Abstract:
A centrifugal braking device switchable between inoperative and operative states enabling the switching operation to be carried out with light force. The centrifugal braking mechanism in a dual-bearing reel unit is for braking the spool under centrifugal force, and includes a plurality of guide shafts, a plurality of shifters, a cylindrical brake element, and a switching mechanism. The guide shafts are radially disposed on a rotor coupled to the spool for rotation together therewith. The shifters are axially movably fitted to the guide shafts, about which they are pivotable, and therein allowed travel diametrically with respect to the spool. The brake element is disposed to the outer peripheral side of the plurality of shifters, and made non-rotatable with respect to the reel unit. The shifters travel diametrically under centrifugal force to come into contact with the brake element. By changing the pivotal position of the shifters about the shaft, the switching mechanism switches the shifters between an inoperative state, preventing them from coming into contact with the brake element, and an operative state enabling brake element contact.

Description:
BACKGROUND OF THE INVENTION 
     1. Technical Field 
     The present invention relates to reel-braking devices; in particular to dual-bearing reel centrifugal braking devices for braking under centrifugal force the spool fitted rotatively to the reel unit. 
     2. Description of Related Art 
     In dual-bearing reels referred to as bait reels, utilized mainly for lure fishing, generally braking force is made to act on the spool so that backlash does not occur when casting. “Backlash” herein is the phenomenon of the rotational speed of the spool being faster than the line wind-out speed. As this type of braking mechanism, centrifugal braking devices that employ centrifugal force developing from spool rotation to brake the spool are known. 
     Centrifugal braking mechanisms of this class are in general provided with: shifters allowed to shift in the diametric direction of the spool (guide shaft axial direction) on guide shafts that are arranged radially on a rotor that rotates coupled with the spool; and a brake element to the outer peripheral side of the shifters, provided enabling shifter contact. Among these sorts of centrifugal braking devices, that disclosed in Japanese Utility Model Gazette Reg. No. 2535505 enables adjusting the number of shifters that can come into contact the brake element. 
     The centrifugal braking device disclosed in the above-noted gazette is provided with a switching mechanism that by translating the shifters diametrically with respect to the spool switches between an inoperative state in which the shifters cannot come into contact with the brake element and an operative state for contact with the brake element. The switching mechanism includes pairs of fixing projections formed projecting toward the shifters on lateral walls of recesses formed in a shifter-fitting section of the rotor, and annular shifter projections that enable interlocking with the fixing projections and that are furnished on the shifters. The shifter projections, or the fixing projections, are elastically deformable components and by elastic deformation enable disengagement of the interlocking. 
     Wherein switching between the operative state and the inoperative state is carried out, the annular shifter projections on the shifters are caught and pulled with the fingertips to shift the shifters diametrically. Shifting the shifters from the operative state diametrically inward by elastically deforming the shifter projections to carry them past the fixing projections and dispose the shifter projections inward thereof switches them into the inoperative state, in which the shifters cannot come into contact with the brake element. Again, shifting the shifters from the inoperative state diametrically outward to dispose the shifter projections outward switches the shifters into the operative state. 
     In the foregoing conventional centrifugal braking devices, the shifters are switched between the operative state and the inoperative state by shifting them diametrically with respect to the spool, elastically deforming either the fixing projections or the shifter projections, wherein the shifter projections ride against and beyond the fixing projections. Accordingly, because the shifting directions when switching and when braking the shifters are the same, loosening the interlocked state of the two sets of projections to make handling easier risks that when braking, the shifter projections on the shifters in the inoperative state will ride past the fixing projections and come into contact with the brake element. Therefore, in the foregoing conventional configuration, the interlocked state between the two sets of projections has to be adjusted tight enough to keep the shifter projections from riding past the fixing projections under centrifugal force. In practice, the interlocked state is tightened by making the elastically deformable projections among the two sets of projections harder, or by enlarging the extent of engagement of the two sets of projections. An accordingly tightened engagement makes a comparatively large force necessary for the switching operation, making handling during switching difficult. 
     SUMMARY OF THE INVENTION 
     An object of the present invention is to enable the switching operation in a centrifugal braking device switchable between inoperative and operative states to be carried out with light force. 
     The centrifugal braking device for a dual bearing reel according to aspect 1 of the present invention is a device for braking a spool which is rotatably provided with a reel body by using a centrifugal force, including a plurality of guide shafts, a plurality of shifters, a brake element of a cylindrical shape, and a switching means. The guide shafts are shafts which are radially provided with a rotor which rotates together with the spool. The shifters are members attached to the guide shafts in a movable manner in an axial direction rotatably around the axis. The shifters are capable of moving in a radius direction of the spool. The brake element is a member disposed at an outer peripheral side of the plurality of shifters. The brake element is non-rotatably provided with respect to the reel body and may be made contact with the shifters which are moved in the radius direction. The switching means is a means for switching a state of the shifters to an inoperative state in which no contact with the brake element is possible or to an operative state in which a contact with the brake element is possible by changing a rotational position of the shifters around the axis. 
