Abstract:
A detented and dampened hinge mechanism, with push-pull, and pull-push operation includes a first and second arms pivotally connected to move relative to one another in a scissor fashion between a closed and open positions. A cam and cam follower track establish a detent-type hold at both closed and open positions and add a radial motion component to the general pivotal motion. A damper limits relative movement of the arms. A biasing spring is utilized to bias the first and second arms toward the open position. A free moving anti-gravity ball moves in a channel when a momentum is imparted to the hinge mechanism. With the ball in its normal, lower position, arms are free to move; and moved to an upper position, the arms become locked out from full movement by the interference of the ball. Bumper materials are added.

Description:
This application claims priority of U.S. provisional application No. 60/395,536, filed Jul. 12, 2002, in the United States Patent and Trademark Office, and incorporates the disclosure thereof as if presented below in full. 

   BACKGROUND OF THE INVENTION 
   The present invention relates generally to hinge mechanisms with push-pull operation. Particularly, the invention relates to such hinge mechanisms, which may be detented to hold a particular position and may have a dampened movement when subjected to the pull-push operation. 
   Hinge mechanisms, scissor arms, and latches having push-push operations are known in the art. An example of this type of latch is shown in U.S. Pat. No. 4,655,489, issued on Apr. 7, 1987, to Robert H. Bisbing. The latch disclosed in this patent operates by capturing a keeper attached to a door or panel when the keeper is initially pushed into the latch housing. The keeper is released by again pushing the keeper into the housing to disengage the keeper from a catch within the housing, hence the term push-push latch. 
   Some other hinge mechanisms have gravity operated lockouts. Bako et al., U.S. Pat. No. 5,106,132, issued Apr. 21, 1992 shows a gravity operated lockout ball for a suitcase closure device. Wilstermann, U.S. Pat. No. 4,906,044, shows a gravity operated lockout ball for an automotive arm rest latch. In each instance the Bako and Wilstermann ball rolls downward under the force of gravity to create a lockout condition. These gravity operated lockout balls prohibit the movement of a hook-ended lever from a keeper. There is no suggestion nor is there consideration given in the prior art for adapting a lockout ball to scissor arm type latch. In fact, scissor arm type latches have a structure, which has not been adapted to a lockout ball operation. 
   An object of the present invention is to provide and improved hinge mechanism with a smooth opening and closing operation. 
   A second object of this invention is to provide such improved hinge mechanism with a fixedly controlled open position and a fixedly controlled closed position. 
   A third object of this invention is to provide such a hinge mechanism with controlled biasing for positive movement once said hinge is moved out of its fixed open or fixed closed position and where this biasing includes resonance vibration absorption. 
   A further object of this invention is to provide such a hinge mechanism with structural components for ease of assembly, low profile structure, and reliable operation and with quieting materials. 
   An even further object is to provide a momentum activated lockout when the latch is in the closed position. 
   SUMMARY OF THE INVENTION 
   The objects of the present invention are realized in a detented and dampened hinge mechanism with push-pull and pull-push controlled-rate operation. This hinge has a low profile, scissor-style structure, which is suitable for operating a vehicle glovebox lid, or bin, door pocket or boot side access panel or bin, and the like. 
   Detent forces assist in holding the closed position and the open position, each of which detent forces, in turn, are overcome by an operator&#39;s manual movement of the structure. A momentum sensitive device, such as an anti-gravity ball, operates to block the movement of the hinge from the closed position in the presence of excessive forces created during a predetermined excessive change in vehicle momentum, and other types of acceleration forces (both positive and negative acceleration). These forces may arise during a jarring, shock, of sudden acceleration or sideways deceleration, as experienced in an accident or with erratic driving, or in the case of door pockets, when slamming a door shut. 
