Patent Publication Number: US-2007101555-A1

Title: Line clutch with quick release

Description:
CROSS REFERENCE TO RELATED APPLICATION  
      The present application is a utility application claiming the benefits of the filing date of provisional applications, application No. 60/733,683 filed on Apr. 4, 2006 by the present applicant, and application No. 60/789,331 filed on Nov. 4, 2005 by the present applicant. 
    
    
     TECHNICAL FIELD  
      The present invention generally relates to line clutch mechanisms and, more specifically, to a line clutch with a quick release mechanism.  
     BACKGROUND  
      It is frequently necessary to control a line by either arresting or stopping its motion or releasing it. On sailing vessels, for example, lines are used to raise and control sails and other operating units often under heavy loads. The same line may first be lightly loaded, and then as the tension required increases, the use of a winch is necessary. To allow one winch to be used for several lines, of the same or varying sizes, a sheet or line stopper is provided for each line. When out of engagement, the line stopper permits the line to run in both directions. In an engaged position, the line runs under light pressure in one direction only. It is therefore possible to haul a line in by hand without slipping as a self-locking action prevents line movement of the line in the opposite direction. As the load increases, a winch is used to set the line in the desired position as control becomes difficult by hand. With the line stoppers presently available, although the line may be taken off the winch and still be held by the line stopper, it is impossible to release the line without the use of a winch to hold the load while the line stopper is released. In sailboat racing, putting a line on a winch in order to effect a release of the line stopper is time consuming as well as tying up a winch which may be necessary for another control function. Also, the line stopper tends to contact and abrade a line on its release under load even using a winch to help effect such a release.  
      The prior art is replete with braking mechanisms for arresting or releasing a line under tension. As suggested, such lines are frequently used to hoisting and trimming of sails in which the line may be subjected to tensions ranging from low to extremely high tensions up to and even exceeding ten tons.  
      A common mechanism for arresting a line includes a cylindrical surface mounted to exhibit an eccentric braking surface in relation to a fixed abutment surface so that movement of the eccentric braking surface can vary or adjust a gap through which the line is guided. When the gap is sufficiently reduced, the line is wedged between the braking and abutment surfaces. Normally, continued tension on the line in the same direction increases the wedging effect and thereby the lock on the line. One example of such a rope holding device is disclosed in U.S. Pat. No. 3,835,507, which shows a cylindrical cam mounted for rotation on a pin to cause the circumferential gripping surface to provide a variable line gap when the cam is rotated. A U-shaped base member having legs with a pilot pin mounted therein is adapted to be anchored on a sailboat. A cam mechanism includes an inner element having a handle attached thereto which is eccentrically mounted for pivotal movement around the pivot pin. A movable outer element is positioned for pivotal movement and a rotational movement on the eccentrically mounted inner element. One or more springs are mounted between the inner and outer elements of the cam mechanism which are acted on when relative movement takes place between the elements. The spring is compressed when the handle is pivoted placing the outer member in locking engagement with the line in the load direction which locking action is increased with increasing load; while allowing the outer member to rotate or float over the line in the other direction. Each release of the load direction is effected by raising the handle. The line stopper can be released under heavy load because the outer element holding the line rotates in the same direction the line is running, the line will not be abraded thereby limiting line wear. The line stopper may be mounted either vertically or horizontally.  
      A disadvantage of existing rope holding or stopping devices is that they require substantial forces to be applied to release the line after is has been locked. Thus, once the line tension causes the eccentric cam surface to close a gap for the line and wedges it to stop it and lock it continued tension on the line in the same direction tends to decrease the gap even further with attendant increased holding pressure on the line. Releasing the line from its wedged condition can be effected by reversing the process and increasing the size of the gap through which the line extends. Clearly, this can be done in one of two ways. One or the other of the wedging surfaces must be moved away from the other opposing surface so that the gap is increased and the line is again permitted to move. As suggested, the prior art devices have typically used a fixed abutment surface that always remains stationary. Therefore, the only way to increase the gap is to move the surface on the eccentric cam in a direction opposite to the initial direction that caused the cam to lock the line. However, this is not always an easy or quick task. The reason for this is that the tension in the line can be so high that applying an opposing tension on the other end of the line may be difficult if manually attempted. Application of a tension greater than the tension at the opposing end of the line could rotate the eccentric cam in the releasing position with attendant increase in the gap. This approach, however, becomes impractical when the tensions in the line are extremely high. For this reason, a winch must at times be used to overcome very high tensions in the line in order to reverse the direction of movement of the eccentric cam surface and thereby the size of the line receiving gap. In some cases, a handle or lever is used that is attached to the eccentric cam that allows a user to obtain mechanical advantage in moving or rotating the eccentric cam to an unlocking position. See, for example, U.S. Pat. No. 4,425,862 for a sail line stopper that uses a handle that cooperates with the cam. Unlocking the line using the stopper still requires significant effort.  