     In this centrifugal braking device, when the spool rotates, the rotor also rotates and the shifter attached to the guide shaft moves in the radius direction to make contact with the brake element. When the shifter makes contact with the brake element, the spool is braked by a frictional force. The braking force generated at this time depends on the number of the shifters which make contact with the brake element, and the number of the shifters which make contact is changeable by using the switching means. That is, if the state of the shifter is switched to the inoperative state by using the switching means, the shifter cannot make contact with the brake element. This switching operation may be carried out by changing a rotational position of the shifter around the guide shaft. Since the rotational direction around the guide shaft is different from the moving direction of the shifter (i.e., the axial direction of the guide shaft), a large force is not necessary for the switching operation in the rotary direction and the operation may be carried out by using a small force. Since the switching operation may be carried out with a small force, it may be performed all at once by using another member instead of performing it one by one manually. Moreover, since the operation direction is the rotary direction, not the radius direction of the spool, the switching operation is easily performed all at once. 
     The centrifugal braking device for a dual bearing reel according to aspect 2 of the present invention is a device as set forth in aspect 1, wherein each of the guide shafts is provided inside of a plurality of recesses which is radially provided around an outer periphery portion of the rotor with an opening facing an outer peripheral side thereof; and the switching means includes: a shifter projection disposed at the shifters so as to project in a radius direction of the guide shafts; a guide provided with one of side walls of the recess which opposed to each other in a rotary direction, the guide being engaged with the shifter projection and non-rotatably guides the shifter to a position at which a contact with the brake element is possible in a manner movable in the axial direction; and a restricter provided with the other one of the side walls, the restricter being engaged with the shifter projection and restricts the shifter so that the shifter cannot make contact with the brake element. In this case, when the shifter projection of the shifter is directed to the guide provided with one of the side walls of the recess, the state of the shifter is switched to the operative state. On the other hand, when the shifter projection is directed to the restricter provided with the other one of the side walls, the state thereof is switched to the inoperative state. For this reason, the direction of the shifter projection is different in the operative state and the inoperative state and, hence, the operative or inoperative state of the shifter can be immediately determined. 
     The centrifugal braking device for a dual bearing reel according to aspect 3 of the present invention is a device as set forth in aspect 2, wherein the guide includes a first linear engaging portion formed as a protuberance or notch in one of the side walls, the first linear engaging portion extending parallel to the guide shaft with a length by which the shifter is capable of making contact with the brake element in a state in which the shifter projection being engaged; the restricter includes a second linear engaging portion formed as a protuberance or notch in the other one of the side walls, the second linear engaging portion extending parallel to the guide shaft with a length by which the shifter is incapable of making contact with the brake element in a state in which the shifter projection being engaged; and the shifter projection includes a moving engaging portion formed at an end portion of the shifter projection as a protuberance or notch, the moving engaging portion being capable of non-rotatably engaging with the two linear engaging portions in a movable manner in the axial direction. In this case, when the moving engaging portion of the shifter projection is engaged with the first linear engaging portion by rotating the shifter, the state of the shifter is switched to the operative state and the operative state is maintained by a dovetailing engagement so that the shifter may be moved outwardly in the axial direction (outwardly in the radius direction of the spool) to make contact with the brake element when the spool rotates. Also, when it is rotated in the opposite direction to be engaged with the second linear engaging portion, the state of the shifter is switched to the inoperative state and the state is maintained. In the inoperative state, if the shifter is moved in the axial direction towards the brake element, it cannot move to a position at which a contact with the brake element is possible and, hence, it cannot make contact with the brake element. In this case, since the two states are maintained and the movement in the axial direction is restricted by the dovetailing engagement of the two linear engaging portions with the moving engaging portion, it is not necessary to maintain the two states by using another member. 
     The centrifugal braking device for a dual bearing reel according to aspect 4 of the present invention is a device as set forth in aspect 3, wherein there are two of the shifter projections provided with an interval between each other around an axis of the guide shaft, one of the shifter projections being engaged with the first linear engaging portion and the other one of the shifter projections being engaged with the second linear engaging portion. In this case, the two states may be maintained without using another member and, since the two shifter projections are provided so as to correspond to each state, the degree of rotation may be decreased as compared with a case in which one shifter projection is engaged with one of the two linear engaging portion and, hence, operability thereof is increased. 
