross-section taken perpendicularly to a longitudinal dimension of the moveable assembly, an actuator attached to said flat panel display and coupled to a force generator which maintains said moveable assembly in a rigid mode when said actuator is in a first state and which allows said moveable assembly to be moveable when said actuator is in a second state, wherein moving said actuator from a first state to a second state converts potential energy stored in a tensioned cable and in a plurality of compressed resilient members and mechanical energy provided by a user into elastic potential energy stored in a compressed spring/piston assembly, and wherein moving said actuator from a second state to a first state transfers a portion of the elastic potential energy stored in a compressed spring/piston assembly into elastic potential energy stored in a tensioned tension cable and in a plurality of resilient members, and converts the remaining stored elastic potential energy to work and to kinetic energy of the actuator. 
 
   
   
     2. A system as in  claim 1  wherein said moveable assembly is moveable such that said flat panel display has at least three degrees of freedom of movement. 
   
   
     3. A system as in  claim 1  wherein said system is moveable as a unit by one person unaided by any assistance. 
   
   
     4. A system as in  claim 3  wherein a weight of said system is less than about 40 lbs and a footprint size of said base is less than about four (4) square feet. 
   
   
     5. A system as in  claim 1  wherein said force generator is a mechanism which may be electronically or electromagnetically activated to change said first and second states of said moveable assembly. 
   
   
     6. A system as in  claim 1  wherein said actuator, through a single actuation of said actuator, allows simultaneous positioning in multiple degrees of freedom (of said flat panel display). 
   
   
     7. A system as in  claim 1 , further comprising:
 a data cable coupled to said input of said flat panel display at a first end of said data cable and coupled to a display controller housed within said base, said data cable being disposed within said moveable assembly. 
 
   
   
     8. A system as in  claim 7  wherein said data cable is concealed within said moveable assembly. 
   
   
     9. A system as in  claim 1 , further comprising:
 an anti-torsion cable coupled to said moveable assembly, said anti-torsion cable restraining said flat panel display from being rotated beyond a pre-determined amount. 
 
   
   
     10. A system as in  claim 1  wherein said longitudinal dimension of the moveable assembly extends from said flat panel display to said base and wherein a weight of said system is less than about 25 lbs and a footprint size of said base is less than an area of about 500 square centimeters. 
   
   
     11. A system as in  claim 10  wherein said base is not fixedly secured to a supporting surface under said base. 
   
   
     12. A system as in  claim 1  wherein said moveable assembly stores potential energy in a tensioned tension cable and in a plurality of compressed resilient members when said actuator is in a first state. 
   
   
     13. A system as in  claim 1  wherein said actuator stores potential energy in a compressed spring/piston assembly when said actuator is in a second state. 
   
   
     14. A method, comprising:
 storing a first potential energy in a tension cable extending through a longitudinal interior portion of a moveable assembly having a first end attached mechanically to a flat panel display and a second end attached to a moveable base, said moveable assembly having a plurality of moveable portions; 
 storing a second potential energy in a plurality of resilient members corresponding to said plurality of moveable portions, wherein said resilient members are compressible and coupled with said plurality of moveable portions; 
 combining a portion of said first potential energy and a portion of said second stored potential energies with an applied mechanical work; 
 converting a portion of said stored energy and work to an elastic potential energy; and 
 storing said elastic potential energy in a force generator which maintains said moveable assembly in a rigid mode when said force generator is in a first state and which allows said moveable assembly to be moveable when said force generator is in a second state wherein combining a portion of said first potential energy and a portion of said second potential energy, further comprises moving an actuator attached to said flat panel display from a first actuator state which maintains said moveable assembly in rigid mode to a second actuator state which allows said moveable assembly to be moveable. 
 
   
   
     15. The method of  claim 14  wherein said force generator is a spring assembly. 
   
   
     16. The method of  claim 14  wherein said force generator is a piston assembly. 
   
   
     17. The method of  claim 14  comprising:
 transferring a portion of an elastic potential energy stored in a force generator which maintains said moveable assembly in a rigid mode when said force generator is in a first state and which allows said moveable assembly to be moveable when said force generator is in a second state into a first potential energy and a second potential energy; 
 storing said first potential energy in a tension cable extending through a longitudinal interior portion of a moveable assembly having a first end attached mechanically to a flat panel display and a second end attached to a moveable base, said moveable assembly having a plurality of moveable portions; and 
 storing a second potential energy in a plurality of resilient members corresponding to said plurality of moveable portions, wherein said resilient members are compressible and coupled with said plurality of moveable portions. 
 
   
   
     18. The method of  claim 17  wherein transferring a portion of the elastic potential energy stored in a force generator, further comprises:
 moving an actuator attached to said flat panel display from a second actuator state which allows said moveable assembly to be moveable to a first actuator state which maintains said moveable assembly in a rigid mode. 
 
   
   
     19. The method of  claim 18  wherein said force generator is a spring assembly. 
   
   
     20. The method of  claim 18  wherein said force generator is a piston assembly. 
   
   
     21. A computer controlled display system, comprising:
 a flat panel display having a display surface and an input for receiving display data to be displayed on said display surface; 
 a moveable assembly coupled mechanically to said flat panel display, said moveable assembly having a cross-sectional area which is substantially less than an area of said display surface, said moveable assembly being moveable to allow said flat panel display to be selectively positioned in space relative to a user of said computer controlled display system; 
 a base coupled mechanically to said moveable assembly and to said flat panel display through said moveable assembly, said base housing computer components comprising a microprocessor, a memory, a bus, an I/O (input/output) controller, and an I/O port, wherein said microprocessor is coupled to said input of said flat panel display and further comprising a data cable coupled to said input of said flat panel display at a first end of said data cable and coupled to a display controller housed within said base, said data cable being disposed within said moveable assembly; 
 a holder device coupled with said moveable assembly, said holder device having an energy stored therein; and 
 an actuator coupled to said holder device, said actuator to change a state of said moveable assembly to permit movement of said moveable assembly, wherein said actuator is assisted in said change of state by said energy stored in said holder device. 
 
   
   
     22. The system of  claim 21  wherein said energy reduces an amount of user force needed to change said state of said moveable assembly. 
   
   
     23. The system of  claim 21  wherein said actuator is attached to said flat panel display and wherein said actuator, through a single actuation of said actuator, allows simultaneous positioning in multiple degrees of freedom (of said flat panel display). 
   
   
     24. A system as in  claim 21  wherein said base houses computer components further comprising an optical drive and a network interface, and wherein said cross-sectional area is defined by a cross-section taken perpendicularly to a longitudinal dimension of the moveable assembly. 
   
   
     25. A system as in  claim 21  wherein said system is moveable as a unit by one person unaided by any assistance. 
   
   
     26. A system as in  claim 21  wherein a weight of said system is less than about 40 lbs and a footprint size of said base is less than about four (4) square feet. 
   
   
     27. A system as in  claim 21  wherein said data cable is concealed within said moveable assembly. 
   
   
     28. A system as in  claim 21 , further comprising:
 an anti-torsion cable coupled to said moveable assembly, said anti-torsion cable restraining said flat panel display from being rotated beyond a pre-determined amount. 
 
   
   
     29. A system as in  claim 21  wherein said longitudinal dimension of the moveable assembly extends from said flat panel display to said base and wherein a weight of said system is less than about 25 lbs and a footprint size of said base is less than an area of about 500 square centimeters. 
   
   
     30. A system as in  claim 21  wherein said base is not fixedly secured to a supporting surface under said base.

Description:
This application is a divisional of U.S. patent application Ser. No. 10/973,923, filed on Oct. 25, 2004, now U.S. Pat. No. 7,136,280, which is a divisional of U.S. patent application Ser. No. 10/035,417, filed Nov. 8, 2001, now issued as U.S. Pat. No. 6,819,550. 

   FIELD OF THE INVENTION 
   The field of the invention relates to computers and data processing systems, and more particularly to support mechanisms for supporting display devices for computers or data processing systems. 
   BACKGROUND OF THE INVENTION 
   The advent of flat panel display devices has revolutionized the architecture and aesthetic appearance of computers. Lightweight and versatile, flat panel display devices (FPDDs) may be mounted almost anywhere. A variety of mechanical support devices have been designed to hold FPDDs in suitable viewing positions. 
   Many FPDDs are supported by rigid assemblies or mechanisms which may be affixed to furniture, walls, or ceilings. Recently, semi-moveable support devices (e.g. swing arm devices) have made their debut. Such devices are typically hinged in one or more places, and their display ends may be equipped with swivel joints. Though offering a greater number of viewing positions, semi-moveable support devices often prove difficult to adjust, and routing data and power cables along exterior portions of the devices can mar aesthetic appearances. 
   In many semi-moveable support devices, two hands are required to adjust the display&#39;s viewing position. Typically, one hand supports the FPDD while the other manipulates a locking device on a hinged joint. Twist-and-lock swivel joints have a knob or handle which may be rotated in one direction to increase the holding friction, or in the opposite direction to decrease holding friction. Increasing the holding friction locks the support device in a desired position. Similarly, decreasing the holding friction allows the swivel joint to move freely through a predetermined range of movement. 
   Twist-and-lock swivel joints are effective, but awkward to use, and difficult to break free if overtightened. On the other hand, if undertightened, twist-and-lock swivel joints will allow a supported FPDD to sag and droop. Moreover, it is not uncommon for a semi-moveable support device to have a plurality of twist-and-lock swivel joints, which makes it virtually impossible for a single user to tighten or loosen all the joints simultaneously. With a plurality of swivel joints, adjustment times are considerably lengthened because the swivel joints must be adjusted individually. 
   A swivel ball joint (e.g. gimbal) affixed to the display end of the arm mechanism allows a supported FPDD to be tilted or angled as desired. Because the holding friction exerted by the swivel ball joint is more or less constant, the user force needed to tilt the FPDD sometimes dislodges the support arm mechanism from its fixed position. Set screws may be provided to adjust a swivel joint&#39;s applied holding friction. However, one shortcoming of swivel joints equipped with set screws is that movement of the joints often feels rough, gritty, or ratchety. 
   Referring now to  FIG. 1A , there is shown a set of pictures illustrating exemplary environments in which support mechanisms for flat panel display devices (FPDDs) may be used. As shown in picture  110 , flat screen monitor arms are used in offices, schools, universities, government agencies, and other environments to provide adjustable support and correct length between the display and the viewer. As shown in picture  111 , additional mounting solutions may be provided to incorporate FPDDs into corporate environments such as banks, financial institutions, trade and brokerage companies, and similar businesses. 
     FIG. 1B  illustrates two further pictures illustrating additional environments in which FPDDs may be used. Picture  112  shows that FPDDs may be used in industrial areas such as manufacturing facilities, production lines, and assembly lines. Picture  113  represents the use of flat panel display devices in hospitals, health care facilities, and medical centers. In each case, the FPDD is attached to a moveable support device that is fixedly attached to a large, heavy object, such as the wall or floor of a building. 
     FIG. 1C  is a diagram of a prior art moveable support device  100 . Moveable support device  100  may be attached to a horizontal planar surface, such as a desktop, using clamp  106 , which adjusts to accommodate different thicknesses of various support surfaces. The base of moveable support device  100  includes a housing  105 , which is a removeable cosmetic covering that conceals a hollow screw mechanism used to affix clamp  106  to a support surface. The base of moveable support device  100  includes a cylindrical steel rod that removably slides within the hollow screw mechanism described above. In the embodiment shown, an arc of vertical movement measuring approximately 72.5 degrees may be provided by turn and lock swivel joint  103 . Similarly, a second arc of vertical movement measuring approximately 115.0 degrees may be provided by turn and lock swivel joint  107 . 
   Moveable support device  100  is made up of three arm members  101 ,  102 , and  117 , connected to each other by two twist and lock swivel joints  107  and  103 . A ball swivel joint (e.g. gimbal)  108  attached to the display end of arm member  101  provides a supported FPDD  109  with an arc of movement, measuring in one dimension, approximately 78.0 degrees. The weight of the supported FPDD  109  is counterbalanced using an internal spring and pulley mechanism (not shown). Cables  120  and  121 , which provide power and data, respectively, to FPDD  109 , are attached to the exterior of moveable support device  100  using a plurality of retention guides  123 . The various components of moveable support device  100  are manufactured from various materials, including, but not limited to: metals, plastics, and composite materials. 
     FIG. 1D  is a diagram illustrating a prior art gooseneck lamp  118 . However, the inclusion of this lamp is not to be construed as an admission that lamps are analogous art to the present invention. Typically, components of lamp  118  include a weighted or magnetic base  116 , a hollow, moveable assembly portion  115 , and a bulb housing  114 . An electrical wire may run inside or outside the neck portion  115 . Typically, the weight of bulb housing  114  is negligible compared to the weight of the base  116  and of the neck portion  115  itself. Otherwise, neck portion  115  would droop, or lamp  118  would topple over. 
   In most cases, neck portion  115  is manufactured of a jointed, spiral-cut metal skin that is easily flexed into one of a number of desired positions. A plurality of plastic or metal ball-and-socket assemblies may be used to form neck portion  115 . Where ball-and-socket assemblies are used, the holding force may be provided by a tension cable running through the ball-and-socket assemblies that loops about a cam attached to a twist-lever disposed on or near the base  116 . Twisting the twist-lever in one direction stretches the cable and stiffens neck portion  115 . Twisting the twist-lever in the opposite direction relaxes the cable, thereby dissolving the holding force, and allowing the neck portion  115  to collapse. 
   The ball-and-socket assemblies may be formed of either metal or plastic, but metal is typically used because it is stronger and more durable than plastic. A problem with prior art ball-and-socket assemblies is that the friction provided by a metal ball mating with a metal socket will not sustain heavy loads. While capable of supporting a lightbulb or other small lightweight object, prior art ball-and-socket assemblies are simply incapable of supporting large heavy objects, such as FPDDs, which typically weigh in excess of two pounds. 
   SUMMARY OF THE DESCRIPTION 
   The present invention is a computer controlled display device. In one embodiment, the display device includes a flat panel display having an input for receiving display data. Additionally, a moveable assembly may be coupled to the display. The moveable assembly may provide at least three degrees of freedom of movement for the flat panel display device. Additionally, the moveable assembly may have a cross-sectional area, which is substantially less than a cross-sectional area of a display structure of the flat panel display. Additionally, the moveable assembly may include a plurality of stacked ball-and-socket assemblies. Other embodiments and aspects of the invention are described below. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The present invention is illustrated by way of example and not limitation in the figures of the accompanying drawings in which like references indicate similar elements. 
       FIG. 1A  is a diagram illustrating a moveable support device, common in the prior art, and used to support a computer display in a home or office environment, or in a corporate environment. 
       FIG. 1B  is a diagram illustrating a prior art wall mounted support device for displaying computer displays in a manufacturing or industrial environment, or in a medical environment. 
       FIG. 1C  is a diagram illustrating a side view of the prior art moveable support device  110  shown in  FIG. 1A . 
       FIG. 1D  is a diagram illustrating a side view of a prior art gooseneck lamp. 
       FIG. 1E  is a diagram of a conventional computer system which may be used with a moveable support device and flat panel display device (FPDD), according to one embodiment of the present invention. 
       FIG. 2A  is a cut-away, perspective view of a moveable assembly and actuator assembly for supporting a FPDD, according to one embodiment of the invention. 
       FIG. 2B  is a rear view of the actuator assembly and moveable assembly shown in  FIG. 2A  (without the base), according to one embodiment of the invention. 
       FIG. 2C  is a plan view of the actuator assembly and moveable assembly shown in  FIG. 2A  (without the base), according to one embodiment of the present invention. 
       FIG. 2D  is a side view of the actuator assembly and moveable assembly shown in  FIG. 2A  (without the base), according to one embodiment of the present invention. 
       FIG. 3  is a diagram illustrating the overturning moments of a computer display coupled with a moveable assembly and a base, according to one embodiment of the invention. 
       FIG. 4A  is a diagram illustrating a sectional side view of the actuator assembly and moveable assembly, according to another embodiment of the invention. 
       FIG. 4B  is an exploded side view of a portion of a moveable assembly in a relaxed state, according to one embodiment of the invention. 
       FIG. 5A  is a diagram illustrating a moveable assembly  500 , according to one embodiment of the invention. 
       FIG. 5B  and  FIG. 5C  are perspective views of the moveable assembly  500  shown in  FIG. 5A . 
       FIG. 5D  is a sectional view of one embodiment of a moveable assembly  500  showing the internal placement of a tension cable  590 . 
       FIG. 5E  is a cross-sectional view of a portion  560  of a moveable assembly usable with an embodiment of the present invention showing the placement of data, tension, torsion, power, antenna, and other computer system related cables within one or more apertures of the moveable assembly. 
       FIG. 6  is a perspective, exploded view of an actuator assembly and moveable assembly, according to one aspect of the present invention. 
       FIG. 7A  is a sectional side view of an actuator assembly in a first tensioned position, according to one embodiment of the present invention. 
       FIG. 7B  is a sectional side view of an actuator assembly in a second untensioned position, according to one embodiment of the present invention. 
       FIG. 8  is an exploded perspective view of an actuator assembly, according to one embodiment of the present invention. 
       FIG. 9A  is a perspective view of an actuator housing, according to one embodiment of the present invention. 
       FIG. 9B  is another view of the actuator housing of  FIG. 9A , according to one embodiment of the present invention. 
       FIG. 9C  is a plan view of the actuator housing of  FIG. 9A , according to one embodiment of the present invention. 
       FIG. 9D  is a cross-sectional view of the actuator housing of  FIG. 9A  taken along the lines A-A in  FIG. 9C , according to one embodiment of the present invention. 
       FIG. 9E  is a cross-sectional view of the actuator housing of  FIG. 9A  taken along the line B-B in  FIG. 9C , according to one embodiment of the present invention. 
       FIG. 10A  is a perspective view of a crank, according to one embodiment of the present invention. 
       FIG. 10B  is a plan view of the crank of  FIG. 10A , according to one embodiment of the present invention. 
       FIG. 10C  is a side view of the crank of  FIG. 1A , according to one embodiment of the present invention. 
       FIG. 10D  is a bottom view of the crank of  FIG. 1A , according to one embodiment of the present invention. 
       FIG. 11A  is a perspective view of a tongue, according to one embodiment of the present invention. 
       FIG. 11B  is a cross-sectional view of a tongue of  FIG. 11A , according to one embodiment of the present invention. 
       FIG. 11C  is a top view of a tongue of  FIG. 11A , according to one embodiment of the present invention. 
       FIG. 11D  is an end view of a tongue of  FIG. 11A , according to one embodiment of the present invention. 
       FIG. 12A  is a perspective view of a spring shaft, according to one embodiment of the present invention. 
       FIG. 12B  is a side view of the spring shaft of  FIG. 12A , according to one embodiment of the present invention. 
       FIG. 12C  is a sectional view of the spring shaft of  FIG. 12A  taken along the line A-A in  FIG. 12B , according to one embodiment of the present invention. 
       FIG. 12D  is an end view of the spring shaft of  FIG. 12A , according to one embodiment of the present invention. 
       FIG. 13A  is a perspective view of a strut, according to one embodiment of the present invention. 
       FIG. 13B  is a plan view of the strut of  FIG. 13A , according to one embodiment of the present invention. 
       FIG. 13C  is a sectional view of the strut of  FIG. 13A  taken along the line A-A in  FIG. 13B , according to one embodiment of the present invention. 
       FIG. 13D  is an end view of the strut of  FIG. 13A , according to one embodiment of the present invention. 
       FIG. 14A  is a perspective view of a shaft, according to one embodiment of the present invention. 
       FIG. 14B  is a side view of the shaft of  FIG. 14A , according to one embodiment of the present invention. 
       FIG. 15A  is a perspective view of a display termination socket, according to one embodiment of the present invention. 
       FIG. 15B  is a sectional view of the display termination socket of  FIG. 15A  taken along the line A-A in  FIG. 15C . 
       FIG. 15C  is a plan view of the display termination socket of  FIG. 15A  according to one embodiment of the present invention. 
       FIG. 16  is a diagram of a tension cable, according to one embodiment of the present invention. 
       FIG. 17A  is a perspective view of a friction limit socket, according to one embodiment of the present invention. 
       FIG. 17B  is a plan view of a friction limit socket of  FIG. 17A , according to one embodiment of the present invention. 
       FIG. 17C  is a sectional view of the friction limit socket of  FIG. 17A , according to one embodiment of the present invention. 
       FIG. 18A  is a perspective view of a limit ball, according to one embodiment of the present invention. 
       FIG. 18B  is a plan view of the limit ball of  FIG. 18A , according to one embodiment of the present invention. 
       FIG. 18C  is a sectional view of the limit ball of  FIG. 18A , according to one embodiment of the present invention. 
       FIG. 19A  is a perspective view of a friction socket assembly, according to one embodiment of the present invention. 
       FIG. 19B  is a perspective view of a first friction insert, according to one embodiment of the present invention. 
       FIG. 19C  is a sectional side view of the friction insert of  FIG. 19A  taken along the line A-A in  FIG. 19F . 
       FIG. 19D  is a top view of the friction insert of  FIG. 19A , according to one embodiment of the present invention. 
       FIG. 19E  is a side view of the friction insert of  FIG. 19A , according to one embodiment of the present invention. 
       FIG. 19F  is a bottom view of the friction insert of  FIG. 19A , according to one embodiment of the present invention. 
       FIG. 19G  is a perspective view of a second friction insert of  FIG. 19A , according to one embodiment of the present invention. 
       FIG. 19H  is a sectional side view of the friction insert of  FIG. 19G  taken along the line A-A in  FIG. 19K , according to one embodiment of the present invention. 
       FIG. 19I  is a top view of the friction insert of  FIG. 19G , according to one embodiment of the present invention. 
       FIG. 19J  is a side view of the friction insert of  FIG. 19G , according to one embodiment of the present invention. 
       FIG. 19K  is a bottom view of the friction insert of  FIG. 19G , according to one embodiment of the present invention. 
       FIG. 20  is a cross-sectional view of a friction assembly, according to one embodiment of the present invention. 
       FIG. 21A  is a perspective view of a base termination ball, according to one embodiment of the present invention. 
       FIG. 21B  is a bottom view of the base termination ball of  FIG. 21A  according to one embodiment of the present invention. 
       FIG. 21C  is a sectional view of the base termination ball of  FIG. 21A  taken along the line A-A, according to one embodiment of the present invention. 
       FIGS. 22A-22C  are side views showing examples of moveable assemblies which incorporate aspects of the present invention. 
       FIG. 23A  is a perspective view of a computer system  2300  having a base  2305  and a moveable assembly  2304  that supports flat panel display device  2301 . 
       FIG. 23B  is a perspective view of another embodiment of a computer controlled display device including a FPDD  2301  coupled with a moveable assembly  2304 , which is coupled with a base  2305 . 
       FIG. 23C  is a side view of the computer system  2300  shown in  FIGS. 23A and 23B , according to one embodiment of the invention. 
       FIG. 23D  is a rear-view of the computer system  2300  shown in  FIGS. 23A-23C , according to one embodiment of the invention. 
       FIG. 23E  is a front view of the computer system  2300  of  FIGS. 23A-23D , according to one embodiment of the invention, and showing FPDD  2301 , viewing surface  2302 , and base  2305 . 
       FIG. 23F  is another side view of the computer system  2300  of  FIGS. 23A-23E , according to one embodiment of the invention, and showing FPDD  2301 , actuator assembly  2306 , moveable assembly  2304 , and base  2305 . 
       FIG. 23G  is a side view of another embodiment of a moveable assembly  2302  coupled with a FPDD  2310  and with an actuator assembly  2300 A, according to one embodiment of the invention. 
       FIG. 24A  is a perspective view of another embodiment of a tongue  2400 , according to one embodiment of the present invention. 
       FIG. 24B  is a cross-sectional view of a tongue of  FIG. 24A , according to one embodiment of the invention. 
       FIG. 24C  is a top view of a tongue of  FIG. 24A , according to one embodiment of the invention. 
       FIG. 24D  is an end view of a tongue of  FIG. 24A , according to one embodiment of the invention. 
       FIG. 25A  is a perspective view of a spherical glide bearing  2500 , according to one embodiment of the invention. 
       FIG. 25B  is a bottom view of a spherical glide bearing  2500  of  FIG. 25A , according to one embodiment of the invention. 
       FIG. 25C  is a side view of a spherical glide bearing of  FIG. 25A , according to one embodiment of the invention. 
       FIG. 25D  is a top view of a spherical glide bearing of  FIG. 25A , according to one embodiment of the invention. 
       FIG. 25E  is a sectional side view of a spherical glide bearing of  FIG. 25A , taken along the line A-A in  FIG. 25D . 
       FIG. 26A  is a perspective view of a socket glide bearing, according to one embodiment of the invention. 
       FIG. 26B  is a side view of a socket glide bearing, according to one embodiment of the invention. 
       FIG. 26C  is a plan view of a socket glide bearing of  FIG. 26A , according to one embodiment of the invention. 
       FIG. 26D  is a cross-sectional view of a socket glide bearing of  FIG. 26A  taken along the line A-A in  FIG. 26C , according to one embodiment of the invention. 
       FIG. 27A  is an exploded perspective view of a socket assembly  2700 , according to one embodiment of the invention. 
       FIG. 27B  is cross-sectional view of an assembled socket assembly of  FIG. 27A , according to one embodiment of the invention. 
       FIG. 28  is an exploded perspective view of an actuator assembly  2800 , according to one embodiment of the invention. 
       FIG. 29A  is a perspective view of a socket assembly  2900 , according to another embodiment of the invention. 
       FIG. 29B  is a cross-sectional view of a socket assembly  2900  of  FIG. 29A , according to one embodiment of the invention. 
       FIG. 29C  is a detailed view of area A circled in  FIG. 29B . 
       FIG. 30A  is a perspective view of a spring shaft assembly  3000 , according to one embodiment of the invention. 
       FIG. 30B  is a cross-sectional view of a spring shaft assembly  3000  of  FIG. 30A , according to one embodiment of the invention. 
       FIG. 31A  is a perspective view of a friction limit socket, according to another embodiment of the invention. 
       FIG. 31B  is a top view of a friction limit socket of  FIG. 31A , according to one embodiment of the invention. 
       FIG. 31C  is a cross-sectional view of a friction limit socket of  FIG. 31A , according to one embodiment of the invention. 
       FIG. 31D  is a detailed view of an area A circled in  FIG. 31C , according to one embodiment of the invention. 
       FIG. 32A  is a perspective view of a tension cable assembly  3200 , according to one embodiment of the invention. 
       FIG. 33A  is a perspective frontal view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to another embodiment of the invention. 
       FIG. 33B  is perspective rear view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to one embodiment of the invention. 
       FIG. 33C  is a side view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to one embodiment of the invention. 
       FIG. 33D  is a front view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to one embodiment of the invention. 
       FIG. 33E  is a rear view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to one embodiment of the invention. 
       FIG. 33F  is another side view of a computer system  3300  including a flat panel display  3310  and moveable base  3306  coupled with a moveable assembly  3302 , according to one embodiment of the invention. 
       FIG. 34  depicts a simplified sectional side view of a computer system  3400  usable with an embodiment of the present invention. 
       FIG. 35  is an exploded perspective view of one embodiment of the moveable assembly  3401  of  FIG. 34 . 
       FIG. 36  shows an exploded perspective view of one embodiment of a base rotation assembly  3600 , according to one embodiment of the invention. 
       FIG. 37  is an exploded perspective view of a display mounting assembly  3700 , according to one embodiment of the invention. 
       FIG. 38  is an exploded perspective view of a moveable assembly  3800 , according to one embodiment of the invention. 
       FIG. 39A  is an exploded, perspective view of one embodiment of a spring assembly  3900 , according to one embodiment of the invention, showing various internal component parts associated therewith. 
       FIG. 39B  is a perspective view of an assembled spring assembly  3900 , according to one embodiment of the invention. 
       FIG. 40  is a force diagram illustrating one embodiment of a computer system  4000  that includes a base  4030  attached to one end of a moveable assembly  4040  and a flat panel display device  4050  attached to the other end of the moveable assembly  4040 , in which a display weight  4010  is counterbalanced using a spring force  4020 . 
       FIG. 41  is a graph depicting illustrative counter-balance sum of moments for a moveable assembly, according to one embodiment of the invention. 
       FIG. 42  is a graph depicting illustrative counter-balance sum of moments with error bars for a moveable assembly, according to one embodiment of the invention. 
       FIG. 43A  depicts one embodiment of a counterbalance adjustment mechanism in a first position. 
       FIG. 43B  depicts one embodiment of a counterbalance adjustment mechanism in a second position. 
       FIG. 44  is a graph depicting counter-balance with manufacturing error bars after tuning for a moveable assembly, according to one embodiment of the invention. 
       FIG. 45  is a graph depicting the pitch counter-balance sum of moments for one embodiment of a moveable assembly. 
       FIG. 46  is a cross-sectional view of the moveable assembly  3401  of  FIG. 34 , showing placement of data, power, and other computer system-related cables therein, according to one embodiment of the invention. 
   