     SUMMARY  
      The present invention generally relates to the line clutch mechanisms and, more specifically, to a line clutch with a quick release mechanism.  
      The clutch mechanism of the present invention is constructed such that in an unlocked, free position, a set of pins and linkages are off line and permit a pivotable wedge member to accommodate movement of a line (e.g., rope) that is carried by a rotatable member without causing wedging of the line since the wedge member is moved away from the rotatable member and therefore the line can freely travel through the clutch mechanism. However, when the set of pins and linkages is brought in line, the wedge member moves toward the rotatable member, thereby downsizing the line path and locking the line when the wedge member pivots to cause the line to become wedged between the pivotable wedge surface and the rotatable member. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING FIGURES  
      This invention, together with further aspects, features and advantages thereof will be more clearly understood by considering the following description in conjunction with the accompanying drawings in which like elements bear the same reference numerals throughout the several views.  
       FIG. 1  is a perspective view of a line clutch device in accordance with the present invention in the locked position;  
       FIG. 2  is a top plan view of the line clutch device in an unlocked or neutral position;  
       FIG. 3  is an exploded perspective view of a number of the components of the line clutch device of  FIG. 1 ;  
       FIG. 4  is a side elevation view of the line clutch device in the unlocked position; and  
       FIG. 5  is another top plan view of the line clutch device in an unlocked or neutral position; and  
       FIG. 6  is a top plan view of the line clutch device in the locked position. 
    
    
     DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS  
      Referring first to  FIGS. 1-6 , a line clutch or locking device in accordance with the invention is generally designated by the reference numeral  10 .  
      The device  10  serves to selectively clamp, lock, stop or arrest a line  12  while it is under tension and moving in either direction M or N ( FIG. 1 ).  
      The device  10  includes a housing or case  14  shown to be relatively flat and elongate in one direction in the general plane of the housing. However, it will be evident that the specific configuration of the housing or case is not critical and any convenient or suitable shape or configuration may be used that is consistent with the mounting and operation of the elements or components contained therein to be described.  
      Generally, the housing or case or chassis  14  includes or defines two sections. The first is a wedging or locking section  16  through which the line  12  to be controlled enters and exits the housing through suitable openings. The other part of the housing defines a control portion  22  which controls the actions that take place in the wedging or locking section  16 . The control portion  22  includes a manual control mechanism  24  that extends through a slot  26  and includes a handle  200  that extends through the slot  26  and may be provided with a knob or gripping portion  201 . The slot  26  is generally straight and provided with right angle recess or detent  26   a  at one respective end of the slot, the recess  26   a  serving as a locking position for the handle  200  that promotes the clamping or locking or stopping of the line  12 , as will be more fully described. It will become evident that the specific configuration of the slot  26  and the use of recess or detent  26   a  is not critical and any other and suitable mechanism, electro-mechanism or circuit may be used to establish and maintain the desired condition of the control portion  22 .  
      In the illustrated embodiment, the housing  14  is actually formed of two parts, namely a base portion  15  that houses and contains most of the working parts of the device  10  and a cover  17  that is secured thereto along an upper edge of the base potion  15 . The base portion  15  includes a first end  60  and an opposing second end  62 , with a first compartment  64  that defines the wedging section  16  being formed at or proximate the first end  60 . The first compartment  64  is defined by a floor  59  that terminates at the first end  60 . The first compartment  64  is open at the first end  60 , as well as the sides  64  thereof to permit reception and movement of the line  12 . When the cover  17  is attached to the base portion  15 , a pair of opposing side slots  20  is formed in the first compartment  64  to accommodate the travel and movement of the line  12 .  
