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PRIORITY CLAIM TO RELATED US APPLICATIONS 
       [0001]    To the full extent permitted by law, the present U.S. Non-provisional patent application, is a Continuation-in-Part of, and hereby claims priority to and the full benefit of U.S. Non-provisional application entitled “Control Motion Hinge,” having assigned Ser. No. 12/775,302, filed on May 6, 2010, incorporated herein by reference in its entirety. 
     
    
     FIELD OF THE INVENTION 
       [0002]    The present invention relates generally to hinge and more specifically to a door hinge with a motion closure system for soft closure of the door. 
       BACKGROUND OF THE INVENTION 
       [0003]    The conventional door hinge or butt-hinge is composed of two leaves each engages with the other by means of a pivot pin and interlocking sleeve, knuckle or pintle. One leaf is fixed on the door edge and the other is fixed on the door frame. One or more hinges are used to pivot the door when opening or closing the door. For automatically closure of the door with a conventional hinge, a hydraulic system, spring system or a combination system is typically affixed to the upper portion of door and to the horizontal beam of the upper door frame, thereby adding an industrial appearance to the door assembly. In addition, such door closing systems generally exerts a continuous resisting force requiring a big force to be applied to push the door open or hold the door in an open position, preventing the door from free swinging. 
         [0004]    Moreover, such door closing systems apply a non-uniform force to the upper portion of the door disadvantageously resulting in a force offset from the rotational axis of the hinge assembly, thus deforming the door, hinge, latch/lock and frame over time. Furthermore, these door closing systems frequently utilize a separate mechanical mechanism to lock the door in a full open position such as a door stop or a mechanical elbow linkage requiring a separate installation. When a door is closed with the assistance of such door closing systems, it is typically forced to move in its closing direction rapidly, causing a noise to the ear and forceful impact, wherein the main elements the hinge, lock and door elements are impaired over time due to such force. 
         [0005]    Therefore, it is readily apparent that there is a recognizable unmet need for control motion hinge for soft and quiet closure of a door during final approach, wherein such control motion hinge is integrated into the hinge or hidden within the door jam, frame or door, and wherein such control motion hinge is non-continuous, thereby allowing the door to swing freely through the door hinges full range of motion to an automatic full open hold position, and reduce the stress on the door, hinge, latch/lock and frame. 
       BRIEF SUMMARY OF THE INVENTION 
       [0006]    Briefly described, in a preferred embodiment, the present apparatus overcomes the above-mentioned disadvantage, and meets the recognized need for such an apparatus by providing a control motion hinge comprising, in general, a first leaf hinge to secure a first pin, a second hinge to secure a first pin, a link positioned between the first and second leaf hinge, a flat spring wrapped around the knuckle of the first and second leaf hinge, activates a closure cycle of the control motion hinge pulling the door closed. 
         [0007]    According to its major aspects and broadly stated, the present apparatus in its preferred form is a control motion hinge, comprising a first leaf hinge with three knuckles to secure a first pin, wherein the two outer knuckles have roller knuckles, a link having a two knuckles on a first end to interlock with the first leaf hinge and a single knuckle on a second end, a second leaf hinge with two knuckles to secure a second pin when interlocked with the second end of the link, wherein the two knuckles of the second leaf hinge have a roller path for engaging the roller of the first leaf hinge, wherein such rollers traverse the roller path, a first spring device positioned between said first leaf hinge and said link to apply a force therebetween, and thus softly closing the door reducing the sound of closure during the final approach of the door. 
         [0008]    More specifically, the preferred embodiment of the present apparatus further comprising a roller path having a roller stop at a first end of the roller path and a roller ramp or plateau at a second end of the roller path for holding the closing system in an open door position, wherein release thereof activates a seamless closure cycle of the control motion hinge pulling the door closed. 
         [0009]    In a further preferred embodiment of the control motion hinge, including a first hinge pin, a first leaf hinge having two or more knuckles to removably secure the first hinge pin and adapted to be fixed to the jam, a second hinge pin, a second leaf hinge having two or more knuckles to removably secure the second hinge pin and adapted to be fixed to the door, and a link having one or more knuckles on a first end to interlock with the two or more knuckles of the first leaf hinge and one or more knuckles on a second end to interlock with the two or more knuckles of the second leaf hinge. 
         [0010]    In a further exemplary embodiment the control motion hinge with a torsion spring, including a first hinge pin, a first leaf hinge having two or more knuckles to removably secure the first hinge pin and adapted to be fixed to the jam, a second hinge pin, a second leaf hinge having two or more knuckles to removably secure the second hinge pin and adapted to be fixed to the door, a link having one or more knuckles on a first end to interlock with the two or more knuckles of the first leaf hinge and one or more knuckles on a second end to interlock with the two or more knuckles of said second leaf hinge, and a first spring device positioned between said first leaf hinge and said link. 
         [0011]    In a further exemplary embodiment a method for an automatic closing hinge, including the steps of: providing a first hinge pin, a first leaf hinge having two or more knuckles to removably secure the first hinge pin and adapted to be fixed to the jam, wherein at least one of the two or more knuckles of the first leaf hinge further comprises a pair of roller sleeves, a roller pin and a roller, a second hinge pin, a second leaf hinge having two or more knuckles to removably secure the second hinge pin and adapted to be fixed to the door, wherein at least one of the two or more knuckles of the second leaf hinge further comprises a roller path for engaging the roller of the first leaf hinge, a link having one or more knuckles on a first end to interlock with the two or more knuckles of the first leaf hinge and one or more knuckles on a second end to interlock with the two or more knuckles of the second leaf hinge, and a spring in contact with an upper surface of the link and an outer surface of the two or more knuckles of the second leaf hinge, rotating the first leaf hinge apart from the second leaf hinge, traversing the roller along the roller path, expanding the spring while the first leaf hinge rotates apart from the second leaf hinge, and contracting the spring returns the first leaf hinge toward the second leaf hinge and the roller returns along the roller path. 
         [0012]    Accordingly, a feature of the present control motion hinge is its ability to provide a hinge with a continuous closure force, thus allowing the door to close at a controlled rate of speed when the hinge is released. 
         [0013]    Another feature of the present control motion hinge is its ability to provide a hinge wherein the closure system integrated as part of the hinge or knuckle, or hidden within the door jam, door frame or within the door, rendering an enhanced aesthetic appearance. 
         [0014]    Still another feature of the present control motion hinge is its ability to provide a dampening closure cylinder utilizing hydraulic oil, nitric oxide, air or other compressible material. 