   DETAILED DESCRIPTION 
   An apparatus and method for supporting flat panel display devices is disclosed. Various embodiments and aspects of the inventions will be described with reference to details discussed below, and the accompanying drawings will illustrate the various embodiments. The following description and drawings are illustrative of the invention and are not to be construed as limiting the invention. Numerous specific details are described to provide a through understanding of various embodiments of the present invention. However, in certain instances, well-known or conventional details are not described in order to provide a concise discussion of embodiments of the present inventions. 
     FIG. 1E  depicts one embodiment of a conventional computer system that may be used with a display device as described herein. The computer system  151  interfaces to external systems through a modem or network interface  167 . It will be appreciated that the modem or network interface  167  may be considered part of computer system  151 . This interface  167  may be an analog modem, an ISDN modem, a cable modem, an Ethernet interface, a satellite transmission interface (e.g. Direct PC), or other network interface for coupling a digital processing system to other digital systems (e.g. the interface  167  couples computer system  151  to a local computer network or to the internet). 
   The computer system  151  includes a processor  153  which may be a conventional processor, such as a Motorola Power PC microprocessor or an Intel Pentium microprocessor. Memory  155  is coupled to processor  153  by the bus  157 . Memory  155  may be dynamic random access memory (DRAM) and may also include static RAM (SRAM). The bus  157  couples the processor  153  to the memory  155  and also to mass memory  163  and to display controller  159  and to the I/O (input/output) controller  165 . Display controller  159  controls in the conventional manner a display on the FPDD  161 , which may be a liquid crystal display device or other flat panel display device (e.g. organic light emitting diode display, vacuum fluorescent on silicon display, field emissive display, plasma display, etc.). The display controller  159  is coupled to the display  161  through a cable  160 , which in one embodiment provides display data and power and control signals between the display  161  and the display controller  159 . 
   The input/output devices  169  may include a keyboard, disk drives, printers, a scanner, a digital camera, and other input and output devices, including a mouse or other pointing device. The display controller  159  and the I/O controller  165  may be implemented with conventional well-known technology. The mass memory  163  is often a magnetic hard disk, an optical disk, or other form of storage for large amounts of data. Some of this data is often written, by a direct memory access process, into memory  155  during the execution of software in the computer system  151 . It will be appreciated that the computer system  151  is one example of many possible computer systems which have different architectures. For example, Macintosh or Wintel systems often have multiple buses, at least one of which may be considered to be a peripheral bus. 
   Network computers may also be considered to be a computer system which may be used with the various display devices described herein. Network computers may not include a hard disk or other mass storage, and the executable programs are loaded from a network connection (e.g. through network interface  167 ) into the memory  155  for execution by the processor  153 . A Web TV system, which is well-known in the art, may be considered to be a computer system according to the present invention, but it may not include certain features shown in  FIG. 2B , such as certain input/output devices. 
   A cell phone, a personal digital assistant, or a digital camera having a suitable display interface (to couple to a display device as described herein) and a processor and memory may also be considered to be a digital processing system or a computer system which may be used with the present invention. A typical computer system will usually include at least a processor, a memory, and a bus coupling the memory to the processor. It will also be appreciated that computer system  151  is typically controlled by an operating system software which includes a file management system and a disk operating system. 
   Referring again to  FIGS. 1E and 2A , in one embodiment of the invention, certain elements of the computer system  151  (e.g. processor  153 , memory  155 , bus  157 , mass memory  163 , display controller  159 , I/O controller  165 , an optical drive (not shown), and possibly also interface  167 ) are housed in a moveable enclosure  242 A which is coupled to the base  242  of the moveable assembly (shown in  FIGS. 2A-2D  as moveable assembly  200 ). The opposite end of the moveable assembly is coupled with a FPDD (e.g. display  240 , which corresponds to display  161 ). In this one embodiment, a cable is disposed within an interior portion of the moveable assembly  200  and couples the display  240  to the display controller  159 , which provides display data to the display  240  through the cable  160 . The cable may also provide power and the control signals (if any, such as brightness or contrast signals sent by an input device on the FPDD  240  to the system  151 ) to the FPDD  240 . 
   In the embodiment of  FIG. 2A , the moveable enclosure  242 A is small enough and light enough to be picked up and moved by a single adult person, and yet is heavy enough to support the FPDD  240  at various different positions without tipping. The moveable enclosure  242 A need not be physically attached (e.g. by clamps or adhesive or other fixtures) to a support surface (such as a desk, shelf, counter, or table) because its size, weight, and shape are sufficient to support the moveable assembly  200  and FPDD  240  at various positions without tipping. 
   It will be appreciated that the size, shape, and weight of moveable enclosure  242 A vary according to the length of the moveable assembly  200  and the weight and size of the FPDD to be supported. Illustratively, a FPDD  240  may measure approximately 6.0 inches or more, as measured diagonally across its viewing surface from one corner to an opposite corner, and may weigh approximately 1.5 pounds or more. 
   Regardless of the embodiment, the size, shape, and weight of moveable enclosure  242 A should be selected such that no tipping occurs when the moveable assembly  200  is bent approximately ninety degrees from vertical. Preferably, no tipping occurs when a downward user force of approximately 2.0 lbs to approximately 3.0 lbs is applied to FPDD  240  when moveable assembly  200  is bent approximately ninety degrees from vertical. 
   In one embodiment, the bottom surface area of moveable enclosure  242 A measures in the range of approximately 0.5 square feet to approximately 4.0 square feet. The system is designed to support a FPDD  240  weighing in the range of approximately 5.0 lbs to approximately 6.0 lbs, at approximately 25.0 lbs of user force. Illustratively, the length of the moveable assembly  200  may range from approximately 7.0 inches to approximately 48.0 inches. 
   In another embodiment, where moveable assembly  200  and/or display  240  are remotely (e.g. wirelessly or otherwise) coupled with moveable enclosure  242 A, the base  242  of moveable assembly  200  may be clamped or otherwise fastened to a ground surface or an overhead surface. Base  242  of moveable assembly  200  may also be clamped or otherwise fastened to a substantially planar surface (e.g. desktop) or vertical surface (e.g. wall or side of a desk). Remote coupling may be accomplished using a wireless system or using extended lengths of power and data cables. 
   Still referring to  FIG. 2A , moveable assembly  200  may be coupled with FPDD  240 , as shown. Components of moveable assembly  200  may include: an actuator assembly  202 , a display termination ball  222 ; a friction limit ball  226 ; a base  242 ; and a plurality of cables  234 , including a tension cable, anti-torsion cable, data, microphone, power supply cables, and other cables. 
   As shown in  FIG. 2A , actuator assembly  202  may be centrally and fixedly coupled with a backside of flat panel display device (FPDD)  240  using any of a number of suitable attachment methods (e.g. bolts, welds, adhesives, etc.) well-known in the art. Actuator assembly  202  is provided to reduce the amount of user force needed to collapse the moveable assembly. Typically, a user force of approximately 180 pounds to approximately 400 pounds is required. However, actuator assembly  202  reduces this force to an amount easily provided by an adult user (e.g. approximately 10.0 pounds to approximately 30.0 pounds). In the views of  FIGS. 2A ,  2 B,  2 C,  2 D,  4 A, and  4 B, several of the ball-and-socket components are not shown in order to provide views of the cables which are within the ball-and-socket components. 
   Actuator assembly  202  may be wholly contained within a housing of FPDD  240  such that handle  241  may afterwards be coupled with a component of actuator assembly  202  via insertion through an opening in the housing. Handle  241  may be formed of a single piece or of multiple pieces of a stiff, durable material such as metal, plastic, or a composite material. Exemplary metals include steel, aluminum, titanium, and alloys thereof. 
   In one embodiment, a proximal end of handle  241  may be shaped to include (or may be coupled with) a finger support member  260 , which provides a first compression surface. Finger support member  260  may be made of the same or a different material that comprises the remainder of handle  241 , and may take any suitable aesthetic or ergonomic shape, size, or contour. Similarly, a distal end of handle  241  may be pivotably coupled with one or more components of actuator assembly  202  such that handle  241  functions as a lever arm. As shown in  FIG. 2A , handle  241  is angled away from the backside of FDD  240  such that the proximal end of handle  241  is positioned near an edge of FPDD  240 . In one embodiment, the edge may be the left-hand edge of FPDD  240  as viewed from the back (e.g. right-hand edge as viewed from the front). 
   In one embodiment, a tension cable, coupled at one end with base  242  and coupled with a component of the actuator assembly  202  at the other, functions to keep the balls  226  and sockets  227  generally aligned. When tensed as shown in  FIG. 2A , the tension cable locks the moveable assembly  200  in a desired viewing position by forcibly pressing balls  226  against friction inserts in sockets  227 . Pulling the proximal end of handle  241  towards the backside of FPDD  240 , relaxes the taut tension cable such that spring activated plungers in sockets  227  lift balls  226  away from the friction inserts to allow moveable assembly  200  to be manipulated into a desired configuration. Once achieved, the desired configuration may be “frozen” or locked into position simply by releasing handle  241 . 
   In one embodiment, a user may adjust the viewing position of FPDD  240  by grasping the left-hand and right-hand edges of FPDD  240  with both hands. The user&#39;s palms may rest on portions of the front surface of FPDD  240 , with the fingers of each hand naturally curling behind FPDD  240  to rest on either its backside or on the finger support member  260 . Assuming an embodiment like that shown in  FIG. 2A , the user may relax moveable assembly  200  by compressing the fingers of the right-hand against the first compression surface, which is the finger support member  260  previously described, while simultaneously compressing the palm of the right hand against a second compression surface, which is a portion of the front surface  240 A of FPDD  240 . This compressing moves the proximal end of handle  241  from a first tensioned position towards the back of the FPDD  240 , while simultaneously moving the handle&#39;s distal end away from the back of FPDD  240 . As the distal end moves away from the back of FPDD  240 , the tensioned cable relaxes and the formerly rigid moveable assembly becomes flexible. 
   Once moveable assembly  200  is relaxed, the user may adjust the viewing position of FPDD  240  using one or both hands. For example, in another embodiment, the user may compress handle  241  with one hand, while manipulating moveable assembly  200  with the other. A desired viewing position may be locked in place by opening the fingers of the hand compressing the handle to allow the handle  241  to move from a second relaxed position back to the first tensioned position. 
   Referring now to  FIG. 2B , a back view of moveable assembly  200  is shown. In this view, it can be seen that display termination ball  222  and actuator assembly  202 , in one embodiment, are positioned substantially in the center of the back of FPDD  240  in order to provide an axis of rotation substantially near FPDD  240 &#39;s center-of-mass. In other embodiments, display termination ball  222  and actuator assembly  202  may be non-centrally positioned on the back surface of FPDD  240 . As shown in  FIG. 2B , the outermost edge of handle  241  may be substantially coterminous with an edge of FPDD  240 , or not. 
   Referring now to  FIG. 2C , there is shown, according to one embodiment of the invention, a plan view of FPDD  240  and moveable assembly  200 . The gap  290  between handle  241  and a back surface of FPDD  240  is more clearly shown. In one embodiment, this distance measures approximately 50.0 mm to approximately 70.0 mm. Gap  290  represents the distance through which handle  241  moves during a power stroke (e.g. depressing the handle to release the tension holding the FPDD  240 ). In another embodiment, where actuator assembly  202  is enclosed within a housing of FPDD  240 , the gap may measure approximately 50.0 mm to approximately 70.0 mm. The size of gap  290  may be determined based on the average measurements of an adult human hand, which average may be calculated from combined measurements of approximately 10 adult male and approximately 10 adult female hands. Optimally, the size of gap  290  should fall within the range of an adult human&#39;s maximum gripping power. Additionally, the size of gap  290  and the length of handle  241  should be coordinated to yield a maximum power stroke from a minimal applied user force. In one embodiment, the applied user force is within the range of approximately 10.0 to approximately 45.0 lbs. However, future developments in technology may reduce the amount of applied user force to approximately 10.0 pounds or less. It will be appreciated that such developments are to be construed as falling within the scope of the present invention. 
   Referring now to  FIG. 2D , there is shown, according to one embodiment of the invention, a side view of moveable assembly  200 . As shown in  FIG. 2D , moveable assembly  200  may be positioned in a variety of sculpted, curved, bent, or spiral positions. As evident from the above Figures, the cable path length of the centrally-positioned tension cable remains substantially constant when moveable assembly  200  is bent or curved. However, the path length of data and power supply cables may vary because they pass through cable guides that are located non-centrally within the interior of balls  226 . Accordingly, an additional length of cable slack approximately equal to about ⅓ of the tension cable length may be included within the moveable assembly  200  for the data and power supply cables. In other embodiments, where the FPDD&#39;s power supply is self contained or wirelessly broadcast, and/or where the FPDD&#39;s data transmissions are wirelessly broadcast, moveable assembly  200  may contain only tension, torsion, and power cables. 
   It can be seen from  FIGS. 2B ,  2 C, and  2 D that the display surface area  240 A of the FPDD  240  (which is usually most (e.g. more than 75%) of the surface area of the front surface of the FPDD) is substantially larger (e.g. at least 10 times larger) than a cross-sectional area of the moveable assembly  200  (which may be referred to as a neck). This cross-sectional area is a cross-section of the moveable assembly taken perpendicularly relative to the length of the moveable assembly (e.g. the cross section obtained at line  2 D- 2 D shown in  FIG. 2D ). This cross-sectional area is typically a small fraction (e.g. about 1/50 to about ⅙) of the display surface area  240 A. It will be appreciated that the display surface area is the surface on which the display data (e.g. a graphical user interface such as the Macintosh OS X or Windows 2000) is displayed to a user of the computer system. 
   Overturning Moments and General System Data 
   Referring now to  FIG. 3 , there is shown a diagram of exemplary torques and overturning moments associated with one embodiment of the invention. The three components of this embodiment, as shown in  FIG. 3 , are the base computer system  310 A, the moveable assembly  310 B, and the FPDD  310 C. The base computer system  310 A corresponds to the moveable enclosure  242 A, and also includes a base which secures the moveable assembly  310 B to the base computer system  310 A. The base computer system  310 A, in one embodiment, includes certain elements of the computer system (e.g. referring to  FIG. 1E , a processor  153 , memory  155 , bus  157 , mass memory  163 , I/O controller  165 , interface  167 , and a CD-ROM drive or other types of optical drives) and is coupled electrically to the FPDD  3   1 C through a power and data cable (or cables), which provides power to the FPDD  310 C and provides data for display on the FPDD  310 C (and optionally conveys data, such as control signals, from controls on the FPDD  310 C to the computer system in the base computer system  310 A. In one embodiment, such cable (or cables) are housed and concealed within the interior of moveable assembly  310 B and are not normally visible to a user. 
   The moveable assembly  310 B mechanically couples the base computer system  310 A to the FPDD  310 C. In one embodiment, this coupling is through a series of ball-and-socket joints which are held together by a tension cable within the ball-and-socket joints. The moveable assembly  310 B is mechanically coupled to the base computer system  310 A at a base end of the moveable assembly  310 B and is mechanically coupled to the FPDD  310 C at a display end of the moveable assembly  310 B. 
   Referring to the embodiment of  FIG. 3 , base radius (rb)  307  measures approximately 4.72 inches, while a neck bend radius (RN)  303  of the moveable assembly measures approximately 3.00 inches. In one embodiment, the total length of the moveable assembly measures approximately 15.00 inches; the weight of the moveable assembly (Wn)  302  measures approximately 1.76 pounds; the weight of FPDD and actuator mechanism (Wd)  301  measures approximately 5.00 pounds; and the weight of the base (Wb)  304  measures approximately 12.00 pounds. 
   Using these exemplary measurements, together with an estimated distance  309  of approximately 13.29 inches, and an estimated distance  308  of approximately 6.64 inches, the upward force (Fu)  306  at the display needed to overturn the system is calculated to be approximately 9.25 pounds, while the downward force (Fd)  310  needed to overturn is calculated to be approximately 1.22 pounds. In one embodiment, distance  309  is measured from base center-of-mass to display center-of-mass. Similarly, distance  308  is measured from the base&#39;s center-of-mass to the moveable assembly&#39;s center-of-mass. 
   It will be appreciated that increasing the weight of the base will tend to improve the stability of the entire assembly. It is preferable that the base, and the rest of the assembly, should not be so heavy that it cannot be easily moved by a single human user (e.g. an adult user). For example, it is preferable that the whole assembly should be less than about 45 pounds (lbs) and have a footprint on the surface on which it rests of less than about four (4) square feet. Normally, the weight and size of the base (including the base computer system) are designed, as described herein, to counterbalance the weight of the moveable assembly and FPDD  310 C so that the FPDD  310 C can be selectively positioned at many possible positions (X, Y, Z, pitch, yaw, roll), and the whole assembly is still stable (e.g. does not tip or overturn). Thus, there is no need, normally, to require the base computer system to be fixedly attached to the surface on which it rests; no clamps or suction or adhesive are, in a preferred embodiment, normally needed to maintain stability of the entire assembly. 
   Display 
   In one embodiment, the FPDD  240  illustratively shown in  FIGS. 2A-2D , is a 15 inch LCD panel having a target weight of approximately 4.20 pounds (1.94 kg). The 15.0 inch length is a diagonal distance measured from one corner of the viewing area to an opposite corner. 
   Moveable Assembly (E.G. Neck Member) 
   In one embodiment, the weight of the moveable assembly  200  shown in  FIGS. 2A-2D  is approximately 2.0 pounds (0.907 kg), including the balls, sockets, and cables. In one embodiment, the overall articulation length (as measured along a longitudinal dimension of the member  200 ) of moveable assembly  200  is approximately 15.5 inches (39.37 cm), and its maximum cantilever distance is approximately 13.5 inches (34.29 cm). The moveable assembly  200  provides the ability to move the FPDD in at least three degrees of freedom and preferably six degrees of freedom (X,Y, Z, pitch, yaw, and roll). 
   Ball-and-Socket Data 
   In one embodiment, there are 10 sockets, 9 articulated balls, and 2 fixed termination balls. The diameter of each ball measures approximately 38.00 mm, and the target articulation angle between segments measures +/−14 degrees. 
   Tension Cable Data 
   In one embodiment, 3/16 inch stainless steel aircraft cable having 7×19 construction (e.g. 0.01 inch strands) is used for the tension cable previously described. The tension cable may be covered in a nylon jacket to approximately 0.25 inch diameter, and may be equipped with a ball shank ferrule on the actuator mechanism end and also equipped with a stop ferrule on the base end. Because the tension cable is centrally positioned within the interior of the moveable assembly, it will be appreciated that the tension cable path length remains substantially constant. It will also be appreciated that the tension cable is not limited to a particular length, but that the length of the tension cable may vary depending on the length of the moveable assembly. (e.g. in one embodiment, the tension cable may be approximately 398.90 mm long). 
   On the other hand, because data, power, microphone, and other computer system-related cables are routed along the outer interior regions of the moveable assembly, it will be appreciated that the path length of these cables is not constant, but changes as the moveable assembly is twisted or bent. Accordingly, additional lengths of data, power, and communications cables may be provided to accommodate the path length change. Illustratively, the additional lengths may measure approximately 20% to 30% more than the straight line path length. The straight line path length is the path length measured from one end of the moveable assembly to the other when the moveable assembly is in a substantially straight, non-twisted, unbent position. 
   Friction Inserts 
   In one embodiment, each abrasive socket assembly contains two abrasive inserts. A first abrasive insert has a base portion containing an internal thread, while the second abrasive insert has a base portion having a corresponding external thread. The interior surfaces of the abrasive inserts are concave and may be coated with granular materials such as silica, aluminum oxide, or tungsten carbide. In one embodiment, the interior surfaces of the abrasive inserts are brazed with tungsten carbide particles having an approximate grain size of about 0.12 mm. In this one embodiment, the friction surface coverage is approximately equivalent to # 140 grit. Additionally, travel of the annular plungers is approximately 0.25 mm per interface. 
   In a further embodiment, a spherical glide ring may be inserted within the socket assembly in place of the abrasive insert. Additionally, one or more rims of the abrasive socket assembly may be equipped with an abrasive ring, as described below. 
   Actuator Mechanism 
   In one embodiment, a lever ratio of the actuator mechanism is approximately 11:1; and the mechanism stroke ranges from approximately 0.0 mm to approximately 0.7 mm, with an operating range of approximately 0.0 mm to approximately 0.5 mm. In one embodiment, the user stroke range (nominal) is approximately 50.0 mm to approximately 70.0 mm. The user force, in one embodiment may range from approximately 20.0 to approximately 25.0 pounds. In other embodiments, the user force may be less than approximately 20.0 pounds. The creep adjustment range may be approximately 3.0 mm. The force adjustment range may be approximately +/−60.0 pounds (e.g. 0.25 inch adjustment @400 pounds/inch). 
   Moveable Enclosure (E.G. Base Computer System): 
   In one embodiment, the moveable enclosure has a weight in the range of approximately 12.0 pounds to approximately 13.0 pounds, with a footprint diameter of approximately 240.0 mm. It will be appreciated that the base is not limited to one particular size, weight, shape, or appearance. Rather, heavier bases may have smaller footprints, and vice versa. Additionally, the bottom surface of the moveable enclosure may be larger or smaller than the top surface. The bottom of the moveable enclosure may also be equipped with a non-slip surface. In one embodiment, the non-slip surface may be a tacky, spongy, rubber-like material. In another embodiment, the non-slip surface may be a rubber suction device. In a further embodiment, the non-slip surface may be a magnetic or electromagnetic device. Additionally, the base may be equipped with one or more input devices (e.g. push buttons, touch sensitive buttons, touch sensitive screens, etc.), peripheral ports, or peripheral devices (e.g. DVD and CD-ROM drives, speakers, etc.). As previously described, one or more components of a computer may be housed within the moveable enclosure. 
   Loads 
   It will be appreciated that the moveable assembly  200  is not limited to supporting a particular load, but that moveable assembly  200  may be designed to accommodate a variety of loads. In one embodiment, the moment sum at the base socket is calculated, thus:
         Display+Mechanism: 5.2 lbs×13.5 inches=70.2 inches*pounds   Moveable Assembly: 2.0 lbs×6.5 inches=13.0 inches*pounds   Total:=83.2 inches*pounds.       

