Abstract:
A spring winding device, a counterbalancing force adjustment device for a counterbalancing mechanism, and a method of adjusting an amount of force stored in a spring of a counterbalancing mechanism are provided. The spring winding device includes a support bracket, a worm gear, and a drive gear. The worm gear is rotatably coupled to the support bracket and includes a mount portion for coupling a first end cone thereto. The drive gear is rotatably disposed adjacent the support bracket and is drivingly engaged with the worm gear. A rotation of the drive gear causes the worm gear to rotate within the support bracket. The spring winding device does not require pretensioning using winding rods, maintains rigidity and alignment when a counterbalancing force is applied, and decreases a cost and a complexity of the counterbalancing mechanism.

Description:
CLAIM OF PRIORITY 
     The present application claims the benefit of and incorporates by reference U.S. Provisional Application No. 61/675,529 filed Jul. 25, 2012, entitled “SPRING WINDING DEVICE FOR USE WITH OVERHEAD DOORS.” 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to a spring winding device, such as for use in pretensioning a counterbalance spring used with an overhead door. 
     BACKGROUND OF THE INVENTION 
     Conventionally, a torsion spring counterbalancing mechanism may be used with an overhead door to counterbalance a weight of the overhead door when moving the overhead door during between an open position and a closed position. When the torsion spring counterbalancing mechanism is installed, one or more springs forming a portion of the torsion spring counterbalancing mechanism need to be pretensioned with an amount of counterbalancing force. Further, following initial installation, adjustment of the amount of counterbalancing force may be necessary to repair or replace the torsion spring counterbalancing mechanism. 
     A conventional method used to adjust the amount of counterbalancing force in one or more springs forming a portion of the torsion spring counterbalancing mechanism may be dangerous. Winding rods are typically inserted into a spring end cone, a rotational force is applied to the one or more springs, the spring end cone is disengaged from a torsion shaft, and the amount of counterbalancing force is one of increased and decreased. When a first winding rod is inserted in the spring end cone, the rotational force may be applied to the one or more springs. Using a second winding rod and an iterative process, the one or more springs may be wound or unwound. Such a process may be dangerous, as the winding rod will rotate quickly when the one or more springs are pretensioned and the winding bar is unrestrained. 
     To reduce such a danger, it is known in the prior art to employ a spring winder having a worm drive gear engaged with a worm wheel to adjust the amount of counterbalancing force. The worm wheel is fitted about a center portion of the torsion shaft and the worn drive gear is rotated to adjust the amount of counterbalancing force in the one or more springs. However, when the one or more springs are pretensionsed, the worm wheel may tilt or move along its axis as it resists the counterbalancing force. When the worn wheel tilts or moves along its axis, the worn drive gear may become disengaged or misaligned, rendering such a spring winder inoperable. 
     It is also known in the prior art to locate the spring winder having the worm drive gear engaged with the worm wheel at an end of the torsion shaft to militate against movement of the worm wheel. In such an arrangement a separate spring winder is employed for each spring, and the spring winder is subject to a thrust force of the spring. Balancing the thrust force of the spring may extend a service life of the spring significantly. Further, in such an arrangement, non-conventional cable drums are employed to house a portion of the spring winder. The spring winder having the worm wheel at an end of the torsion shaft increases a cost and a complexity of the counterbalancing mechanism while decreasing a service life of the one or more springs. 
     It would be advantageous to develop a spring winding device that does not require pretensioning using winding rods, maintains rigidity and alignment when a counterbalancing force is applied, and decreases a cost and a complexity of a counterbalancing mechanism the spring winding device is incorporated in. 
     SUMMARY OF THE INVENTION 
     Presently provided by the invention, a driveline including a continuously variable transmission that is inexpensive, compact, may be configured for a wide range of torque distributions, and able to adjust a drive ratio has surprisingly been discovered. 
     In one embodiment, the present invention is directed to a spring winding device for a counterbalancing mechanism. The spring winding device comprises a support bracket, a worm gear, and a drive gear. The worm gear is rotatably coupled to the support bracket and includes a mount portion for coupling a first end cone thereto. The drive gear is rotatably disposed adjacent the support bracket and is drivingly engaged with the worm gear. A rotation of the drive gear causes the worm gear to rotate within the support bracket. 
     In another embodiment, the present invention is directed to a counterbalancing force adjustment device for a counterbalancing mechanism. The counterbalancing force adjustment device comprises an anti-rotation device and a spring winding device. The anti-rotation device comprises an elongate member and a bumper portion. The bumper portion is coupled to the elongate member. The spring winding device comprises a support bracket, a worm gear, and a drive gear. The worm gear is rotatably coupled to the support bracket. The worm gear includes a mount portion for coupling a first end cone thereto. The drive gear is rotatably disposed adjacent the support bracket. The drive gear is drivingly engaged with the worm gear. The anti-rotation device is drivingly engaged with a second end cone to militate against a rotation thereof. A rotation of the drive gear causes the first end cone to rotate with the worm gear, causing an amount of counterbalancing force stored in a torsion spring coupled to the first end cone and the second end cone to be adjusted. 
     In another embodiment, the present invention is directed to a method of adjusting an amount of force stored in a pair of springs of a counterbalancing mechanism. The method comprises the steps of providing a first spring disposed about a shaft, the first spring and shaft forming a portion of the counterbalancing mechanism, the first spring drivingly engaged with the shaft at a first end thereof; providing a second spring disposed about the shaft, the second spring and shaft forming a portion of the counterbalancing mechanism, the second spring drivingly engaged with the shaft at a first end thereof; providing a spring winding device for the counterbalancing mechanism, the spring winding device comprising a rotatable portion for coupling a second end of the first spring and a second end of the second spring thereto; and adjusting the amount of force stored in the pair of springs of the counterbalancing mechanism simultaneously by rotating the rotatable portion of the spring winding device. 
