Abstract:
An image capture device is provided including more compact components to enable the fabrication of more compact image capture devices. In one particular embodiment, a compact shutter mechanism is provided that requires less space within the camera when the shutter is open. In another particular embodiment, a rotary to linear switch is provided to reduce the amount of real estate required by the switch on the outside housing of the image capture device.

Description:
PRIORITY 
   The present application claims priority from co-pending provisional patent application Ser. No. 60/413,079, Filed on Sep. 23, 2002, entitled IMAGE CAPTURE DEVICE. 

   FIELD OF THE INVENTION 
   The present invention relates to image capture devices and more particularly, to a an image capture device including a compact profile wherein certain shutter mechanisms and switch gears have been designed to require less space on the image capture device. 
   BACKGROUND OF THE INVENTION 
   There is an interest in making cameras more compact. In order to do so, certain parts on the camera can be designed to take up less space when the parts are activated. For example, some cameras having a mechanical shutter may use a shutter blade the full size of the lens aperture opening. However, if the shutter mechanism were to be mounted in the camera such that the shutter blade swings in the width dimension of the camera, than the camera body may need to be made wider to accommodate the full width of the shutter blade when it has been pivoted away from the lens opening aperture. Additionally, image capture devices presently include linear switches which take up a great deal of surface real estate on the camera housing to provide for the length in which the linear switch slide actuator must be slid in order to move the switch between the selectable positions. 
   What is needed is to an image capture device that has been designed to be compact. What is further needed are image capture device components that require less space in or on the image capture device to work. 
   SUMMARY OF THE INVENTION 
   What is provided are more compact components for an image capture device to enable the fabrication of more compact image capture devices. 
   In one particular embodiment of a compact image capture device, a compact shutter mechanism is provided that requires less space within the camera when the shutter is open. 
   In another particular embodiment, a rotary to linear switch is provided to reduce the amount of real estate required by the switch on the outside housing of the image capture device. 
   In another particular embodiment, other switch components may be combined with a rotary to linear switch, to further take advantage of the space available on the camera housing. 
   Other particular features and embodiments will become apparent from the following detailed disclosure of the invention. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The foregoing summary, as well as the following detailed description of the preferred embodiments, is better understood when read in conjunction with the appended drawings. For the purpose of illustrating the invention, there is shown in the drawings an exemplary embodiment that is presently preferred, it being understood however, that the invention is not limited to the specific methods and instrumentality&#39;s disclosed. Additionally, like reference numerals represent like items throughout the drawings. In the drawings: 
       FIG. 1  is a perspective view of an image capture device in accordance with one embodiment of the present inventions. 
       FIG. 2  is a front plan view of the image capture device of FIG.  1 . 
       FIG. 3  is a front plan view of the image capture device of  FIG. 1  wherein the lens cover has been opened to expose the lens and viewfinder front apertures. 
       FIG. 4  is a rear plan view of an image capture device in accordance with one particular embodiment of the present inventions. 
       FIG. 5  is a top perspective view of an image capture device in accordance with one embodiment of the present invention having parts removed to more clearly see features of one embodiment. 
       FIG. 6  is an enlarged view of a portion of FIG.  5 . 
       FIG. 7  is a top partial perspective view of an image capture device in accordance with one embodiment of the present inventions having parts removed to more clearly see features of one embodiment 
       FIGS. 8-57  are described herein. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   Before explaining the disclosed embodiments of the present invention in detail, it is to be understood that the invention is not limited in its application to the details of the particular arrangement shown since the invention is capable of other embodiments. Also, the terminology used herein is for the purpose of description and not of limitation. 
   The Image Capture Device Housing 
   Referring now to  FIGS. 1-5 , there is shown an image capture device  10  made in accordance with one particular embodiment of the present invention. Image capture device  10  includes a front housing  12  and a rear housing  14  that matingly engage to surround the internal workings of the image capture device  10 . A compartment door  15  may engage either or both of the front and rear housings  12  and  14  to provide access to a battery compartment and/or to output connectors. Such output connectors may be used to connect the image capture device  10  to an external device such as a television, a computer a printer, a cell phone, etc. 
   Front housing  12  of image capture device  10  includes a plurality of apertures formed therethrough, such as a taking lens/viewfinder window  12   a , an aperture  13  for a red eye reduction mechanism and a flash window  18 . As shown in  FIG. 3 , when the lens door  16  is opened, the taking lens aperture  17   a  and viewfinder aperture  17   b  of the lens mask  17  are exposed. 
   Rear housing  14  additionally includes a plurality of apertures therethrough. For example, the rear housing  14  of the present particular embodiment includes openings a rotary switch  24 , nested tactile switch  26 , a rotary diopter adjustment knob  28 , an LCD display  30  a view finder rear aperture  32  and signal indicators  34 . Other user interface devices, buttons and switches may be included. 
   A battery door  15  extends across an aperture through a side face of the image capture device  15 . 
   Rotary On/Off Switch with Nested Release Button 
   Referring more specifically to  FIGS. 5-26 , front housing  12  additionally includes an aperture  12   b  and release shaft opening  12   c . A cylindrical bearing shaft  12   d  and three fastener posts  12   e  additionally extend from the upper surface  11  of the front housing  12 . Release shaft post  12   d  includes a rectangular key opening  12   f , therethrough. Door control pin  45   a  extends through the aperture  12   b.    
   The nested switch assembly  21  is secured to the camera in a novel manner as will be described in connection with  FIGS. 6-10 . First, referring to  FIG. 7 , the rotary on/off switch gear  20  is located around the cylindrical bearing shaft  12   d  on the top surface  11  of the front cover  12  and a hole  20   b  on the underside of the rotary on/off switch gear  20  is lockingly engaged with the door control pin  45   a  of a door connector ( 45  of FIG.  14 ). The fastener posts  12   e  pass through openings  20   d  in the rotary on/off switch  20 . Openings  20   d  additionally include enough space to accommodate fastener posts  12   e  when the gear  20  is moved in the direction of arrow X, without permitting the gear  20  to be overdriven or turned in the wrong direction. Further, the rotary on/off switch gear  20  includes openings  20   e  and  20   f  spaced 35 degrees apart, which will engage an on/off detent mechanism, as will be described in connection with FIG.  8 . Although the present particular embodiment shows the openings  20   e  and  20   f  as being 35 degrees apart, it can be seen that the system could be adapted to have the openings different distances or angles apart, and the detent spring  60  of  FIG. 8 , could be likewise adapted. The on/off detent positions of the switch  20  are accomplished using a detent spring finger that moves in and out of two slots of the lens door gear, as will be described more specifically in connection with  FIGS. 7 and 8 . 