     The centrifugal braking device for a dual bearing reel according to aspect 5 of the present invention is a device as set forth in aspect 4, wherein the two shifter projections are provided with an interval between each other in an axial direction of the guide shaft, one of the shifter projections closer to the brake element being engaged with the first linear engaging portion and the other one of the shifter projections farther from the brake element being engaged with the second linear engaging portion. In this case, the two states may be easily switched by simply rotating the shifter, not by moving it in the axial direction. 
     The centrifugal braking device for a dual bearing reel according to aspect 6 of the present invention is a device as set forth in aspect 4, wherein the two shifter projections are provided with an interval between each other in an axial direction of the guide shaft, one of the shifter projections closer to the brake element being engaged with the second linear engaging portion and the other one of the shifter projections farther from the brake element being engaged with the first linear engaging portion. In this case, the two states may be easily switched by simply rotating the shifter, not by moving it in the axial direction. 
     The centrifugal braking device for a dual bearing reel according to aspect 7 of the present invention is a device as set forth in aspect 1, wherein each of the guide shafts is provided inside of recesses of an even number which is radially provided around an outer periphery portion of the rotor with an opening facing an outer peripheral side thereof; and the switching means includes: a first shifter projection disposed at the shifters so as to project in a radius direction of the guide shafts and a second shifter projection provided with an interval from the first shifter in an axial direction of the guide shaft and around the axis; a guide provided with one of a pair of side walls of the even number recesses which opposed to each other in a rotary direction, a continuous half of the guide being engaged with the first shifter projection and the other continuous half of the guide being engaged with the second shifter projection, the guide guides the shifter to a position at which a contact with the brake element is possible in a manner movable in the axial direction; and a restricter provided with the other one of the side walls, a continuous half of the restricter being engaged with the second shifter projection and the other continuous half of the restricter being engaged with the first shifter projection, the restricter restricts the shifter so that the shifter cannot make contact with the brake element. In this case, a continuous half of the guide or the restricter is engaged with one of the two shifter projection, a member for switching operation needs only be rotated a half periphery, not entire periphery, when states of the two shifters are switched at once in sequence. 
     The centrifugal braking device for a dual bearing reel according to aspect 8 of the present invention is a device as set forth in aspect 7, wherein the guide includes a first channel notch provided with the one of side walls so as to be parallel to the guide shaft; and the restricter includes a second channel notch provided with the other one of side walls so as to be parallel to the guide shaft, the second channel notch having a length by which the shifter cannot make contact with the brake element when the first shifter projection or the second shifter projection makes contact with an end portion thereof. In this case, since the guiding and restriction of the shifters may be carried out by the channel notches, the configuration of the guide and restricter may be realized by using the same structure and, hence, the configuration of the switching means is simplified. 
     The centrifugal braking device for a dual bearing reel according to aspect 9 of the present invention is a device as set forth in aspect 7 or 8, further having a shifter controlling mechanism which includes: an adjustment member of a circular plate shape capable of relatively rotating around an rotary axis of the spool with respect to the rotor and rotating together with the rotor while maintaining a relative rotary position; a first arc projection of a half arc shape provided with the adjustment member at a position at which the first arc projection being capable of opposing to the first shifter projection, the first arc projection presses a plurality of the first shifter projections disposed at a continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in a direction so that the first shifter projections are engaged, in that order, with the guide to switch a state of the shifter from the inoperative state to the operative state and maintain the operative state of the switched shifter, the first arc projection presses a plurality of the first shifter projections disposed at the other continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the other direction so that the first shifter projections are engaged, in that order, with the restricter to switch a state of the shifter from the operative state to the inoperative state and maintain the inoperative state of the switched shifter; and a second arc projection of a half arc shape provided with the adjustment member at a position opposite to the first arc projection at which the second arc projection being capable of opposing to the second shifter projection, the second arc projection presses the second shifter projections disposed at the other continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the direction so that the second shifter projections are engaged, in that order, with the guide to switch a state of the shifter from the inoperative state to the operative state and maintain the operative state of the switched shifter, the second arc projection presses the first shifter projections disposed at the continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the other direction so that the second shifter projections are engaged, in that order, with the restricter to switch a state of the shifter from the operative state to the inoperative state and maintain the inoperative state of the switched shifter. 