     In another embodiment, the present invention is directed to a method of adjusting an amount of force stored in a spring of a counterbalancing mechanism. The method comprises the steps of providing the spring disposed about a shaft having a keyway formed therein, the spring and shaft forming a portion of the counterbalancing mechanism, the spring drivingly engaged with the shaft at a first end thereof through the use of a keyed mounting cone, the keyed mounting cone able to be moved along the keyway of the shaft; providing a spring winding device for the counterbalancing mechanism, the spring winding device comprising a rotatable portion for coupling a second end of the first spring and a second end of the second spring thereto; and adjusting the amount of force stored in the counterbalancing mechanism by rotating the rotatable portion of the spring winding device, wherein in response to the amount of force stored in the counterbalancing mechanism being adjusted, a position of the keyed mounting cone moves along the shaft as a length of the spring changes. 
     In another embodiment, the present invention is directed to a method of adjusting an amount of force stored in a spring of a counterbalancing mechanism. The method comprises the steps of providing the spring disposed about a shaft, the spring and shaft forming a portion of the counterbalancing mechanism, the spring drivingly engaged with the shaft at a first end thereof; providing a spring winding device for the counterbalancing mechanism, the spring winding device comprising a support bracket, a worm gear rotatably coupled to the support bracket, the worm gear including a mount portion for coupling a second end of the spring thereto, and a drive gear rotatably disposed adjacent the support bracket, the drive gear drivingly engaged with the worm gear, wherein a rotation of the drive gear causes the worm gear to rotate within the support bracket; providing an anti-rotation device comprising an elongate member and a bumper portion, the bumper portion coupled to the elongate member; drivingly engaging the anti-rotation device with the first end of the spring; releasing the first end of the spring from driving engagement with the shaft; adjusting the amount of force stored in the counterbalancing mechanism by rotating the drive gear; drivingly engaging the first end of the spring with the shaft; and releasing the anti-rotation device from driving engagement with the first end of the spring. 
     Various aspects of this invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiment, when read in light of the accompanying drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The above, as well as other advantages of the present invention, will become readily apparent to those skilled in the art from the following detailed description when considered in the light of the accompanying drawings in which: 
         FIG. 1  is a perspective view of a spring winding device according to an embodiment of the present invention; 
         FIG. 1A  is a side view of an end cone and a torsion shaft according to another embodiment of the present invention; 
         FIG. 2  is a perspective view of the spring winding device shown in  FIG. 1 ; 
         FIG. 3  is a perspective view of the spring winding device shown in  FIG. 1 ; 
         FIG. 4  is a perspective view of the spring winding device shown in  FIG. 1 ; 
         FIG. 5  is a perspective view of a gear shroud used with the spring winding device shown in  FIG. 1 ; 
         FIG. 6  is a perspective view of an anti-rotation device according to an embodiment of the present invention; 
         FIG. 7  is a perspective view of an anti-rotation device according to another embodiment of the present invention; 
         FIG. 8  is a perspective view of an anti-rotation device according to another embodiment of the present invention; 
         FIG. 9  is a perspective view of an anti-rotation device according to another embodiment of the present invention; 
         FIG. 10  is a perspective view of an anti-rotation device according to another embodiment of the present invention; and 
         FIG. 11  is a perspective view of the spring winding device shown in  FIG. 1  including the gear shroud shown in  FIG. 5 , the spring winding device being used with the anti-rotation device shown in  FIG. 10 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     It is to be understood that the invention may assume various alternative orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions, directions or other physical characteristics relating to the embodiments disclosed are not to be considered as limiting, unless the claims expressly state otherwise. 
       FIGS. 1 ,  2 ,  3 ,  4  and  11  illustrate a spring winding device  10  according to an embodiment of the invention. The spring winding device  10  forms a portion of a counterbalancing mechanism (partially shown) for an overhead door (not shown) and preferably comprises a support bracket  12 , a flanged worm gear  14 , a drive gear assembly  15 , and a gear shroud  16  (shown in  FIGS. 5 and 11 ). As shown, the spring winding device  10  is mounted above the overhead door placed in a closed position. As a non-limiting example, the overhead door may be a residential garage door. 
     The counterbalancing mechanism also includes two torsion springs  17  and a torsion shaft  18 . Each of the torsion springs  17  include a first end cone  19  and a second end cone  20  fixed to opposing ends of the torsion spring  17 . Each of the first end cones  19  as shown is known in the art as a winding cone, and may be coupled to the torsion shaft  18  using at least one set screw  21 . Each of the second end cones  20  as shown is known in the art as a stationary cone, and is coupled to the flanged worm gear  14  using at least one fastener. The spring winding device  10  is disposed about the torsion shaft  18 , which also forms a portion of the counterbalancing mechanism. The torsion shaft  18  is a conventional torsion shaft, and is well known in the art. 
     As shown in  FIGS. 1 and 11 , the torsion shaft  18  is a torsion shaft having a keyway  22  formed therein. The keyway  22  formed therein may be disposed through a keyed end cone  19 ′ having a key  23  formed thereon, shown in  FIG. 1A . The keyed end cone  19 ′ having the key  23  is drivingly engaged with the keyway  22  of the torsion shaft  18 . The keyed end cone  19 ′ is able to be moved along a length of the torsion shaft  18  while maintaining driving engagement with the torsion shaft  18 . The keyed end cone  19 ′ is able to move along the torsion shaft  18  as an amount of counterbalancing force stored in each of the torsion springs  17  coupled thereto is adjusted. It is understood that when the amount of counterbalancing force stored in each of the torsion springs  17  is adjusted, a length of each of the torsion springs  17  changes. In response to the length of each of the torsion springs  17  changing, each of the keyed end cones  19 ′ moves along the torsion shaft  18 . The keyed end cone  19 ′ having the key  23  formed thereon eliminates a need for an anti-rotation device when an amount of counterbalancing force stored in each of the torsion springs  17  is adjusted. The keyed end cone  19 ′ militates against a binding that may occur to the torsion springs  17  if the amount of counterbalancing force stored in each of the torsion springs  17  is adjusted without allowing the length of each of the torsion springs  17  to change. 