   Referring now to  FIGS. 7 and 8 , an on/off detent spring  60  sits on top of the inner circumference of the rotary on/off gear  20 . On/off detent spring  60  has holes  61  that align with holes in the posts  12   e  (FIG.  6 ). Additionally, the on/off detent spring  60  includes a spring finger  62 . When the rotary on/off switch gear  20  is in an initial position (i.e. the off position), the detent spring finger  62  rests in the opening  20   f  of the rotary on/off switch gear  20 , capturing the switch gear  20  in the off position. When the rotary on/off switch gear  20  is turned in the direction of arrow X, the detent spring finger  62 , which is maintained stationary due to screws ( 74  of  FIG. 9 ) securing them to the top face  11  of the front housing  12 . However, when the gear  20  is rotated into its second position (i.e. the on position), the gear  20  rotates about the bearing shaft  12   d  in the direction of arrow X, and the detent spring finger  62  is captured by the gear  20  in opening  20   e . Thus, the switch has two distinct detent positions. It can be seen how other additional switch positions may be added. 
   Further, as the gear knob  20   a , and correspondingly the gear  20 , is rotated, the door control pin  45   a  captured in the hole  20   b  is moved linearly along the slot  12   b . Moving the door control pin  45   a  moves the door connector ( 45  of  FIG. 14 ) correspondingly. When the door controller  45  is moved between a first and a second position, a conductive wiper ( 47  of  FIG. 14 ) is also moved between a first and second position, providing a signal to the processor (not shown) that the rotary on/off switch  21  has moved from an “off” position to an “on” position or vice versa. 
   Referring now to  FIG. 9 , sitting on top of the on/off detent spring  60  is a release button spring  70 , which acts as additional capturing support for the release button  22  and on/off switch gear  20 , as well as provides the vertical spring force to the release button  22 . In one preferred embodiment, both flat springs  60  and  70  are being held down by screws  74 , although other pins or heat stake elements would work as well. The screws or pins are secured to the three posts  12   e  formed on the top face  11  of the front housing  12 . 
   The release button spring  70  includes three leaf spring legs  72   a ,  72   b  and  72   c . The leaf spring legs  72   a ,  72   b  and  72   c  extend upward from the plane containing the detent spring, within the rotary on/off switch gear  20 . The upper surfaces of the leaf spring legs  72   a ,  72   b  and  72   c  contact the release button  22 , when installed and return the release button  22  to its normal position after the consumer has depressed the button  22 , when capturing an image. As with the on/off detent spring  60 , the release button spring  70  includes three screw openings  71  aligned with the openings  61  of the on/off detent spring  60  so that the screws  74  pass through and secure the release button spring  70  to the top surface  11  and so that the release button spring resists rotational forces when the rotary on/off switch gear  20  is turned. 
   Referring now to  FIGS. 9-13   b , there is shown is shown a self-locking camera release button assembly. The release button  22  includes a shaft  82  and a key  84 . The shaft  82  and key  84  fit into the opening  12   c  in the post  12   d , with the key  84  fitting through the rectangular key slot  12   f . By turning the release button  22  clockwise, the release button is held downwards by interconnection of the upper key surface to the lower front shell hole surface. Turning the release button  22  further, one release spring leg  72   b  of the release button spring  70  will interlock with a track  86  on the lower surface of the release button  22 . The release button  22  is now permanently captured in the vertical direction and is protected against movement in the rotational direction. The three leaf spring legs  72   a ,  72   b  and  72   c  of the release button spring  70  will push the button upwards. The lowest surface  88  of the release button shaft  84  will push against and activate a tactile switch  87  on the PCB  89  or other switch device. As such, once the release button  22  shaft  84  is inserted through the bearing surface  12   d  and is rotated clockwise with the key  84  no longer aligned with the key slot  12   f  and the leaf spring  72   b  is trapped in the track  86 , the release button  22  is locked into the housing without the need for a “c” ring and corresponding groove on the stem  84 . 
   The Rotary to Linear Door Linkage Mechanism 
   One particular embodiment of the door opening mechanism will now be described in connection with  FIGS. 13   a - 17 . The door opening mechanism of the present embodiment translates the rotary motion of the rotary on/off switch gear  20  to the linear up/down motion of the lens door  16 . As described above, the door controller  45  is engaged with the rotary on/off switch gear  20  via the door control pin  45   a . To secure the open and closed end positions of the lens door  16 , a spring biased lever is used. 
   A lever  50  is attached between the door controller  45  and the lens door  16  by means of a series of bends on the lever  50  and the door  16 . More specifically, a finger  52  of lever  50  is connected to body portion  50   a  of the lever  50  at a bend portion. Similarly, the finger  55  is connected to an arm portion  50   c  of the lever  50  by a bend portion. The lens door loop  26   b  has a corresponding bend to facilitate mating with the finger  55 . Two other bends  19  of the lens door slide portion  16   c  interact with the lens door mask (not shown) and build a guide rail mechanism for the up and down motion of the lens door  16 . 
   The present door lever mechanism has an incorporated spring arm  54 , which is part of the lens door lever  50 . During lens door motion, a wedge portion  54   a  of the spring arm  54  moves over a roller to reach two different end positions and provide an “over the center” approach to ensuring two discrete opened and closed positions of the lens door  16 . Spring portion  54  is attached to lever body portion  50   b.    
   The pre-load of the spring portion  54  (linked through the bends on the lens door and the activation lever by the two end positions of the spring) secures the open and closed positions of the lens door  16 . The lens door lever  50  has a bearing connection through a pin  56  of the lens door that is captured by a thin washer. As such, the door lever  50  pivots around the pin  56  in response to motion of the finger  52 , connector  45  and rotary switch gear  20 . The pivoting of the lever  50  serves to slide the ribs  19  in the guide track and open or closed the lens door  16 . Ribs  19  may be formed in or punched from the guide portion  16   c , or may comprise another material affixed to the guide portion  16   c . The spring wedge  54   a  passing over the roller from one side to the takes over the opening or closing of the door after the initial turn of the rotary switch gear  20 . The lens door  16  is fixed open or closed depending upon which side of the roller  58  the wedge  54   a  stops. 