   The hinge has a first elongate arm and elongate second arm, which move relative to one another in the plane of their elongations thereby pivoting in the scissor-like operation with added radial translation motion for the detent functions. A spring biases the scissor arms, and thereby the hinge, to each extreme position. A dampener operates against arm movements in both directions for push-pull and pull-push operation. A cam cooperates with a curvilinear cam path to implement an articulated motion between the first and second arms as they move relative to one another. This articulation compensates for variations in mounting positions for various applications between different glovebox, bin and door pocket designs. 
   The hinge has its first arm fixedly attachable to a first non-movable structural member, such as a glovebox encasement. It has its second arm, being pivotally connected to the first arm, fixedly attachable to a movable structural member, such as a glovebox lid or bin, door pocket or boot side access panel or bin. Thereby when the arms are moved relative to one another between the first closed position and the second open position, the two structural members move relative to one another. 
   The second arm carries the damper mechanism that is fitted or snapped into a cutout of that second arm. The damper can engage a portion of the first arm and thereby create a controlled movement between the first and second arms. This controlled movement is an inhibiting force that acts against any excessive pivoting motion during normal operation. 
   The damper mechanism includes a pinion gear mounted on the second arm. The pinion gear is connected to a friction clutch or a hydraulic clutch, being in this case a hydraulic clutch surrounded with high viscosity silicone lubricant. Different types of lubricant can be used to obtain the desired controlled motion. This pinion gear operates with its teeth engaging a track or length of teeth mounted on the first arm. This length of teeth forms a curved shaped track, i.e. a “rack” with a depression at the closed position end thereof. This depression assists in the closed position detent function. The pinion rotates and traverses the rack, as the hinge arms move between open and closed positions, it thereby operates against the associated clutch force for controlling the normal opening and closing movements of the associated glovebox lid or bin, door pocket or boot side access panel or bin. 
   The spring is connected between respective hooks, or alternatively between bosses located on each of the two arms. The connection locations on the arms are selected with respect to the pivot location and the configuration of the arms. The spring force is selected to match the damper, door weight, and other factors which are considered. The detent function is implemented with concave surfaces incorporated at both ends of the curvilinear cam follower track or path. The cam abuts the end of the cam follower path when the hinge is in the extreme open position, i.e., when rotated or pivoted to this position. The position of the cam in the closed position is given by the height and shore hardness of the vehicle&#39;s rubber stops mounted on the fixed element or moving element of the vehicle glovebox unit, door pocket unit or boot side access panel or bin unit, i.e., the lid itself or the frame. 
   In the door pocket application, the rubber stops are mounted on the door trim and when the pocket closes, it comes in contact with a rubber stop. The rubber stop assures that there is no direct contact between the pocket and the door trim, thus absorbing any noise when slamming the pocket shut, or vibration noise when in the closed position and the vehicle engine is at idle, or when the vehicle is moving. 
   The hinge of this invention allows for slight variations in the height and softness of the rubber stops, and for the possible distortion of in the bins or lids. The hinge adjusts to ensure that its cam member can always travel further down its cam follower track or path. The hinge also, if required, can compensate for these variations and can compensate to keep a preload on the glovebox lid or bin, door pocket or boot side access panel or bin, as the installation may be, from forcing the lid or bin to open. Therefore, the specific glovebox lid or bin, door pocket or boot side access panel or bin remains closed until opened by the operator. This ensures that the attached structure always remains closed and are properly shut, and also under vibration or shock pressure, will not rattle or open. 
   In addition to the preload weight encountered when the structure is in the closed position, the hinge provides a resistance against opening. This arises as the hinge is mounted so that the surface of the cam follower track or path in the closed position area is at a relative 45 degree angle (inclined) to the direction of the opening force. (The closed position area is that region of the track engaged by the pinion gear when the arms are rotated to place the hinge in its closed state.) This establishes a track incline area, which acts as a large detent area. 
   In this detent area, the rate of radial motion is greater than the rate of pivotal motion (when the hinge opens the first four degrees), and this makes the second arm translate in a perpendicular fashion towards the opening effort direction. This results in a higher opening effort during the first four degrees of rotational motion and defines a detent area rather than a fixed detent point at (or in) the closed position. (A detent point would be at a predetermined point at a specific angle of rotation.) 