     The support bracket  12  is a L-shaped member mounted to a wall  24  above a frame (not shown) for the overhead door. The support bracket  12  includes a mounting portion  25  and a main portion  26 . A retaining portion  27  is coupled to the support bracket  12 . A drive gear assembly aperture  28 , a flanged worm gear fastening perforation  29 , and a plurality of mounting apertures  30  are formed through the main portion  26  and the mounting portion  25 . A portion of an outer peripheral edge of the main portion  26  and a portion of an outer peripheral edge of the retaining portion  27  define a torsion shaft perforation  32 . The support bracket  12  is preferably formed by stamping and bending a sheet metal such as steel; however, it is understood that the support bracket may be formed with other processes from other materials. 
     The mounting portion  25  has a rectangular shape and includes at least two mounting apertures  30  formed therethrough. As most clearly shown in  FIG. 2 , the mounting apertures  30  may be circular apertures or elongate apertures. A plurality of fasteners, such as screws, bolts, or the like, is disposed through the mounting apertures  30  and couple the support bracket  12  to the wall  24 . It is understood that the mounting portion  25  may include a bracket adjustment device (not shown). The bracket adjustment device allows a position of the support bracket with respect to the wall  24  to be adjusted. The bracket adjustment device facilitates installation and service of the counterbalancing mechanism the spring winding device  10  forms a portion of. 
     The main portion  26  is an elongate portion of the support bracket  12  and includes the drive gear assembly aperture  28  formed therethrough. As most clearly shown in  FIG. 3 , the drive gear assembly aperture  28  is substantially rectangular in shape and also defines an alignment tab  34  and a drive gear retention tab  36 . Alternately, the drive gear assembly aperture  28  may be any other shape. The alignment tab  34  is an elongate member bent away from and substantially orthogonal to a surface of the main portion  26 . The drive gear retention tab  36  is an elongate member bent away from and substantially orthogonal to a surface of the main portion  26 . The drive gear retention tab  36  is formed adjacent the alignment tab  34  and is bend in an opposing direction with respect to the alignment tab  34 . At least one flanged worm gear fastening perforation  29  is formed through the main portion  26 . The flanged worm gear fastening perforation  29  is an elongate perforation; however, it is understood that that flanged worm gear fastening perforation  29  may have another shape. As mentioned hereinabove, a portion of the outer peripheral edge of the main portion  26  partially defines the torsion shaft perforation  32 . The torsion shaft perforation  32  is substantially circular in shape. 
     The retaining portion  27  is a member coupled to the main portion  26 . As shown in  FIGS. 1-3  and  11 , the retaining portion  27  is coupled to the main portion  26  using a plurality of rivets disposed through perforations formed through the main portion  26  and the retaining portion  27 ; however it is understood that the retaining portion  27  may be coupled to the main portion  26  using any conventional fastener. As mentioned hereinabove, a portion of the outer peripheral edge of the retaining portion  27  partially defines the torsion shaft perforation  32 . The retaining portion  27  is preferably formed by stamping and bending a sheet metal such as steel; however, it is understood that the support bracket  12  may be formed with other processes from other materials. 
     The flanged worm gear  14  is a disposed between the main portion  26  and the retaining portion  27 , through the torsion shaft perforation  32 . When not coupled to the support bracket  12 , the flanged worm gear  14  is a rotatable portion of the spring winding device  10 . The flanged worm gear  14  includes a gear portion  38  and a first end cone mount portion  40 . A support recess  42  is formed between the gear portion  38  and the first end cone mount portion  40 . A torsion shaft aperture  44  is formed through the flanged worm gear  14 . The flanged worm gear  14  is formed by casting and machining a metal; however, it is understood that other processes may be used to form the flanged worm gear  14 . 
     The gear portion  38  is a disc shaped member having a toothed outer edge  46 . The toothed outer edge  46  of the gear portion  38  is in driving engagement with the drive gear assembly  16 . A plurality of set perforations  48  are formed through the gear portion  38 . Each of the set perforations  48  may be aligned with the flanged worm gear fastening perforation  29  when the flanged worm gear  14  is rotated about a gear portion axis. A fastener  49  is disposed through the flanged worm gear fastening perforation  29  and one of the set perforations  48  to couple the flanged worm gear  14  to the support bracket  12 . As shown in  FIGS. 1 ,  2 ,  3 ,  4  and  11 , the fastener  49  is a fastener having threads corresponding to threads formed in the set perforations  48 ; however, it is understood that the fastener  49  may be any conventional fastener. The gear portion axis is substantially coincident to an axis of the torsion shaft  18 . At least two cone mounting perforations  50  are formed in a second end cone mount portion  51 . The second end cone mount portion  51  comprises two protuberances extending away from the gear portion  38 ; however, it is understood that the second end cone mount portion  51  may comprise other shapes or that the gear portion  38  may not include the second end cone mount portion  51 . Preferably, the cone mounting perforations  50  are threaded, however, it is understood that the cone mounting perforations  50  may be configured for any type of fastener. 
     The first end cone mount portion  40  is a flanged shape member spaced apart from the gear portion  38 . As most clearly shown in  FIG. 3 , the first end cone mount portion  40  includes a hollow central cylindrical portion  52  and two radially extending protuberances  54 . At least two cone mounting perforations  56  are formed in the radially extending protuberances of the first end cone mount portion  40 . Preferably, the cone mounting perforations  56  are threaded, however, it is understood that the cone mounting perforations  56  may be configured for any type of fastener. 
     As shown in  FIGS. 1-3  and  11 , when the counterbalancing mechanism including the spring winding device  10  is in an installed condition, each of the second end cones  20  is coupled to the end cone mount portion  40  and the second end cone mount portion  51  using fasteners inserted through each of the second end cones  20  and into the cone mounting perforations  50 ,  56 . Alternately, it is understood that the second end cones  20  may be integrally formed with the gear portion  38  or coupled to the gear portion  38  in any other conventional manner. 