   The present particular embodiments shown in  FIGS. 15-18  are additionally shown including a damage protection mechanism to prevent the lens door  16 , the door lever  50 ,  90  or the switch connector  45 , from being damaged if the lens door  16  is manually forced open by the user. Located within two opposite slots of the lens door connector  45  are two lens door guide pins  41   a  and  41   b  located coaxially within the springs  40   a  and  40   b . The guide pins  41   a  and  41   b  and springs  40   a  and  40   b  are maintained in place in the slots of the connector  45  by two side walls  45   b  which are heat staked to the connector  45 . The rounded lens door lever finger  52  engages the connector  45  between the two lens door guide pins  41   a  and  41   b . Interacting with the bottom surface of the lens door connector  45  on the lens door lever  50  are two radial shaped fingers  53 , which are locked into position by the bent surface adjacent the finger  52  formed on the lens door lever  50 . The rounded surface portions of the fingers  53  help to guide the lens door connector  45  towards the front lens door surface  16   a.    
   The door springs  40   a  and  40   b  and guide pins  41   a  and  41   b  in combination act as a lens door part damage prevention device. In event that the lens door is being forced open, the springs  40   a  and  40   b  would retract and allow the lens door lever  50  and lens door  16  to move freely. This damage prevention would also act similar if the lens door knob  45   a  were rotated (clockwise or counter clockwise) while the lens door was being opened or closed by force. 
   Referring now to  FIG. 18 , there is shown an alternate embodiment of the rotary to linear door linkage mechanism using an omega type spring  95  to accomplish the two discrete positions of the door lens  16 . Whereas the remainder of the parts are essentially the same as described in connection with  FIG. 15 , the lever  90  differs from the lever  50  such that the lever  90  does not include an integral spring portion. Rather a spring  95  with two end loops, similar to an omega spring function, interacts between a pin  92  on the front cover and a hook  97  on the lens door lever  90 . When the gear  20  is rotated to the “on” position, the lever  90  and spring  95  are rotated, biasing the door  16  into the open position as described above in connection with the embodiment of FIG.  15 . When the switch gear  20  is rotated back to the initial position, the lever  90  is rotated, rotating the spring and biasing the door into the closed position. The present embodiment could be adapted to use other types of springs, such as a hooked coil spring, a torsion spring, etc. 
   The Direct Rotary to Linear Mode Switch with Spring Loaded Detent Mechanism 
   Referring now to  FIGS. 4 ,  5 , and  19 - 22 , there is shown a rotary mode switch assembly  23 . In the present particular embodiment, the rotary mode switch assembly  23  includes the rotary to linear mode switch gear  24  and the nested 5 position joystick  26 . It can be seen that the 5-position joystick  26  may be omitted with out materially changing the present embodiment. 
   The rotary mode switch assembly  23  is mounted to and through the back housing  14  of the image capture device  10 . As can be seen more particularly in  FIGS. 5 and 19 , the outer surface of the rear housing  14  includes a bearing surface  100  formed thereon. A window  14   a  is formed through the rear housing  14 , around an arcuate portion of the periphery of the bearing surface  100 . Additionally, the bearing surface  100  includes an alignment notch  100   a  and a channel  100   b  formed therein. 
   A rotary mode switch gear  24 , having a switch position tab  24   a  surrounds the bearing surface  100 . The inner circumference of switch gear  24  includes an open portion  24   b  sized to accommodate the walls of channel  100   b  and permit the gear  24  to be rotated to different switch positions. In the present embodiment, three switch positions are described, although fewer or greater numbers of positions may be chosen. The outer circumferential wall of the open portion  24   b  includes a number of detent position notches  24   c  corresponding to a plurality of different possible discrete switch positions, in order to stop the rotation of the switch gear  24  at a plurality of distinct detent positions. Additionally, the back face of the switch gear  24  includes a projection  25  (FIG.  22 ). The projection  25  is sized to pass through the window  14   a  when the gear  24  is placed on the bearing surface  100  with the chamber walls  101  placed in the opening  24   b . The projection  25  is adapted to grip the actuator  120  of a linear switch  125 , as shown in FIG.  22 . The linear switch  125  is mounted on a PCB (not shown) in the image capture device  10 . The number of discrete detent positions of the switch gear  24  should correspond to the number of switch positions used on the linear switch  125 . 
   Further, a spring loaded detent assembly  110  is loaded into the chamber  100   b  after the switch gear  24  is engaged with the bearing surface  100  and placed flush with the rear housing  14 . The spring loaded detent assembly  110  includes the loaf shaped detent cap  104  (see  FIG. 22 ) and the spring 102 . Spring  102 , which engages a bearing surface at the rear of the loaf shaped detent cap  104 , additionally contacts the back wall of the channel  100   b  to bias the rounded portion of the loaf shaped detent cap into the discrete detent position notches  24   c . Note that in the present embodiment the loaf shaped detent cap includes a hollow portion to accept one free end of the spring  102  therein in order to stabilize the spring  102 . The rounded top surface of the loaf shaped detent cap is oriented to provide a maximum amount of surface area contact with the inner surface of the detent notches  20   c  for a stable and secure fit. Although the loaf shaped cap  104  is preferred, it can be seen that other shaped detent caps (i.e. bullet shaped, ball shaped) may also be used. 
   As can be seen, rotation of the switch gear  24  causes the spring  102  to compress as the rounded portion of the loaf shaped detent cap  102  leaves the notch  24   c  and decompress as the rounded portion enters the next notch  24   c . Simultaneously, the projection  25  rotates and moves the actuator  120  linearly to the next switch position. As such, rotary motion of the mode switch gear  24  is translated directly into linear motion of the linear switch actuator  120 . 
   Note that a five-position joystick switch is passed through the opening at the center of the bearing surface  100  and connected to a tactile switch  130  mounted on a PCB (not shown). The five position switch is locked into place using key slot  100   a  of the bearing surface  100 . The rotary mode switch may be used for any desired purpose, such as to change the camera mode between the image capture and image viewing modes, as well as other modes. In the present embodiment, the five-position joystick is used to scroll between and choose options on the user interface, as well as to operate the physical zoom and digital zooms between the tele and wide positions. 
   The Zoom Lens System 
   One particular arrangement of lenses and prisms for making a compact zoom lens for an image capture device, such as image capture device  10 , is shown in  FIGS. 26 and 27 , and defined by the following tables read in connection with the FIGS.  26  and  27 : 
   