   In one embodiment, an estimated holding torque at the base is approximately 125.0 inches*pounds, with an estimated margin of approximately 1.5. 
   Moveable Assembly Displacement Estimates 
   The following table provides exemplary measurements associated with one embodiment of the present invention. 
                               TABLE 1               Item   mm   %   Notes                                                Cable Elastic   0.66   11%   Calculated based on datasheets       Stretch @250 lbf       Long Term Stretch   0.20   3%   0.001 inch per inch per VerSales                   @ 60% of rated load       Compression   1.20   19%   Estimate based on                   experimental data       Geometric Path Length   0.40   6%   Calculated based on geometry       Change       Cable Bending   0.60   10%   Estimates based on       Stiffness           empirical data       Thermal Expansion   0.17   3%   Calculated based on 70° C.                   temperature change       Plunger Travel   3.00   48%   Based on one embodiment                   (0.25 mm × 12)       Total (Estimated)   6.23   100%                    
Assemblies and Components
 
   Referring now to  FIG. 4A , there is shown a cross-sectional top view of a moveable assembly  400 , actuator assembly  400 A, and FPDD  440 , according to one embodiment of the invention. Tension cable  490  runs through central portions of balls  426  and terminates at the display end in a ball ferrule  434 , which is coupled with distal end of handle  460 . In another embodiment, ball ferrule  434  may be coupled with a crank (not shown), which is coupled with handle  460 . In  FIG. 4A , the distal end of handle  460  is coupled with a strut  409 , which is coupled with a spring or piston assembly  470 . The crank, handle  460 , strut  409 , and spring or piston assembly  470  are further described below. 
   Principle of Operation 
   Experiments performed to test the suitability of support mechanisms highlighted two significant drawbacks: substantial holding friction and the need to support the flat panel display device with one hand while manipulating the friction actuating device with the other. Although, gooseneck designs, such as a group of ball-and-socket joints, provide more degrees of freedom and a wider range of viewing positions than traditional support mechanisms, they require large amounts of holding friction to support heavy objects like flat panel display devices (FPDD&#39;s) in stable positions. Typically, the amount of holding friction required is greater than an adult user can overcome (e.g. 180-400 lbs or more). In cases where the holding friction is of an amount (e.g. 20-30 lbs) that can be easily overcome by an adult user, the prior art gooseneck-like support mechanisms gradually droop, or suddenly fail altogether, causing damage to the FPDD. 
   In gooseneck designs, where the friction actuating mechanism is disposed on or near the base of the support mechanism, users must manipulate the friction actuating device with one hand while simultaneously supporting the FPDD with the other to keep the FPDD from dropping and being damaged. The disadvantages of such systems are that they are awkward and time consuming to use. 
   With reference to  FIGS. 4 ,  7 A, and  8 , operation of the actuating mechanism leverages conservation of energy principles to reduce the amount of user force required to relax the tensioned moveable assembly (e.g. neck)  400 . During assembly, tension cable  490  is stretched with an applied force (e.g. tension) of approximately 200.00 to approximately 400.0 pounds. This applied force compresses resilient members (e.g. wave springs)  480  and plungers  428  such that balls  426  contact friction inserts  430  and  431 . As the moveable assembly  400  is compressed (e.g. tensioned), kinetic stretching energy associated with an applied user force is converted to elastic potential energy, which is stored in the tensioned cable  490  and in the wave springs  480 . 
   Because the tension cable  490  and the wave springs  480  are not massless and ideal (e.g. having no internal friction when compressed or stretched), a portion of the kinetic stretching energy is “lost” (e.g. converted to other forms of energy, such as heat); however, the overall mechanical energy associated with the system remains constant. The stretched tension cable  490  and the compressed wave springs  480  (e.g. resilient members) exert a restoring force perpendicular to the distal end of handle  460  that tends to pull the stretched cable back into its original unstretched position. Because one end of the tension cable is attached to the distal end of handle  460  (e.g. distal end of tongue  705  in  FIG. 7A ), the restoring force tends to pull the handle&#39;s (or tongue&#39;s) distal end upwards, which tends to move the proximal end of handle  460  (or tongue  705 ) downwards, which tends to move a lower end of strut  409  (or  709  in  FIG. 7A ) laterally against spring/piston assembly  470  (or spring assembly  711  in  FIG. 7A ). Thus, in one embodiment, moving the actuator from a second state (e.g. the distance separating the actuator handle from the back of the FPDD is minimized) to a first state (e.g. the distance separating the actuator handle from the back of the FPDD is maximized) transfers a portion of the elastic potential energy stored in a compressed spring/piston assembly into elastic potential energy stored in a tensioned tension cable and in a plurality of resilient members. At the same time, the remaining stored elastic potential energy is converted to work done on the user and to kinetic energy of the actuator. 
   In a preferred embodiment, the spring constant of spring assembly  711  ( FIG. 7A ) or  811  ( FIG. 8 ) is chosen such that the spring force exerted by spring or piston assembly  470  (or  711  in  FIG. 7A ) on strut  409  (or on spring shaft  708  and  806  in  FIGS. 7A and 8 , respectively) equals or slightly exceeds the restoring force exerted by the tensioned cable and wave springs. In this manner, the moveable assembly  400  ( FIG. 4A ) remains compressed and rigid. An illustrative range of spring constants may include: approximately 180.0 lbs/in to approximately 200.0 lbs/in, but preferably approximately 190.0 lbs/in. 
   Referring back to the embodiment shown in  FIG. 4A , depressing proximal end  451 A of handle  460  moves strut  409  laterally to compress spring/piston assembly  470 . Simultaneously, the distal end of handle  460  moves upwards to relax the tension cable  490  and decompress the wave springs. Depressing proximal end  451 A of handle  460  converts mechanical energy (e.g. that provided by the user depressing the handle  451 ) and potential energy (e.g. that stored in the tensioned cable and compressed wave springs) into kinetic energy as strut  409  moves laterally to compress spring/piston assembly  470  (e.g.  711  in  FIG. 7A ). This kinetic energy is converted into elastic potential energy, which is stored in the compressed spring/piston assembly  470 . Likewise, releasing proximal end  451 A of handle  451  converts the spring&#39;s stored elastic potential energy into kinetic energy as strut  409  moves laterally to depress the distal end of handle  451 . This kinetic energy is stored as potential energy in cable  490  is tensioned the wave springs as the moveable assembly is compressed. 
   Similar conversions of energy occur with respect to the embodiments shown in  FIGS. 7A and 8 . These conversions of energy allow the moveable assembly to wilt instantly upon depression of the proximal end of handle  460  toward the back of the FPDD, and to stiffen instantly upon release of the proximal end of handle  460 . The FPDD, in one embodiment, may be moved/re-positioned over at least three (and up to as many as five or six) degrees of freedom from a single actuation (e.g. depression) of the handle (actuator), rather than having to loosen two or more locks in order to obtain the ability to move the FPDD simultaneously in more than one degree of freedom. 
   It will be appreciated that the energy stored in the tensioned cable  490  and in the compressed wave springs (e.g. resilient members)  480  significantly reduces the amount of user force required to compress spring/piston assembly  470  (or spring assembly  711  in  FIG. 7A ). For example, in a preferred embodiment, compression of spring/piston assembly  470  (or  711 ) requires an applied user force in the range of approximately 10.0 to approximately 30.0 lbs. 
   With reference to  FIG. 7A , it will also be appreciated that the amount of applied user force required to compress the spring/piston assembly  470  (or  711 ) may be further reduced by modifying the angle at which the distal end of tongue  705  (or handle  751 ) connects with tension cable  709 . 
   Description of Component Parts 
   Referring again to  FIG. 4A , spring or piston assembly  470  may be one of a number of suitable pre-manufactured metal springs or gas piston assemblies known in the art, so long as the spring or piston assembly  470  exerts a restoring force of approximately 200.0 pounds/inch. In one embodiment, the exterior dimensions of spring or piston assembly  470  measure approximately 2.0 inches to approximately 2.25 inches long. Illustratively, the restoring force exerted by the spring or piston assembly  470  may fall within the range of approximately 180.0 pounds/inch to approximately 400.0 pounds/inch. In one embodiment, the spring or piston assembly  470  may include a resilient member, which when compressed, exerts a restoring force tending to return the compressed resilient member to its uncompressed state. Examples of resilient members include: metal springs, springs made of composite materials, hydraulic pistons, etc. 
   In  FIG. 4A , a display termination ball  424 , having a substantially planar mating surface connects moveable assembly  400  to FPDD  440 , but any suitable attachment method, such as bolts and/or interlocking grooves, may be used to attach display termination ball to FPDD  440 . Anti-torsion cable  491  may be provided to prevent moveable assembly  400  from over-twisting and stretching the data, microphone, and/or the power supply cables. 
   Additional components of the moveable assembly are now described. In one embodiment, the diameter  459  of balls  426  measures approximately 38.00 mm, while the diameter  458  of tension cable  490  measures approximately 6.25 mm. The center-to-center distance  457  between balls  426  measures approximately 36.00 mm; and the height of socket assembly  427  may measure approximately 24.00 mm. The length  451  of handle  460 , measured from a proximal end  461  to a pivot pin  462  measures approximately 169.277 mm. The distance  455 , measured from the center of tension cable  490  to the center of pivot pin  462 , is approximately 15.830 mm; while the distance  454 , measured from the center of tension cable  490  to a proximal end  463  of spring or piston assembly  470 , is approximately 153.60 mm. In one embodiment, width  453  of FPDD  440 &#39;s exterior casing measures approximately 21.162 mm. In another embodiment, the power stroke distance  452 , measured from proximal end  461  to the front surface of FPDD  440 , is approximately 89.924 mm. 
   Referring now to  FIG. 4B , there is shown a cross-sectional view of moveable assembly  400 . As shown, tension cable  490  runs through cable guides in the center of balls  426 , and anti-torsion cable  439  runs through cable guides spaced apart from the center of balls  426 . As shown in  FIG. 4B , balls  426  and sockets  427  may bend approximately +/−14.0 degrees to curve moveable assembly  400  into a desired shape. However, in other embodiments, balls  426  and sockets  427  may bend a greater or lesser amount. 
   Referring now to  FIG. 5A , there is shown a side view of an assembled moveable assembly  500 , including actuator assembly  502  (but without the FPDD and the base of the moveable assembly and the base computer display). In one embodiment, the length  551  of moveable assembly as measured from surface  503  of base termination ball  533  to surface  504  of display termination ball  522 , measures approximately 397.00 mm. 
     FIGS. 5B and 5C  show perspective views of one embodiment of moveable assembly  500 . 
     FIGS. 5A-5C  show the moveable assembly with all of the ball-and-socket components (and hence the data, tension, power, and anti-torsion cables are concealed). 
     FIG. 5D  is a sectional view of one embodiment of a moveable assembly  500  showing the internal placement of a tension cable  590 . Moveable assembly  500  includes socket assemblies  570 A and  570 B, and a ball  560  having a first hollow cavity  551  and a second hollow cavity  552  separated by a central wall in which are located an annular ring  598 , bore  516 , and bore  510 , each of which extend from one side of the central wall to the other. In one embodiment, the inside surfaces  598 A and  598 B of annular ring  598  are bowed slightly to taper outwards such that the sliding friction between a tension cable  590  passing through the interior of annular ring  598  is minimized. Bores  510  and  516  contain a torsion cable, not shown, which prevents data and power cables (not shown) contained within other bores (not shown) from being damaged or stretched by over-rotation. As shown in previous figures, friction socket assembly  570 A includes a first plunger  592 A, a resilient member  594 A, and a second plunder  596 A. Similarly, friction socket assembly  570 B includes a first plunger  592 B, a resilient member  594 B, and a second plunger  596 B. 
     FIG. 5E  is a cross-sectional view of a portion  560  of a moveable assembly usable with an embodiment of the present invention showing the placement of data, tension, torsion, power, antenna, and other computer system related cables within one or more apertures  508 ,  512 ,  514 ,  504 ,  506 ,  520 , and  508  of the moveable assembly. In one embodiment, portion  560  of the moveable assembly is a friction limit ball, having a wall (e.g. brace) containing a plurality of apertures (or bores) centrally located therein. Apertures  510 ,  516 , and  520  are substantially circular in cross-section, while apertures  508 ,  514 ,  504 , and  506  are irregularly shaped. Anti-torsion cables  512  and  518  extend through apertures  510  and  516 , respectively, while torsion cable  590  extends through aperture  520 . In one embodiment, one or more of the irregularly shaped apertures may include one or more data, power, antenna, and/or similar computer system-related cables. 
   As shown in  FIG. 5E , aperture  508  includes an inverter cable  528  and a microphone cable  526 , while aperture  514  contains a Transmission Minimized Differential Signaling (TDMS) cable  524 . The inverter cable  528  powers the LCD flat panel display, while the TDMS provides data signals to the flat panel display. The TDMS cable is made up of four bundles of three wires each. Two wires within each bundle are twin-axial (e.g. helically twisted) signal wires, and the third wire is a drain wire. In one embodiment, the twin axial signal wires and drain wires are individually insulated with aluminum-mylar. Additionally, a plurality (in one embodiment, three) additional Extended Display Identification Data (EDID) wires may be included within TDMS cable  524  to provide additional signals to the flat panel display. 
   In an alternate embodiment, a Low Voltage Differential Signaling (LVDS) cable may be used. Low Voltage Differential Signaling is a low noise, low power, low amplitude method for high-speed (gigabits per second) data transmission over copper wire. LVDS differs from normal input/output (I/O ) in a few ways: Normal digital I/O works with 5 volts as a high (binary 1) and 0 volts as a low (binary 0). When a differential is used, a third option (−5 volts), is added, which provides an extra level with which to encode and results in a higher maximum data transfer rate. A higher data transfer rate means fewer wires are required, as in UW (Ultra Wide) and UW-2/3 SCSI hard disks, which use only 68 wires. These devices require a high transfer rate over short distances. Using standard I/O transfer, SCSI hard drives would require a lot more than 68 wires. Low voltage means that the standard 5 volts is replaced by either 3.3 volts or 1.5 volts. 
   LVDS uses a dual wire system, running 180 degrees of each other. This enables  noise to travel at the same level, which in turn can get filtered more easily and effectively. With standard I/O signaling, data storage is contingent upon the actual voltage level. Voltage level can be affected by wire length (longer wires increase resistance, which lowers voltage). But with LVDS, data storage is distinguished only by positive and negative voltage values, not the voltage level. Therefore, data can travel over greater lengths of wire while maintaining a clear and consistent data stream. 
   Referring now to  FIG. 6 , there is shown an exploded perspective view of a moveable assembly  600  and actuator assembly  602 , according to one embodiment of the present invention. In one embodiment, tension cable  690  terminates at the actuator assembly end in a ball ferrule  634 . Socket assembly  627  may be equipped with a wave spring (e.g. resilient member), plungers, and friction inserts, such that plungers supportably engaging friction limit ball  626  raise ball  626  from and lower ball  626  to a friction insert when the wave spring (e.g. resilient member) is either expanded or compressed. In one embodiment, moveable assembly  600  may have first friction area provided by a sequential series of socket assemblies  627  and a second friction area provided by a sequential series of friction limit sockets  625 , which are not equipped with friction inserts, plungers, or wave springs. Instead, friction limit sockets  625  may be cast or machined out of a single material such as aluminum or stainless steel. 
   From an engineering point of view, the bottom third of moveable assembly experiences the highest stressing forces, and thus higher friction surfaces are needed to fix ball  626  in position, than are needed to fix ball  626 A in position. In other embodiments, moveable assembly may be constructed using only friction limit sockets  625 , or using only socket assemblies  627 . Alternatively, one or more friction limit sockets  625  may be interspersed between two or more socket assemblies  627 . In another embodiment, the concave interior contact surfaces of friction limit sockets  625  may be brazed with tungsten carbide to provide an improved friction surface. 
   Referring again to  FIG. 6 , an anti-torsion cable  639  may be provided to limit how much moveable assembly  600  may be twisted. Other components of moveable assembly  600  may include a base termination socket  637 , a base termination ball  633 , a tension cable ferrule  635 , a strain relief  638  for the data cables, and ferrules  636  for the anti-torsion cable. In one embodiment, strain relief  638  is made of rubber or plastic. 
   Referring now to  FIG. 7A  there is shown another embodiment of an actuator assembly  702 . In this embodiment, an actuator assembly  702  is shown in a first tensioning position. In one embodiment, actuator assembly includes a tongue  705 , a crank  703 , a strut  709 , a spring shaft  708 , and a spring assembly  711 . Tongue  705  may be coupled to tension cable ferrule  734  at one end, and coupled via a shaft  713  to a crank  703 . Proximal end  703 A of crank  703  may be angled upwards and coupled with strut  709 , which angles downwards to couple with spring shaft  708  via pivot pin  736 . Though not shown, a handle may be coupled with crank  703  to form an angle  752  with the horizontal. 
   In this first tensioning position, the distance  753  between a front surface of actuator assembly  702  and a center of ferrule  734  may measure approximately 14.26 mm. A distance  751  measured from the center of shaft  713  to the center of pivot pin  736  may measure approximately 59.75 mm. In one embodiment, the angle  752  at which crank  703  is angled upward from the horizontal may measure approximately 20.4 degrees. 
   Referring to  FIG. 7B , there is shown a cross-sectional view of an actuator assembly  702  in a second relaxed position, according to one embodiment of the invention. In this embodiment, a handle (not shown) coupled with crank  703  has been depressed to flatten crank  703  and strut  709  while raising the distal end of tongue  705  to relax the tensioned cable. As a result of this flattening, spring  711  ( FIG. 7A ) has been compressed a distance  755 , which may measure approximately 15.25 mm in one embodiment of the invention. In one embodiment, the length  756  of spring assembly  711  ( FIG. 7A ) may measure approximately 43.18 mm, and the distance  754  separating shaft  713  from pivot pin  736  may measure approximately 69.11 mm. Additionally, the distance  757  separating the center of ball ferrule  734  from a front surface of actuator assembly  702  may increase to approximately 21.70 mm. 
     FIG. 8  is an exploded perspective view of one embodiment of an actuator assembly  802 . Actuator housing  807  may be made of any suitable durable material (e.g. metal, plastic, etc.) known in the manufacturing and computer arts. In one embodiment, housing  807  may be machined from a single block of aluminum or stainless steel, or cast from a liquid metal or liquid plastic injected or poured into a mold. It will be appreciated that the exterior and interior contours and protrusions or intrusions of housing  807  may be of any size, shape, or dimension necessary to fit a particular desired application. 
   For example, as shown in  FIG. 8 , a proximal end of housing  807  is blocked, with rounded edges and corners, while a proximal end is rounded and drilled to contain three screw holes  890 . Additionally, a lip  891  may be formed on the proximal end and bored to allow housing  807  to be bolted to a chassis of a FPDD. In one embodiment, housing  807  is enclosed on three sides with the fourth side left open to allow insertion of various components and sub-assemblies. The sides and blocked end of housing  807  may contain one or more circular or rectangular orifices through which various components (e.g. spring shaft cap  808 , shaft  816 , shaft  814 , and shaft  813 ) may be inserted to assemble actuator assembly  802 . In one embodiment, spring shaft cap  808  covers the end of spring assembly  811 , and may be formed of a plastic or metal using the injection molding or machining processes described above. 
   Similarly, shafts  813 ,  814 , and  816  may be formed of a metal such as stainless steel. The ends of shafts  813 ,  814 , and  816  may be threaded to receive a nut, or equipped with an annular groove to receive a pressure fitted washer (e.g. retaining rings  817  and  821 ). Thrust washer  818  may be inserted within housing  807 , at the blocked end, to provide a support surface for die spring  811 . Spring shaft  806  may be coupled with die spring  811 , and may be formed of a plastic or metal (e.g. stainless steel) using injection molding or machining processes well-known in the art. 
   As shown in  FIG. 8 , rounded and narrowed proximal end  806 A of spring shaft  806  may contain an orifice of sufficient size and diameter to receive shaft  813 . The outer dimensions of proximal end  806 A may such that the proximal end  806 A slidably fits between a first pair of arms of H-shaped strut  809 . In one embodiment, the first pair of strut arms contain circular orifices corresponding in dimension and placement to circular orifices in proximal end  806 A and housing  807 , such that shaft  813  may be slid through the aligned orifices to operatively link spring shaft  806  with strut  809 . Similarly, the other end of strut  809  may contain a second pair of strut arms that slidably straddle a nubbed portion  803 A of crank  803 , such that shaft  814 , passing through aligned circular orifices in the second pair of strut arms and in housing base  807 , operatively couple shaft  809  with crank  803 . 
   Crank  803  may be formed of plastic or metal (e.g. stainless steel) using injection molding or machining processes well known in the art. It will be appreciated that crank  803 , like the other components of actuator assembly  802 , is not limited to a particular size, weight, configuration, appearance, or shape. Rather, crank  803  may have any size, shape, appearance, or configuration necessary to fit a particular application. At one end, crank  803  is extruded and narrowed to form nubbed portion  803 A, through which a circular orifice is formed. In one embodiment, a horizontally disposed flat planar surface forming the top of nubbed portion  803 A may cascade down into an open portion between two parallel crank arms, each of which contains an orifice to receive shaft  817 . 