     The support recess  42  is a recess between the gear portion  38  and the two radially extending protuberances  54 . A portion of the first end cone mount portion  40  having a reduced diameter defines the support recess  42 . When the flanged worm gear  14  is disposed in the support bracket  12 , at least a portion of the main portion  26  and the retaining portion  27  enter and rotatably support the flanged worn gear  14 . A width of the support recess  42  is slightly greater than a thickness of the main portion  26  and the retaining portion  27 , permitting the main portion  26  and the retaining portion  27  to be disposed therein. The width of the support recess  42  militates against a substantial axial deviation of the flanged worm gear  14  within the support bracket  12 . 
     The drive gear assembly  16  is coupled to the main portion  26  of the support bracket  12 . The drive gear assembly  16  includes a drive gear housing  58  and a drive gear  60 . The drive gear housing  58  is coupled to the main portion  26  and the drive gear  60  is rotatably disposed in the drive gear housing  58 . As shown in  FIGS. 1 ,  2 ,  3 ,  4  and  11 , the drive gear assembly  16  includes a single drive gear; however, it is understood that the drive gear assembly may include two or more drive gears arranged in a gear train to facilitate adjusting an amount of counterbalancing force in one or more torsion springs. 
     The drive gear housing  58  is a member formed by casting and machining a metal such as steel; however, it is understood that the drive gear housing  58  may be formed with other processes from other materials. The drive gear housing  58  is disposed in the drive gear assembly aperture  28  and coupled to the main portion  26 . A first drive gear slot  62  and a second drive gear slot  64  are formed in opposing portions of the drive gear housing  58 . The first drive gear slot  62  and the second drive gear slot  64  align and rotatably support the drive gear  60  when the spring winding device  10  is assembled. As most clearly shown in  FIGS. 3 and 4 , a plurality of mounting perforations corresponding to mounting perforations formed through the main portion  26  receive rivets to couple the drive gear housing  58  to the main portion  26 . However, it is understood the drive gear housing  58  may be coupled to the main portion  26  in any conventional manner. The drive gear housing  58  also includes an alignment tab  66  extending from a remaining portion of the drive gear housing  58 . When the drive gear housing  58  is coupled to the main portion  26 , the alignment tab  66  is disposed through the drive gear assembly aperture  28  and supported by the main portion  26 . When the drive gear housing  58  is coupled to the main portion  26 , a portion of the drive gear housing  58  is disposed against the alignment tab  34 , as shown in  FIGS. 2 and 3 . 
     The drive gear  60  is a threaded member rotatably disposed in the drive gear housing  58 . When the spring winding device  10  is assembled, at least one thread  68  formed in the drive gear  60  is in driving engagement with the toothed outer edge  46  of the flanged worm gear  14 . The drive gear  60  includes two annular journals  70  which are disposed in the drive gear slots  62 ,  64  and militate against axial movement of the drive gear  60  with respect to the drive gear housing  58 . A drive end  72  of the drive gear  60  is disposed adjacent an outer surface of the drive gear housing. As most clearly shown in  FIG. 4 , the drive end  72  includes a hexagonal shaped protuberance for drivingly engaging a driving tool (not shown); however, it is understood that the drive end  72  may include other features formed therein for engaging other drive tools. When the driving tool is engaged with the drive end  72  and the driving tool is rotated, the drive gear  60  rotates and the at least one thread  68  applies a force to the toothed outer edge  46  of the flanged worm gear  14 , causing the flanged worm gear  14  to rotate within the support bracket  12 . When the drive gear  60  is disposed in the drive gear housing  58 , a second end  74  of the drive gear  60  is disposed adjacent to or abuts the drive gear retention tab. 
     As shown in  FIGS. 5 and 11 , the gear shroud  16  is a ring shaped member coupled to the support bracket  12 . The gear shroud  16  is formed from a plastic using a molding process; however, it is understood that the gear shroud  16  may be formed from other materials using other processes. The gear shroud  16  has a substantially L-shaped cross-section and encloses at least a portion of the flanged worm gear  14 . Further, it is understood that the gear cover may enclose at least a portion of the drive gear assembly  16 . It is also understood that the gear cover may form a portion of a torsion spring cover (not shown). The gear shroud  16  includes a plurality of shroud fasteners  76  and a drive gear protuberance  78 . The gear shroud  16  militates against debris from collecting on or within the toothed outer edge  46 , the drive gear housing  58 , the drive gear  60 . Further, the gear shroud  16  militates against an entanglement that may occur between a foreign object, the toothed outer edge  46 , and the drive gear  60 . 
     Each of the shroud fasteners  76  is a hollow, bifurcated protuberance having a barbed end. Each of the shroud fasteners correspond to a shroud perforation  80  formed in one of the main portion  26  and the retaining portion  27  of the support bracket  12 . An elastic deformation of each of the shroud fasteners  76  allows each of the shroud fasteners  76  to be disposed in the shroud perforation  80 , coupling the gear shroud  16  to the support bracket  12 . 
     The drive gear protuberance  78  is a portion of the gear shroud  16  extending away from a remaining portion of the gear shroud  16 . The drive gear protuberance  78  has a substantially rectangular shape; however, it is understood that the drive gear protuberance  78  may have other shapes or may be formed separate from the remaining portion of the gear shroud  16 . When the gear shroud  16  is coupled to the support bracket  12 , the drive gear protuberance  78  is disposed adjacent or abuts the drive gear housing  58 . 
       FIG. 6  illustrates an anti-rotation device  100  for use with each of the first end cones  19 . The anti-rotation device  100  may be used with the spring winding device  10  when the counterbalancing mechanism is installed or serviced. The anti-rotation device  100  is coupled to each of the first end cones  19  to resist a torque applied to the first end cones  19  when a tension of the torsion spring  17  is adjusted during installation or service of the counterbalancing mechanism. When the tension of the torsion spring  17  is adjusted during installation or service of the counterbalancing mechanism, the anti-rotation device  100  permits the first end cones  19  to move along the torsion shaft  18  to accommodate changes in length of the torsion spring  17  that occur during adjustment of the tension of the torsion spring  17 . As shown in  FIGS. 1 ,  2 , and  11 , the counterbalancing mechanism comprises two torsion springs, disposed on opposite sides of the spring winding device  10 , and would require the use of two anti-rotation devices  100  to install or service the counterbalancing mechanism.  FIG. 11  illustrates an anti-rotation device  100 ″″ according to another embodiment of the invention being used to install or service the counterbalancing mechanism. 