   The resultant detent area renders the hinge more operator friendly (and wear forgiving) as it provides the detent function over a wide band (of angular rotation) thereby establishing a wide band of closed position tolerance. Moreover, with the detent area, small inconsistencies between installations are not as critical. This becomes a factor when two hinges are installed on a single structure, i.e., one on either side. 
   The strength of the detent area is adjusted by the angle of the cam follower path or track at the closed position. (Strength of the detent area is the force needed to move out of the detent.) The angle for the path is typically 45 degrees to the opening effort direction, but can be lower to reduce the strength (forces required to move the hinge) and higher than 45 degrees to increase the strength needed (to open the hinge). It is understood that curvilinear path for the gear track follows the path of the cam follower slot, i.e., guideway or path. 
   The second, movable arm can pivot on an open socket formed in its heel end. This socket mates with a boss located near the lower end of the first, fixed arm. This open socket is slightly elongate which permits the second arm to move radially outwardly off of a deep-seated position, when the arm rotates from the closed position. This permits the articulation motion referred to above. The biasing spring position and its spring force operates to seat the elongate socket on its mating boss when the second arm is in the closed position. This is applicable in the absence of rubber stops, when the hinge installation requires that there should be a clearance gap between the lid or bin and the glovebox, or other housing&#39;s, mounting frame or door trim. In this case, the second arm moves to the extreme closed position and thereby defines the closed position for the respective lid or bin. 
   This extreme closed position is also the normal state of the hinge during shipment and prior to installation. In the case where rubber stops are found in an installation, the hinge should be positioned and fixed on the glovebox frame or door trim such that in the closed position the second arm socket falls just short of its mating boss in order to allow the rubber stops to function in dampening the lid or bin force when contacting the respective frame or trim. 
   A PVC (polyvinyl chloride) sleeve is positioned over a sufficient portion of the spring&#39;s body to dampen spring vibration noise when the hinge slams to the open or to the closed position. Known TPE (thermoplastic elastomer) materials are molded into abutment surfaces for dampening the shock force and noise created at mechanical stop surfaces. Examples of TPE materials may include talc-loaded polypropylene and may include (SEBS) poly-styrene-b-ethylene-co-butylene-b-styrene, or other suitable polymer-bonded materials. 
   The fixed arm carries a channel in which the anti-gravity ball operates. This ball has a predetermined mass, which permits it to move at a predetermined rate from a non-lockout position at one end of its channel to a lockout position at the other end of its channel, under incurred excessive acceleration forces. The channel angle and the mass of the ball are also affected by the design parameters for the hinge, including the design parameters of the damper structure, the biasing spring and the average weight exerted by the glovebox lid or bin, door pocket or boot side access panel or bin and the weight of the contents inside. The momentum imparted to the ball causes it to travel to the lockout position. Gravity causes the ball to return to the non-lockout position after the acceleration induced momentum force effect subsides. Typically, the channel is oriented at approximately a forty-five degree angle with the non-lockout position being at the bottom. 