     In this case, if the adjustment member is rotated in one direction when all of the shifters are in their inoperative states, the first shifter projection of the shifter disposed at the continuous half of the recesses is pressed by the first arc projection to be engaged with the guide in order of pressing so that the shifters of the continuous half are switched to the operative state in order and the operative state is maintained by the first arc projection. At the same time, the second shifter projection of the shifter disposed at the other half of continuous recesses is pressed by the second arc projection to be engaged with the restricter in order of pressing so that the shifters of the other continuous half are switched to the inoperative state in order and the inoperative state is maintained. Also, if the adjustment member is rotated in the other direction when all of the shifters are in their operative states, the second shifter projection of the shifter disposed at the continuous half of the recesses is pressed by the second arc projection to be engaged with the restricter in order of pressing so that the shifters of the continuous half are switched to the inoperative state in order and the inoperative state is maintained. At the same time, the first shifter projection of the shifter disposed at the other half of continuous recesses is pressed by the first arc projection to be engaged with the restricter in order of pressing so that the shifters of the other continuous half are switched to the inoperative state in order and the inoperative state is maintained. At that time, the shifters may be switched to the operative state or the inoperative state in a stepwise manner by staggering a timing of pressing by the first arc projection and that by the second arc projection. 
     The centrifugal braking device for a dual bearing reel according to aspect 10 of the present invention is a device as set forth in aspect 7 or 8, wherein the guide and restricter maintain the engaged shifter in a non-rotatable state around the guide shaft. In this case, since not only the two shifters are guided and restricted by the guide and the restricter but also the engaged shifters may be maintained in a non-rotatable state, a mechanism for maintaining the state of the shifters becomes unnecessary. 
     The centrifugal braking device for a dual bearing reel according to aspect 11 of the present invention is a device as set forth in aspect 10, wherein the recesses are disposed at an outer periphery portion of the rotor with an equal interval between each other in a circumferential direction; and further including a shifter controlling mechanism which includes: an adjustment member capable of relatively rotating around an rotary axis of the spool with respect to the rotor and rotating together with the rotor while maintaining a relative rotary position; a first control nub provided with the adjustment member in a protruding manner at a position at which the first control nub being capable of opposing to the first shifter projection, the first control nub presses the first shifter projections disposed at a continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the direction so that the first shifter projections are engaged, in that order, with the guide; a second control nub provided with the adjustment member at a position located at an upper stream side in the direction with respect to a symmetrical position formed by the first control nub and a spool shaft center and at which the second control nub being capable of opposing to the second shifter projection, the second control nub presses the second shifter projections disposed at the other continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the direction so that the second shifter projections are engaged, in that order, with the guide; a third control nub provided with the adjustment member at a position located at a downstream side in the direction with respect to the second control nub with the same radius position as the first control nub, the third control nub presses the first shifter projections disposed at the other continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the other direction so that the first shifter projections are engaged, in that order, with the restricter; and a fourth control nub provided with the adjustment member at a position located at a downstream side in the direction with respect to the first control nub with the same radius position as the second control nub, the fourth control nub presses the second shifter projections disposed at the continuous half of the recesses in order by an end portion thereof when the adjustment member rotates in the other direction so that the second shifter projections are engaged, in that order, with the restricter. 
     In this case, if the adjustment member is rotated in one direction when all of the shifters are in their inoperative states, the first shifter projection of the shifter disposed at the continuous half of the recesses is pressed by the first control nub to be engaged with the guide in order of pressing so that the shifters of the continuous half are switched to the operative state in order and the operative state is maintained by the guide. At the same time, the second shifter projection of the shifter disposed at the other half of continuous recesses is pressed by the second control nub to be engaged with the guide in order of pressing so that the shifters of the other continuous half are switched to the operative state in order and the operative state is maintained. Also, if the adjustment member is rotated in the other direction when all of the shifters are in their operative states, the first shifter projection of the shifter disposed at the other continuous half of the recesses is pressed by the third control nub to be engaged with the restricter in order of pressing so that the shifters of the other continuous half are switched to the inoperative state in order and the inoperative state is maintained by the restricter. At the same time, the second shifter projection of the shifter disposed at the half of continuous recesses is pressed by the fourth control nub to be engaged with the restricter in order of pressing so that the shifters are switched to the inoperative state in order and the inoperative state is maintained. At that time, the shifters may be switched to the operative state or the inoperative state in a stepwise manner by staggering a timing of pressing by the first control nub and that by the second control nub and a timing of pressing by the third control nub and that by the fourth control nub. 