     As shown in  FIGS. 1 ,  2 , and  6 - 11 , the first end cone  19  includes apertures  102  formed therein oriented transversely to a torsion shaft aperture  104 . The first end cone  19  includes four apertures  102  formed therein, the apertures  102  spaced apart equally. The at least one set screw  21  is threadingly disposed in the first end cone  19  for coupling the first end cone  19  to the torsion shaft  18 . The first end cone  19  is a conventional winding cone, and is well known in the art. 
     The anti-rotation device  100  includes a main body  108 , an arm member  110 , and a first cone pin  112 . The arm member  110  and the first cone pin  112  are adjustably disposed within the main body  108 . When the anti-rotation device  100  is coupled to the first end cone  19 , the anti-rotation device  100  is in driving engagement therewith. 
     The main body  108  is a L-shaped member the arm member  110  and the first cone pin  112  are adjustably disposed within. The main body  108  includes a first leg  114 , a second leg  116 , a second cone pin  118 , and at least one arm member fastener  120 . An arm member perforation  122  is formed through the first leg  114  and a cone pin perforation  124  is formed through the second leg  116 . The main body  108  is formed by casting and machining a metal; however, it is understood that other processes may be used to form the main body  108 . 
     The first leg  114  is an elongate member having a rectangular cross section. The arm member perforation  122  is formed lengthwise through the first leg  114  and has a diameter which permits the arm member  110  to be disposed therethrough. The at least one arm member fastener  120  is threadingly disposed in a perforation that intersects the arm member perforation  122 . When the at least one arm member fastener  120  is driven to engage the arm member  110  disposed in the arm member perforation  122 , the arm member  110  is coupled to the main body  108 . The second cone pin  118  extends outwardly from the first leg  114  and is coupled thereto in any conventional manner. A diameter of the second cone pin  118  substantially corresponds to the apertures  102  of the first end cone  19 . 
     The second leg  116  is an elongate member having a rectangular cross section. The second leg  116  is oriented transversely to the first leg  114 . The cone pin perforation  124  is formed through the second leg  116  transverse to the second cone pin  118  and has a diameter which permits the first cone pin  112  to be disposed therethrough. The first cone pin  112  is disposed through the cone pin perforation  124  and extends outwardly from the second leg  116  and is removably coupled thereto by a head  126  of the first cone pin  112  and a pin  128  removably disposed through a perforation in the first cone pin  112 ; however, it is understood that the first cone pin  112  may be removably coupled to the second leg  116  in any conventional manner. The first cone pin  112  includes a plurality of perforations formed therethrough, which permit a length of the first cone pin  112  extending through the cone pin perforation  124  to be adjusted by moving a location of the pin  128 . A diameter of the first cone pin  112  substantially corresponds to the apertures  102  of the first end cone  19 . 
     The arm member  110  is an elongate member having a shaft portion  130  and a bumper portion  132 . The shaft portion  130  has a circular cross section and is rotatably coupled to the bumper portion  132  at a first end thereof. The shaft portion  130  is formed by forging a metal; however, it is understood that other processes may be used to form the shaft portion  130 . The bumper portion  132  is a disc shaped member rotatably coupled to a distal end of the shaft portion  130 . At least a portion of the bumper portion  132  is formed from a resilient material, such as rubber. However, it is understood that the bumper portion  132  may have other shapes and may be formed from other materials. 
       FIG. 7  shows an alternative embodiment of the anti-rotation device  100 . Similar structural features of the anti-rotation device  100  include the same reference numeral and a prime (′) symbol. 
     An anti-rotation device  100 ′ includes a main body  208 , an arm member  210 , and a first cone pin  112 ′. The arm member  210  and the first cone pin  112 ′ are adjustably disposed within the main body  208 . When the anti-rotation device  100 ′ is coupled to the first end cone  19 , the anti-rotation device  100 ′ is in driving engagement therewith. 
     The main body  208  is a L-shaped member the arm member  210  and the first cone pin  112 ′ are adjustably disposed within. The main body  208  includes a first leg  214 , a second leg  116 ′, a second cone pin  118 ′, and an arm member pin  234 . An arm member perforation  222  is formed through the first leg  214  and a cone pin perforation  124 ′ is formed through the second leg  116 ′. The main body  208  is formed by casting and machining a metal; however, it is understood that other processes may be used to form the main body  208 . 
     The first leg  214  is an elongate member having a rectangular cross section. The arm member perforation  222  is formed lengthwise through the first leg  214  and has a diameter which permits the arm member  210  to be disposed therethrough. An arm member fastening slot  236  is formed in the first leg  214 , the arm member fastening slot  236  intersecting the arm member perforation  222 . The arm member fastening slot  236  is V-shaped; however, it is understood that other shapes may be used. The arm member pin  234  is disposed in the arm member fastening slot  236  and through one of a series of perforations formed in a shaft portion  230  of the arm member  210  to couple the arm member  210  to the main body  208 . The second cone pin  118 ′ extends outwardly from the first leg  214  and is coupled thereto in any conventional manner. A diameter of the second cone pin  118 ′ substantially corresponds to the apertures  102  of the first end cone  19 . 
     The second leg  116 ′ is an elongate member having a rectangular cross section. The second leg  116 ′ is oriented transversely to the first leg  214 . The cone pin perforation  124 ′ is formed through the second leg  116 ′ transverse to the second cone pin  118 ′ and has a diameter which permits the first cone pin  112 ′ to be disposed therethrough. The first cone pin  112 ′ is disposed through the cone pin perforation  124 ′ and extends outwardly from the second leg  116 ′ and is removably coupled thereto by a head  126 ′ of the first cone pin  112 ′ and a pin  128 ′ removably disposed through a perforation in the first cone pin  112 ; however, it is understood that the first cone pin  112 ′ may be removably coupled to the second leg  116 ′ in any conventional manner. The first cone pin  112 ′ includes a plurality of perforations formed therethrough, which permit a length of the first cone pin  112 ′ extending through the cone pin perforation  124 ′ to be adjusted by moving a location of the pin  128 ′. A diameter of the first cone pin  112 ′ substantially corresponds to the apertures  102  of the first end cone  19 . 