   The channel provides an enclosure to hold the free moving ball. Such enclosure may project beyond the outside wall of the second, movable arm, when a larger sized ball is need. Alternately, when the anti-gravity ball size permits, the channel may be shaped into a wall of the second arm. In either case, an interlock or a stop surface must be engaged on the first, fixed arm. This interlock can be a shaped abutment, or a socket, or another structure into which the ball can roll to thereby be pinned against the interlock, resulting in the lockout condition. This lockout condition will last for the duration of any excessive acceleration and resultant momentum imparted to the ball. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The features, advantages and operation of the present invention will become readily apparent and further understood from a reading of the following detailed description of the invention with the accompanying drawings, in which like numeral refer to like elements, in which: 
       FIG. 1  is frontal view of the assembled hinge mechanism of the present invention showing in the closed position with the first/fixed arm in the background and the second moveable arm in the foreground; 
       FIG. 2  is a reverse or back view of the closed hinge mechanism of  FIG. 1 ; 
       FIG. 3  is a frontal view of the hinge of  FIG. 1  in the locked-out position; 
       FIG. 4  is a back view of the locked-out hinge of  FIG. 3 ; 
       FIG. 5  is a frontal view of the hinge of  FIG. 1  in the open position; 
       FIG. 6  is a back view of the open hinge of  FIG. 5 ; 
       FIG. 7  shows a back/outside view of the first/fixed arm of the hinge mechanism of  FIG. 2 ; 
       FIG. 8  shows the juxtaposed/inside face of the fixed arm of  FIG. 7 ; 
       FIG. 9  shows the frontal/outside face of the movable arm of the hinge mechanism of  FIG. 1 ; 
       FIG. 10  shows the juxtaposed/inside face of the movable arm of  FIG. 9 ; 
       FIG. 11  is a perspective view seen from the left of the inside face of the fixed arm of  FIG. 8 ; 
       FIG. 12  is a right perspective view of the inside face of the fixed arm of FIG. showing the lockout ball in the non-lockout location; 
       FIG. 13   a  is a left perspective view of the inside face of the movable arm of  FIG. 10 ; 
       FIG. 13   b  is a left perspective view of the movable arm of  FIG. 13   a  with the damper pinion gear installed; 
       FIG. 14   a  is a right perspective view of the movable arm of  FIG. 13   a;    
       FIG. 14   b  is a left perspective view of the damper installed movable arm of  13   b;    
       FIG. 15  shows a partial detail view of the movable arm overlaying the fixed arm carrying lockout ball in the non-impact state, non-lockout position for the hinge closed; 
       FIG. 16  shows a view of the partial structure of  FIG. 15  with the lockout ball in the lockout position after impact or acceleration for the hinge locked; 
       FIG. 17  shows a view of the partial structure of  FIG. 15  with the lockout ball in the non-locked position and the hinge opening; 
       FIG. 18  shows a view of the partial structure and ball position of  FIG. 17  with the hinge fully opened; 
       FIG. 19  is a partial detail view of the inside face of the fixed arm of  FIG. 12  showing soft touch materials; 
       FIG. 20  is a partial detail view of the fixed arm and ball of  FIG. 19  with a partial cut-away view of the movable mounted thereon; 
       FIG. 21  shows the inside face of the movable arm of  FIG. 10  with the ball superimposed for its mating abutted position with the hinge fully open; 
       FIG. 22  shows the movable arm and abutted ball of  FIG. 21  with the hinge in the closed position; 
       FIG. 23  shows the movable arm and abutted ball of  FIG. 21  with the hinge immediately after impact or acceleration; 
       FIG. 24  shows the movable arm and abutted ball of  FIG. 21  with the hinge in the fully locked-out closed position; 
       FIG. 25  shows a partial detain of the moving arm as it abuts the fixed arm boss in the fully opened hinge position; 
       FIG. 26  shows a partial perspective detail view of the movable arm below the fixed arm about to leave the detent area on the damper track; 
       FIG. 27  shows the back view of the assembled hinge of  FIG. 2  illustrating movement from the closed detent area position; and 
       FIG. 28  shows the back view the assembled hinge of  FIG. 27  illustrating movement at a position midway long the damper track, in between closed and open positions. 
   

   DETAILED DESCRIPTION OF THE INVENTION 
   The present invention provides a motion lockout, detented and dampened hinge mechanism. A shock or acceleration (being a positive or negative acceleration), can cause a lockout member to prohibit the hinge from opening from its closed position. The hinge has a low profile scissor configuration having two arms, which are spring biased to the closed hinge position. Mechanical detents are utilized at either end of the scissoring operation to detent both the closed and the open positions. Soft materials are used to dampen spring vibration noise. Soft materials are also used a abutment locations to dampen abutment noises. 