      The base portion  15  also includes a pair of opposing side walls  80 ,  82  that extend upwardly from the floor  59  along peripheral side edges of the base portion  15 . More specifically, the side walls  80 ,  82  extend from a bottommost portion of the first compartment  64  all the way to the second end  62  which includes a transverse wall  84  that extends between the side walls  80 ,  82 . The side walls  80 ,  82  contain side wall protrusions  86  that are formed along a length thereof and protrude inwardly from an inner surface of the side walls  80 ,  82 . The pair of side wall protrusions  86  is preferably opposite one another at the same locations along their respective side walls  80 ,  82 . The side walls protrusions  86  serve to define and mark the boundary between the first compartment  64  and a second compartment  69  that contains the control portion  22 . While the side wall protrusions  86  can take any number of different shapes, the illustrated side wall protrusions  86  are generally block-shaped structures. Each side wall protrusion  86  has a top side or top face  90  that faces the first compartment  64  and an opposite underside or lower face  92  that faces the second compartment  69 . The second compartment  69  generally has a square or rectangular shape.  
      The slot  26  is formed in the side wall  80  to permit operation of the device  10  as described below.  
      A plurality of clutch devices  10  can be stacked to make efficient use of space while accommodating three lines  12 . Each of the devices  10  may be similarly constructed and, accordingly, may be provided with independent control portions  22 . These units may be secured to each other in any conventional way. The construction and operation of each of the units is the same and the description that follows in connection with  FIGS. 1-6  is applicable to each of the units.  
      Referring to  FIGS. 1-3 , one exemplary embodiment, by way of example, is illustrated and described below. The wedging or locking part  16  of the clutch device  10  includes a fixed pin or rivet  34  that can also be used to secure two or more of the units to each other. The pin or rivet  34  is fixed to the base  15  and cover  17  of the housing  14  and defines a center or “axis” of rotation  36 . Rotatably mounted on the pin or rivet  34  is a bearing  38  that can freely rotate about the fixed center or “axis”  36 . Mounted on the bearing  38  is a rotatable wheel  40 . The wheel  40  is thus mounted to the floor  59  of the first compartment  64  and more specifically, the wheel  40  is mounted at or near the first end  60 . The wheel  40  can be mounted such that a first portion thereof is disposed in the first compartment  64 , while a second portion thereof extends beyond the first end  60  since the wheel  40  is disposed and mounted above the floor  59  and thus can extend or protrude beyond the end  60  of the floor  59 .  
      The wheel  40  is constructed so that it includes an outer circumferential groove  42  (guide track) for receiving the line  12 . The circumferential groove  42  has an arcuate shape and in particular, the groove  42  has a concave shape that is complementary to the circular shape of the line  12  to permit the line  12  to be snugly received within the groove  42  (guide track) and whereupon, movement of the line  12  causes rotation of the wheel  40 . The wheel  40  is thus mounted in the middle section of the floor  59  at or near the end  60 . In one embodiment of the present invention, the wheel  40  can be removable and interchangeable with a wheel of a smaller or larger diameter and corresponding outer circumferential groove  42  (guide track) to accommodate various sized ropes and lines.  
      As will become evident, the stopping, locking or clamping action on the line  12  occurs when it is wedged within gap or space  50  between the wheel  40  and an opposing surface to be described.  
      The line clutch device  10  of the present invention includes a line clutch mechanism  100  (control portion  22 ) which is a mechanical device that is operable to either tie or release the line  12  (e.g., rope) as will be described in detail below. The line clutch mechanism  100  includes a rotatable/pivotal wedge member  110  that has an arcuate inner surface  112  that faces the wheel  40 . The inner surface  112  of the wedge member  110  in combination with the wheel  40  defines the space  50  in which the line  12  is wedged when the line clutch mechanism  100  is in the locked position and the wedge member  110  is rotated so that it assumes a position that causes the line  12  to be securely wedged within the gap  50  as described below. The wedge member  110  is in the form of a body  114  that preferably includes one or more bosses  116  that extend outwardly therefrom in the form of a projection. In the illustrated embodiment, the boss  116  has a circular shape and resembles a pivot pin that extends outwardly from the body  114 . For example, one boss  116  can be formed on a top surface of the body  114 , while the other boss  116  can be formed on a bottom surface of the body  114 . The two bosses  116  are axially aligned in thus defines a common axis about which the body  114  can pivot as described below.  