     The arm member  210  is an elongate member having the shaft portion  230  and a bumper portion  132 ′. The shaft portion  230  has a circular cross section and is rotatably coupled to the bumper portion  132 ′ at a first end thereof. The shaft portion  230  includes a plurality of perforations formed therethrough, which permit a length of the shaft portion  230  extending through the arm member perforation  222  to be adjusted by moving a location of the arm member pin  234 . The shaft portion  230  is formed by forging and machining a metal; however, it is understood that other processes may be used to form the shaft portion  230 . The bumper portion  132 ′ is a disc shaped member rotatably coupled to a distal end of the shaft portion  230 . At least a portion of the bumper portion  132 ′ is formed from a resilient material, such as rubber. However, it is understood that the bumper portion  132 ′ may have other shapes and may be formed from other materials. 
       FIG. 8  shows an alternative embodiment of the anti-rotation device  100 . Similar structural features of the anti-rotation device  100  include the same reference numeral and a double prime (″) symbol. 
     An anti-rotation device  100 ″ includes two main bodies  340  and an arm member  110 ″. The arm member  110 ″ is adjustably disposed within the main bodies  340 . The main bodies are opposingly disposed on the arm member  110 ″. When the anti-rotation device  100 ″ is coupled to the first end cone  19 , the anti-rotation device  100 ″ is in driving engagement therewith. The anti-rotation device  100 ″ is coupled to the first end cone  19  by moving each of the main bodies  340  along the arm member  110 ″. 
     Each of the main bodies  340  is a U-shaped member the arm member  110 ″ is adjustably disposed within. The main body  340  includes a fastening portion  342 , a central portion  344 , a cone pin  346 , at least one arm member fastener  348 , and an arm member perforation  350 . The main body  340  is formed by casting and machining a metal; however, it is understood that other processes may be used to form the main body  340 . 
     The fastening portion  342  is an elongate member having a rectangular cross section. The arm member perforation  350  is formed lengthwise through the fastening portion  342  and has a diameter which permits the arm member  110 ″ to be disposed therethrough. The at least one arm member fastener  348  is threadingly disposed in a perforation that intersects the arm member perforation  350 . When the at least one arm member fastener  348  is driven to engage the arm member  110 ″ disposed in the arm member perforation  350 , the arm member  110 ″ is coupled to the main body  340 . The fastening portion  342  includes an alignment protuberance  352  and an alignment recess  354 . 
     The alignment protuberance  352  has a rectangular cross-section and extends from the fastening portion  342  in a manner substantially parallel to the arm member perforation  350 . The alignment recess  354  is formed in the fastening portion  342  and has a substantially rectangular cross-section. A shape of the alignment recess  354  corresponds to at least a portion of the alignment protuberance  352 . When two of the main bodies  340  are opposingly disposed on the arm member  110 ″, the main bodies may be positioned so that the alignment protuberances  352  and alignment recesses  354  respectively engage one another, militating against relative rotational movement therebetween about the arm member  110 ″. 
     The central portion  344  is an elongate member having a rectangular cross section. The central portion  344  is oriented transversely to the fastening portion  342 . The cone pin  346  extends from a distal end of the central portion  344 . 
     The cone pin  346  is integrally formed with the central portion  344 , has a substantially circular cross-section and extends outwardly from the central portion  344  and is substantially parallel to the fastening portion  342 . Alternately, the cone pin  346  may be coupled to the central portion  344  in any conventional manner. A diameter of the cone pin  346  substantially corresponds to the apertures  102  of the first end cone  19 . 
       FIG. 9  shows an alternative embodiment of the anti-rotation device  100 . Similar structural features of the anti-rotation device  100  include the same reference numeral and a triple prime (′″) symbol. 
     An anti-rotation device  100 ′″ includes an adjuster body  456 , a support body  458 , and an arm member  410 . The arm member  410  is adjustably disposed within the adjuster body  456  and the support body  458 . When the anti-rotation device  100 ′″ is coupled to the first end cone  19 , the anti-rotation device  100 ′″ is in driving engagement therewith. The anti-rotation device  100 ′″ is coupled to the first end cone by moving the arm member  410  through an adjuster perforation  460  and by disposing an adjuster fastener  462  through the adjuster body  456 . 
     The adjuster body  456  is a U-shaped member the arm member  410  is adjustably disposed within. The adjuster body  456  includes a primary portion  464  and a secondary portion  466 . The adjuster body  456  is formed by coupling the primary portion  464  to the secondary portion  466  with a plurality of fasteners; however, it is understood that the adjuster body may be unitarily formed. 
     The primary portion  464  is a L-shaped member. The primary portion  464  includes the adjuster perforation  460  formed therein at a first distal end and a perforation for receiving the adjuster fastener  462  formed therein at a second distal end. The adjuster perforation  460  includes a thread formed thereon, which is engaged with a corresponding thread formed on a shaft portion  468  of the arm member  410 . 
     The secondary portion  466  is a L-shaped member. The secondary portion  466  includes a cone pin  470  extending therefrom at a first distal end and a perforation for receiving the adjuster fastener  462  formed therein at a second distal end. The cone pin  470  is coupled to the secondary portion  466  and has a substantially circular cross-section and extends outwardly from the secondary portion and is substantially coincident with the shaft portion  468  of the arm member  410 . Alternately, the cone pin  470  may be coupled to the secondary portion  466  in any conventional manner. A diameter of the cone pin  470  substantially corresponds to the apertures of the first end cone. 
     The support body  458  is a L-shaped member. The support body  458  is coupled to the primary portion  464  at a first distal end and includes a perforation formed therethrough for receiving the shaft portion  468  at a second distal end. The perforation formed through the support body  458  is substantially aligned with the adjuster perforation  460 . The support body  458  is preferably welded to the primary portion  464 ; however, it is understood that the support body  458  may be integrally formed with the primary portion  464  or coupled thereto in any conventional manner. 