         [0015]    Yet another feature of the present control motion hinge is its ability to provide a hinge that softly closes the door reducing the sound of closure during the final approach of the door. 
         [0016]    Yet another feature of the present control motion hinge is its ability to provide a door hinge with a soft closure system that prevents a door from rapid closing so as to protect the door, jam, doorframe, or surroundings from being damaged. 
         [0017]    Yet another feature of the present control motion hinge is its ability to provide a hinge with a soft closure system that cushions door closure, thereby reducing the stress on the door, hinge, latch/lock, jam, and frame. 
         [0018]    Yet another feature of the present control motion hinge is its ability to provide a hinge with seamless motion throughout the hinges full range of motion. 
         [0019]    Yet another feature of the present control motion hinge is its ability to provide a simple, compact, and inexpensive hinge with a seamless lock open and release mechanism and a closure system. 
         [0020]    Yet another feature of the present control motion hinge is its ability to provide a door closer, which can smoothly and effectively close the door after opening and releasing. 
         [0021]    Yet another feature of the present control motion hinge is its ability to hold the door in a full open position, release the door there from, and maintain a controlled closure motion through the door&#39;s final approach. 
         [0022]    Yet another feature of the present control motion hinge is its ability to reduce the opening force required to open the door facilitating accessibility for small children, elderly, handicapped and those with disabilities. 
         [0023]    Yet another feature of the present control motion hinge is its ability to provide a door hinge that can motion the door to a closed position in a smooth and slow manner during final approach. 
         [0024]    Yet another feature of the present control motion hinge is its ability to provide a hinge assembly that can be sold as a replacement hinge assembly for retrofitting and improving existing hinges. 
         [0025]    Yet another feature of the present control motion hinge is its ability to provide a hinge assembly that meets industry life cycle requirements. 
         [0026]    Yet another feature of the present control motion hinge is its ability to provide a hinge assembly that 
         [0027]    These and other features of the control motion hinge will become more apparent to one skilled in the art from the following Detailed Description of the Preferred and Selected Alternate Embodiments and Claims when read in light of the accompanying drawing Figures. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0028]    The present control motion hinge will be better understood by reading the Detailed Description of the Preferred and Selected Alternate Embodiments with reference to the accompanying drawing figures, in which like reference numerals denote similar structure and refer to like elements throughout, and in which: 
           [0029]      FIG. 1  is a front view of a prior art door assembly showing three hinges spaced vertically between a door frame and a swinging door, showing the hinges in a closed state; 
           [0030]      FIG. 1.1  is an enlarged perspective view showing a prior art door hinge shown in  FIG. 1  in the open state; 
           [0031]      FIG. 2  is a perspective view of a control motion hinge according to a preferred embodiment; 
           [0032]      FIG. 3  is an enlarged perspective view of the control motion hinge of  FIG. 2 , shown in the open state; 
           [0033]      FIGS. 4 ,  4 . 1 ,  4 . 2 ,  4 . 3 , and  4 . 4  are exploded perspective views of the two leaf hinges, link and flat spring assembly according to a preferred embodiment; 
           [0034]    FIG.  4 . 1 . 1  is a perspective view of the leaf hinge and torsion spring assembly according to an exemplary embodiment; 
           [0035]    FIG.  4 . 2 . 1  is a perspective view of link and torsion spring assembly according to an exemplary embodiment; 
           [0036]      FIGS. 5 ,  5 . 1 ,  5 . 2 ,  5 . 3 ,  5 . 4  and  5 . 5  are expanded partial cross-sectional side views of the control motion hinge of  FIG. 2 , shown in the closed, partially open, and open states; 
           [0037]    FIG.  5 . 4 . 1  expanded partial cross-sectional side views of the control motion hinge of FIGS.  4 . 1 . 1  and  4 . 2 . 1 , shown in the and open state; 
           [0038]      FIGS. 6 ,  6 . 1  and  6 . 2  are expanded partial cross-sectional side views of the control motion hinge with integrated dampener of  FIG. 2 , shown in the closed and open states; and 
           [0039]      FIGS. 7 ,  7 . 1 ,  7 . 2 ,  7 . 3 ,  7 . 5  and  7 . 6  are expanded partial cross-sectional side views of the control motion hinge of FIGS.  4 . 1 . 1  and  4 . 2 . 1 , shown in the closed, partially open, and open states. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0040]    In describing the preferred and alternate embodiments of the present invention, as illustrated in  FIGS. 1-7  specific terminology is employed for the sake of clarity. The present invention, however, is not intended to be limited to the specific terminology so selected, and it is to be understood that each specific element includes all technical equivalents that operate in a similar manner to accomplish similar functions. 
         [0041]    Referring now to FIGS.  1  and  1 . 1 , there is depicted a prior art door D, door jam J, door header I and three hinge assembly H 1 , H 2 , and H 3 . The door D, which swings inward, toward the viewer as depicted in  FIG. 1 , fits closely to jam J at both its hinge edge A 1  and its opposite or latch edge A 2 . Door A may be configured to swing inward or outward by switching the configuration of hinge assembly H 1 , H 2 , and H 3 . It should be noted, also, that no hinge is exposed to view along the hinge edge A 1  when the door is closed as viewed from the other side of door D. 
         [0042]    Referring now to  FIG. 1.1 , a perspective view of a typical prior art hinge assembly H having two hinge leaves formed as a pair, stationary hinge leaf L 1  and rotatable hinge leaf L 2 , and connected therebetween by hinge pin P. The hinge leaves (L 1 , L 2 ) have offset knuckles K which when interlinked are preferably joined together by the hinge pin P. Each hinge leaf is shown with three mount holes M 1 , M 2 , and M 3  formed in the hinge leaves. The stationary hinge leaf L 1  is secured to door jam J utilizes a flathead screw, nail or the like driven through mount holes M of such stationary hinge leaf L 1 , while the rotatable hinge leaf L 2  is secured to opening-and-closing door D, or the like, also utilizes a flat screw, nail or the like driven through mount holes M of such rotatable hinge leaf L 2 . To hang door D to door jam J, door D is positioned near door jam J so that knuckles K of stationary hinge leaf L 1  are interlinked with knuckles K of rotatable hinge leaf L 2  and pin P is inserted into such interlinked knuckles of stationary hinge leaf L 1  and rotatable hinge leaf L 2 , thereby enables door A to freely rotationally swing about pin P with stationary hinge leaf L 1  affixed to door jam J. 