   The scissor hinge mechanism  11 , shown in a front view in the closed position,  FIG. 1 , includes a first/fixed arm  13  and a second/movable arm  15  mounted for rotation thereon. The first/fixed arm  13  carries three mounting bosses  17 ,  19 ,  21  for mounting the fixed arm to a fixed bin or pocket or glovebox compartment structure, or the like with mounting screws. The first mounting boss  17  is situated at the upper most area of the fixed arm at, what will be further described below as, the open position location of the fixed arm  13 . The second mounting boss  19  is located at the closed position location of the fixed arm  13 , while the third mounting boss  21  is located at the bottom of the fixed arm  13 . These bosses  17 ,  19 ,  21 , each have an upstanding cylindrical wall  23 , extending outwardly from the juxtaposed/inside face of the fixed arm  13  a distance above the mounting screw head, seating surface. For the first and second bosses  17 ,  19 , the cylindrical wall will present and abutment for the extreme end of rotational motion of the movable arm  15 . 
   The movable arm carries a damper structure, which includes a friction clutch or hydraulic clutch surrounded by high viscosity silicone lubricant. The damper has a pinion gear (described below),  FIG. 2 , which operates in conjunction with a toothed track or rack  29 , FIG.  1 .  FIG. 2  is shows the hinge mechanism closed from a back view. A projecting back flange  FIGS. 1 ,  2 , provides an interlock structure for holding the movable arm  15  on the fixed arm  13 , when this projecting back flange is overlapped by a projecting lip  33 ,  FIG. 2 , on the back cover  35  of the damper structure  25 . 
   Both the fixed arm  13  and the movable arm  15  are irregularly, elongate shaped. The movable arm  15  is mounted to rotate on the fixed arm from its bottom or heel portion. The hinge  11  is generally mounted so that the two arm  13 ,  15  elongations extend essentially vertically. The outward end  39  (opposite the heel  37 ) of the movable arm  15  has a fork structure  41 , which creates and open ended elongate slot  43 . This slot  43  receives a pin or post mounted to a movable member, such as a lid, bin, door pocket, access panel or bin and the like. As the movable arm  15  moves, the movable member is moved. The slot  43  is sided (surrounded) by a depression surface  45 , which is the seating surface for the head of the movable member&#39;s post. 
   The damper structure  25  is located at the outward end  39  of the movable arm  15 , adjacent the elongate slot  43 . This damper structure  25  snaps into a receiving hole in the movable arm and is held in place by diametrically positioned compression fingers  47 . 
   Positioned at the outward end of the fixed arm  13  is a curvilinear shaped cam follower path or cam slot  49 , FIGS.  1 , 2 . A solid cylindrical projection  51  extending outwardly from the juxtaposed/inside face of the movable arm  15  acts as the cam  51  and extends through the cam slot  49 . A coil spring  53  mounts between an intermediate location on the movable arm  15  where an attachment, such as the first hook  55 , is located, and a projecting lower leg  57  of the fixed arm  13 , where a second hook  59  is located. The coil spring  53  carries a cylindrical PVC sleeve  61  the majority of its unextended length. This PVC sleeve absorbs spring vibration noise when the hinge  11  is slammed open or closed. 
   The open position end of the cam slot  49  has transversely extending upper and lower concave pushouts  63 ,  65 . The upper pushout  63  permits ease of assembly of the movable arm  15  on the fixed arm  13 . The lower pushout  65  acts as an open position detent. The depth of this lower pushout  65  and the extended spring  53  force determine the open position detent strength. 
   The heel end  37  of the movable arm  15  is fork shaped with an elongate slot  67 . An outwardly extending journal  69  on the juxtaposed/inside face of the fixed arm  13  acts as the pivot for the rotation of the movable arm  15 . This journal  69  has a pair of diametrically opposed, transversely extending lobes  71 ,  73  at its outer end. The first lobe  71  points away from the first hook  55  location and is used to overlap the right fork arm  75  of the heel  37  when the movable arm  15  is in the extreme open position. The second lobe  73  points towards the first hook  55  location and is used to overlap the left fork arm  77  when the movable arm  15  is in the extreme closed position. Both the right and left fork arms have undercut surfaces  79 ,  81 ,  FIG. 3 , with the right fork undercut  79  extending under the first lobe  71  and the left fork undercut  81  extending under the second lobe  73 . 