     The arm member  410  is an elongate member having the shaft portion  468  and a bumper portion  132 ′″. The shaft portion  468  is a threaded rod and is rotatably coupled to the bumper portion  132 ′″ at a first end thereof. A diameter of the shaft portion  468  substantially corresponds to the apertures  102  of the first end cone  19  and a second end thereof may be disposed in the apertures  102 . The shaft portion  468  is threadingly disposed through the adjuster perforation  460  and may be secured thereto with a fastener such as a nut, for example. The shaft portion  468  is formed by forging a metal; however, it is understood that other processes may be used to form the shaft portion  468 . The bumper portion  132 ′″ is a disc shaped member rotatably coupled to a distal end of the shaft portion  468 . At least a portion of the bumper portion  132 ′″ is formed from a resilient material, such as rubber. However, it is understood that the bumper portion  132 ′″ may have other shapes and may be formed from other materials. 
       FIG. 10  shows an alternative embodiment of the anti-rotation device  100 . Similar structural features of the anti-rotation device  100  include the same reference numeral and a quadruple prime (″″) symbol. 
     The anti-rotation device  100 ″″ includes two main bodies  540  and an arm member  110 ″″. The arm member  110 ″″ is adjustably disposed within the main bodies  540 . The main bodies are opposingly disposed on the arm member  110 ″″. When the anti-rotation device  100 ″″ is coupled to the first end cone  19 , the anti-rotation device  100 ″″ is in driving engagement therewith. The anti-rotation device  100 ″″ is coupled to the first end cone  19  by moving each of the main bodies  540  along the arm member  110 ″″. 
     Each of the main bodies  540  is a L-shaped member the arm member  110 ″″ is adjustably disposed within. The main body  540  includes a fastening portion  542 , a central portion  544 , a cone pin  546 , and at least one arm member fastener  548 . The main body  540  is formed by casting and machining a metal; however, it is understood that other processes may be used to form the main body  540 . 
     The fastening portion  542  is a substantially cylindrical shaped body defining an arm member perforation  550  therethrough. The arm member perforation  550  has a diameter which permits the arm member  110 ″″ to be disposed therethrough. The at least one arm member fastener  548  is threadingly disposed in a perforation that intersects the arm member perforation  550 . When the at least one arm member fastener  548  is driven to engage the arm member  110 ″″ disposed in the arm member perforation  550 , the arm member  110 ″″ is coupled to the main body  540 . 
     The central portion  544  is an elongate member having a rectangular cross section. The central portion  544  is oriented transversely to an axis of the fastening portion  542 . The cone pin  546  extends from a distal end of the central portion  544 . 
     The cone pin  546  is integrally formed with the central portion  544 , has a substantially circular cross-section and extends outwardly from the central portion  544  and is substantially parallel to the axis of the fastening portion  542 . Alternately, the cone pin  546  may be coupled to the central portion  544  in any conventional manner. A diameter of the cone pin  546  substantially corresponds to the apertures  102  of the first end cone  19 . 
     In use, the spring winding device  10  and the anti-rotation device  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ are used to adjust an amount of counterbalancing force in one or more torsion springs  17  forming a portion of the torsion spring counterbalancing mechanism.  FIG. 11  illustrates the anti-rotation device  100 ″ being used to adjust an amount of counterbalancing force in one or more torsion springs  17 . 
     First, one of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ is coupled to each of the first end cones  19 . The cone pins  112 ,  118 , the cone pins  112 ′,  118 ′, the cone pins  346  of each of the main bodies  340 , the cone pin  470  and the second end of the shaft portion  468 , or the cone pins  546  of each of the main bodies  540  are respectively disposed in the apertures  102  of each of the first end cones  19  to drivingly engage the first end cone  19  with one of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″. By adjusting one of the first cone pin  112 ,  112 ′, each of the arm member fasteners  348 , the adjuster fastener  462  and the shaft portion  468 , or each of the arm member fasteners  548 , each of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ may be coupled and drivingly engaged with one of the first end cones  19 . Further, it is understood that a length of the arm member  110 ,  210 ,  110 ″,  410 ,  110 ″″ may be adjusted based on an amount of counterbalancing force stored in the torsion springs  17  or an amount of counterbalancing force to be stored in the torsion springs  17 . 
     Next, the fastener  49  coupling the flanged worm gear  14  to the support bracket  12  is removed. The fastener  49  is removed from one of the set perforations  48  of the gear portion  38  and the flanged worm gear fastening perforation  29  of the main portion  26 . Preferably, the fastener  49  is disposed through the flanged worm gear fastening perforation  29  and engaged with a thread formed in one of the set perforations  48 ; however, it is understood that other fasteners, such as a nut and a bolt, may be used. 
     Next, the at least one set screw  21  of each of the first end cones  19  are adjusted to disengage the first end cone  19  from the torsion shaft  18 . When the first end cones  19  are disengaged from the torsion shaft  18 , the amount of counterbalancing force stored in the torsion springs  17  is applied to the anti-rotation device  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ engaged with each of the first end cones  19 . As a result, the bumper portion  132 ,  132 ′,  132 ″,  132 ′″,  132 ″″ of each of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ contacts the wall  24  or the overhead door to resist the amount of counterbalancing force stored in the torsion springs  17 . 