         [0043]    Referring now to  FIGS. 2 and 3 , by way of example, and not limitation, there is illustrated a perspective view of control motion hinge  10  in accordance with a preferred embodiment of the present invention. Preferably, control motion hinge  10 , having a first hinge member such as stationary hinge leaf  12 , a second hinge member such as rotatable hinge leaf  14 , knuckles  18 ,  19 , counter leaver member such as link  21 , and a first hinge pin such as stationary hinge pin  16  and a second hinge pin such as rotatable hinge pin  17  are preferably formed of a suitable material, such as aluminum, brass, iron, steel, or other metals, plastic, including various finishes from chrome, antiqued copper, black, and brass (either plated or pure brass) or the like, capable of providing structure and strength to hinge assembly H. Preferably, the material includes other suitable characteristics, such as durability, water-resistance, light weight, malleable, oxidation resistance, ease of workability, or other beneficial characteristic understood by one skilled in the art. Moreover, hinge  10  may come in an endless variety of types, shapes, sizes and purposes, including but not limited to butt hinges, strap hinge, spring hinge, wide throw hinge, left hand, right hand hinge and the like. 
         [0044]    Referring now to  FIGS. 2 and 3 , the present invention in its preferred embodiment is a control motion hinge  10 . Preferably, control motion hinge  10  comprises two hinge leaves formed as a pair, stationary hinge leaf  12 , and rotatable hinge leaf  14 , and connected therebetween by a link  21  and stationary hinge pin  16  and rotatable hinge pin  17 . The hinge leaves ( 12 ,  14 ) preferably have offset knuckles  18 , which interlocked with offset knuckles  19  of link  21  and thereby joined together as a combination linkage by stationary hinge pin  16  and rotatable hinge pin  17 . 
         [0045]    Referring now to  FIGS. 2 and 3 , control motion hinge  10  is preferably shown in a partial open position and shown having a spring device such as flat spring  22  coupled around offset knuckles  18  of stationary hinge leaf  12  and offset knuckles  19  of link  21 . 
         [0046]    Referring now to  FIG. 3 , control motion hinge  10  is preferably shown in an approximately full open position and shown having roller  32  positioned between roller sleeve  33  and roller sleeve  35 , which preferably are positioned on the underside surface of one or more offset knuckles  18  of rotatable hinge leaf  14  and held rotationally in position by roller pin  36 . In operation, roller  32  traverses roller path  34  of offset knuckles  18  of stationary hinge leaf  12  between roller stop  38  and roller closing ramp  31 . Moreover, one or more mount holes  37  (four shown) are positioned in stationary hinge leaf  12  and rotatable hinge leaf  14 . 
         [0047]    Referring now to  FIGS. 4 ,  4 . 1 ,  4 . 2 ,  4 . 3 ,  4 . 4 , by way of example, and not limitation, there is illustrated an exploded perspective view of control motion hinge  10  in accordance with a preferred embodiment of the present invention. Referring again to  FIG. 4.1 , there is illustrated an exploded perspective view of rotatable hinge leaf  14  of control motion hinge  10 . Preferably, rotatable hinge leaf  14  includes flat single geometric plane  41  arranged as rectangle or other geometric shape and further preferably having one or more mount holes  37  (four shown) positioned in rotatable hinge leaf  14  for removably attach rotatable hinge leaf  14  to door D (as shown in  FIGS. 2 and 3 ) utilizes a flathead screw, nail or the like driven through mount holes  37  of such rotatable hinge leaf  14 . Edge  43  preferably runs the perimeter of plane  41 . On one segment of edge  43  of rotatable hinge leaf  14  preferably includes one or more offset knuckles  18 . 1 ,  18 . 2 , and  18 . 3  having pin hole  45 . 1  operative to run linearly there through each offset knuckle  18 . 1 ,  18 . 2 , and  18 . 3 . Referring again to  FIG. 4.2 , there is illustrated an exploded perspective view of link  21  of control motion hinge  10 . Preferably, link  21  includes on one end of link one or more offset knuckles  19 . 1  and  19 . 2  having pin hole  45 . 2  operative to run linearly there through each offset knuckle  19 . 1  and  19 . 2 . 
         [0048]    In use, offset knuckles  19 . 1  and  19 . 2  of link  21  are preferably interlock or fit together closely with offset knuckles  18 . 1 ,  18 . 2 , and  18 . 3  of rotatable hinge leaf  14 , whereby rotatable hinge pin  17  is positioned within pin holes  45 . 1  of offset knuckles  18 . 1 ,  18 . 2 , and  18 . 3  and pin holes  45 . 2  of offset knuckles  19 . 1  and  19 . 2  to rotationally connect link  21  and rotatable hinge leaf  14 . 
         [0049]    Referring again to  FIG. 4.1 , there is illustrated an exploded perspective view of rotatable hinge leaf  14  of control motion hinge  10 . Preferably, roller sleeve  33  and roller sleeve  35  are affixed to the adjacent or situated near or close or touching exterior surface of both knuckles  18 . 1  and  18 . 3  and roller  32  is positioned there between roller sleeve  33  and roller sleeve  35  and held in position when roller pin  36  is positioned within pin holes  45 . 3  of roller sleeve  33  and roller sleeve  35 . 
         [0050]    Referring to FIG.  4 . 1 . 1 , there is illustrated an exploded perspective view of rotatable hinge leaf  14  of control motion hinge  10 . Preferably, in place thereof of knuckle  18 . 2  (or one or more knuckles  18 . 1 - 18 . 3 ) rotatable hinge leaf  14  includes a trimmed or cutout or formed section such as area  18 . 2 . 1 , wherein a second spring device such as second torsion spring  92  may be positioned. Preferably second torsion spring  92  is configured to coil around rotatable hinge pin  17  within area  18 . 2 . 1  when rotatable hinge pin  17  is positioned within pin hole  45 . 2  of knuckles  19 . 1  and  19 . 2  of link  21  and pin holes  45 . 1  of offset knuckles  18 . 1  and  18 . 3  of rotatable hinge leaf  14 . 