      The inner surface  112  of the body  114  is a toothed surface in that a plurality of teeth or teeth-like structure  118  are formed along the inner surface  112  of the body  114 . The teeth  118  provide gripping structures and define a roughened, uneven surface that engages and helps urge the line  12  against the wheel  40  and as the body  114  rotates, the line  12  is wedged against the wheel  40 . As with the other components of the line clutch mechanism  100 , the wedge member  110  is typically formed of a metal material; however, it will be understood that it may be formed from other materials that are suitable for the intended function.  
      While the body  114  is arcuate in nature, it does not define a complete circle but rather has a shape that is more semi-circular in nature. In other words and as illustrated, the body  114  extends about 180 degrees and can be slightly greater than 180 degrees, as illustrated, but still less than 270 degrees. In addition, the radial distances from the pivot axis of the body  114  to the outer surface of each tooth  118  are not uniform but rather the radial distances are great at and near the ends  119  of the body  114 . As illustrated in  FIG. 2 , a radial distance from the innermost teeth  118  to the center axis of rotation C, as measured by distance I-C, is less than a distance from the teeth in end region  119  to the center axis C, as measured by distance O-C.  
      Thus, in an engaged state, when the body  114  is pivoted so that one end  119  is in a 12 o&#39;clock position, the distance between point R of the wheel  40  and the teeth  118  located at and proximate the ends  119  of the body  114  is less than the distance between point R and the inner teeth  118  of the body  114  when the inner teeth  118  are in the 12 o&#39;clock position. This construction permits the line  12  to be wedged between the wheel  40  and the end regions  119  of the body  114  as described below.  
      The line clutch mechanism  100  also includes a guide member  120  that has a first end  122  and an opposing second end  124 . At the first end  122 , the guide member  120  has an elongated upper section that is formed by a pair of arms or fingers  126  that are spaced apart from one another to define a space  127  therebetween. Each of the arms  126  terminates in an arcuate (rounded) end that defines the first end  122 . The arms  126  are superimposed with respect to one another (overlying relationship) and extend axially within the mechanism  100 . Each of the arms  126  has an opening  128  formed therethrough near the arcuate first end  122 . The openings  128  are axially aligned with one another so as to define an axial through opening through the guide member  120 , with this axial opening  128  constructed to receive the bosses  116  of the body  114  of the urging element  112  so as the rotatably (pivotally) mount the urging element  112  to the guide member  120  at its end  122  thereof.  
      The upper section that is defined by the arms  126  is integrally connected to a base section  140  of the guide member  120 . The base portion  140  includes a first boss  142  in the form of a slightly raised protuberance which in this case has a circular shape and is spaced from an arcuate lip or edge  144  of the base portion  140 . The base portion  140  has a generally planar first face  150  that is formed around the first boss  142  and extends from the arcuate edge  144  to the end  122  of the guide member and thus, the edge  144  resembles a shoulder between two stepped portions defining the guide member  120 . The planar second face  151  thus defines one (the upper) arm  126 .  
      At the end  124 , the guide member  120  has a pair of arcuate walls  160  that are spaced oppositely apart one another so as to define a receiving space or compartment  162  that is also defined by a floor section of the guide member  120 . In other words, the space  162  does not include a ceiling and is thus open but is otherwise defined by the pair of arcuate walls  160  and the floor. Proximate the end  124 , the guide member  120  includes a pair of opposing side flanges or fingers  170  that extend outwardly from the base portion  140  toward the sides of the housing  14 . The side flanges  170  are axially aligned with one another and each forms a right angle with the base portion  140 . Preferably, each side flange  170  includes a planar inner surface or face  172  which faces an underside  92  of the side wall protrusions  86 .  
      The guide member  120  is disposed within the base  15  of the house  14  such that the arms  126  extend through an axial channel  99  formed between the side wall protrusions  86  and at least partially into the first compartment  64 . The dimensions of the arms  126  are thus complementary to the dimensions of the axial channel  99  to permit reception therein and to permit axial movement of the guide member  120  (arms  126 ) within the axial channel  99 . At least the upper portions (end  122 ) of the arms  126  are disposed on one side (a top side)  90  of the side walls protrusions  86 , while the side flanges  170  are disposed on the opposite side (the underside)  92  of the side wall protrusions  86 . In this manner, the top sides  90  of the side wall protrusions  86  define a stop for the axial movement of the guide member  120  and the wedge member  110  in a direction toward the end  62  of the housing  14 . As shown in  FIG. 2 , the upper edge portions  81 ,  83  are arcuate surfaces (concave) surfaces that define the respective top sides  90  of the side wall protrusions  86  and since the dimensions of the urging element  110  are greater than the dimensions of the width of the axial channel  99 , the edge portions  81 ,  83  restrict the axial movement of the coupled wedge member  110  and guide member  120  by acting as a stop. Similarly, the underside  92  of the side wall protrusions  86  acts as a stop surface for the side flanges  170  and restricts axial movement thereof in the opposite direction toward the end  60 .  