   The lockout member is a metal ball  83  discussed further below, and hidden (not shown) in  FIGS. 1-3 . A soft touch bumper  85  is positioned at the movable arm  15  contact point on the first mounting boss  17 , FIG.  3 .  FIGS. 3-4  also show the lockout position, i.e., the anti-gravity lock, of the hinge  11 , with  FIG. 3  being a front view and  FIG. 4  being a back view. This lockout position “A” is established at a rotation of about 4 degrees from the fully closed position “B”. How this lockout position “A” is determined is discussed below. 
   In  FIGS. 5-6 , which show the hinge  11  mechanism in the open and the closed positions respectively, the movable arm  15  has moved to the fully open position “C” to abut the TPE soft touch bumper  85  on the cylindrical wall  19  of the first mounting boss  17 . 
   When the hinge  11  is in the fully open position “C” the spring  53  is fully extended and the movable arm  15  has moved radially outward  87  following the cam slot  49  shape. In the fully closed position “A” the movable arm  15  seats completely down on the journal  69  as seen in FIG.  1 . As the movable arm  15  begins to rotate from the fully closed position, it also begins to articulate, i.e., to move radially outwardly as can be seen in FIG.  2 . The fully open position “C” shows the hinge fully opened and the movable arm fully rotated and fully extended outward in the radial direction  87 , FIG.  3 . This articulation is a design consideration for operating variety of gloveboxes, door pockets, boot access panels/bins, and the like. 
     FIGS. 7 ,  8  show the outside face and inside face, respectfully, of the fixed arm  13 . The shape of the curvilinear cam slot  49  is easily seen. The closed position “A” end of the cam slot  49  dips downward to form an inclined region  89  of the bottom cam slot edge. This downward projecting region  91  and the inclined region  89  of the bottom cam slot edge provide a detent function at the closed position “A” and the area of rotation immediately adjacent the closed position “A”. The length of this detent area is a design consideration in the force used in the opening operation of the hinge  11 . The toothed track, rack  29  dips downward for a parallel region  93  to follow the dip  91  in the cam slot  49 . 
   A closed ended channel  95  for holding the ball  83  is positioned in the juxtaposed/inside face of the fixed arm  11 , FIG.  8 . This channel has TPE soft touch bumpers  85  at each closed end. The channel  95  permits the ball  83  to roll between a first position “D” and a second position “E”, with the “D” position being the non-lockout position and the second position “E” being the lockout position. The sidewalls of the channel  95  can have any shape, which will permit the ball  83  to freely roll between positions “D” and “E”. However, if the sidewalls of the channel  95  are rounded to provide a “neater fit” with the ball and reduce side play, the operation of the ball in the channel will be less noisy and without significant rattling. 
   The journal  69 ,  FIG. 8 , upon which the heel  37  end of the movable arm  15  rotates has its two lobes  71 ,  73  being pie-shaped or fan-shaped. The first lobe  71  has an upstanding wall  97  which rises from the surface of the inside face of the movable arm  15  at the edge of the lobe  71  closest to third mounting boss  21 . This upstanding wall  97  is an additional abutment for the end of the right fork arm  75  at the heel end of the movable arm  15  when that arm  15  is in the fully open position “C”. The second hook  59 , in the projecting lower arm  57 , is formed as an upstanding projection from the inside face of the fixed arm  13 . 
   A spacer block  99  is at the lockout end “E” of the channel near the side facing the cam follower slot  49 . This first spacer block  99  acts as a spacer to assure that the two arms  13 ,  15  are sufficiently separated to allow the free operation of the ball  83 . A concave cutout  101  in this first spacer block  99  abuts the channel and is a size and shape to receive the ball  83  in the lockout position “E”. 