         [0051]    In use, one end such as first end  91  of second torsion spring  92  is slidably affixed or anchored in an aperture such as hole  94  of rotatable hinge leaf  14  and the other end such as second end  93  of second torsion spring  92  is configured to engage a wheel such as roller  35 . 1  mounted on roller mount  38 . 1 , shown in FIG.  5 . 4 . 1 , (or second end  93  may engage any other independent position of stationary hinge leaf  12 ). Roller mount  38 . 1  is preferably positioned on plane  41  of stationary hinge leaf  12  and preferably positioned approximate area  18 . 2 . 1  (or positioned approximate one or more knuckles  18 . 1 - 18 . 3 ) of stationary hinge leaf  12 . Preferably, second torsion spring  92  functions as a torsional force such as non-continuous secondary force f between rotatable hinge leaf  14  and roller  35 . 1  when door D is pushed to near-full-open position (approximately 110 degrees; however, this may be between approximately 90 degrees and 130 degrees). In general second torsion spring  92  operates as an aid or assist to first torsion spring  82  (shown in FIG.  4 . 2 . 1 ), preferably when rotatable hinge leaf  14  (or door D) is in a neutral zone/near-full-open position (approximately 90 degrees and 130 degrees) where torsional force such as force f of first torsion spring  82  is unable to close door D and requires assistance from second torsion spring  92  to enable soft closure of door D. In the alternative, in order to close door D, torsional force such as force f of first torsion spring  82  must be oversized resulting in too much energy from first torsion spring  82  at door D closure, which are greater than fire code and Americans with Disability Act force limits of a maximum of five (5) pounds; thus causing a hard closure rather than a soft closure of door D. 
         [0052]    It is contemplated herein that second torsion spring  92  assistance through door D&#39;s neutral zone enables reduced sizing of first torsion spring  82  to meet fire code and Americans with Disability Act force limits of a maximum of five (5) pounds. Moreover, the combination torsion spring  82 / 92  preferably enables reduced sizing of first torsion spring  82  to approximately one (1) pound or less to effective soft closure of door D. 
         [0053]    Referring again to  FIG. 4.3 , there is illustrated an exploded perspective view of stationary hinge leaf  12  of control motion hinge  10 . Preferably, stationary hinge leaf  12  includes flat single geometric plane  41  arranged as rectangle or other geometric shape and further preferably having one or more mount holes  37  (four shown) positioned in stationary hinge leaf  12  for removably attach stationary hinge leaf  12  to jam J (as shown in  FIGS. 2 and 3 ) utilizes a flathead screw, nail or the like driven through mount holes  37  of such stationary hinge leaf  12 . Edge  43  preferably runs the perimeter of plane  41 . On one segment of edge  43  preferably includes one or more offset knuckles  18 . 4  and  18 . 5  having pin hole  45 . 4  operative to run linearly there through each offset knuckle  18 . 4  and  18 . 5 . Referring again to  FIG. 4.2 , there is illustrated an exploded perspective view of link  21  of control motion hinge  10 . Preferably, link  21  preferably includes on the other end at least one offset knuckle  19 . 3  having pin hole  45 . 5  operative to run linearly there through knuckle  19 . 3 . 
         [0054]    In use, offset knuckle  19 . 3  of link  21  is preferably interlocked with offset knuckles  18 . 4  and  18 . 5  of stationary hinge leaf  12 , whereby stationary hinge pin  16  is positioned within pin hole  45 . 5  of offset knuckle  19 . 3  and pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  to rotationally connect link  21  and stationary hinge leaf  12 . 
         [0055]    Furthermore, when in combination use, stationary hinge pin  16  is positioned within pin hole  45 . 5  of offset knuckle  19 . 3  and pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  to rotationally connect link  21  and stationary hinge leaf  12 , and rotatable hinge pin  17  is positioned within pin holes  45 . 1  of offset knuckles  18 . 1 ,  18 . 2 , and  18 . 3  and pin holes  45 . 2  of offset knuckles  19 . 1  and  19 . 2  to rotationally connect link  21  and rotatable hinge leaf  14 , control motion hinge  10  preferably is a three member linkage hinge constructed of stationary hinge leaf  12 , link  21 , and rotatable hinge leaf  14 . 
         [0056]    Alternatively, referring to FIG.  4 . 2 . 1 , there is illustrated an exploded perspective view of link  21  of control motion hinge  10 . Preferably, link  21  preferably includes on the other end one or more offset knuckles  19 . 3 A and  19 . 3 B having pin hole  45 . 5  operative to run linearly there through knuckle offset knuckles  19 . 3 A and  19 . 3 B. 
         [0057]    Furthermore, when in combination use, stationary hinge pin  16  is positioned within pin hole  45 . 5  of offset knuckle offset knuckles  19 . 3 A and  19 . 3 B and pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  to rotationally connect link  21  and stationary hinge leaf  12 , and rotatable hinge pin  17  is positioned within pin holes  45 . 1  of offset knuckles  18 . 1 ,  18 . 2 , and  18 . 3  and pin holes  45 . 2  of offset knuckles  19 . 1  and  19 . 2  to rotationally connect link  21  and rotatable hinge leaf  14 , control motion hinge  10  preferably is a three member linkage hinge constructed of stationary hinge leaf  12 , link  21 , and rotatable hinge leaf  14  (as shown in  FIG. 4 ). 
         [0058]    Moreover, an open area such as notch  19 . 4  is preferably formed between one or more offset knuckles  19 . 3 A and  19 . 3 B of link  21 , wherein a spring device such as first torsion spring  82  may be positioned. Preferably first torsion spring  82  is configured to coil around stationary hinge pin  16  within notch  19 . 4  when stationary hinge pin  16  is positioned within pin hole  45 . 5  of knuckles  19 . 3 A and  19 . 3 B of link  21  and pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  of stationary hinge  12 . 
         [0059]    In use, one end such as first end  81  of first torsion spring  82  is slidably affixed or anchored in an aperture such as hole  84  in link  21  and the other end such as second end  83  of first torsion spring  82  is slidably anchored or affixed in an aperture such as notch  85  in stationary hinge leaf  12  (as shown in FIG.  5 . 2 . 1 ). Preferably, first torsion spring  82  functions as a torsional force such as continuous primary force f (as shown in FIG.  5 . 4 . 1 ) when link  21  rotates counter-clockwise about stationary hinge pin  16 . Force f returns link  21  to its starting position where rotatable hinge leaf  14  is in contact with stationary hinge  12 . In general first torsion spring  82  operates, preferably when an arc rotation (kinetic) of link  21  about stationary hinge pin  16  positioned within pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  rotationally separates link  21  from stationary hinge leaf  12 , which further results in an opposite primary force f (potential) of first torsion spring  82  to return link  21  and stationary hinge leaf  12  to their original positions. 
         [0060]    It is contemplated herein that first torsion spring  82  applies a continuous primary force f on link  21  to return link  21  and stationary hinge leaf  12  to their original positions. Fire code and Americans with Disability Act limit door D force to a maximum of five (5) pounds of force. 