     Next, the amount of counterbalancing force stored in the torsion springs  17  is adjusted using the spring winding device  10 . The amount of counterbalancing force stored in the torsion springs  17  may be increased or decreased by rotating the drive gear  60 . When the driving tool engaged with the drive end  72  of the drive gear  60  is rotated, the drive gear  60  rotates and the at least one thread  68  applies a force to the toothed outer edge  46  of the flanged worm gear  14 , causing the flanged worm gear  14  to rotate within the support bracket  12 . The second end cones  20 , which are coupled to the flanged worm gear  14 , rotate in response to rotation of the drive gear  60  and the amount of counterbalancing force stored in the torsion springs  17  is adjusted simultaneously. As shown in  FIGS. 1-3  and  11 , the spring winding device  10  is used to adjust the amount of counterbalancing force stored in two torsion springs  17 . Depending on a direction the drive gear  60  is rotated, the amount of counterbalancing force stored in the torsion springs  17  may be increased or decreased. It is understood that at least one of the flanged worm gear  14  and the support bracket  12  may be fitted with a device (not shown) for counting a number of rotations made by the flanged worm gear  14  during the process used to adjust the amount of counterbalancing force stored in the torsion springs  17 . Such a device facilitates properly adjusting the amount of counterbalancing force stored in the torsion springs  17 . 
     The anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ are able to move with respect to the torsion shaft  18  as the amount of counterbalancing force stored in each of the torsion springs  17  coupled thereto is adjusted. It is understood that when the amount of counterbalancing force stored in each of the torsion springs  17  is adjusted, a length of each of the torsion springs  17  changes. In response to the length of each of the torsion springs  17  changing, the bumper portion  132 ,  132 ′,  132 ″,  132 ′″,  132 ″″ of each of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ rotates about the arm member  110 ,  210 ,  110 ″,  410 ,  110 ″″ against the wall  24  and the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ and the first end cones  19  move along the torsion shaft  18 . The anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ militate against a binding that may occur to the torsion springs  17  if the amount of counterbalancing force stored in each of the torsion springs  17  is adjusted without allowing the length of each of the torsion springs  17  to change. 
     Once a desired amount of counterbalancing force stored in the torsion springs is obtained, the flanged worm gear  14  is coupled to the support bracket  12 . The fastener  49  is disposed through the flanged worm gear fastening perforation  29  of the main portion  26  and into one of the set perforations  48  of the gear portion  38  and the fastener  49  is tightened to militate against relative movement from occurring between the flanged worm gear  14  and the support bracket  12 . 
     Next, the at least one set screw  21  of each of the first end cones  19  are adjusted to engage each of the first end cones  19  with the torsion shaft  18 , allowing the amount of counterbalancing force stored in the torsion springs  17  to be applied to the torsion shaft. 
     Lastly, each of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ coupled to the first end cones  19  is removed. By reversing the above procedure used to couple the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ to the first end cones  19 , the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ are removed from the first end cones  19 , and the process used to adjust the amount of counterbalancing force in one or more torsion springs  17  is completed. 
     Further, it is understood that the spring winding device  10  and a pair of the keyed end cones  19 ′ may also be used to adjust an amount of counterbalancing force in one or more torsion springs  17  forming a portion of the torsion spring counterbalancing mechanism. In use, the spring winding device  10  and the keyed end cones  19 ′ are used to adjust an amount of counterbalancing force in one or more torsion springs  17  forming a portion of the torsion spring counterbalancing mechanism, without the use of one of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″. 
     First, the at least one set screw  21  of each of the keyed end cones  19 ′ are adjusted to disengage the keyed end cones  19 ′ from the torsion shaft  18 . When the keyed end cones  19 ′ are disengaged from the torsion shaft  18 , each of the keyed end cones  19 ′ is able to be moved along a length of the torsion shaft  18  while maintaining driving engagement with the torsion shaft  18 . 
     Next, the amount of counterbalancing force stored in the torsion springs  17  is adjusted using the spring winding device  10 . The amount of counterbalancing force stored in the torsion springs  17  may be increased or decreased by rotating the drive gear  60 . When the driving tool engaged with the drive end  72  of the drive gear  60  is rotated, the drive gear  60  rotates and the at least one thread  68  applies a force to the toothed outer edge  46  of the flanged worm gear  14 , causing the flanged worm gear  14  to rotate within the support bracket  12 . The second end cones  20 , which are coupled to the flanged worm gear  14 , rotate in response to rotation of the drive gear  60  and the amount of counterbalancing force stored in the torsion springs  17  is adjusted simultaneously. 
     In response to the amount of counterbalancing force stored in the torsion springs  17  being adjusted, each of the keyed end cones  19 ′ move along the torsion shaft  18  as a length of each of the torsion springs  17  coupled thereto is adjusted. The key  23  of each of the keyed end cones  19 ′ move along keyway  22  of the torsion shaft  18  in response to an axial force generated by the amount of counterbalancing force stored in the torsion springs  17  being adjusted. When the amount of counterbalancing force stored in the torsion springs  17  is increased, the length of each of the torsion springs  17  decreases, and each of the keyed end cones  19 ′ move along the torsion shaft  18  towards the spring winding device  10 . When the amount of counterbalancing force stored in the torsion springs  17  is decreased, the length of each of the torsion springs  17  increases, and each of the keyed end cones  19 ′ move along the torsion shaft  18  away from the spring winding device  10 . 
     Once a desired amount of counterbalancing force stored in the torsion springs is obtained, the flanged worm gear  14  is coupled to the support bracket  12 . The fastener  49  is disposed through the flanged worm gear fastening perforation  29  of the main portion  26  and into one of the set perforations  48  of the gear portion  38  and the fastener  49  is tightened to militate against relative movement from occurring between the flanged worm gear  14  and the support bracket  12 . 
     Lastly, the at least one set screw  21  of each of the keyed end cones  19 ′ are adjusted to fix each of the keyed end cones  19 ′ with respect to the torsion shaft  18 . When the keyed end cones  19 ′ are fixed to the torsion shaft  18 , each of the keyed end cones  19 ′ is unable to be moved along a length of the torsion shaft  18 . 
     The keyed end cone  19 ′ having the key  23  formed thereon eliminates a need for one of the anti-rotation devices  100 ,  100 ′,  100 ″,  100 ′″,  100 ″″ when an amount of counterbalancing force stored in each of the torsion springs  17  is adjusted. 
     In accordance with the provisions of the patent statutes, the present invention has been described in what is considered to represent its preferred embodiments. However, it should be noted that the invention can be practiced otherwise than as specifically illustrated and described without departing from its spirit or scope.