      The underside  92  of the side wall protrusions  86  also serves another purpose in that it provides a planar surface that is opposite the planar surfaces  172  of the side flanges  170  and thus permits a biasing member  180  to be disposed between one side flange  170  and the respective underside  92  of the side wall protrusion  86 . As described below, the biasing members  180  serve to bias the line clutch mechanism  100  to the open or unlocked position illustrated in  FIG. 2 . In one embodiment, the biasing member  180  are in the form of coil springs that are disposed against and between the planar surfaces of the side flanges  170  and the undersides  92  of the side wall protrusions  86 . In the unlocked position of the clutch mechanism  100 , the stored energy of the biasing members  180  has been at least substantially released, while in the locked position, energy is stored in the biasing member  180 .  
      Similar to the wedge member  110 , the base portion  140  of the guide member  120  is sized to fit within the axial channel  99  formed between the side wall protrusions  86 . Side walls  141  of the base portion  140  slidingly travel along the inner surfaces or walls of the side wall protrusions  86 .  
      The wedge member  110  is coupled to the guide member  120  in a biased manner and in particular, by means of a biasing element  129 . The guide member  120  includes a transverse wall  125  that extends across a width of the space  127  formed between the arms  126 . More specifically, the transverse wall  125  is formed near the location of the arcuate edge  144  facing the first end  122 . The transverse wall  125  includes a feature for securing one end  131  of the biasing element  129 . For example, the transverse wall  125  can contain an open catch or pin structure that receives and engages a complementary structure of the biasing element  129 .  
      The other end  133  of the biasing element  129  is coupled to a base section  111  of the wedge member  110 . In one exemplary embodiment, the biasing element  129  is in the form of a spring that has two hook structures at its opposite ends to permit the spring  129  to be attached to and between the fixed transverse wall  125  and the rotatable wedge member  110 . One hook (e.g., open circular shaped hook) of the spring  129  is attached to a circular pin structure that protrudes upwardly from either the transverse wall  125  or if there is no transverse wall  125 , then the pin can extend upwardly from the floor defined by the bottom or lower arm  126 . Similarly, the base section  111  of the wedge member  110  can contain a pin structure that extends upwardly therefrom for engagement with a hook (e.g., open circular shaped hook) at the other end of the biasing element  129 . Between the hooks is the spring, such as a coil spring.  
      When the spring  129  is in its rest position, the spring  129  biases the wedge member  110  into a position where the innermost teeth are orientated in the 12 o&#39;clock position as shown in  FIG. 2 . The spring  129  is biased such that when a force is applied thereto (e.g., as by movement of the line  12  in direction N or M when the wedge member  110  engages the line  12 ), the spring  129  stores energy as the wedge member  110  rotates in either a clockwise direction or counterclockwise direction. As soon as the stored energy is released, as when the wedge member  110  is disengaged from the line  12  and the wedge member  110  can freely rotate back to its rest position, the wedge member  110  rotates back to the orientation shown in  FIG. 2  where the innermost teeth  118  are in the 12 o&#39;clock position. In the rest position, the innermost teeth  118  are again ready for engagement with the line  12  when the clutch mechanism  100  is placed into the locked position. The spring  129  is thus provided to restore the spring  129  to the rest position shown in  FIG. 2 . The biasing force also ensures a smooth movement of the wedge member  110  as it rotates due to movement of the line  12  in either the M direction or the N direction.  
      The clutch mechanism  100  also includes a pivot housing  190  that is defined by a body portion  192  that has a pair of opposing flanges  194  that extend therefrom and are spaced apart from one another so as to define a channel or space  196  therebetween for receiving a handle  200  as described below. Preferably, the opposing flanges  194  are parallel to one another and are formed at right angles with respect to the body portion  192 . Each of the side flanges  194  has a bore  197  formed therethrough so as to form an entrance into the space  196 . The two bores  197  are opposite one another and axially aligned with one another to permit a first shaft or pin  198  to extend therethrough across the space  196  for pivotally holding the handle  200  of the clutch mechanism  100 .  