     
       
             
           
             
             
             
             
             
             
           
             
             
             
             
             
             
           
         
             
               TABLE 1 
             
           
           
             
                 
             
             
               3x zoom lens 
             
             
               Curvature list for all lens elements 
             
           
        
         
             
                 
                 
                 
                 
               Effective 
                 
             
             
                 
               Radius 
                 
               Thickness 
               Diameter 
             
             
               Lens 
               (mm) 
               Shape 
               (mm) 
               (mm) 
               Material 
             
             
                 
             
           
        
         
             
               G1 
               33.132 
               CX 
               1.00 
               23.4 
               LaK4 
             
             
                 
               15.040 
               CC 
                 
               20.5 
             
             
               G2 
               21.000 
               CX 
               3.55 
               13.4 
               ZK14 
             
             
                 
               21.000 
               CX 
                 
               12.8 
             
             
               G3 
               21.000 
               CC 
               0.85 
               12.8 
               ZF17 
             
             
                 
               32.576 
               CX 
                 
               12.5 
             
             
               G4 
               134.728 
               CC 
               0.80 
               10.1 
               ZK21 
             
             
                 
               6.610 
               CC 
                 
               8.5 
             
             
               G5 
               176.087 
               CC 
               0.80 
               8.4 
               ZK14 
             
             
                 
               14.350 
               CC 
                 
               8.3 
             
             
               G6 
               9.670 
               CX 
               1.99 
               8.4 
               SFL6 
             
             
                 
               23.000 
               CC 
                 
               8.0 
             
             
               G7 
               33.532 
               CX 
               1.10 
               5.5 
               QK3 
             
             
                 
               101.092 
               CX 
                 
               5.6 
             
             
               G8 
               16.650 
               CX 
               1.60 
               6.2 
               ZK21 
             
             
                 
               30.200 
               CX 
                 
               6.3 
             
             
               G9 
               8.878 
               CX 
               2.31 
               6.4 
               E-FL6 
             
             
                 
               14.837 
               CX 
                 
               6.1 
             
             
               G10 
               14.837 
               CC 
               5.29 
               6.1 
               ZF12 
             
             
                 
               5.900 
               CC 
                 
               5.2 
             
             
               G11 
               55.720 
               CX 
               1.32 
               5.3 
               QK3 
             
             
                 
               24.660 
               CX 
                 
               5.6 
             
             
               G12 
               14.950 
               CX 
               1.33 
               7.0 
               LaSF016 
             
             
                 