   Formed of a metal (e.g. stainless steel), tongue  805  is an oblong piece of metal, thick in its central portion and tapering to substantially flat ends. Each end may contain a circular orifice extending through its thickness. Similarly, a circular orifice may be bored through the tongue&#39;s central portion from one side to the other. The edges of orifice may be recessed such that nylon washers  805 A may be inserted into the orifice flush with the outer portions of tongue  805 . Tongue  805  may be slidably inserted between the arms of crank  803  such that shaft  817  may be inserted through the orifices in housing  807 , the crank arms, and the tongue&#39;s central portion, to operatively couple tongue  805  with crank  803 . A set screw  819  may be provided to adjust the tilt of tongue  805 . Additionally, termination socket  824 , equipped with insert  823 , may be used to couple termination ball  822  with the proximal end of housing  807 . In another embodiment, a flat base portion of display termination ball  822  that contains screw holes corresponding in number, dimension, and placement to the screw holes in the proximal end of housing  807  may be bolted directly to housing base  807 . 
     FIG. 9A  is a perspective view of one embodiment of a housing base  907 , which corresponds to housing base  807 . 
   Referring now to  FIG. 9B , there is shown a side view of the housing base  907  shown in  FIG. 9A . The height  951  of housing base  907  may be approximately 30.75 mm. The diameter of circular orifice  990  may measure approximately 6.05 mm. The length  953  of rectangular orifice  991  may measure approximately 23.13 mm. A distance  952 , measured from the center of circular orifice  990  to a first edge of rectangular orifice  991 , may measure approximately 23.13 mm. A distance  954  from the center of circular orifice  990  to the bottom edge of rectangular orifice  991  may measure approximately 10.07 mm. In one embodiment, the depth  955  of rectangular orifice  991  is approximately 12.63 mm. 
     FIG. 9C  is a bottom view of the actuator housing  907 . In one embodiment, the distance  957  from a center of holes  992  to the center of holes  966  measures approximately 142.06 mm. Distance  958 , measured from the center of holes  993  to the center of holes  966 , is approximately 133.69 mm. Distance  959 , measured from the center of holes  994  to the center of holes  996 , is approximately 42.05 mm. The center-to-center distance  960  of holes  966  is approximately 20.30 mm. The center-to-center distance  964  of holes  993  is approximately 23.11 mm. The center-to-center distance  956  of holes  992  is approximately 22.22 mm. Measurement  965  is approximately 3.18 mm. The diameter  967  of hole  996  may measure approximately 14.0 mm. Width  961  of housing  907  may measure 30.81 mm. 
     FIG. 9D  is a sectional end view of housing  907  taken along line A-A in  FIG. 9C . Measurement  962 , in one embodiment, is approximately 18.77 mm. 
     FIG. 9E  is a sectional end view of housing  902  taken along line B-B in  FIG. 9C . In one embodiment, measurement  963  is approximately 20.40 mm. 
     FIG. 10A  is a perspective view of one embodiment of crank  1003 , which corresponds to crank  803 . Proximal end  1094  of crank  1003  may include arms  1098 , which contain circular orifices  1091 . In one embodiment, circular orifices  1091  correspond in size and placement to each other. At the distal end  1097 , crank  1003  may include a nubbed portion  1096 , which corresponds to nubbed portion  803 A. Nubbed portion  1096  may include a circular orifice  1092 . Additionally, the top of distal end  1097  may be flat, or equipped with sidewalls to form depression  1095 . In one embodiment, the each sidewall is equipped with screw holes  1093 . 
     FIG. 10B  is a top view of the crank  1003  shown in  FIG. 10A  illustrating placement of holes  1093 . In one embodiment, the diameter  1058  of holes  1093  is approximately 3.0 mm. 
     FIG. 10C  is a side view of the crank  1003  shown in  FIG. 10A . Circular orifices  1091  and  1092  have a diameter  1059  of approximately 8.05 mm. The center-to-center distance  1051  of orifices  1091  and  1092  is approximately 41.57 mm. 
     FIG. 10D  is a bottom view of crank  1003 . In one embodiment, the length  1052  of crank  1003  is approximately 53.60 mm. At its widest point, the width  1055  of crank  1003  measures approximately 19.25 mm. Similarly, width  1053  measures approximately 16.80 mm, and width  1054  measures approximately 10.78 mm. Length  1057  measures approximately 20.00, and distance  1056  measures approximately 7.98 mm. 
     FIG. 11A  is a perspective view of one embodiment of a tongue  1105 , which corresponds to tongue  805 . Proximal end  1197  of tongue  1105  contain an concave orifice  1195 , while distal end  1196  may contain a bore  1191  extending through the thickness of distal end  1196 . Similarly, a bore  1192  may extend from one side of the tongue&#39;s central portion to the other. Additionally, the top central portion of tongue  1105  may be ridged to form convex channel  1194 . 
   Referring now to  FIG. 11B , there is shown a side view of tongue  1105 . In this figure, tongue  1105  is shown upside down from the position shown in  FIG. 11A . The length  1151  of tongue  1105  may measure approximately 44.69 mm. The diameter  1198  of bore  1192  may measure approximately 8.5 mm. The interior surface of orifice  1195  may be curved at an angle of approximately 12.70 degrees. Distance  1152  may measure approximately 11.08 mm. Distance  1154  may measure approximately 7.01 mm. Distance  1153  may measure approximately 3.00 mm. The center-to-center distance between bore  1192  and orifice  1191  is approximately 15.82 mm. 
   Referring to  FIG. 11C , which is a plan view one embodiment of tongue  1105 , distance  1156  is approximately 21.38 mm. The diameter of orifice  1191  may measure approximately 6.00 mm. Additionally, within orifice  1195 , there may be disposed a substantially oval orifice  1199 , the width of which may measure approximately 6.92 mm. 
     FIG. 11D  is an end view of one embodiment of tongue  1105 . In this one embodiment, distance  1157  measures approximately 17.88 mm, and width  1158  measures approximately 13.95 mm. 
     FIG. 12A  is a perspective view of one embodiment of a spring shaft  1206 , which corresponds to spring shaft  806 . In this embodiment, spring shaft  1206  has a nubbed portion  1298  at one end that flares to a perpendicularly disposed circular flange  1297 A, which terminates in a planar surface  1297 B. An orifice  1292  may extend through nubbed portion  1298 . A flange  1291  may be disposed on an edge of nubbed portion  1298 . Extending from the center of planar surface  1297 B is a barrel  1294 . Barrel  1294  is cylindrical and of a diameter smaller than the diameter of circular flange portion  1297 A. Additionally, barrel  1294  may contain evenly spaced rectangular orifices  1293 . Barrel  1294  terminates in a planar surface  1294 B. Extending from the center of planar surface  1294 B is a second barrel  1295  of smaller diameter than the first, which terminates in knobbed ferrule  1296 . 
     FIG. 12B  is a side view of one embodiment of the spring shaft  1206  shown in  FIG. 12A . The distance  1257  from the center of orifice  1292  to the edge of planar surface  1297 B is approximately 10.00 mm. 
     FIG. 12C  is a cross-sectional side view of spring shaft  1206  taken along the line A-A in  FIG. 12B . Distance  1254  measures approximately 7.12 mm. Distance  1255 , measured from the center of orifice  1292  to the edge of ferrule  1296 , is approximately 46.99 mm. The diameter  1253  of the circular flange portion  1297  measures approximately 19.00 mm. Similarly, the diameter of ferrule  1296  measures approximately 5.00 mm at its widest point. The diameter of barrel  1294  may measure approximately 9.52 mm. 
     FIG. 12D  is an end view of spring shaft  1206 . In this one embodiment, the thickness  1256  of flange  1291  may measure approximately 3.00 mm. 
     FIG. 13A  is a perspective view of one embodiment of strut  1303 , which corresponds to strut  803 . In this one embodiment, strut  1303  is H-shaped. One pair of arms  1396  may curve downwards as shown, while a second pair of arms  1395  may be straight. Arms  1396  may contain orifices  1394  extending through each individual arm. Similar orifices  1393  may extend through the each of arms  1395 . In one embodiment, the outside edges of orifices  1393  may be flared to produce annular rings  1397 . Disposed between arms  1396  is a first channel  1391 . Disposed between arms  1395  is a second channel  1392 . 
     FIG. 13B  is a plan view of strut  1303  shown in  FIG. 13A . Length  1356  of strut  1303  may be approximately 36.59 mm. The width  1359  of strut  1303 , as measured from the outer edges of annular rings  1397  may be approximately 17.00 mm. The width  1358  of the second channel may measure approximately 8.50 mm. The width  1357  of the first channel may measure 9.58 mm. 
     FIG. 13C  is a cross-sectional side view of strut  1303 , taken along the line A-A in  FIG. 13B . In one embodiment, the horizontal center-to-center distance  1351  between orifices  1394  and  1393  is approximately 27.54 mm. Distance  1352  measures approximately 7.63 mm. Distance  1353  measures approximately 8.03 mm. Additionally, the vertical center-to-center distance between orifices  1394  and  1393  is approximately 4.03 mm. 
     FIG. 13D  is an end view of strut  1303 . In one embodiment, the width  1360  of strut  1303  measures approximately 17.43 mm. 
     FIG. 14A  is a perspective view of one embodiment of a shaft  1416 . It will be appreciated that shafts having various lengths and diameters may be used with the present invention, and that the present invention is not limited to the dimensions of one embodiment described herein. Shaft  1416  is generally cylindrical, and may be either solid or hollow. Shaft  1416  includes a barrel portion  1493 , and an annular channel  1491  disposed near one end of shaft  1416 , and an annular channel  1492  disposed near the opposite end of shaft  1416 . In one embodiment, a retaining ring (not shown) fits within annular channel  1492  to secure shaft  1416  in position. 
     FIG. 14B  is a side view of shaft  1416  showing the various measurements thereof. In one embodiment, the length  1451  of barrel portion  1493 , measured from the interior edges of annular channels  1491  and  1492 , is approximately 17.52 mm. Alternatively, length  1451  may measure approximately 25.12 mm or approximately 24.92 mm. The outer diameter  1452  of shaft  1416  may measure approximately 4.0 mm. 
     FIG. 15A  is a perspective view of one embodiment of a display termination socket  1524 . In this one embodiment, socket  1524  is a hollow, annular ring. A first annular lip  1592  may be disposed within one end of socket  1524 , and an annular lip  1591  may be disposed inside the socket  1524  near the other end. Socket  1524  is used to couple a display termination ball (not shown) with the actuator assembly previously described. 
     FIG. 15B  is a cross-sectional side view of socket  1524  taken along the line A-A in  FIG. 15C , which is a top view of socket  1524 . Distance  1551  measures approximately 17.50 mm, and radius  1553  measures approximately 19.00 mm. The interior diameter  1552  of socket  1524  may measure approximately 34.50 mm. 
     FIG. 16  is a side view of one embodiment of a tension cable  1634 . Tension cable  1634  includes a ball ferrule  1654  on one end. The other end may be provided with a compression-fit ferrule (not shown) during assembly of the moveable assembly, as previously described. Additionally, a plastic or nylon sleeve  1656  is centrally disposed about cable  1634 . In one embodiment, the distance  1651 , measured from the center of ball ferrule  1654  to a first end of sleeve  1656 , is approximately 398.90 mm. Approximately a 12.00 mm length  1655  of exposed cable  1634  may extend past the first end of nylon sleeve  1656 . A distance  1653 , measured from a second end of nylon sleeve  1656  to the center of ball ferrule  1654 , is approximately 12.00 mm. In one embodiment, the diameter of ball ferrule  1654  may measure approximately 11.18 mm. 
     FIG. 17A  is a perspective view of one embodiment of a friction limit socket  1725 . Socket  1725  may be formed of a metal (e.g. stainless steel or aluminum), and may include a first portion  1793 A, a second portion  1793 B, and an annular ring (or channel)  1791  disposed between the first and second portions. Friction limit socket  1725  is static, meaning that first portion  1793 A and second portion  1793 B are not moveable. A concave surface  1792 A may be formed within first portion  1793 A to receive a friction limit ball (not shown). In one embodiment, friction limit socket  1725 , including concave surfaces  1792 A and  1792 B ( FIG. 17C ), is formed of a single piece of stainless steel. In another embodiment, concave surfaces  1792 A and  1792 B separate pieces, which may be threaded together at their base portions to form socket  1725 . In one embodiment, as previously described, concave surfaces  1792 A and  1792 B may be coated with a high friction material such as tungsten-carbide or aluminum oxide. Alternatively, concave surfaces  1792 A and  1792 B may be left uncoated. 
     FIG. 17B  is a plan view of friction limit socket  1725 . 
     FIG. 17C  is a cross-sectional side view of socket  1725  taken along the line A-A in  FIG. 17B  and showing interior concave surfaces  1792 A and  1792 B. Distance  1753  measures approximately 36.00 mm. Distance  1754  measures approximately 21.50 mm. A first radius  1752  measures approximately 20.00 mm, while a second radius  1751  measures approximately 19.10 mm to form an annular lip about the outer edges of portions  1793 A and  1793 B. 
     FIG. 18A  is a perspective view of one embodiment of a friction limit ball  1826 . Friction limit ball  1826  includes a cosmetic middle portion  1891 ; a first annular friction ring  1892 A disposed on a first end of friction limit ball  1826 ; a second annular friction ring  1892 B disposed on a second end of friction limit ball  1826 ; and a cable guide insert  1893  centrally located within a bore  1896  running through friction limit ball  1826  from one side to the other. Friction limit ball is formed of a metal (e.g. stainless steel or aluminum). In one embodiment, annular friction rings  1892 A and  1892 B are manufactured independently of friction limit ball  1826  and are adhered to friction limit ball  1826  using adhesives well-known in the art. In another embodiment, annular friction rings  1892 A and  1892 B, cable guide insert  1893 , and friction limit ball  1826  are machined from a single block of aluminum. 
   Referring to  FIG. 17A and 18A , in a further embodiment, annular friction rings  1892 A and  1892 B are coated with a high friction material such as tungsten-carbide to provide a high friction surface as previously described. Alternatively, annular friction rings  1892 A and  1892 B may be left uncoated. The annular friction rings not only contact concave surfaces  1792 A and  1792 B when moveable assembly  200  is tensioned, but also serve to limit the friction limit ball&#39;s  1826  axis of rotation when moveable assembly  200  is relaxed. For example, friction limit ball  1826  may be tilted within socket  1725  until one of the friction limit rings contacts the inner lip of portion  1793 A or  1793 B. In embodiment, the axis of rotation is approximately in the range of approximately 10.0 to approximately 25.0 degrees. In other embodiments, the axis of rotation may be greater or lesser than the range illustratively given above. 
     FIG. 18B  is a plan view of friction limit ball  1826 . Cable guide insert  1893  may include four perpendicular cross members. Two holes  1895 A and  1895 B may be centrally disposed in two of the cross members, with the center of each hole located a distance  1861  or  1862 , respectively, from the center of friction limit ball  1826 . In one embodiment, holes  1895 A and  1895 B house an anti-torsion cable. Additionally, a central tension cable bore  1894  may be formed in the center of cable guide insert  1893  to house a tension cable. In one embodiment, distances  1861  and  1862  each measure approximately 8.00 mm. 
     FIG. 18C  is a cross-sectional side view of a friction limit ball  1826  taken along the line A-A in  FIG. 18B . In one embodiment, the thickness  1851  of friction limit ball is approximately 30.00 mm. The outer diameter  1854  of friction limit ball  1826  may be approximately 38.00 mm. Distances  1855  and  1856 , measured from a vertical line extending though the center of friction limit ball  1826  to the edge of annular friction rings  1892 A and  1892 B, each measure approximately 11.03 mm. The radius  1857  is equivalent to the radius  1858  and measures approximately 35.5 degrees. The diameter  1852  of a first bore is approximately 23.00 mm. The diameter  1853  of a tension cable bore is approximately 6.80 mm. 
     FIG. 19A  is a perspective view of one embodiment of an abrasive socket assembly  1927 . A first plunger  1928 A slidably fits around first friction insert  1930 , which is coupled with a second friction insert  1931 , which slidably fits within a second plunger  1928 B. The plungers and friction inserts may be made of a metal (e.g. stainless steel or aluminum). Wave spring  1932  is disposed between the first and second plungers to space the plungers apart when moveable assembly  200  is relaxed. When thrust apart by wave spring (resilient member)  1932 , plungers  1928 A and  1928 B lift friction limit balls  1826  out of contact with friction inserts  1930  and  1931 , thus allowing friction limit balls  1826  to rotate freely within plungers  1928 A and  1928 B. In one embodiment, base portions of friction inserts  1930  and  1931  are threaded such that the friction inserts may be screwed together to assemble abrasive socket assembly  1927 . Additionally, the concave inner surfaces of friction inserts  1930  and  1931  may be coated with an abrasive material such as tungsten carbide, aluminum oxide, or other abrasive material, as previously described, to provide a high friction support surface. 
   With reference back to  FIG. 2A , in a further embodiment, abrasive socket assemblies  1927  are used in the bottom one-half to one-third portion of moveable assembly  200 , while friction limit sockets  1725  are used in the upper one-half to two-thirds of moveable assembly  200 . In this manner, moveable assembly  200  is equipped with at least two zones of friction: a high friction zone located near the base of moveable assembly  200 , where the most torque occurs; and a low friction zone located towards the display end of moveable assembly  200 . Alternatively, abrasive socket assemblies  1927  and friction limit sockets  1725  may be alternated throughout the length of moveable assembly  200 . 
     FIG. 19B  is a perspective view of a first friction insert  1930  having a concave interior surface designed to mate with an annular friction ring of a friction limit ball. Base portion  1992  may be threaded to mate with a base portion of a corresponding second friction insert. 
     FIG. 19C  is a cross-sectional side view of the friction insert  1930  of  FIG. 19B . Distance  1952  measures approximately 15.25 mm, and distance  1953  measures approximately 5.00 mm. In one embodiment, the outer diameter  1955  of the base portion measures approximately 30.25 mm, and the outer diameter of first friction insert  1930  measures approximately 35.50 mm. Additionally, the interior  1954  of the base portion of first friction insert  1930  may be internally threaded. Second friction insert  1931  (not shown) has corresponding measurements, except that the base portion of second friction insert  1931  may be externally threaded. 
     FIG. 19D  is a top view of first friction insert  1930 , showing orifice  1991  bored through the base portion of first friction insert  1930  to allow passage therethough of data, torsion, tension, power, and other computer system-related cables. 
     FIG. 19E  is a side view of first friction insert  1930 , showing base portion  1992 . 
     FIG. 19F  is a bottom view of first friction insert  1930 . 
     FIG. 19G  is a perspective view of a second friction insert  1931 , showing a second, externally-threaded base portion  1993 . 
     FIG. 19H  is a cross-sectional side view of second friction insert  1931  taken along the line A-A in  FIG. 19K . Distance  1961  measures approximately 15.25 mm. Distance  1963  measures approximately 5.00 mm. Outer diameter  1964  of the base portion measures approximately 30.25 mm, and outer diameter  1965  of second friction insert  1931  measures approximately 35.50 mm. The exterior  1966  of the base portion may be threaded such that the base portions of second friction insert  1931  and first friction insert  1930  screw into each other. 
     FIG. 19I  is a plan view of second friction insert  1931  showing an orifice  1994  bored through the base portion of the insert to allow for the passage therethrough of data, power, anti-torsion, tension, power, and other computer system-related cables. 
     FIG. 19J  is a side view of the second friction insert  1931  showing base portion  1993 . 
     FIG. 19K  is a bottom view of second friction insert  1931 . 
     FIG. 20  is a cross-sectional side view of an assembled abrasive socket assembly  2027 , which corresponds to abrasive socket assembly  1927 , according to one embodiment of the invention. In this figure, plunger  2093  corresponds to plunger  1928 A and plunger  2094  corresponds to plunger  1928 B. In this one embodiment, plunger  2093  has been fashioned to slidably fit around plunger  2094  so as to present a more desirable aesthetic external appearance. Plungers  2093  and  2094  may be made of plastic or a metal (e.g. aluminum or stainless steel), and colored as desired. Annular wave spring  2032 , corresponding to wave spring (e.g. resilient member)  1932 , is disposed between plungers  2093  and  2094  to space plungers  2093  and  2094  apart when moveable assembly  200  is relaxed. Friction insert  2030 , corresponding to friction insert  1930 , is screwed into friction insert  2031 , which corresponds to friction insert  1931 , at thread interface  2092 . In one embodiment, the friction inserts may be glued together at glue area  2091  using adhesives well-known in the art. 
     FIG. 21A  is a perspective view of one embodiment of a base termination ball  2133 . Base termination ball  2133  is similar to friction limit ball  1826 , except that one end of base termination ball  2133  includes a flattened base portion  2192  to couple moveable assembly to a moveable base structure. An annular friction ring  2191 , such as those previously described, is formed or attached at one end of base termination ball  2133 . Flattened base portion  2192  may be coupled with a moveable base structure using screw holes  2197 ,  2195 C,  2195 A, and  2195 B. Additionally, flattened base portion  2192  may include a central tension cable guide orifice  2194 , a pair of anti-torsion cable orifices  2193 , and a plurality of cable guide orifices  2196 . Like friction limit balls  1826 , base termination bail  2133  may be made of metal (e.g. stainless steel or aluminum). 
     FIG. 21B  is a bottom view of base termination ball  2133 . The horizontal center-to-center distance  2151  between orifice  2195 C and  2195 B is approximately 24.00 mm. Orifice  2195 B is located a distance  2152  of approximately 12.00 mm from a vertical line running through the center of tension cable guide orifice  2194 , and located a distance  2154  of approximately 7.50 mm from a horizontal line running through the center of tension cable guide orifice  2194 . The vertical center-to-center distance  2155  between orifice  2195 B and  2195 A is approximately 15.00 mm. In one embodiment, distance  2156  measures approximately 14.50 mm. 