         [0061]    Moreover, torsion spring  82 / 92  are preferably formed of a suitable material, such as metal, steel, stainless steel or the like, capable of providing suitable characteristics, such as torque, twisting force, rotational resistance/force, shape memory, magnetism, durability, water-resistance, light weight, heat-resistance, chemical inertness, oxidation resistance, ease of workability, or other beneficial characteristic understood by one skilled in the art. 
         [0062]    It is contemplated herein that the size and dimensions of roller path  34  is preferably utilized to set the neutral point between stationary hinge leaf  12  and rotatable hinge leaf  14 . For example, without roller path  34  (i.e. plane  41  of stationary hinge leaf  12 ) the approximate neutral point is approximately 66 degrees between stationary hinge leaf and rotatable hinge leaf  14 . By introducing a upward, linear or f(x) slope to roller path  34  this in turn raises the approximate neutral point to preferably approximately 85 degrees between stationary hinge leaf  12  and rotatable hinge leaf  14 ; however, this may be between approximately 80 degrees and approximately 110 degrees and thereafter raise with diminishing return. It is recognized herein that roller path  34  is not critical for the counter leaver action of control motion hinge  10 , but rather stationary hinge leaf  12 , stationary hinge pin  16 , link  21 , rotatable hinge pin  17 , and rotatable hinge leaf  14  create control motion hinge  10  counter leaver action. 
         [0063]    It is recognized that plane  41  of rotatable hinge leaf  14  and stationary hinge leaf  12  is preferably configured as a four (4) inch pattern rated for approximately 75 pounds or a four and a half (4.5) inch pattern rated for approximately 75-115 pounds; however, different sizes and/or configurations are contemplated herein. 
         [0064]    Referring again to  FIG. 4.4 , there is illustrated an exploded perspective view of flat spring  22  of control motion hinge  10 . Preferably, flat spring  22  is formed to match the exterior surface and contours of offset knuckles  18 . 4  and  18 . 5  of stationary hinge leaf  12  and is generally ‘C’ shaped. Moreover, flat spring  22  is preferably formed of a suitable material, such as metal, steel, stainless steel or the like, capable of providing suitable characteristics, such as tension, extension, expansion, shape memory, magnetism, durability, water-resistance, light weight, heat-resistance, chemical inertness, oxidation resistance, ease of workability, or other beneficial characteristic understood by one skilled in the art. Preferably, flat spring  22  includes inner-upper surface  49  and inner-lower surface  51  and when in use both surfaces are in contact with the outer surface of offset knuckles  18 . 4  and  18 . 5  of stationary hinge leaf  12 . Moreover, inner-upper surface  49  of flat spring  22  is preferably arranged to rest on upper surface  44  of link  21  and attached thereto by spring screws or the like inserted in screw holes  53  formed in flat spring  22  and screw holes formed in upper surface  44  of link  21 . In use, flat spring  22  is preferably positioned on the outer surface of offset knuckles  18 . 4  and  18 . 5  of stationary hinge leaf  12  and on upper surface  44  of link  21 , in order to function as a spring when link  21  rotates about stationary hinge pin  16  positioned within pin hole  45 . 5  of offset knuckle  19 . 3  of link  21  and pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5 . In general flat spring  22  operates, preferably when an arc rotation (kinetic) of link  21  about stationary hinge pin  16  positioned within pin holes  45 . 4  of offset knuckles  18 . 4  and  18 . 5  separates inner-upper surface  49  of flat spring  22  from inner-lower surface  51  of flat spring  22 , which further results in an opposite force (potential) of flat spring  22  to return inner-upper surface  49  and inner-lower surface  51  of flat spring  22  to their original positions. 
         [0065]    It is contemplated that roller pin  36 , rotatable hinge pin  17 , stationary hinge pin  16 , and screws  47  could be interchangeably replaced with pins, screws bolts, pins and cotter keys, rivets or other like attachment devices. 
       Hinge Open Cycle 
       [0066]    Referring now to  FIGS. 5 ,  5 . 1 ,  5 . 2 ,  5 . 3 ,  5 . 4 ,  5 . 5  by way of example, and not limitation, there is illustrated a series of side views of control motion hinge  10  in motion, in accordance with a preferred embodiment of the present invention. Referring again to  FIG. 5.1 , there is illustrated a side view of control motion hinge  10  shown in a hinge-closed position with door D closed against jam J. Preferably, roller  32  and roller sleeve  35  of rotatable hinge leaf  14  are positioned against roller stop  38  of roller path  34  of offset knuckles  18 . 5  of stationary hinge leaf  12 . Preferably, arch a in  FIG. 5.1  is the angle between plane  41  of stationary hinge leaf  12  and upper surface  44  of link  21 . Preferably, arc a in  FIG. 5.1  comprise equivalent arc angle of −5 degrees; however, arc a may be between approximately 0 degrees and −10 degrees. Preferably, arc a 1  in  FIG. 5.1  is the angle between plane  41  of stationary hinge leaf  12  and rotatable hinge leaf  14 . Preferably, arc a 1  in  FIG. 5.1  comprise equivalent arc angle of 0 degrees; however, arc a 1  may be between approximately 2 degrees and −2 degrees. 
         [0067]    Referring again to  FIG. 5.2 , there is illustrated a side view of control motion hinge  10  shown in a hinge-beginning-to-open position. Preferably, as door D is pushed open expands arc a 1 , rotatable hinge leaf  14  rotates about rotatable hinge pin  17  of offset knuckle  18 . 3  (similarly with  18 . 1 ,  18 . 2  not shown) of rotatable hinge leaf  14 , which further rotates link  21  about stationary hinge pin  16  of offset knuckle  18 . 5  (similarly with  18 . 4  not shown) of stationary hinge leaf  12 . Rotatable hinge leaf  14  is preferably configured having the center-point of rotatable hinge pin  17  of offset knuckle  18 . 5  and the center-point of roller pin  36  of roller  32  and roller sleeve  35  are preferably length L 1  apart. Preferably, center-points comprise equivalent length L 1  of ⅜ inch; however, length L 1  may be between approximately ¼ inch and approximately ½ inches. Moreover, when in use, the greater length L 1  between center-points of rotatable hinge pin  17  and roller pin  36  of roller  32  and roller sleeve  35  results in an increased arc a of rotation of link  21  about stationary hinge pin  16  of offset knuckles  18 . 4 , which further results in an increased opposite force f of flat spring  22  to return inner-upper surface  49  and inner-lower surface  51  of flat spring  22  to their original positions. Preferably, as arc a moves slightly, a 1  moves at much greater arc angle; thus, allows flat spring  22  to maintain optimum force f between inner-upper surface  49  and inner-lower surface  51  of flat spring  22 . The ratio of arc a to arc a 1  and equivalent force f are proportional to length L 1 . 