               63.450 
               CC 
                 
               7.0 
             
             
                 
             
           
        
       
     
   
   
     
       
             
           
             
             
             
             
             
             
             
           
             
             
             
             
             
             
             
           
         
             
               TABLE 2 
             
           
           
             
                 
             
             
               Lens spacing in 9 steps zoom range 
             
           
        
         
             
                 
               Focal length 
               FB 
               D8 
               D14 
               D17 
               D24 
             
             
                 
                 
             
           
        
         
             
                 
               5.994 
               2.118 
               1.004 
               10.118 
               8.494 
               1.671 
             
             
                 
               6.569 
               2.115 
               1.956 
               9.166 
               8.021 
               2.147 
             
             
                 
               7.240 
               2.111 
               2.908 
               8.214 
               7.490 
               2.682 
             
             
                 
               8.034 
               2.108 
               3.860 
               7.262 
               6.886 
               3.289 
             
             
                 
               8.988 
               2.104 
               4.811 
               6.310 
               6.188 
               3.991 
             
             
                 
               10.159 
               2.104 
               5.763 
               5.359 
               5.364 
               4.815 
             
             
                 
               11.651 
               2.104 
               6.715 
               4.407 
               4.348 
               5.831 
             
             
                 
               13.674 
               2.104 
               7.667 
               3.455 
               3.007 
               7.173 
             
             
                 
               16.877 
               2.104 
               8.618 
               2.504 
               0.898 
               9.282 
             
             
                 
                 
             
           
        
       
     