     FIG. 21C  is a cross-sectional side view of base termination ball  2133  taken along the line A-A in  FIG. 21B . Outer diameter  2157  of the flattened base portion measures approximately 34.45 mm. Distance  2158  measures approximately 13.50 mm. Arc  2159  measures approximately 36.0 degrees. Distance  2162  measures approximately 23.00 mm. The diameter  2161  of the tension cable guide orifice measures approximately 6.80 mm. Distance  2160  measures approximately 11.17 mm. The outer diameter  2164  of base termination ball  2133  measures approximately 38.00 mm. 
   It will be appreciated that aspects of the present invention may be used with a variety of moveable assemblies which allow for selectable positioning of a flat panel display device (FPDD).  FIGS. 22A ,  22 B, and  22 C show examples of such moveable assemblies which incorporate aspects of the present invention. Examples of these aspects include a base computer system which is moveable by a person and is not physically attached to a surface (expect through the weight of the system due to gravity), or the use of a single actuator on the back of the FPDD in order to control the repositioning of the FPDD without requiring the actuation or loosening of multiple locks for the various joints, or a data cable which is housed within the structure of the moveable assembly. 
     FIG. 22A  shows an example of a moveable assembly  2202  which is coupled to an FPDD  2203  at one end of the moveable assembly and is coupled to a base computer system  2201  at another end of the moveable assembly  2202 . The base computer system  2201  is similar to the base computer system  242 A. It includes many of the typical components of a computer system and has been designed in both size and weight to adequately and stably support the FPDD at a variety of different positions. For example, the base computer system  2201  is designed with sufficient weight such that, without physically attaching the base computer system  2201  (except through gravity) to the surface  2204 , the base computer system  2201  will allow the FPDD  2203  to be extended out beyond the edge of the computer system  2201  as shown in  FIG. 22A  without causing the whole system to overturn. Thus the entire system  2200  allows the FPDD  2203  to be positioned at any one of a multitude of locations in which the FPDD  2203  can be positioned given the extent of reach provided by the moveable assembly  2202 . 
   The moveable assembly  2202  includes a post (e.g. arm member)  2205 , a post  2206 , and a post  2207  which are coupled to each other through joints  2210  and  2209  as shown in  FIG. 22A . The post  2205  is coupled to the base computer system  2201  through the rotatable joint  2208  which allows the post  2205  to rotate as shown by arrow  2216  around the joint  2208 . The joint  2209  allows post  2206  to rotate relative to post  2205 , allowing an angular displacement along the arrow  2214  as shown in  FIG. 22A . Similarly, the angle between post  2206  and  2207  may be varied as these two posts are moved through the joint  2210 , allowing motion along the arrow  2215 . Both joints  2209  and  2210  include locking mechanisms  2212  and  2213  respectively, allowing the relative angular position between the corresponding posts to be fixed. 
   In the embodiment shown in  FIG. 22A , articulation of both joints simultaneously will require loosening of both joints in order to allow complete control of the movement of the FPDD. In an alternative embodiment of the system shown in  FIG. 22A , a single locking actuation control may be disposed on the surface of the FPDD  2203  in a manner which is similar to the handle  241  described above. In one embodiment, this single actuation control may be an electromagnetic control which loosens or tightens the joints electromagnetically under the control of the single actuation switch disposed on the FPDD  2203 . The post  2207  terminates in a gimbal joint  2211  which is coupled to the FPDD to allow movement of the FPDD relative to the post  2207 . Within the interior portions of the posts  2205 ,  2206  and  2207 , there are disposed data and power cables  2220  and  2221 . In one embodiment, these cables are concealed within the interior of the posts, which represent another form of a moveable assembly for supporting an FPDD. It will be appreciated that other computer system-related cables may be housed within the interior portions of posts  2205 ,  2206 , and  2207 . 
     FIG. 22B  shows another example of a moveable assembly  2233  in a system  2233  which includes a base computer system  2232  and an FPDD  2248 . The entire system  2233  rests, through gravity, on the surface  2239  without being physically attached to the surface except through gravity. As noted above, the bottom of the computer system  2232  may include a non-slip surface, such as rubber feet. Given that the weight and size of the base computer system  2232  is designed according to the teachings of the present invention to allow the support of the FPDD  2248  in a variety of selectable positions of the FPDD  2248 , there is no need for the base computer system  2232  to be physically attached to the surface  2239  through the use of clamps or glues or bolts or screws, etc. 
   In one embodiment of the example shown in  FIG. 22B , the computer system  2232  has a weight and size which allows a single human user to be able to move the computer system without assistance from another person or from a mechanical assistance. The base computer system  2232  is attached to post  2235  through a rotatable joint  2238 , which allows the post  2235  to rotate around the base computer system along the arrow  2243 . Post  2236  is coupled to post  2235  through the joint  2239 , which will be locked through the locking mechanism  2240 . The joint  2239  allows the angle between post  2235  and  2236  to be varied by moving the post  2236  along the arrow  2241 . One end of the post  2236  supports a counterweight  2237  and another end of the post terminates in a gimbal joint  2244  which is attached to the back of the FPDD  2248 . Posts  2235  and  2236 , in the embodiment shown in  FIG. 22B , include power and data cables  2270  and  2249 , respectively, which are disposed within these posts and thereby concealed by these posts. A single actuating device or switch  2250  may optionally be located on the FPDD  2248  to allow for the release of one or more lockable joints in order to allow the selectable positioning or repositioning of the FPDD. 
     FIG. 22C  shows another example of a moveable assembly  2264  in a system  2260  which includes the moveable assembly as well as an FPDD  2263  and a base computer system  2261  which rests on a surface  2262 , which may be a desk surface. As noted above, the base computer system  2261  is typically designed to have a weight and size such that it will support the selectable positioning and repositioning of the FPDD  2263  over a large range of movement of the FPDD  2263 . The moveable assembly  2264  includes three posts,  2267 ,  2268  and  2269 , and also includes three joints  2271 ,  2272  and  2273 , and also includes two counterweights  2277  and  2278 . The moveable assembly  2264  also includes a gimbal joint  2274  which couples the post  2269  to the FPDD  2263 . An optional single actuator control  2280  may be disposed on the FPDD  2263  in order to unlock or lock one or more of the joints. The embodiment shown in  FIG. 22C  may also optionally include the use of power and data cables, which are disposed within the posts  2267 ,  2268 , and  2269 . 
   In  FIG. 23A , the computer controlled display system  2300  includes: a flat panel display device  2301  having a display surface  2302  and an input  2303  for receiving display data to be displayed on the display surface  2302 . A moveable assembly  2304  is mechanically coupled to the flat panel display  2301 . The moveable assembly  2304  has a cross-sectional area, which is substantially less than an area of the display surface  2302 . Moveable assembly  2304  is moveable when handle  2307  is depressed, to allow the flat panel display device  2301  to be selectively positioned in space relative to a user of the computer controlled display system  2300 . A base (e.g. moveable enclosure)  2305  is coupled mechanically to the moveable assembly  2304  and to the flat panel display device  2301  through the moveable assembly  2304 . In one embodiment, the base houses concealed computer components, which include, but are not limited to: a microprocessor, a memory, a bus, an I/O (input/output) controller, optical drive, network interface, and I/O port. In such an embodiment, the microprocessor is coupled to the input of the flat panel display  2301 . In a preferred embodiment, the cross-sectional area is defined by a cross-section taken perpendicularly to a longitudinal dimension of the moveable assembly  2304 . 
   In one embodiment, the moveable assembly  2304  is moveable such that the FPDD  2301  has at least three degrees of movement. In one embodiment, the overall weight of the entire system is less than about 45.0 lbs and a footprint size of the base  2305  is less than an area of about 4.0 square feet. 
   In a further embodiment, an actuator  2306  is attached to the flat panel display  2301  and coupled to a force generator (e.g. spring/piston assembly) which maintains the moveable assembly  2304  in a rigid mode when the actuator (handle)  2306  is in a first state, and which allows the moveable assembly  2304  to be moveable when the actuator (handle)  2306  is in a second state. In a preferred embodiment, the actuator  2306 , through a single actuation, allows simultaneous positioning of the flat panel display  2301  and moveable assembly  2304  in multiple degrees of freedom. 
   In one embodiment, a data cable (not shown) is coupled to the input of the flat panel display  2301  at a first end, and coupled to a display controller (not shown) housed within the base  2305 , the cable being disposed (and/or concealed) within the moveable assembly  2304 . In a further embodiment, an anti-torsion cable (not shown) is coupled to (and preferably within) the moveable assembly  2304  to restrain the flat panel display (and the moveable assembly  2304 ) from being rotated beyond a pre-determined amount. 
   In a further embodiment, the longitudinal dimension of the moveable assembly  2304  extends from the flat panel display  2301  to the base  2305 , and a weight of the system  2300  is less than about 25.0 lbs and a footprint size of the base  2305  is less than an area of about 500.0 square centimeters. 
   In a further embodiment, the base  2305  is not fixedly secured to a supporting surface under the base  2305 . 
     FIG. 23B  is a perspective view of another embodiment of a computer controlled display device including a FPDD  2301  coupled with a moveable assembly  2304 , which is coupled with a base  2305 . As shown, actuator assembly  2306  is mounted on or contained within the rear housing  2308  of FPDD  2301 . In one embodiment, the internal structure of FPDD is strengthened to withstand the compressive user forces applied simultaneously to handle  2306 A and the front surface of FPDD  2301 . The external shape of base  2305 , in one embodiment, forms a toroid, as shown, and includes an inner metal Faraday cage, concealed by a layer of plastic, which repels external Electromagnetic Frequencies (EMF) that may interfere with operation of the computer components concealed within the base  2305 . The Faraday cage also contains internal EMF generated by the concealed computer components. In one embodiment, the concealed metal Faraday cage, like the outer plastic layer, is manufactured in two pieces, a top portion and a bottom portion, which when fitted together form a toroid. The Faraday cage may be made of zinc, zinc alloys, or other suitable metals known in the art. 
   In one embodiment, the base  2305  and its internal components weighs approximately 13.0 pounds, while the FPDD  2301  weighs approximately 4.5 pounds. Additionally, the moveable assembly  2304 , base  2305 , and FPDD  2301  are manufactured such that a user can safely lift computer system  2300  using moveable assembly  2304  as a carrying handle. Additionally, the system is manufactured such that a user can safely hoist the entire system simply by grasping the FPDD  2301  and lifting. The terms “safely lift” and “safely hoist” mean that the various system components suffer minimal or no external or internal damage as a result of the user&#39;s lifting actions. 
   As shown in  FIG. 23B , the exterior plastic housing of base  2305  may be formed of two parts, a top portion and a bottom portion  2305 A, which, when fitted together, form a toroid. The bottom portion  2305 A may contain a plurality of peripheral ports and/or computer system-related controls  2310 . Such ports and controls illustratively include, but are not limited to one or more of: a Firewire port, an Ethernet port, a modem jack, a power button, a reset button, a USB port, an infrared port, and similar computer system-related ports and controls. 
     FIG. 23C  is a side view of the computer system  2300  shown in  FIGS. 23A and 23B , according to one embodiment of the invention. System  2300  includes a FPDD  2301  having an actuator assembly  2306  attached thereto; a moveable assembly  2304  attached to the actuator assembly  2306 , and a base  2305  attached to the moveable assembly  2304 . In this embodiment, moveable assembly  2304  is a snake-like ball-and-socket assembly; however, it will be appreciated that other types of assemblies may also be used. Additionally, an optical drive (e.g. CD and/or DVD) aperture  2312  is provided in the top portion of base  2305 . Aperture  2312 , in one embodiment, includes an electronically activated fold-down door and an electronically activated slide-out optical disk tray. In one embodiment, pressing a button on a keyboard coupled with base  2305  activates the fold-down door and slide-out tray. 
     FIG. 23D  is a rear-view of the computer system  2300  shown in  FIGS. 23A-23C , according to one embodiment of the invention. As shown, system  2300  includes FPDD  2301 , actuator assembly  2306 , moveable assembly  2304 , and base  2305 , which includes a plurality of peripheral ports and computer system-related controls  2310 , as described above. 
     FIG. 23E  is a front view of the computer system  2300  of  FIGS. 23A-23D , according to one embodiment of the invention, and showing FPDD  2301 , viewing surface  2302 , and base  2305 . 
     FIG. 23F  is another side view of the computer system  2300  of  FIGS. 23A-23E , according to one embodiment of the invention, and showing FPDD  2301 , actuator assembly  2306 , moveable assembly  2304 , and base  2305 . 
   Referring now to  FIG. 23G , a moveable assembly  2302  similar to that previously described with reference to  FIGS. 4A and 4B  is shown coupled with a flat panel display  2310 , which, in one embodiment, includes a housing  2301  attached to a portion of the flat panel display obverse from a viewing portion  2311  of the flat panel display  2310 . Housing  2301  is coupled to moveable assembly  2302  using at least one screw  2331  or a plurality of screws  2331 . Within housing  2301  are various components of actuator assembly  2300 A. Illustratively, such components include a tongue  2305 , a crank  2303 , a strut  2309 , a spring guide  2308 , and a spring  2370 . Tongue  2305  has a distal end  2306 B coupled with a ball ferrule  2335 , which is attached to a tension cable  2334  extending through an interior portion of moveable assembly  2302 . A proximal end  2306 A of tongue  2305  is coupled with a distal end  2303 B of crank  2303 . The proximal end  2303 A of crank  2303  is operatively coupled with the distal end of a strut  2309 , and a proximal end of strut of  2309  is coupled with a distal end  2308 B of spring guide  2308 , which is inserted within the interior of a spring  2370 . In one embodiment, spring guide  2308  progressively narrows or tapers downwards from the distal end  2308 B to its proximal end  2308 A, which includes a bushing  2350 , which helps reduce friction and wear as proximal end  2308 A slides within channel  2307 . In one embodiment, tongue  2305  may include at its proximal end  2306 A a channel extending therethrough into which a set screw or other screwlike mechanism  2305 A is placed. Set screw  2305 A may be adjusted to vary the angle at which the distal end of tongue  2305  contacts the ball ferrule of tension cable  2334 . 
   In one embodiment, a handle  2360  having a distal end  2360 B and a proximal end  2360 A may be operatively coupled with the actuator assembly  2300 . In one embodiment, distal end  2360 B of handle  2360  is coupled with a top portion of crank  2303  using a set screw  2332 . In one embodiment, proximal end  2360 B is fashioned into an ergonomic design. 
   Referring again to  FIGS. 4A and 23G , it will be appreciated that the actuator assembly  2300  shown in  FIG. 23G  differs from the actuator assembly  400 , shown in  FIG. 4A . In  FIG. 4A  the distal end of handle  460  was coupled with ball ferrule  434  attached to tension cable  490 , whereas in  FIG. 23G , the distal end  2360 B of handle  2360  is coupled crank  2303 , which is operatively coupled with tongue  2305 . Tongue  2305 , in turn, is coupled with the ball ferrule  2335  attached to tension cable  2334 . 
   Comparing  FIGS. 4A and 23G , It will be appreciated that the angle at which tongue  2305  contacts ball ferrule  2335  is greater than the angle at which distal end of handle  460  contacts ball ferrule  434 . In  FIG. 23G , the changed tongue angle provides the tensioning mechanism (e.g. actuator assembly  2300 A), with increased mechanical advantage as the cable  2334  becomes tighter, which reduces the amount of user force required to relax moveable assembly  2302 . In one embodiment, an angle measured between a first horizontal line drawn through the center of pivot  2370  and a second oblique line extending from the center of pivot  2370 , centrally through the distal end  2306 B of tongue  2305 , measures in the range of approximately 40.0 degrees to approximately 85.0 degrees, preferably approximately 70.0 degrees. 
     FIG. 24A  is a perspective view of a tongue  2400 , which corresponds to tongue  2305  in  FIG. 23G . In  FIG. 24A  tongue  2400  includes a distal end  2497  and a proximal end  2496 . A cylindrical bore  2492  extends through the middle portion of tongue  2400  in one embodiment. In one embodiment, the distal end  2497  of tongue  2400  includes a bore (or cavity)  2495  extending from a top surface of tongue  2400  downward towards a bottom surface of tongue  2400 . Similarly, at proximal end  2496  of tongue  2400  there is included a cylindrical bore  2491  extending from a top surface of tongue  2400  to a bottom surface of tongue  2400 . These features are better shown with reference to  FIG. 24B , which is a cross-sectional side view of tongue  2400  shown in  FIG. 24A . 
   In  FIG. 24B  tongue  2400  has an overall length  2451  of approximately 41.47 mm. A distance  2452 , as measured from the center point of bore  2491  to a center point of horizontal bore  2492  measures approximately 15.83 mm. A center-to-center distance  2454  from bore  2492  to bore  2495  measures approximately 13.64 mm. A distance  2453  from a bottom surface of distal end  2497  to a horizontal line  2499  extending through the midpoint of bore  2492  measures approximately 14.63 mm. In one embodiment, the radius  2455  of bore  2492  measures in the range of approximately 11.100 mm to approximately 11.125 mm. Similarly, an interior beveled portion of cavity  2495  has a radius of approximately 11.40 mm plus or minus 0.25 mm. 
   With reference to  FIG. 24D , which is an end view of tongue  2400 . It will be appreciated that tongue  2400  in one embodiment, has a depth (or height)  2459  of approximately 22.63 mm as measured from a top surface  2400 A to a bottom surface  2400 B of tongue  2400 .  FIG. 24C  shows a top view of tongue  2400  according to one embodiment of the invention. In  FIG. 24C  tongue  2400  has a width  2456  of approximately 11.15 mm minus 0.15 mm. Width of  2456  is measured from a first side  2492 A to a second side  2492 B of bore  2492  extending through a mid portion of tongue  2400 . In one embodiment, a bottom portion of cavity  2495  is substantially elliptical in shape and has a width  2457  of approximately 6.97 mm. A width  2458  of distal end  2497  as measured from a first side  2497 A to a second side  2497 B measures in one embodiment, approximately 13.50 mm. 
   Referring now to  FIG. 25A  there is shown a perspective view of a glide ring  2500 , which in one embodiment is inserted within a friction socket plunger to preserve the cosmetic finish of the balls. As shown in  FIG. 25A , glide ring  2500  is substantially spherical in shape having a base portion  2505  which in one embodiment is an annular ring attached to a bottom surface of glide ring  2500 . In one embodiment, glide ring  2500  has a first diameter  2501  which is larger than a second diameter  2502 , wherein the interior and exterior surfaces of glide ring  2500  curvingly taper from the first diameter  2501  toward the second diameter  2502 . In one embodiment, the upper sidewall portions of glide ring  2500  may include a plurality of slots  2503  extending downward from a top surface of glide ring  2500  towards the second diameter  2502 . In one embodiment, a plurality of pegged feet  2504 , may be attached to the outer bottom portion of glide ring  2500 . These pegged feet  2504  may be used to hold glide ring securely within an abrasive socket plunger (not shown) by inserting one or more of feet  2504  within a corresponding plurality of holes positioned within an abrasive socket plunger (not shown). 
     FIG. 25B  is a bottom view of glide ring  2500 , shown in  FIG. 25A . In one embodiment, an angle as measured from a line  2509  extending from a center point of glide ring  2500  through a pegged foot  2504  to a second line  2510  extending through the midpoint of glide ring  2500  through the center of a slot  2503 A measures approximately 30.0 degrees. 
     FIG. 25C  is a side view of glide ring  2500 , shown in  FIG. 25A , further illustrating placement of slots  2503  and pegged feet  2504 . 
     FIG. 25D  is a top view of glide ring  2500 . 
     FIG. 25E  is a cross-sectional side view glide ring  2500  taken along the line A-A in  FIG. 25D . In  FIG. 25E  a focal point  2557  is centered a distance  2556  of approximately 17.875 mm above the base of glide ring  2500  as measured from a vertical line  2556 A extending through focal point  2557  to a second parallel line  2556 B. In  FIG. 25E , a line  2555 B, perpendicular to line  2556 A extends from focal point  2557  through the center portion of glide ring  2500 . 
   Angle  2555 , as measured between lines  2555 A and  2555 B, measures, in one embodiment, approximately 63.70 degrees. The outer radius  2551  of the outer wall of glide ring  2500  measures approximately 41.500 mm minus 0.025 mm, while the inner wall  2552  has a radius measuring approximately 40.000 mm minus 0.025 mm. In one embodiment, the inner diameter  2553  of base portion of glide ring  2500  measures approximately 21.50 mm while the outer diameter  2554  measures approximately 23.00 mm minus 0.025 mm. 
   Glide ring  2500  may be made of various materials, including but not limited to: plastics, polymers, metals, glass, and fiberglass. Preferably, glide ring  2500  is made of Ryton®, having a nominal wall thickness of approximately 3.0 mm. In one embodiment, the material comprising glide ring  2500  may include an abrasive material or a lubricating material. For example, fiberglass strands may be incorporated within a glide ring formed of plastic, to increase the frictional qualities of glide ring  2500 . Similarly, a lubricant such as (but not limited to) Teflon® may be incorporated within a glide ring formed of a polymer or a plastic. In one embodiment, a plurality of plastic glide rings  2500  may be manufactured, each having a different frictional quality. For example, Teflon® may be incorporated into a first glide ring positioned within a first socket assembly coupled with a flat panel display, while fiberglass may be incorporated within a second and third glide rings positioned within corresponding second and third socket assemblies operatively coupled with the first socket assembly. In one embodiment, glide rings  2500  are only used in the three socket assemblies nearest the flat panel display. In alternate embodiment, a plurality of glide rings  2500 , having the same or different frictional qualities, may be used throughout the length of a moveable assembly. 