      The body portion  192  also includes a slot or channel  210  formed therein at a location between the side flanges  194  and one which faces the space  196  and in fact is open to the space  196 . The slot  210  is defined by a floor as well as opposing side walls so as to define a vertical space that receives a handle biasing member  220  as well as a nub or protrusion  212  that is part of a handle block  230 . More specifically, the handle block  230  includes the nub  212  at one end thereof, while the opposite end includes a bore  236  for securely receiving one end of the elongated handle  200 . For example, the bore  236  can be a threaded bore and the respective end of the elongated handle  200  can include complementary threads such that the handle  200  can be threadingly attached to the handle block  230 . It will be appreciated that the other types of attachment techniques can be used to securely fix the handle  200  to the handle block  230  including but not limited to other types of mechanical fits, such as a frictional fit, etc.  
      The handle block  230  also includes a transverse bore  239  that extend therethrough and is sized to receive the first shat  198 . Accordingly, when the handle block  230  is disposed within the space  196 , the transverse bore  239  axially aligns with the bores  197  to permit the first shaft  198  to pass therethrough so as to pivotally attach the handle block  230  to the pivot housing  190 . The handle biasing member  220  (e.g., a spring) is disposed within the slot  210  so as to apply a biasing force against the nub  212  of the handle block  230 , thereby biasing the handle block  230  and handle  200  in an up position. The handle biasing member  220  is thus disposed between the floor  202  and the nub  212 . In this manner, the handle block  230  not only pivots about an axis defined by the first shaft  198  but also is biased in up position to assist the handle  200  being placed into the locked position as described below.  
      The elongated handle  200  preferably includes a knob element  201  or the like at an end opposite the end which is fixedly secured to the handle block  230 . The knob  201  assists the user in grasping and manipulating the handle  200  so as to permit the clutch mechanism  100  to be moved between the locked position and the unlocked position.  
      The pivot housing  190  also includes a through bore  193  through the body portion  192  proximate but not in communication with the slot  210  and the space  196 . The body portion  192  of the pivot housing  190  also includes a receiving space  195  that is defined in part by an arcuate wall  197  and a floor  199  which contains an opening or bore  201  formed therethrough. The receiving space  195  is similar and complementary to the receiving space or compartment  162  associated with the guide member  120 .  
      The clutch mechanism  100  further includes several linkages that pivotally and operably connect the pivot housing  190  to the guide member  120 . More specifically, a pivot block  240  is provided and is generally in the shape of an oval or a block that has a pair of rounded ends  242 . The pivot block  240  also includes a second boss  244  and a third boss  246  that extend above a planar upper surface  245  of the pivot block  240 . In the illustrated embodiment, each of the bosses  244 ,  246  has a circular shape to permit pivoting of the block  240  relative to both the pivot housing  190  and the guide member  120 ; however, the other shapes may be possible. The planar surface  245  between the two bosses  244 ,  246  is thus recessed relative to the bosses  244 ,  246  themselves and has a pair of arcuate (concave) edges or surfaces  247  that face the bosses  244 ,  246 .  
      The pivot block  240  acts as a linkage between the pivot housing  190  and the guide member  120  and in particular, one rounded end  242  is received within the receiving space  195  associated with the pivot housing  190 , while the other rounded end  242  is receive din the receiving space  162  associated with the guide member  120 . The boss  244  that is received in the receiving space  162  of the guide member  120  is pivotally attached to the guide member  120  by means of the first pivot plate  250  which is in the form of a planar plate that has rounded ends  252  that are complementary to the arcuate edge  247  and the arcuate edge  144  of the guide member  120 . The first pivot plate  250  has a pair of openings  254  formed therethough proximate the rounded ends  252 . The openings  254  are complementary to the boss  242  of the pivot block  240  and the boss  142  of the guide member  120  such that the bosses  242 ,  142  are received therethrough so as to fixedly yet pivotally connect the pivot block  240  to the guide member  120 . A fastener or the like can be used to fixedly secure the first pivot plate  250  to the guide member  120 . For example, a screw or the like can be received within an opening that is formed within the guide member  120  between the side flanges  170 .  