     FIGS. 9-10  show the outside face and inside face, respectively, of the movable arm  15 , respectively. Referring to the outside face,  FIG. 9 , the undercut section  45  forming the depressed surface is easily understood. The tab-like shapes of the respective right and left undercut surfaces  79 ,  81 , in the right and left fork arms  77 ,  79  at the heel end of the movable arm  15  are easily seen to be a size and shape to match the first and second lobes  71 ,  73  of the fixed arm&#39;s  13  journal  69 . The right undercut  79  is essentially shovel shaped, while the left undercut  81  has a projecting tang at its base. The spring  53  attachment first hook  55 , on the movable arm  15 ,  FIG. 9 , projects outwardly from the outside face at an undercut area  99 . This spring undercut area  103  permits the spring  53  to be positioned in a lower profile at a plane about where the inside faces of each arm  13 ,  15  abut. This aligns the spring  53  force with the scissor plane and eliminates binding of the arms  13 ,  15 . 
   Buildup shoulders  105 ,  107  surround the elongate slot,  FIG. 10 , at the fork  41  end of the movable arm  15 . These shoulders assure the resultant thickness of the fork  41  and compensate for the undercut  45 . Therefore the arm  15  is not weakened in the fork  41  area and will not break in operation. Compensating buildup shoulders  109 ,  111  also surround the heel slot  67  and provide thickness to compensate for the undercuts  79 ,  81 , respectively. 
   An irregular but truncated trapezoidal-like shaped undercut area  113  is positioned to extend towards the damper  25  end of the arm  15  from the bottom of the heel slot  67 . This undercut provides the spacing for the operation of the ball  83  in the channel  95  and the pivoting of the arms  13 ,  15  without binding against the ball  83 . A dimpled pad  115  operates as a second spacer block  115  for assuring the spacing between the arms  13 ,  15  for the free operation of the lockout ball  83 . A concave cutout  117  is of a size and shape to receive the ball  83 . This second cutout  117  faces away from the heel slot  67  and acts to abut the ball  83  in the lockout position “E” and pin it against the cutout  101  in the spacer block  99  when the hinge  11  is locked out in the closes position. 
     FIGS. 11 and 12  are left and right perspective views, respectively, of the inside face of the fixed arm  13 , and further illustrate the shapes of the elements above-described. The steel ball  83  is shown in filled-in (black) is positioned at the lower, non-lockout location, in the channel  95 , FIG.  12 . 
     FIGS. 13   a ,  13   b , show a left perspective view of the moving arm  15  inside face, without the damper gear  27  installed, and with the damper gear  27  installed, respectively.  FIGS. 14   a ,  14   b  show a right perspective view of the moving arm  15  inside face, without the damper gear  27  installed, and with the damper gear  27  installed, respectively. 
     FIGS. 15-18  illustrate a partial detail view of the operation of the antigravity ball  83  and the movable arm  15  (foreground) and fixed arm  13  (background). Partial dashed lines are shown as “fine” lines. The antigravity ball  83  is normally free to move up and down thee channel  95  freely when the hinge is closed, FIG.  15 . Under no acceleration, the ball  83  stays in the lower channel  95  area “D” due to its own weight, FIG.  15 . The spring  53  holds the movable arm  15  in the closed position. 
   Under an impact or acceleration,  FIG. 16 , the ball  83  moves in the direction of acceleration due to the momentum imparted to it. As the ball  83  is designed to have a lower inertia than the movable arm  15  connected to the damper  25  and acting against the spring  53  force, it arrives in the lockout position “E” up the channel before the movable arm  15 . The arm  15  then starts to move but is stopped by the ball being in between the two arms  13 ,  15 . In this state the ball  83  becomes cradled between the curved pockets  101 ,  117  in the bumper/spacer shoulders  99 ,  115 , respectively. These pockets  101 ,  117  are shown in later figures. 