   
     FIGS. 26 and 27  show the zoom lens layout of one particular embodiment in two position, which are f=5.994 mm and f=16.877 mm. In the diagram, lenses G 4 , G 5  and G 6  are the moving groups comprising the front group. Lenses G 8 , G 9 , G 10  and G 11  are another moving group comprising the rear group. Front and rear groups will be moved together as per zoom table to get different zoom ranges. The other elements except G 12  are always in fixed location. Lens G 12  will be moved by a focusing motor (not shown) for focusing purposes. 
   The Zoom Mechanism 
   The image capture device  10  may include a zoom mechanism. One particular embodiment of a zoom mechanism that may be used with the image capture device  10  will now be described in connection with  FIGS. 37-46 . Housed in a zoom housing  450  are the two zoom barrels, front barrel  460  and rear barrel  470 . Aligned on the optical axis through the front and rear barrels  460 ,  470  is an image sensor  475 . Other elements including the shutter lens  370  (G 7  of FIG.  27 ), a focusing lens  455  (G 12  of  FIG. 27 ) and a glass plate  476  are additionally included within the zoom housing  450 . 
   The distance between the front barrel  460  and the rear barrel  470  determines the magnification factor of the image between the wide angle ( FIGS. 38 and 39 ) and the telephoto positions (FIGS.  40  and  41 ). In the present particular embodiment, a linear cam flat  480  controls the zooming of the image capture device  10  by locating the front and rear lens barrels  460 ,  470  at discrete positions, each with the barrels  460 ,  470  a predetermined distance apart. 
   The cam flat  480  is directly coupled with one barrel (in the present embodiment, the front barrel  460 ) of the zoom lens via the zoom coupling linkage  498  and is coupled to the other barrel  460  by a zoom lever  490 . The cam flat  480  is located on and guided by the zoom housing  450 . Guides are realized on the zoom housing  450  by two straight ribs  452 ,  454  and counter surfaces  456 ,  457 ,  458  on the zoom housing  450 . These ribs  452 ,  454  and counter surfaces  456 ,  457 ,  458  define the position of the cam in two directions and permit only linear motion. For example, the ribs  452 ,  454  interact with linear grooves  481   a  and  481   b  defined on the bottom surface of the cam flat  480 . If desired, tracks, such as tracks  482   a  and  482   b , may additionally be defined on the cam flat  480  to interact with the counter surfaces  456 ,  457 ,  458 . Due to the counter surfaces  456 ,  457 ,  458  contact with the surface, the zoom housing provides a 3 point guide for the cam flat  450 . Three small areas near these points but in opposite directions serve the same function. This permits the cam flat  480  to operate even if there is a slight deflection or if there is variation to the tolerances during manufacture, but without a loss of performance. 
   Additionally, misalignment of the straight ribs  452  and  454  would create high friction or prevent free movement of the cam flat  480 . This is avoided by reducing the guide lengths  481   a ,  481   b  inside the cam flat  480  to a minimum. Therefore an additional deflection of the cam flat  480  and/or misalignment of the straight ribs  452 ,  454  will not deteriorate the guide quality. 
   The non-proportional movement of the zoom lever  490  is realized by the cam profile  482  inside the cam flat  480 , which generates the relative positions of both barrels as defined by an optical calculation, the results of which are reported in Table 2 above for a nine position zoom lens mechanism. The integral cam profile  482  that the lever  490  follows, is optimized in order to have the lever  490 , and correspondingly the lenses, follow a particular optical prescription which incorporates a non-proportional motion. 
   A spring  495  (chosen to be a torsion spring in the present embodiment) is supported on the zoom housing  450  by a pin  450   a  and presses a finger  471  on the rear barrel  470  against the zoom lever  490 , which in turn leans on the inner side of the cam profile  482  to make it follow the prescribed path when the cam flat  480  is moving. A second supporting spring  496  (FIG.  41 ), which in this particular embodiment, has also been chosen to be a torsion spring, is used to generate an additional force on the cam flat  480 . The reason for this spring  496  in this embodiment is to ensure that the cam flat  480  is biased so as to create a force in the direction of arrow Z ( FIG. 37 ) against the nut  500  ( FIG. 37 ) of the driving device, regardless of the position or direction of travel of the cam flat  480 . The driving mechanism chosen for the present embodiment includes a stepping motor  510  with a threaded lead screw  512  which passes through the nut  500 . 
   Note that in the present embodiment, the cam profile  482  is chosen to be very shallow towards the tele position and the force vector of the pin  491  of the zoom lever  490  is nearly zero in the linear direction (not considering friction). 
   The coupling zoom linkage  498  creates the direct link between the cam flat  480  and the front barrel  460 . It is stiff and acts in a push/pull linear manner for precise movement of the front barrel  460 , but is flexible for torsion and deflection to compensate for misalignment of the cam flat. The coupling zoom linkage  498  is attached to connector portions  485   a  and  485   b  on the side of the cam flat  480 , and is similarly attached to the frame of the front lens barrel  460  at connector portions  460   a  and  460   b.    
   As can be seen from the zoom curve profile, in operation, when the cam flat is advancing away from the motor  510 , the directly linked front lens group  460  is additionally advancing away from the motor  510 , while the rear group is moving towards the motor  510  and away from the front lens group  460 . Similarly, when the cam flat  480  and front lens group  460  are moving towards the motor  510 , the rear lens group  470  is moving away from the motor  510  and towards the front lens group  460 . As such, it can be seen that during operation of the present particular embodiment, the front and rear lens barrels  460 ,  470  are always moving in the opposite direction from each other. A finger  465  on the front lens barrel  460  may be used in connection with a photointerrupter (not shown) to inform a processor of the precise location of the lens barrel  460 . 
   One particular method of assembling the mechanism in a simple fashion will be described. In this method, the zoom lever  490  is mounted first, then the barrels  460 ,  470 , and the cam flat  480  is placed last. During assembly, the zoom lever  490  is moved beyond its operational position. At that time the cam flat  480  is slid into place on the housing  450  and the zoom lever  490  is rotated into its position through the open side  483   a  of the cam profile  483 . The coupling zoom linkage  498 , is then mounted to the front lens barrel  460  and fixed onto the cam flat  480 . Also at this time, the cam drive stepping motor  510  will be engaged with the cam flat  480  at the cam flat yoke  484  and with the nut  500 . 
   It should be understood that other methods of assembling the zoom lens mechanism may be used. Additionally, although in the described embodiment the front barrel  460  is linked to the cam using the cam zoom linkage  498  and the rear barrel  470  using the lever  490 , with a slight modification to the cam profile  483 , the cam zoom linkage  498  may be used to drive the rear group  470  and the lever  490  used to drive the front group  460 . 
   A Viewfinder Mechanism 