         [0068]    Referring again to  FIG. 5.3 , there is illustrated a side view of control motion hinge  10  shown in a hinge-mostly-open position. Preferably, as door D is pushed further open expands arc a 1 , rotatable hinge leaf  14  rotates further about rotatable hinge pin  17  of offset knuckle  18 . 3  (similarly with  18 . 1 ,  18 . 2  not shown) of rotatable hinge leaf  14 , which slightly rotates link  21  about stationary hinge pin  16  of offset knuckle  18 . 5  (similarly with  18 . 4  not shown) of stationary hinge leaf  12 . It is contemplated herein that as arc a moves slightly, a 1  moves at much greater arc angle; thus, allows flat spring  22  to maintain optimum force f between inner-upper surface  49  and inner-lower surface  51  of flat spring  22 . First, when roller  32  reaches neutral point  52  of roller path  34  then arc a of rotation of link  21  about stationary hinge pin  16  of offset knuckles  18 . 5  has reached its maximum rotation (arc a is 38 degrees; however, arc a may be between approximately 15 degrees and 50 degrees) and inner-upper surface  49  and inner-lower surface  51  of flat spring  22  have reached the maximum distance of separation, which results in the maximum opposite force f of flat spring  22  to return inner-upper surface  49  and inner-lower surface  51  of flat spring  22  to their original positions. Second, when roller  32  reaches neutral point  52  of roller path  34  then arch a 1  in  FIG. 5.2  the angle between plane  41  of stationary hinge leaf  12  and upper surface  44  of link  21  is comprise equivalent arc angle of 82 degrees; however, arc a 1  may be between approximately 60 degrees and 95 degrees. It should be recognized that force f can change arc a 1  in either direction to maximum angle of 110 degrees; however, arc a 1  may be between approximately 100 degrees and 180 degrees, or return arc a 1  to a closed position of 0 to −5 degrees. Third, when roller  32  reaches neutral point  52  of roller path  34  then upper surface  44  of link  21  lifts above upper exterior surface of offset knuckles  18 . 5  (similarly with  18 . 4  not shown) of stationary hinge leaf  12  loads flat spring  22 . Moreover, when roller  32  reaches neutral point  52  of roller path  34  then roller  32  preferably climbs to the top of roller path  34  an altitude preferably of length L 3  (shown in  FIG. 5.4 ), wherein door D reaches approximately eighty-two (82) degrees arc a 1  hold-open position of door D (other degrees are contemplated herein). Preferably, length L 3  comprise equivalent of 3/16 inch as shown; however, length L 3  may be between approximately 0 inch and approximately ⅜ inch. 
         [0069]    Referring again to  FIG. 5.4 , there is illustrated a side view of control motion hinge  10  shown in a hinge near full-open position. Preferably, as door D is pushed to full open arc a 1  (approximately 110 degrees; however, arc a 1  may be between approximately 100 degrees and 130 degrees,) and rotatable hinge leaf  14  rotates still further about rotatable hinge pin  17  of offset knuckle  18 . 3  (similarly with  18 . 1 ,  18 . 2  not shown) of rotatable hinge leaf  14  about offset knuckle  19 . 1  and  19 . 2  of link  21 , which partially reverse rotates (opposite direction) link about stationary hinge pin  16  of offset knuckle  18 . 5  (similarly with  18 . 4  not shown) of stationary hinge leaf  12  about offset knuckle  19 . 3  of link  21 , and reduces arc a and force f; but, moves arc a 1  to maximum open angle of 110 degrees, however, arc a 1  may be between approximately 100 degrees and 130 degrees; thus allows roller  32  to traverse horizontally along hold-open ramp  54  of roller path  34  in a linear direction away from the center-point of stationary hinge pin  16 . Moreover,  FIG. 5.4  illustrates additional measurements. The first is preferably the center-points between stationary hinge pin  16  and rotatable hinge pin  17 , length L 4 . Preferably, length L 4  comprise equivalent of ⅝ inch as shown; however, length L 3  may be between approximately ⅜ inch and approximately ¾ inch. The second is preferably the travel distance of roller  32  from closed door to neutral point  52  of roller path  34 , length L 2 . Preferably, length L 2  comprise equivalent of ⅝ inch as shown; however, length L 2  may be between approximately ½ inch and approximately ¾ inch. 
         [0070]    It is contemplated herein that flat spring  22  is preferably configured to enable rotatable hinge leaf  14  to traverse arc a 1  as door D is pushed to the full open position (approximately 110 degrees). 
         [0071]    The dimensions referenced as preferred herein above are understood as one preferred configuration herein, and are not intended to be dimensions which are limiting in any way to other suitable configurations, door and jam configuration and/or weight of the applicable door being supported. 
         [0072]    Alternatively, referring to FIG.  5 . 4 . 1 , there is illustrated a side view of control motion hinge  10  shown in a hinge extreme full-open position parallel wall B. Preferably, as door D is pushed to extreme full open arc a 2  (approximately 180 degrees; however, arc a 2  may be between approximately 130 degrees and 200 degrees,) and rotatable hinge leaf  14  rotates still further about rotatable hinge pin  17  of offset knuckle  18 . 3  (similarly with  18 . 1 ,  18 . 2  not shown) of rotatable hinge leaf  14  about offset knuckle  19 . 1  and  19 . 2  of link  21 , which still further rotates link about stationary hinge pin  16  of offset knuckle  18 . 5  (similarly with  18 . 4  not shown) of stationary hinge leaf  12  about offset knuckle  19 . 3 A and  19 . 3 B of link  21 , which is maximum torsional rotation primary force f applied to first torsion spring  82 ; and thus allows roller  32  to temporarily depart from roller path  34  in an arc a 3  about the center-point of stationary hinge pin  16 . 
         [0073]    It is contemplated herein that first torsion spring  82  is preferably configured to enable rotatable hinge leaf  14  to traverse arc a 2  as door D is pushed to the extreme full open position (approximately 180 degrees). 