   Glide ring  2500  should be manufactured such that its straight edges have a straightness tolerance of 0.05 per centimeter, not to exceed 0.4 over the entire surface; and such that its flat surfaces have a flatness tolerance of 0.05 per centimeter, not to exceed 0.4 over the entire surface. 
   Where glide ring  2500  is molded, the mold should be designed to minimize ejection pin marks, gate blush, lines, and weld marks. Mold construction should conform to good molding industry practices as stated in the current edition of “Standard Practices of Custom Molders” by the Society of Plastic Industry, Inc. Similarly all exterior surfaces should be free of sinks, gate marks, ejection marks, and other type of cosmetic defects including but not limited to splay, included particles, bum marks, and similar imperfections. 
     FIG. 26A  shows an abrasive socket bearing  2600 , which in one embodiment, may be inserted within the rim of a friction socket (not shown). In one embodiment, abrasive socket bearing  2600  may be brazed or coated with an abrasive material such as silica, aluminum oxide, tungsten-carbide, or other abrasive material. 
   Referring now to  FIG. 26B , there is shown a side view of an abrasive socket bearing  2600 . In one embodiment, abrasive socket bearing  2600  has a thickness  2605  measuring approximately 1.40 mm. In one embodiment, an outer diameter  2606  of abrasive socket bearing  2600  measures approximately 37.300 mm. 
     FIG. 26C  is a top view of abrasive socket bearing  2600 , shown in  FIG. 26A . 
   Referring now to  FIG. 26D , there is shown a cross-sectional side view of abrasive socket bearing  2600  of  FIG. 26A  taken along the line A-A in  FIG. 26C . As shown in  FIG. 26D , abrasive socket bearing  2600  has a wall  2602  whose outer surface is substantially perpendicular and whose inner top surface slightly curves toward a base portion  2602 A, which in one embodiment, is wider than a curved top portion  2602 B. In one embodiment, a rim  2601  may have a thickness  2661  of approximately 0.48 mm and a width  2662  approximately 0.24 mm. In one embodiment, a base portion of rim  2601  is attached to the substantially perpendicular side of wall  2602 . A base portion  2602 A of wall  2602  has a width  2663  of approximately 0.849 mm, plus or minus 0.015 mm. 
   Abrasive socket bearings  2600  may be comprised of various materials including, but not limited to: glass, metals, plastics, polymers, or fiberglass. In one preferred embodiment, abrasive socket bearing  2600  is comprised of Delrin® 500, AF, white; and has a nominal wall thickness of approximately 3.0 mm. In one embodiment, straight edges have a straightness tolerance of 0.05 per centimeter not to exceed 0.4 over the entire surface, and the flat surfaces have a flatness tolerance of 0.05 per centimeter, not to exceed 0.4 over the entire surface. The abrasive socket bearing  2600  may be added to a friction socket (not shown) to provide an improved and more stable friction performance than can be obtained using the friction inserts shown in  FIGS. 19A-19C . 
     FIG. 27A  is an exploded perspective view of a friction socket assembly  2700 , according to another embodiment of the present invention. Socket assembly  2700  is similar to socket assembly  1927  shown in  FIG. 19A . Referring again to  FIG. 27A , socket assembly  2700  includes abrasive socket bearings  2701 A and  2701 B, abrasive inserts  2702 A and  2702 B. In one embodiment, abrasive insert  2702 A couples with abrasive insert  2702 B to hold socket assembly  2700  together. 
   Referring again to  FIG. 27A , socket assembly  2700  further includes an outer socket plunger  2703 , an inner socket plunger  2705 , and a resilient member (wavespring)  2704 , which may be used to store potential energy when plungers  2703  and  2705  are compressed. The stored potential energy may later be used to reduce the amount of a user force needed to change a state of a moveable assembly in which socket assembly  2700  is incorporated. In one embodiment, the components of socket assembly  2700  may be manufactured using the materials and methods used to manufacture the components of socket assembly  1927  in  FIG. 19A . 
   Referring now to  FIG. 27B , there is shown a cross-sectional side view of an assembled socket assembly  2700 . In one embodiment, abrasive insert  2702 A is coupled with abrasive insert  2702 B, such that outer socket plunger  2703  and inner socket plunger  2705  compressively contact resilient member  2704 , which in one embodiment may be a wavespring. Also included in assembled socket assembly  2700  shown in  FIG. 27B  are abrasive socket bearings  2701 A and  2701 B. Abrasive socket bearing  2701 A is disposed within an outer rim of outer socket plunger  2703 . Similarly, abrasive socket bearing  2701 B is disposed within an outer rim of inner socket plunger  2705 . 
     FIG. 28  shows an exploded perspective view of an actuator assembly  2800 , similar to the actuator assembly shown in  FIG. 8 . Referring again to  FIG. 28 , actuator assembly  2800  includes a housing  2813 , having a distal end  2813 A and a proximal end  2813 B. In one embodiment, the end of proximal end  2813 B of housing  2813  includes a bore  2817 , into which a dogpoint self-locking hex socket screw  2801  may be inserted to retain spring  2815  within housing  2813 . 
   A spring shaft  2803 , having a bushing  2803 A located on its proximal end  2803 B, may be inserted within the interior of spring  2815 . Bushing  2803 A, in one embodiment, may slide within a channel formed in an end of screw  2801 . A shaft  2804  may be used to couple the distal end of spring shaft  2803  with a proximal end of strut  2805 . Similarly, shaft  2806 , retaining pin  2812 , needle bearing  2810 , and retaining end nylon washer  2811  may be used to couple the distal end of strut  2805  with the proximal end of crank  2809 . Likewise, a needle tongue bearing  2818 , a lever bushing  2808 , a shaft  2807 , and a retaining ring  2814  may be used to couple the distal end of crank  2809  with a center portion of tongue  2810 . 
   In one embodiment, the distal end of spring shaft  2803  contains a bore through which shaft  2804  may be inserted. Track bearing  2802 A and track bearing  2802 B may be coupled with ends of shaft  2804  such that the track bearings slide within apertures  2816  when actuator assembly  2800  is actuated. As shown in  FIG. 28 , apertures  2816  may be substantially rectangularly shaped openings disposed substantially horizontally within the sides of housing  2813 . In other embodiments, however, aperture  2816  may be inclined toward the proximal end  2813 B of housing  2813 , or inclined toward distal end  2813 A of housing  2813 . Similarly, front portions  2816 A of apertures  2816  may be inclined upward, such that apertures  2816 , when viewed from the side, resemble a substantially “L” or “J” shape. Other configurations of apertures  2816  will be readily apparent to those skilled in the art, and the shape and placement of apertures  2816  should be designed to minimize the user force required to compress spring  2815 . 
   In one embodiment, the components of actuator assembly  2800  may be manufactured using the materials and methods used to manufacture the components of the actuator assembly shown in  FIG. 8 . 
   Referring now to  FIG. 29A , there is shown a perspective view of a friction socket  2900 , into which glide rings  2910 A and  2910 B may be inserted. In one embodiment, an interior diameter  2905  includes a plurality of holes or apertures  2920 , into which one or more pegged feet  2904 A and  2904 B may be inserted to secure glide rings  2910 A and  2910 B within socket  2900 . In one embodiment, socket  2900  is manufactured using aluminum, and in one embodiment, inner diameter  2905  is made of the same material as socket  2900 . In one embodiment, holes or apertures  2920  extend through inner diameter  2905 . 
   Referring now to  FIG. 29B , there is shown a cross-sectional side view of an assembled socket  2900 , showing placement of glide rings  2910 A and  2910 B therein. 
     FIG. 29C  is a detailed view pf section A shown in  FIG. 29B . 
   Referring to  FIG. 30A , there is shown a perspective view of a spring guide (e.g. spring shaft)  3000 , according to one embodiment of the present invention. Spring guide  3000  includes a proximal end  3000 A and a distal end  3000 B. Proximal end  3000 A includes a bore  3006  extending therethrough, into which a needle bushing  3004  may be inserted. Proximal end  3000 A terminates in a substantially planar face  3007 , from the center of which extends a cylindrical barrel portion  3003 , having at least a recessed portion  3005  therein. Cylindrical barrel portion  3003  terminates in a concave face  3009 , from which extends another cylindrical barrel portion  3008 , having a smaller diameter than the first cylindrical barrel portion  3003 . Spring guide  3000  terminates at its distal end  3000 B. In one embodiment, a plastic bushing  3002  may be placed on the distal end  3000 B and secured with a retaining ring  3001 . 
   Referring now to  FIG. 30B , there is shown a cross-sectional side view of the spring guide  3000  shown in  FIG. 30A . As shown in  FIG. 30B , spring guide  3000  includes a proximal end  3000 A and a distal end  3000 B. Proximal end  3000 A is shown, including a bore  3006 , into which a needle bushing  3004  is inserted. Again, proximal end  3000 A terminates at the substantially planar face  3007 , from which extends a cylindrical barrel portion  3003 , having one or more recessed portions  3005  therein. Extending from the proximal end  3000 A of cylindrical barrel portion  3003  is a second cylindrical barrel portion  3008 , having a small diameter than cylindrical barrel portion  3003 . At the proximal end  3000 B of spring guide  3000  is disposed a plastic bushing  3002 , secured in place with a retaining ring  3001 . 
   Referring now to  FIG. 31A , there is shown a perspective view of a socket  3100 , having an interior diameter  3101 , which contains a plurality of apertures or holes  3120 . In one embodiment, socket  3100 , including annular ring  3101 , is manufactured of aluminum or similar metal. 
   Referring now to  FIG. 31B , there is shown a top view of the socket  3100  shown in  FIG. 31A . In one embodiment, annular ring  3101  contains approximately 12 holes (or apertures)  3120 , each hole having a diameter of approximately 3.0 mm, plus 0.20 mm. In one embodiment, the centers of holes  3120  are centered within the annular ring  3101 , which has a radius of approximately 30.0 mm as measured from the center point  3130  of socket  3100 . In one embodiment, a line  3160 A passing through the center of hole  3120 A makes an angle  3160 , with a horizontal line  3160 B passing through center point  3130  of socket  3100 , of approximately 30.0 degrees. 
   Referring now to  FIG. 31C , there is shown a cross-sectional side view of socket  3100  taken along the line A-A in  FIG. 31B . In one embodiment, the diameter  3162  of annular ring  3101  measures approximately 23.10 mm. The focal point  3166  is located on a line  3165  passing through the center of socket  3100 , approximately a distance  3167  of 5.243 mm, plus or minus 0.015 from an outer edge of socket  3100 . 
   Distance  3161 , extending from focal point  3166  to focal point  3168 , measures approximately 36.0 mm. A radius  3164 , extending from focal point  3166 , measures in one embodiment approximately 20.750 mm, minus 0.025 mm. Similarly, a second radius  3163 , extending from focal point  3166 , measures approximately 20.15 mm, plus 0.15 mm. A third radius, shown in  FIG. 31D  as radius  3169 , as measured from focal point  3166 , measures in one embodiment approximately 19.50 mm, plus or minus 0.8 mm. 
   Referring now to  FIG. 32A , there is shown a perspective view of a tension cable assembly  3200 , according to an embodiment of the present invention. Tension cable assembly  3200  may include a tension cable  3202 , having a proximal end  3205 A and distal end  3205 B. In one embodiment, proximal end  3205 A may include a ball ferrule  3201  attached to tension cable  3202 . 
   In one embodiment, a nylon sleeve  3203  may be fitted over tension cable  3202 , and a Teflon® sheath  3204  may be fitted over the nylon sleeve  3203 . Use of the nylon sleeve  3203  and the Teflon® sheath  3204  reduces sliding friction as tension cable  3202  passes through a moveable assembly (not shown). The reduced friction lessens the amount of work a user must provide on a state of the moveable assembly. 
   In one embodiment, sheath  3204  may be formed of a slippery (e.g. low friction) material such as polyethylene or delron. Sheath  3204  may be comprised entirely of Teflon® or a structural material forming sheath  3204  may be coated with a Teflon® coating. 
   In one embodiment, friction is generated between tension cable  3202  and interior parts of a moveable assembly whenever tension cable  3202  is tensioned. To reduce sliding friction and even out the load, a lubricant such as a dry grease may be applied between nylon sleeve  3203  and sheath  3204 . In one embodiment, the lubricant has a high molecular weight and is of a type which is compatible with nylon, Teflon®, and plastics. The lubricant should be non-migrating, meaning that it has a high viscosity, because it is important that whatever lubricant is used does not escape the sheath  3204  to contaminate the friction surfaces of the sockets comprising a moveable assembly (not shown). 
   In one embodiment, migration of sheath  3204  and sleeve  3203  during movement of the moveable assembly may be prevented by crimping and/or melting sheath  3204  and sleeve  3203  at various points along tension cable  3202 . Additionally, a rib (not shown) may be formed on the outer portion of sleeve  3204  to contact a sheath stop located within the interior of the moveable assembly. 
     FIG. 33A  is a perspective frontal view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302 , according to another embodiment of the invention. In  FIG. 33A , moveable assembly  3302  is coupled with a flat panel display  3310  to support the flat panel display  3310  at a designated space around the base  3306 . In the embodiment shown, moveable base  3306  is hemispherical or toroidal in shape, and has a substantially flat, substantially circular, bottom portion  3306 B from which a curved housing  3306 A rises. The apex of housing  3306 A is substantially centered at a pre-determined vertical distance above the center of the substantially circular bottom portion  3306 B. In one embodiment, bottom portion  3306 B is formed of a single piece of material and shaped so as to operatively couple with the hemispherical (or toroidal) top portion of housing  3306 A. It will be appreciated that though the moveable base  3310  illustratively shown has a hemispherical shape, other designs, such as squarish shapes, rectangular shapes, cylindrical shapes, substantially pyramidal shapes, or other geometric shapes (together with modifications and/or combinations thereof) may be used. Thus, such designs, regardless of shape are to be construed as falling within the scope of the present invention. 
   The moveable base, together with the rest of the computer system  3300 , weighs in the range of about 10.0 lbs to about 45.0 lbs, and is moveable by a single, unaided person. The moveable base is not required to be fixedly attached to the surface on which it rests. The size and weight of the moveable base is designed, in the manner described above, to allow the selective positioning of display  3310  at a wide variety of different positions without causing the system to overturn or flip over. 
   The outer and inner sections of top portion  3306 A and bottom portion  3306 B of base  3306  may be formed of the same or different materials. Illustrative materials, which may be used in various embodiments of the invention, include but are not limited to metals, plastics, polymers, glass, and fiberglass. Illustrative metals include stainless steel, aluminum, titanium, similar metals, and composites thereof. It will be appreciated that various plastics, polymers, and composites thereof suitable for making the outer and inner portions of base  3306  will be known to persons skilled in the engineering and manufacturing arts. 
   In one embodiment, top portion  3306 A and bottom portion  3306 B are coupled together using snap fittings, screws, and/or adhesives. In another embodiment, base  3306  is substantially formed (e.g. 80% or more) of a single piece of material. In such embodiments, base  3306  may contain one or more access ports (not shown) to permit user or technician access into the interior of base  3306 . 
   A plurality of holes  3304  may perforate the top of the hemispherical top portion of housing  3306 A to allow airflow to flux in and out of the interior of base  3306  to cool electronic components housed within moveable base  3306 . Such components may include, but are not limited to: a central processing unit, a memory, a display driver, and an optical drive (e.g. DVD and/or CD-rom drive). 
   In one embodiment, an elongated aperture  3308  is substantially horizontally disposed within base  3306 . Aperture  3308  may be equipped with a protective covering, aesthetically pleasing to the eye, which, in alternate embodiments, may take the form of sliding doors, flip-up or flip-down doors, side-opening doors, a slide-out loading tray, a protective membrane, or a dust curtain. In one embodiment, aperture  3308  houses a loading slot and/or tray for an internal DVD/CD rom drive. In another embodiment, aperture  3308  houses sound, volume, brightness, contrast, and other controls. Aperture  3308  may also include a wireless port. 
   Flat panel display device  3310 , which may be of any type suitable for use with computer systems, includes a front viewing surface  3310 . Its overall size and weight are chosen in coordination with the footprint and weight of the base  3306 , such that base  3306  does not tilt when flat panel display  3310  is supported beyond the perimeter of base  3306  by moveable assembly  3302 , which is attached to a rear surface of flat panel display  3310  and to a top portion  3306 A of base  3306 . The weight of base  3306  is chosen such that base  3306  adequately supports moveable assembly  3302  and flat panel display  3310  attached thereto without tipping; and such that a user can easily move computer system  3300 . Thus, in one embodiment, the weight of base  3306  is in the illustrative range of approximately 10.0 to approximately 25.0 pounds. 
     FIG. 33B  is perspective rear view of a computer system  3300  including a flat panel display device  3310  and a moveable base  3306  coupled with a moveable assembly  3302  according to one embodiment of the invention. In the embodiment shown in  FIG. 33B , moveable assembly  3302  includes a tubular member  3326  having a distal end coupled with the rear portion  3310 B of flat panel display  3310  and a proximal end coupled with the base  3306 . The distal end of tubular member  3326  may include a flexible joint  3322 A, secured to the distal end of tubular member  3326  by retaining assembly  3324 A, which, in one embodiment, includes a tubular shaft and a retaining pin. Flexible joint  3322 A may terminate in or be attached to a shaft  3320 A, which is coupled to the rear portion  3310 B through washer  3318 A. The proximal end of tubular member  3326  may include a flexible joint  3322 B, secured to the proximal end of tubular member  3326  by retaining assembly  3324 B. Flexible joint  3322 B may terminate in or be attached to a shaft  3320 B, which is coupled to base  3306  through washer  3318 B. Additionally, a gimbal (not shown) may be used to attach shafts  3320 A and/or  3320 B with flat panel display  3310  and/or base  3306 , respectively. Retaining assembly  3324 B secures flexible joint  3322 A to tubular member  3326 . 
   Also shown in  FIG. 33B , are a plurality of peripheral ports  3316  and a power button  3314 , located within the rear exterior portion of the bottom portion  3306  of base  3306 . Particular types of ports are detailed with respect to  FIG. 33E , below. 
     FIG. 33C  is a side view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302  according to one embodiment of the invention. In  FIG. 33C , computer system  3300  is viewed from the right hand side. Bottom portion  3306 B of base  3306  may include a plurality of ventilation apertures  3326  used to cool the electronic components housed within the interior of base  3306 . 
     FIG. 33D  is a front view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly (not shown) according to one embodiment of the invention. Flat panel display  3310  includes a viewing area  3310 A. Base  3306  includes an aperture  3308 , as previously described. 
     FIG. 33E  is a rear view of a computer system  3300  including a flat panel display  3310  and a moveable base  3306  coupled with a moveable assembly  3302  according to one embodiment of the invention. Flat panel display  3310  includes a rear portion  3310 B to which a distal end of moveable assembly  3302  is attached. As shown, a plurality of peripheral ports and system controls  3314 ,  3328 ,  3329 ,  3330 ,  3332 ,  3334 ,  3336 ,  3338 ,  3340 ,  3342 , and  3344  may be included within base portion  3306 B. Such ports and controls include but are not limited to: power button, microphone jack, speaker jack, Ethernet port, power plug, analog or digital telephone jack, infrared port, USB port, Firewire port, system reset button, and other computer system-related ports and controls. 
     FIG. 33F  is another side view of a computer system  3300  including a flat panel display  3310  and moveable base  3306  coupled with a moveable assembly  3302  according to one embodiment of the invention. In  FIG. 33F , computer system  3300  is viewed from the left hand side. 
   Referring now to  FIG. 34 , there is shown a simplified sectional side view of a computer system  3400  usable with an embodiment of the present invention. Computer system  3400  includes a base  3406  to which is attached one end of a moveable assembly  3401 . The other end of moveable assembly  3401  is attached to a flat panel display device (FPDD)  3404 . In the embodiment shown in  FIG. 34 , the moveable assembly  3401  is a mechanical linkage that supports the weight of FPDD  3404  as it is moved in one or more degrees of freedom relative to a weighted, moveable base  3406 , which rests on a support surface such as a desk, table, or other substantially planar support surface. Alternatively, the end of moveable assembly  3401  attached to base  3406  (or the base  3406  itself) could be mounted on a wall or other support device. 
   It will be appreciated that the embodiments of the invention shown in  FIGS. 34-39 , and described below, use a novel four-bar linkage (e.g. closed loop mechanism), which generally includes three moving links, one fixed link, and four pin joints. For example, one embodiment of the invention includes a ground link (e.g. base biscuit)  3410 B, an input link (e.g. canoes)  3401  (which correspond to canoes  3502 A and  3502 B in  FIG. 35 ), an output link (e.g. compression rod)  3412 , and a coupler link (e.g. display biscuit)  3410 A. The uniqueness of the disclosed and claimed embodiments is that the packaging creates an illusion that an apparatus other than a four-bar linkage is used because the output link (e.g. compression rod)  3412  is hidden inside the structure of the input link (e.g. canoes)  3401 . 
   It will be appreciated that a variety of relative motions of the coupler link (e.g. display biscuit) relative to the ground link (e.g. base biscuit) can be generated by varying the lengths of each of the lengths and the relative angles at which they attach to each other. Thus, the lengths of the input link (e.g. canoes)  3401  and output link (e.g. compression rod)  3412  may have the same or different lengths. Preferably, however, the lengths of the input link (e.g. canoes)  3401  and the output link (e.g. compression rod)  3412  are approximately the same. In such a configuration, the coupler link (e.g. display biscuit)  3410 A maintains its orientation relative to the ground link (e.g. base biscuit)  3410 B throughout the range of motion. 