     From the following detailed description in conjunction with the accompanying drawings, the foregoing and other objects, features, aspects and advantages of the present invention will become readily apparent to those skilled in the art. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a perspective view of a dual bearing reel to which an embodiment of the present invention is applied; 
     FIG. 2 is its cross-sectional view; 
     FIG. 3 is an enlarged cross-sectional view of a centrifugal braking mechanism; 
     FIG. 4 is a side view when a first side cover is rotated; 
     FIG. 5 is a diagram corresponding to FIG. 3 when the first side cover is rotated; 
     FIGS. 6A and 6B are enlarged plan views showing a switching of a state of a shifter; 
     FIG. 7 is partial cross sectional view of a centrifugal braking mechanism according to a second embodiment; 
     FIG. 8 is a front elevational view of a centrifugal braking mechanism according to the second embodiment; 
     FIGS. 9A and 9B are diagrams corresponding to FIG. 6 showing the second embodiment; 
     FIG. 10 is a diagram corresponding to FIG. 8 showing a third embodiment; 
     FIGS. 11A and 11B are diagrams corresponding to FIG. 6 showing the third embodiment; and 
     FIGS. 12A and 12B are diagrams corresponding to FIG. 6 showing a modification of the third embodiment. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Overall Configuration 
     In FIG. 1, a dual bearing reel according to an embodiment of the present invention is a low profile type reel for bait-casting. The reel includes a reel body  1 , a handle  2 , and a star drag  3  for adjusting drag. The handle  2  is provided for rotating a spool and is disposed at one side of the reel body  1 . The star drag  3  is disposed at the reel body  1  side of the handle  2 . 
     As shown in FIG. 2, the reel body  1  includes a frame  5 , a first side-cover  6   a,  and a second side-cover  6   b.  The first side-cover  6   a  and the second side-cover  6   b  are disposed at a respective side of the frame  5 . Also, the reel body  1  includes, as shown in FIG. 1, a front cover  7  for covering the front side and a thumb rest  8  for covering the top. A spool  12  for winding fishing line is rotatably and detachably provided in the reel body  1 . 
     The frame  5  includes a pair of side plates  5   a  and  5   b,  which are disposed opposing each other at a predetermined spacing, and a plurality of connecting members (not shown in figures), each of which connects the side plates  5   a  and  5   b.    
     The first side-cover  6   a  is pivotally attached to the frame  5  so as to be opened and closed with respect to the frame  5  so that the spool  12  may be attached and detached. As shown in FIG. 2, the first side-cover  6   a  includes a pivoting mechanism  34  and a locking mechanism  36  for an opening/closing operation. The pivoting mechanism  34  pivotally supports the first side-cover  6   a  in a movable manner in a direction away from the frame at a front portion of the frame  5 . The locking mechanism  36  is a mechanism for locking or unlocking the first side-cover  6   a  in its closing state. As shown in FIG. 3, the locking mechanism  36  includes an operation portion  37  which is attached to an opening  33  formed on the first side-cover  6   a  and a locking member  38  attached to the operation portion  37  in a movable manner in the back and forth directions. The operation portion  37  includes a main portion  37   a  rotatably attached to the opening  33  in a movable manner in the axial direction and an operation knob  37   b  pivotally attached to the main portion  37   a  around an axis in the radius direction. 
     The main portion  37   a  is a substantially cylindrical member and urged to a direction approaching to the first side-cover  6   a  by a coil spring  44 . A brake case  65  of a cylindrical shape having a bottom, which is a part of a centrifugal braking mechanism to be described later, is fixed to the main portion  37   a  by a screw. The brake case  65  is detachably attached to an opening  5   d  for attaching the spool formed on the side plate  5   a  by using a screw structure. 
     The screw structure includes a male screw portion  25  formed on an outer periphery surface of the brake case  65  and a female screw portion  26  which is formed on an inner periphery surface of the opening  5   d  and engaged with the male screw portion  25 . 
     The operation knob  37   b  is pivotally provided between a locking state in which it is accommodated in the main portion  37   a  shown in FIG. 2 and a unlocking state in which it projects from the main portion  37   a  shown in FIG. 5. A part of the operation knob  37   b  is engaged with the locking member  38 . 
     The locking member  38  is a member for locking the rotation of the main portion  37   a  so that the first side-cover  6   a  enters its closing state and does not open. A tip of the locking member  38  may be engaged with any of a plurality of recesses  33   b  which are formed at the opening  33  with a space between each other in the circumferential direction when it is placed at a locking position shown in FIG.  2 . When the locking member  38  is receded to a lock releasing position shown in FIG. 5, the engagement with the recess  33   b  is disengaged and the main portion  37   a  enters a rotatable state. The locking member  38  is urged by a coil spring  39  that is attached to the main portion  37   a.    
     As shown in FIG. 2, the spool  12  which is disposed in a direction orthogonal to the fishing rod, a level wind mechanism  15 , and a clutch lever  17  are disposed inside the frame  5 . The level wind mechanism  15  is provided for uniformly winding fishing line around the spool  12 . The clutch lever  17  may function as a thumb rest during a thumbing. A gear mechanism  18 , a clutch mechanism  13 , a clutch switching mechanism  19 , a drag mechanism  21 , and a casting control mechanism  22  are disposed in the space between the frame  5  and the second side-cover  6   b.  The gear mechanism  18  transmits a rotational force from the handle  2  to the spool  12  and the level wind mechanism  15 . The clutch switching mechanism  19  switches the clutch mechanism  13  in accordance with the operation of the clutch lever  17 . The casting control mechanism  22  adjusts a resistance force generated when the spool  12  rotates. Also, a centrifugal braking mechanism  23  that prevents backlash when casting fishing line is disposed between the frame  5  and the first side-cover  6   a.    