       Hinge Close Cycle 
       [0074]    Referring again to  FIG. 5.4 , when door D is pushed to full open position (as shown) and in this position door D preferably is held in a hold-open position until door D is nudged closed wherein roller  32  traverses back past neutral point  52 , which releases force f of flat spring  22 , which results in roller  32  to traverse from hold-open ramp  54  to neutral point  52  to roller stop  38  of closing ramp  31  in a direction toward the center-point of stationary hinge pin  16 , which further causes rotatable hinge leaf  14  to return along arc a 1  until geometric plane  41  of rotatable hinge leaf  14  and stationary hinge leaf  12  contact or come in close proximate contact with one another. 
         [0075]    Referring now to  FIG. 5.5 , preferably when door D is in the closed position the weight of door D may place pull away force fd on flat spring  22  causes door D to possibly sag (door D pulls away and tilts down via pull away force fd as shown in  FIG. 1 ); however, interior lip  19  of offset knuckle  18 . 5  (similarly with  18 . 4  not shown) combines with force f applied by flat spring  22  to prevent sag in door D and/or to prevent roller  32  from traversing roller path  34 . Moreover, roller  32  preferably is cradled in a pocket formed by roller stop  38  of roller path  34  and bottom edge  19  of offset knuckle  18 . 5  to hold rotatable hinge leaf  14  and stationary hinge leaf  12  in the shown closed position countering pull away force fd on door D. 
         [0076]    It is contemplated that lengths L 1 , L 2 , L 3 , L 4 , a, and/or a 1  may be modified or one or more combinations may be modified to achieve increased force f, more or less door closing power, and/or to prevent sag of door D. 
         [0077]    It is further contemplated that roller path  34  may be configured to have straight line(s) with or without sharp corners, or other contours, curves, and/or lengths to accomplish motions set forth herein or further contemplated for alternative control of motion hinge  10 . 
         [0078]    It is contemplated that flat spring  22  may be modified, sized, derived from different materials and/or configured to achieve increased force and/or more or less door closing power. 
         [0079]    It is contemplated that stationary hinge leaf  12  and rotatable hinge leaf  14  may flip positions. 
         [0080]    Referring now to  FIGS. 6 ,  6 . 1 , and  6 . 2 , by way of example, and not limitation, there is illustrated a series of side views of control motion hinge  10  in motion, in accordance with an alternate embodiment of the present invention. Referring again to  FIG. 6.1 , there is illustrated a side view of control motion hinge  10 , included is dampener  60  shown in a hinge-closed position with door D closed against jam J. Preferably, jam J is fitted with housing tube  65  offset from control motion hinge  10  and connected to jam J on first end  69  of housing tube  65  and approximately centered in jam J and preferably positioned along jam J other than where assembly H 1 , H 2 , and H 3  (as shown in  FIG. 1 ) are located. Housing tube  65  preferably is ¾ inch in diameter, wherein such diameter hole is correspondingly drilled or otherwise defined into jam J to the preferred depth of 1.5 to 3 inches or alternatively into door D if stationary hinge leaf  12  and rotatable hinge leaf  14  flip positions. Jam J preferably includes hole  73  bored into jam J where housing tube  65  is positioned therein. Moreover, dampener  60  preferably includes plunger  62  and coil spring  64 . Preferably, plunger of dampener  60  passes in and out of housing tube  65  through which plunger  62  and plunger  62  preferably connects to coil spring  64  (shown in a compressed mode in  FIG. 6.1 ) to smooth out or dampen the shock impulse and dissipate the kinetic energy of door D when closing. Housing tube  65  and plunger  62  are further preferably manufactured from aluminum, however, steel, plastic, fiberglass or other suitable material having characteristics, such as durability, water-resistance, lightweight, or the like, capable of providing structure to housing tube  65  and plunger  62 . 
         [0081]    Referring again to  FIG. 6.2 , there is illustrated a side view of control motion hinge  10  included is dampener shown in a hinge-open position with door D swung open from jam J. Plunger  62  preferably includes on one end striker head  61  and on the other end compression head  63  and travels in and out of housing tube  65  via rod seal  72 . Compression head  63  of plunger  62  is preferably attached to first end  66  of coil spring  64  and second end  67  of coil spring  64  is preferably attached to second end  68  of housing tube  65 , and housed therein. Moreover, coil spring  64  (shown in an expanded mode with rod  62  extends through hole  72  in  FIG. 6.2 ) is preferably manufactured from hardened steel, however, stainless steel, plastic, or other suitable material having characteristics, such as shape memory, resistance, lightweight, or the like. 
         [0082]    During door D closure cycle, rotatable hinge leaf  14  preferably returns along arc a 1  until geometric plane  41  of rotatable hinge leaf  14  contacts striker head  61  and transfers the kinetic energy of rotating door D to compression head  63 , which preferably is absorbed by coil spring  64  within housing tube  65 , resulting in geometric plane  41  of rotatable hinge leaf  14  preferably pushes plunger  62  towards second end  68  of housing tube  65  and compresses coil spring  64 , wherein rotatable hinge leaf  14  gently contacts or comes in close proximate contact with geometric plane  41  of stationary hinge leaf  12  for a soft closure of door D. 
         [0083]    It is contemplated that dampener  60  may be configured as any dashpot or shock absorber whether pneumatic or hydraulic having common form of a cylinder with a sliding piston inside wherein the cylinder is filled with a fluid (such as hydraulic fluid) or air and designed to smooth out or dampen shock impulse, and dissipate kinetic energy or other known dampener known by one of ordinary skill in the art. 
         [0084]    It is recognized that dampener  60  may be integrated within stationary hinge leaf  12 , rotatable hinge leaf  14 , or alternatively in door D. 
         [0085]    It is further recognized that dampener  60  may encompass the features and functionality set forth in U.S. Non-provisional Application entitled “Door Hinge with a Hidden Closure System,” having assigned Ser. No. 12/012,690, filed on Feb. 4, 2008, incorporated herein by reference in its entirety. 
       Alternate Hinge Open Cycle 
       [0086]    Referring now to  FIGS. 7 ,  7 . 1 ,  7 . 2 ,  7 . 3  by way of example, and not limitation, there is illustrated a series of side views of control motion hinge  10  in a door D open motion, in accordance with an example embodiment. Referring again to  FIG. 7.1 , there is illustrated a side view of control motion hinge  10  with the hinge beginning-to-open position. Preferably, as door D is pushed open rotatable hinge leaf  14  rotates about rotatable hinge pin  17 , which further rotates link  21  about stationary hinge pin  16  of stationary hinge leaf  12 ; thus, an open motion of door D preferably begins to load first torsion spring  82 , which further results in an increased opposite force f of first torsion spring  82  to return rotatable hinge leaf  14  to it&#39;s original position (shown in  FIG. 5.1 ). Second torsion spring  92  preferably floats with no pre-load during this phase of beginning-to-open position of door D. 