   One embodiment of the invention uses connector links  3410 A and  3410 B on either end of the four-bar linkage (e.g. moveable assembly). The moveable assembly may be made by coupling round, disk shaped members  3410 A and  3410 B, together with an input link (e.g. compression rod)  3412 , and an output link (e.g. canoes)  3401  to form a closed-loop apparatus. In a unique embodiment, the output link (e.g. canoes)  3401  forms the exterior of the mechanism (e.g. moveable assembly), and conceals the compression rod  3412  and counterbalance spring  3408  assembly within its interior. The output link  3401  may be formed of two, semi-cylindrical sections (e.g. canoes) ( 3502 A and  3502 B in  FIG. 35 ) with half-spheres on either end. When the canoes are fastened together, the result is an outside skin that functions both as an aesthetic cover and as the output link for the four-bar mechanism. 
   One of several unique features associated with the embodiment shown in  FIG. 34 , is that the counterbalancing spring  3408  and a moveable link (e.g. compression rod)  3412  of the four-bar mechanical linkage are housed within a cosmetic arm  3402  that acts as a fixed link. Cosmetic arm  3402  is formed of canoes  3502 A and  3502 B assembled together. The term “moveable link” means a link that moves relative to a fixed link. Unlike a fixed link, the angle(s) at which a moveable link attaches to a coupler link (e.g. display biscuit)  3410 A and to a ground link (e.g. base biscuit)  3410 B change as the four-bar linkage is raised and lowered. In the unique four-bar linkage shown in  FIG. 34 , canoes  3401  function as a fixed link when coupled to the center portions of display biscuit  3410 A and ground biscuit  3410 B. Thus, the angle at which canoes  3401  contact biscuits  3410 A and  3410 B remains substantially constant as the four-bar linkage is raised and lowered. 
   On the other hand, end  3412 A of internal compression rod  3412  is attached to an off-center portion of ground biscuit  3410 B. The other end of rod  3412  is attached at a corresponding off-center portion of display biscuit  3410 A. When the four bar linkage is moved up and down, the lengths of compression rod  3412  and canoes  3401  do not change. However, the angle(s) at which compression rod  3412  attaches to biscuits  3410 A and  3410 B change relative to the angle(s) at which canoes  3401  attach to biscuits  3401 A and  3410 B. Thus, compression rod  3412  is said to “move” relative to canoes  3401 . This movement occurs, in part, because compression rod  3412  is mounted to each biscuit a distance off center of the biscuit&#39;s center, which creates a path length change. 
   Referring to  FIGS. 34 ,  35 ,  39 A and  39 B, spring  3408  includes an end  3408 B and an end  3408 A. Spring  3408  is a compression spring compressed between a spring core  3430  attached to canoes  3401  (which correspond to canoes  3502 A and  3502 B in  FIG. 35 ) and a pair of spring struts  3440  attached to an off center portion of ground biscuit  3410 B (which corresponds to biscuit  3503  in  FIG. 35 ). Spring core  3430  includes a first end  3431  that attaches to a rod  3416  which attaches to the interior of canoes  3502 A and  3502 B. A second end  3432  to spring core  3430  contains a flanged portion  3433  that mates with end  3408 A of spring  3408 . Spring struts  3440  include first ends  3441  that attach to an off center portion of base biscuit  3410 B (which corresponds to base biscuit  3503  in  FIG. 35 ), and second ends  3442  having eared portions  3443  that mate with end  3408 B of spring  3408 . In this manner, pre-tensioned spring  3408  exerts a restoring force along the length of spring core  3430  and spring struts  3440  that acts to push flanged portion  3433  and eared portion  3443  apart. 
   Referring again to  FIG. 34 , it will be appreciated that the spring  3408  is not necessary to the operation of the four-bar linkage. Rather spring  3408  is provided, in one embodiment to counterbalance the weight of a flat panel display  3404  attached to display biscuit  3410 A, such that the display feels substantially weightless to a user when the user grabs the display and attempts to move it. It will also be appreciated that the path length of spring  3408  changes as the four-bar linkage (e.g. moveable assembly) is moved up and down. For example, in one embodiment, spring  3408  expands as the four-bar linkage is raised, and contracts as the four-bar linkage is lowered. In its contracted state, spring  3408  stores potential energy. This stored energy is released to assist the user when spring  3408  expands during upward movement of display  3404 . 
   Referring again to  FIG. 34 , cosmetic arm  3402  may also enclose and conceal a display data cable and a power cable for providing display data and power to the FPDD  3404 . As shown in  FIG. 35 , base biscuit  3503  may include a channel  3507  through which the data and power cable may run. 
   It will be appreciated that the embodiments shown in  FIGS. 34 ,  35 , and  39  are illustrative only in that they can be scaled or modified to accommodate a wide variety of FPDD&#39;s  3404  of different weights and sizes. Additionally, the cosmetic appearance of the embodiment of  FIG. 34  may be modified to fit the needs of a particular user or consumer. 
   In one embodiment, the physical specifications associated with computer system  3400  are as follows: Arm  3402  has a diameter of approximately 42.0 mm; rotational frictional elements (biscuits)  3410 A and  3410 B have centers spaced approximately 160.0 mm apart; and FPDD  3404  weighs approximately 4.94 lbs +/−10%. Regarding the range of motion provided in one embodiment, moveable assembly  3401  may yaw approximately +/−90.0 degrees from side to side; arm  3402  may pitch up and down approximately +/−90.0 degrees from the horizontal to the vertical; and FPDD  3404  may pitch approximately −5.0 degrees to approximately +30.0 degrees from vertical display orientation. 
   When manufacturing a computer system  3400  such as that shown in  FIG. 34 , it is desirable, but not necessary, that the system have one or more of the following characteristics. The display  3404  should be easily moved throughout the entire range of motion (when it is desired to move it). When the user has stopped moving the display, display  3404  should remain fixed at any point within the range of motion without noticeable sagging or backlash. During movement to display  3404 , the motion of the moveable assembly  3402  should be smooth and silent (e.g. no “spronging” or other spring noises) and the friction feel should be constant, regardless of position or direction of motion. The moveable assembly  3402  should have no pinch points, and all cabling (e.g. display, data, and power cables) should be internal to the mechanism and not visible. Additionally, the moveable assembly  3402  should be designed for at least a 15,000 cycle lifetime without degradation of performance. The weight and size of the base  3406 , arm  3402  and display  3404  should be light enough that one adult person, and even a child, can move the whole computer system (base, containing the majority of the electrical components of the computer system, arm and display) without any assistance and the base should be sufficiently heavy that it can support the whole computer system, with the display at a wide variety of locations, without requiring that the base be fixedly attached to the surface (e.g., a desk) on which it rests. 
     FIG. 35  is an exploded perspective view of one embodiment of the moveable assembly  3402  of  FIG. 34 . As shown in  FIG. 35 , component parts of moveable assembly  3402  include a first canoe  3502 A designed to couple with a second canoe  3502 B, and in so doing, to conceal various inner parts such as base rotation assembly  3503  and display mounting assembly  3505 . A spring  3408  and a compression link  3412  may also be concealed within canoes  3502 A and  3502 B. Rod  3416  may be used to coupled spring core  3430  to canoes  3502 A and  3502 B. 
     FIG. 36  shows an exploded perspective view of one embodiment of a base biscuit assembly  3600  (which corresponds to base biscuit  3410 B). Biscuit plate  3607  contains an adjustment mechanism and incorporates ratcheting features of that mechanism. Positioned behind the biscuit plate  3607 , the counterbalance adjustment cam  3605  provides a way to change the effective moment arm of the counterbalance spring to allow for differences in display weight due to manufacturing tolerances. The operation of this cam is described in more detail in  FIGS. 43A and 43B . 
   Friction element  3606 , in one embodiment, is a conventional pivoting element that provides enough friction in the display pitch motion to effectively mask any inaccuracies in the counterbalance. The base arm pitch joint housing (e.g. biscuit)  3610  provides pivot joints for the arm, parallelogram linkage, and counterbalance spring. In one embodiment, a base yaw joint (not shown) includes a pair of plane bearings preloaded against each other to minimize bearing slop and to provide joint friction to control the motion of the flat panel display device. An extension post  3602  extends from the biscuit  3610  to visually separate the arm (not shown) from the base (not shown). During yaw rotation, the base flange  3601  remains fixed, while the extension post rotates. Base flange (or mounting flange)  3601  provides an interface for attaching the extension to the base (not shown). Various sub-components of base rotation assembly  3600  further include a wave washer  3609 , wave spring  3612 , washers  3613  and  3618 , and retaining ring  3614 . 
     FIG. 37  is an exploded perspective view of a display mounting assembly  3700 , according to one embodiment of the invention, the major components of which are: a display hub  3702 , a friction element  3704 , a counterbalance spring  3705 , a display joint housing (biscuit)  3707 , and a mounting flange  3709  and extension tube  3713 . Display hub  3702  is a portion of the display mounting assembly  3700  that remains rotationally fixed relative to the base  3406  (not shown in  FIG. 37 ) and provides a horizontal reference frame for display pitch rotation. Friction element  3704  includes an extension tube  3713  and friction elements contained within a friction housing  3706 . Friction element  3704  is fixed relative to the biscuit  3707 . Counterbalance spring  3705  is a torsion spring that biases the display upwards to counteract the downward gravitational moment. Display joint housing (biscuit)  3707  provides a housing for the pitch friction and counterbalance elements, and the display hub. The mounting flange  3709  and extension tube  3713  are integral to the biscuit  3707 , and the display (not shown) does not rotate about axis of extension tube  3713 . Also included within assembly  3700  are nylon washer  3712 , steel washer  3711 , retaining ring  3708 , and limit stop  3710 . 
     FIG. 38  is an exploded, perspective view of a moveable assembly  3800  according to one embodiment of the invention. Moveable assembly  3800  corresponds to moveable assembly  3402  in  FIG. 34 . In one embodiment, moveable assembly  3800  includes a first canoe  3801 A, a second canoe  3801 B, bearings  3803 A,  3803 B,  3807 A,  3807 B, spring assembly  3809 , and compression link  3805 . Canoes  3801 A and B are hollow, rectangular, half-tubular sections having rounded exterior ends. When assembled, canoes  3801 A and  3801 B couple with the biscuit of a base rotation assembly (not shown) and with the biscuit of a display mounting assembly (not shown) to conceal compression link  3805  and spring assembly  3809 . Additionally, one or more data, power, or other computer system-related cables may be concealed within the hollow portion of canoes  3801 A and  3801 B. 
   Also called “case halves”, canoes  3801 A and  3801 B mate together to form the main structural element of the extension. Bearings  3803 A,  3803 B,  3807 A, and  3807 B, are pressed into bores in the canoes  3801 A and  3801 B to provide rotational joints for the biscuits (not shown). Compression link  3805 , together with the moveable assembly  3800  itself, couples the rotation of the upper and lower biscuits, and also supports the moment loads at the display end. One end of spring assembly  3809  is attached to the lower biscuit of the base rotation assembly (not shown), while the other end is attached to an inner portion of canoes  3801 A and  3801 B via rod  3821 . Spring assembly  3809  provides a force to counteract the gravitational moment on the arm and the display. Spring assembly  3809  compresses as the moveable assembly  3800  moves downwards, but extends as the moveable assembly  3800  moves upwards. 
     FIGS. 39A and 39B  show views of the spring assembly  3900  (which corresponds to the spring assemblies  3408  and  3809  of  FIG. 34  and  FIG. 38 , respectively).  FIG. 39A  is an exploded, perspective view of one embodiment of a spring assembly  3900 , showing various internal component parts associated therewith. Such parts include, but are not limited to: a spring core  3430 , spring struts  3440 , glide bearings  3903 , and spring  3408  (as shown in  FIG. 39B ).  FIG. 39B  is a perspective view of an assembled spring assembly  3900 , according to one embodiment of the invention. 
   As shown in  FIGS. 39A and 39B , spring core  3430  is a rectangular, tubular shaped member having a proximal end  3432 , a distal end  3431 , and a middle portion  3435 . An annular flange (or lip)  3433  is provided on the proximal end  3432  to mate with one end  3408 A of spring  3408 , when spring core  3430  is inserted within the interior of spring  3408 . The spring core&#39;s distal end  3431  protrudes past the opposite end  3408 B of spring  3408  and contains a bore  3460  therethrough, which is used to couple spring core  3430  with canoes  3502 A and  3502 B. A pair of spring struts  3440  fit within a corresponding pair of grooves  3437  running longitudinally along the sides of spring core  3430 . A corresponding pair of glide bearings  3903  mate with the exterior surfaces of spring struts  3440  such that spring  3408  smoothly and easily compresses and expands along the middle portion  3435  of spring core  3430 . 
   Spring struts  3440  have a proximal ends  3441  and distal ends  3442 . The distal ends  3441  are bowed slightly outwards to form a pair of ears  3443  separated by an empty space into which a biscuit (not shown) may slidably and rotatably fit. A corresponding set of bores  3911  is provided in the proximal ends  3441  to attach spring struts  3440  to the biscuit of a base mounting assembly. The distal ends  3442  are flared outwards to mate with the end  3408 B of spring  3408  as shown in  FIG. 39B . 
   Referring again to  FIG. 34 , in one embodiment, the torsion spring  3411  (not shown) used to counter-balance a display pitch has an outer diameter of approximately 0.840 inches (free), a wire diameter of approximately 0.075 inches, and a spring rate of approximately 0.067 in-lbs/degree. Additionally, a right-hand wind spring having an inner diameter of approximately 0.767 inches and a 0.403 inch body length at a approximately a 9.0 in-lb working load may be used. 
   In one embodiment, a left-hand wound compression spring  3408  has an outer diameter of approximately 0.75 inches, a wire diameter of approximately 0.095 inches, a spring rate of 17 lbs/in, and a free length of approximately 7.0 inches. It will be appreciated that the spring specifications given are meant only as illustrations, and that various springs having other specifications may be used in various embodiments of the invention. 
     FIG. 40  is a force diagram illustrating one embodiment of a computer system  4000  that includes a base  4030  attached to one end of a moveable assembly  4040  and a flat panel display device  4050  attached to the other end of the moveable assembly  4040 , in which a display weight  4010  is counterbalanced using a spring force  4020 . 
   In  FIG. 40 , a spring counterbalance mechanism is used to support the weight of the display  4050  and its moveable assembly  4040 . This configuration allows adjustment of the display position with minimal user effort. One of several illustrative advantages associated with this approach is that, for the linkage geometry shown, it is theoretically possible to precisely counterbalance the gravity load for all arm positions. If a spring with precisely the required rate and preload is used, and the linkage geometry is correct, the resulting spring force will always generate a moment around the base pivot that is equal and opposite to the moment of the display gravity load. In other words, the display will seem to “float,” restrained only by the resisting effects of bearing friction. (Some non-zero joint friction in the mechanism is a desirable feature, so that the display position will remain stable in spite of minor bumps or other disturbances). The characteristics of the ideal compensation are shown in  FIG. 40 . 
   In practice, the spring characteristics, linkage geometry, and display weight cannot be precisely controlled, and some counterbalancing errors will always occur. Accordingly, the moveable assembly  4040  includes an adjustment mechanism that allows each system to be adjusted to minimize compensation errors, and also employs joint friction to stabilize the display and to mask any remaining errors. 
     FIG. 41  is a graph depicting illustrative counter-balance sum of moments for one embodiment of a moveable assembly. As shown, in  FIG. 41 , the most torque is experienced when moveable assembly is in the substantially horizontal position (e.g. approximately 0.0 degrees). As the moveable assembly is raised, torque decreases, as indicated by the downward curving data line. 
     FIG. 42  is a graph depicting illustrative counter-balance sum of moments with error bars for one embodiment of a moveable assembly. As shown, in  FIG. 42 , the most torque is experienced when moveable assembly is in the substantially horizontal position (e.g. approximately 0.0 degrees). As the downward curving data line indicates, the torque decreases as the moveable assembly is raised. 
   In one embodiment, the moveable assembly is very sensitive to movement because the moment mismatch between the display and the spring has been reduced as much as possible. Although when viewing the graph in  FIG. 41  the mismatch appears small, the error can become quite large as soon as some reasonable manufacturing tolerances are introduced. Sources of error include manufacturing tolerances in display weight, spring constant, spring free length, as well as dimensional tolerances in the mechanism. 
   In order to compensate for tolerances, the moveable assembly may be tunable. After each unit is assembled in production, it may be adjusted to compensate for the particular spring, display, and every other part that went into it. By doing this, the error bars in  FIG. 42  can be drastically reduced. With reference to  FIGS. 43A and 43B , the tuning is performed by rotating the spring pivot cam  4301  (which corresponds to cam  3605 ) in the base biscuit. This moves the anchor point of the spring assembly up and down, thereby increasing or decreasing the moment arm (length) of the spring  3408  (not shown in these figures). Adjusting the moment arm of the spring allows the four-bar linkage (e.g. moveable assembly) to be optimally tuned to the weight of a particular flat panel display attached to the other end of the moveable assembly. Positioning cam  4301  in a first position about 10.0 mm off center of the base biscuit  3410 B, as shown in  FIG. 43A , creates a shorter moment arm, which creates additional compression of spring  3408 , and thus stores more potential energy. The additional potential energy may be useful in counterbalancing heavier flat panel displays. On the other hand, positioning cam  4301  in a second position about 14.0 mm off center of base biscuit  3410 B, as shown in  FIG. 43B , lengthens the moment arm, which lessens the compression of spring  3408  (of  FIG. 34 ), and thus stores less potential energy. The lesser potential energy may be useful in counterbalancing lighter flat panel displays. 
     FIG. 44  is a graph depicting counter-balance with manufacturing error bars after tuning for one embodiment of a moveable assembly. As shown in  FIG. 44 , tuning greatly reduces the error bars. 
   It will be appreciated that the user force when operating various embodiments of the moveable assembly must be carefully controlled. In a frictionless system, the sum of moments varies between 0.19 and −0.28 in-lbs, meaning that the force required to move the display varies between around 0.03 and 0.04 lbs, depending upon the arm angle. In an absolute sense, there is a very small difference between the two values, but the sign change alone results in a very perceivable variance in feel. This effect is magnified when reasonable manufacturing tolerances are considered. However, the effect is diminished as extra friction is added. If an extra 5 in-lbs of friction were added to the system, the resulting sum of moments would range between 5.03 and 4.96 in-lbs, and the corresponding user force would range between approximately 0.80 and approximately 0.79 lbs. In which case, the same absolute difference is only about 1.4% of the total user force. 
     FIG. 45  is a graph depicting the pitch counter-balance sum of moments for one embodiment of a moveable assembly. Pitch refers to tilting the flat panel display device without moving the moveable assembly. As shown in  FIG. 45 , the torque decreases as the angle of tilt increases. 
   In addition to the moveable assembly being counter-balanced, the pitch angle of the display is also counter-balanced, but with a torsion spring, given the size constraints and the smaller moment load. Although this approach cannot counter-balance as well as the approach used for the main arm, reasonable friction in the joint is more than adequate to mask any errors that may arise. 
     FIG. 46  is a sectional, perspective view of an assembled moveable assembly  4600  according to one embodiment of the invention. Left canoe  4601 A and right canoe  4601 B are mated together to form a hollow tubular structure, within which are housed spring  4603 , spring guide bearings  4605 , spring strut  4607 , spring core  4609 , and compression rod  4611 . One or more data, power, or other computer system-related cables may be positioned within the area  4613  between the exterior of spring  4603  and the interior wall of canoe  4601 B. It will be appreciated that the size, shape, and positioning of area  4613  is illustrative only, and that other sizes, shapes, and positioning are included within the scope and spirit of the present invention. 
   It will be appreciated that many kinds and combinations of materials may be used to manufacture the various components of the moveable assembly depicted in  FIGS. 34-39 . Illustratively, the biscuits may be machined from aluminum, while the canoes may be cast from aluminum. Other components, such as washers and the compression rod, may be manufactured of such materials as nylon and stainless steel, respectively. The materials used to manufacture various other component parts will be well known to persons skilled in the engineering and manufacturing arts. 
   Selected Terms 
   It will be appreciated that at various points in the specification and claims, various terms are used interchangeably. Accordingly, such terms are to be interpreted consistently with each other. Terms that are used interchangeably include: “flexible support mechanism,” “flexible neck,” “neck,” and “moveable assembly.” Additional terms include “base” and “moveable enclosure.” Further additional terms include: “flat panel display device,” “flat panel display,” and “display.” Further additional terms include “spring/piston assembly,” “spring,” “piston,” and “force generator.” It will be appreciated that additional terms not specified here, but appearing within the specification and/or claims, may also be used interchangeably. 
   Thus, a computer controlled display device is disclosed. Although the present invention is described herein with reference to a specific preferred embodiment, many modifications and variations therein will readily occur to those with ordinary skill in the art. Accordingly, all such variations and modifications are included within the intended scope of the present invention as defined by the following claims.