     The spool  12  has flange portions  12   a,  each of which has a plate shape, at both sides thereof and a spool body  12   b  of a cylindrical shape is provided between the flange portions  12   a.  Also, the spool  12  has a boss portion  12   c  of a cylindrical shape which is integrally formed with the spool body  12   b  at a substantially center position of the spool body  12   b  in the axial direction. The spool  12  may be fixed to the spool shaft  16  which penetrates through the boss portion  12   c,  in a non-rotatable manner by, for instance, a serration engagement. The fixing method is not limited to the serration engagement and various methods such as a key engagement and a spline engagement may be employed. The spool  12  may penetrate the opening  5   d  on the side plate  5   a.    
     The spool shaft  16  penetrates through the side plate  5   b  and extends outside the second side-cover  6   b.  The extended end of the spool shaft  16  is rotatably supported by a bearing  24   a  of a boss portion  6   c  which is provided with the second side-cover  6   b.  Also, a bearing  24   b  in the centrifugal braking mechanism  23  rotatably supports the other end of the spool shaft  16 . The bearings  24   a  and  24   b  are shield ball bearings. 
     The right end of a large diameter portion  16   a  of the spool shaft  16  is disposed at the penetration portion of the side plate  5   b  and an engaging pin  16   b  which forms a part of the clutch mechanism  13  is fixed thereto. The engaging pin  16   b  penetrates the large diameter portion  16   a  along the diameter direction and both ends thereof project in the radius directions. 
     The gear mechanism  18  includes a handle shaft  30 , a main gear  31 , and a pinion gear  32 . The main gear  31  is coupled to a handle shaft  30 . The pinion gear  32  has a cylindrical shape and is engaged with the main gear  31 . The position of the handle shaft  3  of the gear mechanism  18  is lower than a conventional position in order to lower the height of the thumb rest  8 . For this reason, the lower portion of the side plate  5   b  and that of the second side-cover  6   b  for accommodating the gear mechanism  18  are positioned lower than the lower portion of the side plate  5   a  and that of the first side-cover  6   a.    
     As shown in FIG. 2, the pinion gear  32  is a cylindrical member that extends from outside of the side plate  5   b  to inside thereof and the spool shaft  16  penetrates the center portion thereof. The pinion gear  32  is coupled to the spool shaft  16  in a movable manner in the axial direction. The left end portion (in FIG. 2) of the pinion gear  32  is rotatably supported by a bearing  43  with respect to the side plate  5   b  in a movable manner in the axial direction. The bearing  43  is also a shield ball bearing. 
     The pinion gear  32  includes a teeth portion  32   a,  an engaging portion  32   b  and a compressed portion  32   c.  The teeth portion  32   a  is formed on a right-hand side outer periphery portion in FIG.  2  and engaged with the main gear  31 . The engaging portion  32   b  is formed at the other side. The compressed portion  32   c  is disposed between the teeth portion  32   a  and the engaging portion  32   b.  The engaging portion  32   b  includes a channel notch formed on an end surface of the pinion gear  32  in the diameter direction and an engaging pin  16   b  which penetrates the spool shaft  16  and fixed is engaged therewith. In this embodiment, when the engaging portion  32   b  is disengaged from the engaging pin  16   b  of the spool shaft  16  as the pinion gear  32  moves outwardly, the rotational force of the handle shaft  30  is not transmitted to the spool  12 . The engaging portion  32   b  and the engaging pin  16   b  constitute the clutch mechanism  13 . When the engaging pin  16   b  is engaged with the engaging portion  32   b,  twisted deformation is reduced and a torque transmission efficiency is increased since the torque is directly transmitted to the spool shaft  16  from the pinion gear  32  having a larger diameter than the spool shaft  16 . 
     As shown in FIG. 2, the clutch lever  17  is disposed at the back of the spool  12  between the pair of the side plates  5   a  and  5   b.    
     The clutch switching mechanism  19  includes a clutch yoke  40  as shown in FIG.  2 . The clutch switching mechanism  19  is disposed at outer peripheral side of the spool shaft  16  and supported by two pins  41  (only one in shown in the figure) in a movable manner parallel to the axial center of the spool shaft  16 . Also, the clutch yoke  40  includes an engaging portion  40   a  that engages with the compressed portion  32   c  of the pinion gear  32  at the center portion thereof. Moreover, a spring  42  is disposed at an outer periphery of each of the pins  41  for supporting the clutch yoke  40  between the clutch yoke  40  and the second side-cover  6   b.  The clutch yoke  40  is always urged towards inside by the spring  42 . 