   The hinge  11  can open,  FIG. 17 , under a no impact and no acceleration condition. Here the ball  83  remains in the lower channel, non-lockout location “D” under its own weight. There is no interference with the arms  13 ,  15 . Therefore, when an operator opens the glovebox to which the hinge is connected, the operation of the hinge members  13 ,  15  continues because the ball  83  remains in the non-interference location “D”. The arms  13 ,  15  do not lock and the hinge mechanism  11  can open with a low effort. 
   When the hinge  11  is fully opened, and without acceleration or shock,  FIG. 18 , the ball  83  remains in the lower channel  95 , non-lockout position “D”. The arms  13 ,  15  are free to scissor rotate with respect to one another. 
     FIGS. 19-20  illustrate the use of the TPE soft touch materials  83 , over-moulded onto the fixed arm  13  to quiet the antigravity ball  83  operation. These materials  83  at either end of the channel  95  dampen the ball clicking noise when it hits either end.  FIG. 20  illustrates the lockout position of the ball  83  against the spacer block  99  and the concave cutouts  101 ,  117 . As previously stated, because of the inertial design the ball  83  arrives at the lockout location between the cutouts  101 ,  117  before the arms  13 ,  15  rotate beyond that point, thereby causing a lockout. 
     FIGS. 21-24  illustrate the position of the antigravity ball  83  with respect to the undercut trapezoidal-like undercut area  113 , the second spacer block  115  and its concave cutout  117 .  FIG. 21  shows the position of the ball  83  against a far shoulder of the undercut area  113  of the movable arm  15 , when there is no impact, acceleration or shock, and the weight of the ball has it in its lowest position in the channel  95 . The hinge  11  is open. 
     FIG. 22  shows the hinge  11  closed and there is no impact with the ball  83  at its lowest position in the channel  95 . Here the ball  83  is mid-way across the undercut area  1131 . 
     FIG. 23  illustrates the ball  83  position after a shock or impact drives the ball  83  up the channel  95 , wherein the ball  83  moves faster than the movable arm  15  can react to the shock or impact. Here the ball  83  is about in contact with the concave cutout surface  117  in the second spacer/bumper block  115 . A fraction of a second later the moving arm  15 ,  FIG. 24  comes into contact with the ball  83  and seats it against the concave cutout  117  when the mating concave cutout  101  in the first block  99  on the fixed arm  13  cradles the ball  83  thereby stopping all motion between the arms  13 ,  15  at about four degrees of rotation out of the closed position “A”. 
     FIG. 25  illustrates a detail of the soft touch TPE material  85  absorbing the mechanical shock as the moving arm  15  abuts the cylindrical surface  23  at the first mounting boss  17  in the fully open hinge position “C”, shown in FIG.  26 . 
     FIG. 26  illustrates the movement of the detent  25  out of the detent area between positions “A” and “B”. When the hinge  11  is in the closed position, shown in  FIG. 27 , the opening effort is in a direction always perpendicular to the fork  41  of the moving arm  15 . This fork  41  drives the pin connection  119 , with the pin  119  attached to the structure to be moved free to move up and down the fork elongate slot  43 , FIG.  28 . The movable arm  15  movement direction is generally at 45 degrees to the opening effort direction. This assists create the detent effect at the closed position “A” and the length of the incline defines a “detent area”. This area is defined by the incline region  89  of the cam slot, seen in  FIGS. 26-28  and in  FIG. 7  where it carries its identification numeral. 
   If the relative angle is decreased to less than 45 degrees, the detent strength is reduced. The detent strength is foremost established by the angle of the incline region  89  which the cam  51  has to climb against the weight of the moveable arm  15  and the spring  53  force. As the angle increases the detent strength increases. Above about 80 degrees there is a “blockage threshold”, i.e., the detent strength is too excessive for vehicle installations. Once the pinion gear  27  of the damper structure  25  clears the “detent area” upon the hinge  11  opening, the resistance reduces and the further opening effort needed is greatly reduced, FIG.  28 . 
   Many changes can be made in the above-described invention without departing from the intent and scope thereof. It is therefore intended that the above description be read in the illustrative sense and not in the limiting sense. Substitutions and changes can be made without departing from the scope and intent of the invention.