   Referring now to  FIGS. 47-54 , there will be shown a viewfinder mechanism through which the user can view the scene at the same magnification chosen using the zoom mechanism. A viewfinder housing  550  is located adjacent to the zoom housing  450  (see FIG.  55 ). All viewfinder lenses are captured in the viewfinder housing  550 . The viewfinder housing  550  additionally contains two prisms  557 ,  559 , for directing the view of the user around a turn in the housing  550 . The middle lens  565  and the rear lens  560  are being guided in the lower portion on pins  575  and  570 , which are cylindrical in the present particular embodiment. 
   In the upper portion, pins  560   a  and  565   a  (part of the lenses  560  and  565 , respectively) are being guided within a slot (not shown) in the viewfinder cover. An extension spring  580  pushes the rear and the middle lenses  560 ,  565  apart from one another (See  FIGS. 49-51 ) to allow a constant force on the lens levers  590  and  595 . The two lens levers  590  and  595  are captured an adjustment plate  600 . Additionally, pins on the free ends of the levers  590 ,  595  are captured in grooves  486  and  487  on the cam flat  480 , respectively. The levers  590 ,  595  are being driven by the same cam flat  480  as the zoom mechanism, which correspondingly moves the rear and middle lenses  565  and  560  of the viewfinder due to the contact between the lens levers  590 ,  595  and the lens frame tabs  575   a  and  565   a . As such, as the lens levers  590 ,  595  move together and apart based on the profiles of the cam grooves  486  and  487  on the cam flat  480 , the viewfinder experiences an apparent zooming view that corresponds to the zooming action experienced at the image sensor, due to the cam flat  480  moving the front and rear barrels  460 ,  470  of the zoom lens mechanism. 
   The middle lens lever  595  couples to the middle lens  565  by a connector bearing  565   a . The arrangement of the connector bearing  565   a  is such that it always pulls the lenses into one sideways direction, thus preventing an erratic sideways motion of the middle lens  565  during zooming. No additional spring is necessary for the prevention of erratic sideways movement. 
   The rear lens lever  590  interacts with slanted surface onto the pin of the rear lens, which also prevents sideways motion. As such, the two levers  590 ,  595  are driving, by means of the cam flat  480 , the two movable zoom lenses  560 ,  565  according to the designated motion with the use of only one spring. The spring  580  is captured in a unique way by forcing the lenses always against the lever bearing connection. Backlash is relatively eliminated and a smooth motion of the viewfinder zoom action is secured. The additional connector bearing piece prevents an erratic sideways motion of the lenses during zoom activation. 
   Tuning the Viewfinder During Assembly 
   Referring now To  FIGS. 56-58 , the rear lens lever  590  and the middle lens lever  595  are captured on an adjustment plate  600 . The adjustment plate is located on the zoom structure by a bearing rivet  605 , although other means of attachment are possible. An accentor pin  610  is riveted to the adjustment plate as well and guided between a slot of the zoom structure. By turning the accentor pin  610  clockwise ore counter-clockwise, the adjustment plate  600  can be rotated around the bearing rivet  605 . The rear lens lever  590  can now be moved in a rotary motion and in return, through the connection between the rear lenses, moves the rear lens forward and backwards. The rear lens can now be adjusted in the viewfinder lens system to correct any deviation between the lenses. The accentor pin  610  at the same time is being held by friction (in the present embodiment, by the use of a washer) against unwanted rotation. By mounting the two lens levers  590 ,  595  on one rotational adjustment plate  600  and by the use of one accentor pin  610 , an easy adjustment (using merely a screwdriver, in the present embodiment) of the viewfinder lens system is possible. 
   A Viewfinder Diopter Adjustment Mechanism 
   Referring now to FIGS.  4  and  23 - 25 , there is shown one particular embodiment of a viewfinder diopter adjustment mechanism that may be used with an image capture device, such as image capture device  10 . The viewfinder eye lens (diopter lens)  32  is adjusted using a knob  28  mounted to the rear housing  14 . The eye lens  32  is mounted to the viewfinder housing  550  by means of slot  550   a , in which tab  32   a  is seated. The slot includes enough clearance for the tab  32   a  to move forward and back, in response to rotation of knob  28 . However, rotation of the knob  28  would be limited by the confines of the slot, such that when the tab  32   a  would hit the front or back end bearing surfaces of the slot, the knob  28  could not be turned further. As will be described below, a detent spring or mechanism may be included to prevent the rotation of the knob to these extremes. The slot bearing area is closed and secured by the viewfinder housing cover (see FIG.  47 ). Opposite the tab  32   a , an arm  325  connects the lens  32  to a bearing pin  310 . A protrusion  325   a  is located on the planar face of the arm  325 , opposite the planar face supporting the bearing pin  310 . 
   One end  310   a  of the bearing pin  310  is located in a cylindrical hole in the viewfinder housing  150 . A compression spring  300  mounted coaxially around the bearing pin  310  biasing the protrusion  325   a  against a rotational cam  28   a  resembling, a helical ramp, which is incorporated within the diopter knob  28 . The rotational cam  28   a  is located in a bearing hole of the back cover  14  of the image capture device  10 . By rotating the diopter knob  28  clockwise or counterclockwise, the cam  28   a  inside the diopter knob  28  rotates, moving the diopter lens forward or backward, as the protrusion  325   a  is biased against portions of the ramp having greater or lesser heights. This movement of the diopter lens enables the user to adjust the sharpness of the viewfinder zoom lens system. As can be seen more particularly in  FIG. 23 , the coil spring  300  is compressed between a bearing shoulder on the bearing pin  310  and the viewfinder housing  150 . As the knob  28  is rotated, the compression spring  300  maintains the protrusion  325   a  in contact with the cam  28   a  based on the force on the bearing shoulder of the bearing pin  310  compressing or decompressing the spring  300  against the viewfinder housing  150  as the cam ramp  28   a  height increases or decreases, respectively. 
   Additionally, a detention spring  320  having a frictional spring arm  320   a  is connected to the diopter knob  28  against the inner surface  14   b  of the rear housing  14 . The detention spring  320  can be used as a friction position device or as a detent mechanism. The diopter knob  28  may be fastened to the rear cover by means of a heat stake or ultrasonic welding. 
   Shutter and Aperture Adjustment Mechanism 
   Referring now to  FIGS. 28-36  there is shown one particular embodiment of a shutter/aperture mechanism  350  that may be used with an image capture device, such as image capture device  10 . A shutter base component  360  includes guide rail apertures  362   a  and  362   b  that, in combination with guide rails  410   a  and  410   b , serve to align the shutter base  360  on the optical axis, with an opening  363  centered on the optical axis. In the present embodiment, a lens  370  is aligned with the opening  363 . The base  360  includes pins  364   a ,  364   b ,  366   a  and  366   b  formed thereon, which are used to locate and/or maintain the shutter and aperture blades  394 ,  395 ,  396  and  397  in certain discrete positions, as will be described more completely in connection with  FIGS. 30-32 . The shutter and aperture assembly  350  is mounted into a barrel  400  within the optical path of the zoom lens. The barrel  400  additionally holds a lens element  370  in the correct position which defines a primary, maximum lens aperture. The shutter and aperture blades 394 ,  395 ,  396 ,  397  are mounted onto the barrel such that the f-stop plane is right in front of the vertex of the lens element  370 . The shutter blades  394 ,  395 , as well as the aperture blades  396 ,  397  are each driven by a solenoid  382 ,  380 , respectively. The solenoids  380 ,  382  have stable end positions in which they remain without external power to the shutter mechanism. 