Metadata:
Filing Date: 20060919
Publication Date: 20080325
Grant Date: 20080325
Priority Date: 20011108
Inventors: JOBS STEVEN P
IVE JONATHAN
HILLMAN MICHAEL D.
TSAI FRANK
MCBROOM MICHAEL D.
MCBROOM DANIEL L.
SUDDERTH BRIAN T
BRIGHAM ARTHUR S.
JENSEN JOEL F.
BROWNELL, JR. ROBERT B.
KIM SUNG
MCDONALD ANWYL M.
MEAD, JR. RUSSELL C.
MEUNIOT ARTURO
BELTRAN JESUS
ANDRE BARTLEY K.
STRINGER CHRISTOPHER J.
RICCIO, JR. DANIEL J.
Assignee: APPLE INC
CPC Classifications: [{"code": "Y10S248/919", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M11/40", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M2200/022", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M11/2078", "inventive": true, "first": false, "tree": "[]"}, {"code": "Y10S248/919", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M11/14", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M11/14", "inventive": true, "first": true, "tree": "[]"}, {"code": "F16M11/04", "inventive": true, "first": true, "tree": "[]"}, {"code": "F16M2200/065", "inventive": false, "first": false, "tree": "[]"}, {"code": "G06F1/1601", "inventive": true, "first": false, "tree": "[]"}, {"code": "G06F2200/1612", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M11/40", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M2200/022", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M2200/065", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M2200/044", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M11/2078", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M2200/044", "inventive": false, "first": false, "tree": "[]"}, {"code": "G06F1/1601", "inventive": true, "first": false, "tree": "[]"}, {"code": "Y10S248/919", "inventive": false, "first": false, "tree": "[]"}, {"code": "G06F1/1601", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M11/40", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M11/2078", "inventive": true, "first": false, "tree": "[]"}, {"code": "F16M11/14", "inventive": true, "first": true, "tree": "[]"}, {"code": "F16M2200/044", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M2200/065", "inventive": false, "first": false, "tree": "[]"}, {"code": "F16M2200/022", "inventive": false, "first": false, "tree": "[]"}]
Family ID: 21882551