      It will be appreciated and described in more detail below that the manner of linking the pivot block  240  to the guide member  120  permits the pivot block  240  to freely pivot relative to the guide member  120 , while the guide member  120  moves within the channel  99  and along axis  88 .  
      Similarly, a second pivot plate  260  is provided and is similar to the first pivot plate  250  in that it is in the form of a planar plate that has rounded ends  262  that are complementary to the arcuate edge  247  of the guide member  120 . The second pivot plate  260  has a pair of openings  264  formed therethrough proximate the rounded ends  262 . The openings  264  are complementary to the boss  244  of the pivot block  240  and a main shaft  270  that is received within and through the through bore  193  of the body portion  192  of the pivot housing  190  and then through an opening  19  formed in the floor of the base  15  of the assembled housing  14 , as well as an opening  21  formed in the cover  17 , so as to be fixedly connected to the housing  14 . In other words, the main shaft  270  is stationary and does not rotate relative to the base  15  or any other component for that matter, but rather, the pivot housing  190  pivots thereabout. The pivot housing  190  is pivotally attached to the stationary shaft  270  by the second pivot plate  260  which acts as a linkage between the two components.  
      As with the first pivot plate  250 , a fastener or the like can be used to fixedly secure the second pivot plate  260  to the pivot housing  190 . For example, a screw or the like can be received within an opening that formed within the pivot housing  190  between the through bore  193  and the receiving space  195 .  
      The operation of the clutch device  10  will now be described in connection with  FIGS. 1-6 . In  FIG. 2 , the control portion  22  is set to allow the line  12  to move in either direction M or N. As the line  12  moves through the clutch device  10 , the frictional engagement of the line  12  with the wheel  40  causes the wheel to rotate either in a clockwise direction, if the line is moving in the direction M or in a counter-clockwise direction if the line moves in the opposite direction N. For purposes of the illustration it will be assumed that the line  12  is tensioned and moves in the direction N.  
      In the unlocked position, the wedge member  110  is sufficiently spaced from the line  12  such that it does not engage the line  12  and therefore, the line  12  is free to move about the wheel  40 . In addition, in the unlocked position, the guide member  120  can slide axially through the channel  99  toward the second end  62  without any resistance (since this is not against the biasing force applied by the springs  180 ), and consequently, the gap or space  52  for the line  12  remains substantially the same and the line  12  is not wedged, stopped or arrested in any way. This will continue until a decision is made to stop, arrest, or clamp the line  12 .  
      It will be appreciated that in the unlocked position shown in  FIG. 2 , the handle  200  is all the way or close to the right end of the slot  26  and the pivot housing  190  is pivoted about the fixed (stationary) main shaft  270  such that the pivot block  240  and second pivot plate  260  are not axially aligned with the first pivot plate  250  and base portion  140  of the guide member  120  but rather are offset therefrom (“offline”), thereby permitting the biasing members  180  to be in a relaxed state (stored energy is released) which results in the guide member  120  and the wedge member  110  that is coupled thereto being sufficiently spaced from the wheel  40  to permit free movement of the line  12  as the wheel  40  rotates due to a pulling or pushing action on the line  12  in either clockwise or counterclockwise directions. The handle  200  is biased in an up position due to the release of stored energy of the handle biasing member  220  against the nub  212  of the handle block  230 .  
      To move the clutch mechanism  100  to the locked position shown in  FIG. 1 , the operator simply moves the handle  200  within the slot  26  toward the left end and the detent  26   a  until the handle  200  engages the detent  26   a . As the handle  200  travels in the slot  26  in this direction, the pivot housing  190  is caused to pivot in an opposite direction (clockwise direction) about the fixed (stationary) main shaft  270  since the handle  200  is coupled to the pivot housing  190  by means of the handle block  230 . As soon as the handle  200  is aligned with the detent  26   a , the biasing force of the handle biasing member  220  causes the handle  200  to be directed into the detent  26   a  since this position of the handle  200  over the detent  26   a  permits a release of the stored energy of the biasing member.  