   The arcuate portions  368   a  and  368   b  of the shutter base  360  are designed to permit the arms  380   a  and  382   b  of the solenoids  380  and  382 , to swing in an arc from a first stable, open position to a second powered, closed position. The solenoids  380  and  382  are mounted externally on the lens body tube structure  400  and the solenoid drive pins  380   a  and  382   a  pass through slots  394   a ,  395   a ,  396   a ,  397   a  of the respective blade groups. This design results in a compact shutter build. 
   The shutter group is realized with one main blade  394  and one supporting blade  395 . The main blade  394  has a reduced size that does not cover the entire optical opening  363  when the solenoid  382  is energized. Rather, the supporting blade  395  covers the remaining area as shown more particularly in FIG.  31 . This produces a subassembly with small outer dimensions. For example, in the present embodiment, the shutter mechanism is located in the camera such that the shutter blades open in the width direction of the camera. As such, a larger shutter blade(s) would require a greater width dimension when the shutter blade(s) swung open. 
   In one particular embodiment, the ratio of main blade  394  average width to supporting blade  395  average width is about 3:1. In another particular embodiment the ratio of main blade  394  average width to supporting blade  395  average width is about 2:1. 
   The main blade  394  is pivoted on the pin  364   b , which passes through the hole  394   b  while the supporting blade  395  moves linearly on the pins  366   a  and  366   b , when the solenoid  382  is energized, as shown in FIG.  31 . 
   The same principle applies for the aperture group with the main difference being that the main blade  396  provides in the closed stage a small opening which creates the smaller aperture therethrough. Referring more particularly to  FIGS. 32 ,  33   b  and  34 , it can be seen that when the solenoid arm 380   a  swings to its second, energized position, the aperture blade  396  covers a portion of the lens  370 , wherein the supporting blade  397  covers another portion of the lens  370 , leaving only the aperture  396   d  through the main blade  396  open to permit light through the lens  370 . As with the main shutter blade  394 , the main aperture blade  396  pivots on a pin  364   b  and the supporting blade  397  moves linearly on the pins 364   a  and  364   b , when the solenoid  380  is energized. Additionally, in one particular embodiment, the ratio of the aperture blade  396  average width to supporting blade  397  average width is about 3:1. In another particular embodiment the ratio of the aperture blade  396  average width to supporting blade  397  average width is about 2:1. 
   As shown in  FIG. 30 , the present particular embodiment has been shown wherein when both solenoids  380  and  382  are in the stable position, the aperture is at “full open” i.e. neither the shutter blades  394  and  395  or the aperture blades  396  or  397  cover the lens  370 . In one particular embodiment, full open represents, for example, 2.8 while the small opening represents, for example, 5.6. The two aperture values are useful for increasing the depth of field, improvement of optical quality and to aid the flash system at close distances. 
   In the present embodiment, aperture is normally open to light. When a signal is received indicating that the release button ( 22  of  FIG. 1 ) has been depressed, the main shutter blade  394 , and its supporting blade  395  are closed. If, prior to depression of the release button  22  it is determined that less light needs to pass through the aperture, such as to more greatly define field of depth or in highly lit environments, then the main aperture blade  396  and supporting blade  397  cover the lens  370 , defining a smaller aperture. As with the full aperture embodiment, when the release button  22  is depressed, the shutter blades  394  and  395  are closed. However, since they are not located in the same plane as aperture blades  396  and  397 , and may even be offset by separation sheets (not shown), a collision between the various blades is avoided. The blades  394 ,  395 ,  396  and  397  are additionally secured in place by the cover  399 , which is fastened to the shutter base  360 . Each set of shutter blades  394 ,  395  and aperture set of blades  396 ,  397  can be driven independently or in combination based on the actuation of the solenoids  380  and  382 . Note that although we have defined a stable and energized state for each of the shutter and aperture subassemblies, the solenoid states could be assigned differently in software and/or hardware but accomplish the same functions of providing a full open, a small aperture and a closed position, if desired. 
   Referring more particularly to  FIGS. 35 and 36 , as noted above, in the present particular embodiment a lens element  370  is additionally positioned inside the barrel  400 . This requires a precise optical alignment of the shutter barrel elements, which can be effected in the present particular embodiment because the barrel is positioned on the guide pins  410   a  and  410   b . Additionally, in the present particular embodiment, the heavy solenoids  380  and  382  are mounted onto the outer fixed structure  400  so that the shutter/aperture subassembly mass is respectively minimal. When the external solenoids  380  and  382  are activated they will still transfer some energy into the shutter/aperture assembly  350 . This is due to the acceleration of the blades  394 ,  395 ,  396 ,  397  and some friction. This energy is absorbed by the alignment system  350  and a friction damping assembly  405  which includes the external tension springs  394   a  and  394   b , which are connected to the shutter base  360  at the hooks  361   a ,  361   b . The friction damping assembly  405  pulls the shutter/aperture assembly  350  in an axial direction against a reference surface (for optical reasons) of the lens body tube structure. The spring force is weak enough to allow the guide pins  410   a  and  410   b  to keep their straightness after the external shock, but strong enough to generate the beneficial damping. 
   It should be recognized that, although the above shutter embodiment is described in connection with a digital camera wherein the shutter is closed to capture an image, the above shutter embodiment can be adapted to be used in connection with a film camera. To do so, the shutter blades  394  and  395  are normally closed over the lens  370 . The solenoid  380  can then be pulsed to momentarily open the shutter blades  394  and  395  to permit light to come through the lens  370 . The aperture blades  396  and  397  and solenoid  382  would operate as described above in connection with the digital embodiment. 
   While the invention has been described with reference to certain embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications can be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this invention, but that the invention will include all embodiments falling within the scope of the appended claims.