     In this configuration, the pinion gear  32  is located at an inner clutch engaging position in a normal state so that the engaging portion  32   b  is engaged with the engaging pin  16   b  of the spool shaft  16  to be a clutch-on state. On the other hand, when the pinion gear  32  is moved outwardly by the clutch yoke  40 , the engaging portion  32   b  is disengaged from the engaging pin  16   b  to be a clutch-off state. 
     The drag mechanism  21  includes a drag washer  45  and a pressing plate  46 . The main gear  31  presses the drag washer  45 . The pressing plate  46  presses the drag washer  45  against the main gear  31  with a predetermined force by a rotational operation of the star drag  3 . 
     The casting control mechanism  22  includes a plurality of drag washers  51  and a braking cap  52 . The plurality of drag washers  51  is disposed so as to hold both ends of the spool shaft  16 . The braking cap  52  adjusts a holding force of the drag washers  51  holding the spool shaft  16 . The drag washer  51  at the left hand side is disposed in the brake case  65 . 
     Centrifugal Braking Mechanism Configuration 
     As shown in FIGS. 3 and 5, the centrifugal braking mechanism  23  includes a brake element  68 , a rotor  66 , and a plurality (for instance, six) of shifters  67 . The brake element  68  is fixed to the brake case  65 . The rotor  66  is disposed at inner peripheral side of the brake element  68  so as to be concentric with the brake element and fixed to the spool shaft  16 . The shifters  67  are attached to the rotor  66  in a movable manner in the radius direction. 
     The brake element  68  is a thin cylindrical member made of, for instance, copper alloy and fixed to an inner periphery surface of the brake case  65 . The brake element  68  has a braking surface  68   a  of a cylindrical shape at the inner periphery surface thereof. The brake case  65  is a short cylindrical member having a bottom and a bearing accommodating portion  65   a  of a cylindrical shape which projects inwardly is formed on the inner bottom surface thereof. The bearing  24   b  for supporting the spool  16  is disposed at the inner peripheral side of the bearing accommodating portion  65   a  and the drag washer  51  of the casting control mechanism  22  is attached thereto. 
     The rotor  66  includes a boss portion  66   a,  a cylindrical portion  66   b,  and a circular plate portion  66   c.  The boss portion  66   a  is fixed to the spool shaft  16 . The cylindrical portion  66   b  extends to an outer peripheral side of the bearing accommodating portion  65   a  from the boss portion  66   a.  The circular plate portion  66   c  has a thick ring shape and protrudes outwardly in the radius direction from an outer periphery surface of an extending end of the cylindrical portion  66   b.    
     As shown in FIG. 4, for instance, six, guide recesses  70  are formed at the outer periphery portion of the circular plate portion  66   c  with an equal space between each other in the circumferential direction. The guide recesses  70  accommodate the shifters  67  and switch the state of the shifters  67  to the operative state in which they may make contact with the brake element  68  from the inoperative state in which they cannot make contact with the brake element  68  or vice versa. A guide shaft  73  for guiding the respective shifter  67  is disposed at the bottom of the respective guide recess  70  radially in the radius direction. The shifter  67  is attached to the corresponding guide shaft  73  in a movable manner in the axial direction. 
     As shown in FIGS. 4 and 6A, first and second protuberant linear projections  71  and  72  are formed at wall surfaces  70   a  and  70   b,  which opposed to each other, of the guide recess  70 . The first linear projection  71  is formed at the wall surface  70   a  located at the right hand side in FIG. 6 from the bottom portion of the guide recess  70  to its opening end. The first linear projection  71  is a guide which non-rotatably guides the shifter  67  in a movable manner in the axial direction to a position at which a contact with the brake element  68  is possible. The second linear projection  72  is formed at the wall surface  70   b  shown in the left hand side in FIG. 6A with a little length from the bottom of the guide recess  70 . The second linear projection  72  is a restricter for restricting the shifter  67  not to make contact with the brake element  68 . The second linear projection  72  has a length by which the shifter  67  cannot make contact with the brake element  68  and its end portion  72   c  at an outward side in the spool radius direction is closed at the same position as the end portion of the second linear projection  72 . As a result, when a second shifter projection  67   c  (to be described later) is engaged with the second linear projection  72 , the shifter  67  makes contact with the end portion  72   c  and cannot make contact with the brake element  68 . 