      As the pivot housing  190  pivots in this clockwise direction about pivot  270 , the pivot block  240  pivots relative to both the pivot housing  190  and the guide member  120  due to the reception of the bosses  244 ,  246  in the respective openings of the first and second pivot plates  250 ,  260 . As the pivot housing  190  pivots in this manner, both the pivot block  240  and the second pivot plate  260  pivot into a position where they are axially aligned with the first pivot plate  250  and the base portion  140  of the guide member  120  (“in line”) which results in a force being applied to the guide member  120  in a direction toward the first end  60 . This force is sufficient to overcome the biasing force of the biasing members  180 , thereby causing the biasing member  180  to compress between the side flanges  170  and the side wall protrusions  86 . It will thus be appreciated that as soon as the pivot block  240  is moved to the aligned position along the “axis A”, the guide member  120  and wedge member  110  are prevented from the unrestricted movements toward the second end  62 .  
      In this “in line” position, the urging element  110  is placed into contact and engagement with the line  12 . However, when the inner teeth  118  of the body  114  engage the line  12 , there is some play for further movement of the line  12 . Now, as the line  12  is moved further and the wheel  40  rotates, the wedge member  110  rotates/pivots in an opposite direction. For example, when the line  12  moves in direction N, the wheel  40  rotates in a counterclockwise direction, while the wedge member  110  results in the end region  119  moving towards the 12 o&#39;clock position where the distance between point R of the wheel  40  and the teeth  118  (point O) is at a minimum.  
      The continued rotation of the wedge member  110  causes an increasing reduction in the size of the gap or space  52 . This causes a wedging effect and the line  12  is abruptly stopped when the wedge member  110  is rotated to bring one end  119  to a predetermined position(s) (e.g., when the end  119  (point O) is in a position between 10-12 o&#39;clock positions in  FIGS. 1 and 6 ). As will be appreciated, the pivot block  240  and the pivot housing  190  together from a toggle joint. Such a joint, formed of the two arms or links, can be used to implement a “snap-action” when the links are moved out of alignment. However, when in alignment such arms or links can be used to apply significant pressures at both ends by forcing the arms or links into straight alignment when the ends of the arms or links are constrained or fixed in place.  
      As the end region  119  rotates closer to the 12 o&#39;clock position, the distance between the wedge member  110  and the wheel  40  decreases to a point where the line  12  is attested/stopped due to the wedging action. In this position, no further movement of the line  12  in the N direction is possible. It will be appreciated that when the innermost teeth  118  of the wedge member  110  (point I) are in the 12 o&#39;clock position, the wedge member  110  is rotated less than 90 degrees to cause the line  12  to be stopped due to the movement of the end region  119  toward the 12 o&#39;clock position.  
      One of the advantages of the present mechanism  100  is that the degree of play in the opposite direction, in this case direction M, is minimized and optimized due to the construction of the wedge member  110  and the wheel  40  and more particularly, due to the restricted degree of rotation of the wedge member  110  relative to the line  12 . If the line  12  is moved in the opposite direction M from is locked position in the direction N, the wheel  40  and the wedge member  110  rotate in the opposite directions such that the inner teeth  118  move through the 12 o&#39;clock position and the other end  119  of the body  114  moves toward the 12 o&#39;clock position until the end  119  rotates enough to case a wedging of the line  12 .  
      It will thus be appreciated that the clutch mechanism of the present invention is constructed such that in the unlocked, free position, a set of pins and linkages are off line and permitting a cam surface to accommodate the movement of the wheel that carries the line (e.g., rope) and wedge member without causing wedging of the line since the teeth are spaced away from the wheel; however, when the set of pins and linkages is brought in line, the wedge member is moved toward the wheel, thereby downsizing the line path and locking the line when the wheel rotates causing the line to become wedged between the wedge member and wheel.  
      While manual controls have been described, it will also be understood that remote or wireless controls of the “blocking” elements can be used to thereby cause locking, wedging or stopping of the line by a remote user or even by a programmed controller that senses when such action should take place and a blocking element be interposed that will results in wedging or stopping of the line.  
      In one embodiment of the present invention, the wheel  40  can be removable and interchangeable with a wheel that is a full circular wheel or a semi-circular wheel to accommodate the expected backlash.  
      Since other changes and modifications varied to fit particular operating requirements and environments will be apparent to those skilled in the art, the invention is not considered limited to the examples chosen for purposes of illustration, and includes all changes and modifications which do not constitute a departure from the true spirit and scope of this invention as claimed in the following claims and equivalents thereto.