         [0087]    Referring again to  FIG. 7.2 , there is illustrated a side view of control motion hinge  10  shown with the hinge near-full-open position (neutral position). Preferably, as door D is pushed to near-full-open position (approximately 110 degrees; however, may be between approximately 100 degrees and 130 degrees,) and rotatable hinge leaf  14  rotates still further about rotatable hinge pin  17  of link whereby second end  93  of second torsion spring  92  engages roller  35 . 1 . Preferably, as door D is pushed open rotatable hinge leaf  14  rotates about rotatable hinge pin  17 , which further rotates link  21  about stationary hinge pin  16  of stationary hinge leaf  12 ; thus, a further open motion of door D preferably continues to load first torsion spring  82 , which further results in an increased opposite force f of first torsion spring  82  to return rotatable hinge leaf  14  to it&#39;s original position (shown in  FIG. 5.1 ). Moreover, the same further open motion of door D preferably begins to load second torsion spring  92 , which further results in an increased opposite force f of second torsion spring  92  to return rotatable hinge leaf  14  to it&#39;s original position (shown in  FIG. 5.1 ). Preferably, second torsion spring  92  functions as a torsional force such as secondary force f between rotatable hinge leaf  14  and roller  35 . 1  when door D is pushed to near-full open position (approximately 110 degrees; however, this may be between approximately 90 degrees and 130 degrees). If door D is released or nudged toward closure from its near-full-open position second torsion spring  92  assists first torsion spring  82  to softly close door D. It is recognized herein that second torsion spring  92  enables the return rotatable hinge leaf  14  to its original position (shown in  FIG. 5.1 ) i.e. door D reaches full closure. The alternative non-combination torsion spring is if first torsion spring  82  is undersized, which results in door D not reaching full closure or still another alternative is if first torsion spring  82  is oversized, which results in door D having a hard loud close. 
         [0088]    Referring again to  FIG. 7.3 , there is illustrated a side view of control motion hinge  10  shown in a hinge extreme-full-open position. Preferably, as door D is pushed to extreme full open position (approximately 180 degrees; however, may be between approximately 130 degrees and 200 degrees or more,) rotatable hinge leaf  14  rotates about rotatable hinge pin  17 , which still further rotates link  21  about stationary hinge pin  16  of stationary hinge leaf  12 ; thus, an extreme open motion of door D preferably continues to load first torsion spring  82 , which further results in an increased opposite force f of first torsion spring  82  to return rotatable hinge leaf  14  to its original position (shown in  FIG. 5.1 ). Moreover, second torsion spring  92  preferably floats with no pre-load during this phase of extreme-full-open position of door D. Still further, roller  32  departs from roller path  34  during extreme open motion of door D and the counter leaver action of rotatable hinge leaf  14 , link  21 , and stationary hinge leaf  12  works without roller  32  being in contact with roller path  34  when door D is pushed to extreme-full-open position. Referring again to  FIG. 7.3 , when door D is pushed to extreme-full-open position (as shown) door D preferably is held in a hold-open position until door D is nudged closed. Second torsion spring  92  preferably floats with no pre-load during this phase of extreme-full-open position of door D. 
       Alternate Hinge Close Cycle 
       [0089]    Referring now to  FIGS. 7 ,  7 . 5 ,  7 . 6  by way of example, and not limitation, there is illustrated a series of side views of control motion hinge  10  in a door D close motion, in accordance with an example embodiment. Referring again to  FIG. 7.2  when door D is pushed to near-full-open position (as shown) and released rotatable hinge leaf  14  rotates clock-wise about rotatable hinge pin  17  of link  21  and link  21  rotates clock-wise about stationary hinge pin  16  of stationary hinge leaf  12  under the primary force f of first torsion spring  82  and the secondary force f of second torsion spring  92  to return rotatable hinge leaf  14  to it&#39;s original position (shown in  FIG. 5.1 ). Moreover, second end of second torsion spring  92  maintains contact with roller  35 . 1  to provide secondary force f of second torsion spring  92  to return rotatable hinge leaf  14  to its original position, and to enable soft closure of door D. 
         [0090]    Referring again to  FIG. 7.3 , when door D is pushed to full open position (as shown) and in this position door D preferably is held in a hold-open position until door D is nudged closed. Referring again to  FIG. 7.5  there is illustrated a side view of control motion hinge  10  shown with the hinge returning to closed position. Preferably, as door D is nudged or pushed closed from the extreme-full-open position of door D rotatable hinge leaf  14  rotates clock-wise about rotatable hinge pin  17  of link  21  and link rotates clock-wise about stationary hinge pin  16  of stationary hinge leaf  12  under the primary force f of first torsion spring  82  to return rotatable hinge leaf  14  to it&#39;s original position (shown in  FIG. 5.1 ). Moreover, second end  93  of unloaded second torsion spring  92  tucks in behind roller  35 . 1  to enable soft closure of door D. 
         [0091]    Referring again to  FIG. 7.6  there is illustrated a side view of control motion hinge  10  shown with the hinge in the closed position. Here, first torsion spring  82  and second torsion spring  92  are preferably configured with no pre-load during this phase of closed position of door D. 
         [0092]    It is contemplated herein that terminology of hinge leaf or leaf hinge is interchangeable herein. 
         [0093]    The foregoing description and drawings comprise illustrative embodiments. Having thus described exemplary embodiments, it should be noted by those skilled in the art that the disclosures within are exemplary only, and that various other alternatives, adaptations, and modifications may be made within the scope of the present disclosure. Many modifications and other embodiments will come to mind to one skilled in the art to which this disclosure pertains having the benefit of the teachings presented in the foregoing descriptions and the associated drawings. Although specific terms may be employed herein, they are used in a generic and descriptive sense only and not for purposes of limitation. Accordingly, the present disclosure is not limited to the specific embodiments illustrated herein, but is limited only by the following claims.

Summary:
A control motion hinge, comprising a first leaf hinge with three knuckles to secure a first pin, wherein the two outer knuckles have roller knuckles, a link having a two knuckles on a first end to interlock with the first leaf hinge and a single knuckle on a second end, a second leaf hinge with two knuckles to secure a second pin when interlocked with the second end of the link, wherein the two knuckles of the second leaf hinge have a roller path for engaging the roller of the first leaf hinge, wherein such rollers traverse the roller path, a first spring device positioned between said first leaf hinge and said link to apply a force therebetween, and thus softly closing the door reducing the sound of closure during the final approach of the door.