     The shifters  67  are members of substantially a cylindrical shape made of a synthetic resin. The shifters  67  are attached to the guide shafts  73  in a slidable manner in the radius direction and make contact with the brake element  68  by a centrifugal force generated by the rotation of the spool  12 . Each of the shifters  67  includes a main portion  67   a  of a cylindrical shape, a first shifter projection  67   b,  and the second shifter projection  67   c.  The guide shaft  73  guides the main portion  67   a.  The first shifter projection  67   b  is integrally formed with the main portion  67   a  at a middle portion thereof in the axial direction. The second shifter projection  67   c  is integrally formed with the main portion  67   a  at an inner side of its end portion in the axial direction. The shape of the first shifter projection  67   b  and that of the second shifter projection  67   c  are the same and they are disposed with an interval between each other in the axial direction and the circumferential direction. Both of the shifter projections  67   b  and  67   c  project outwardly in the radius direction from the main portion  67   a  so that they may be engaged with the first and the second linear projections  71  and  72  which are formed at the guide recess  70 . Recessed engaging portions  67   d  and  67   e  which are engaged with the first and the second linear projections  71  and  72 , respectively, are formed at end portions thereof. The length of the second linear projection  72  is adjusted so that it becomes longer than the thickness of the second shifter projection  67   c  and does not allow the shifter  67  make contact with the brake element  68 . The switching mechanism  69  is formed by the linear projections  71  and  72  and shifter projections  67   b  and  67   c.    
     When the first shifter projection  67   b  is engaged with the first linear projection  71  (FIG.  6 B), the shifter  67  may make contact with the brake element  68  and this state is called the operative state. Also, when rotated around the guide shaft and the second shifter projection  67   c  is engaged with the second linear projection  72  (FIG.  6 A), the shifter  67  is engaged with the end portion  72   c  of the second linear projection  72  and cannot make contact with the brake element  68 . This state is the inoperative state. As mentioned above, the number of the shifters  67  that may make contact with the brake element  68  may be adjusted by switching the shifters  67  to the operative state or to the inoperative state. Also, since the state of the shifters  67  is switched by the rotation around the guide shaft, the state of the shifters  67  may be switched by using a direction different from the moving direction of the shifters  67  during a braking operation. For this reason, a large force is not required for a switching operation in the rotary direction and a switching operation may be carried out with a light force. Since the switching operation can be performed with a small force, each step of the switching operation may be carried out all at once by using another member instead of doing it manually one by one. Moreover, since the direction of the operation is the rotary direction and not the radius direction of the spool, the simultaneous operation is easy to carry out. 
     Braking Force Adjustment 
     When the braking force is adjusted, the opening  5   d  in the side plate  5   a  is exposed by opening the first side-cover  6   a.    
     In order to open the first side-cover  6   a,  the operation knob  37   b  is firstly raised to enter an unlocking state from a locking state shown in FIG.  2 . When the operation knob  37   b  is entered to the unlocking state, the locking member  38  is pushed by the operation knob  37   b  and moved to an unlocking position against an urging force of the coil spring  39 . When the locking member  38  is moved to the unlocking state, its end portion is disengaged from the recess  33   b  of the opening  33  and the main portion  37   a  becomes rotatable. 
     When the operation knob  37   b  is rotated in this state, the brake case is rotated together with the main portion  37   a  as shown in FIG.  5  and the engagement between the screw portions  25  and  26  is disengaged to release the engagement between the brake case  65  and the side plate  5   a.  When the engagement between the brake case  65  and the side plate  5   a  is disengaged, the brake case  65  is moved outwardly together with the main portion  37   a  by the coil spring  44 . Simultaneously, the first side-cover  6   a  supported by the pivoting mechanism  34  is moved in a direction away from the side plate  5   a.  When the brake case  65  is completely separated from the side surface of the side plate  5   a,  the first side-cover  6   a  is separated from the reel body  1  and pivoted to a releasing position shown in FIG. 4 around an axis of the pivoting mechanism  34  due to the weight itself. Accordingly, the opening  5   d  is exposed to outside and the rotary state of the shifters  67  may be easily confirmed by naked eyes. In FIG. 4, for instance, only the shifter at upper side are engaged with the second linear projection  72  and other shifters  67  are engaged with the first linear projection  71 . Thus, only one of the shifters is in the inoperative state and other five shifters  67  are in the operative state. Since the states of shifters  67  are switched by rotating the shifters  67  in this manner, the two states may be determined immediately. 
     The adjustment of the brake element is carried out by, for example, pushing one of the shifter projections  67   b  and  67   c  with fingers so that the shifters  67  rotate around the guide shaft to switch to operative state or inoperative state. When the shifter  67  is rotated so that the first shifter projection  67   b  is directed to the first linear projection  71 , the first shifter projection  67   b  is elastically deformed and engaged with the first linear projection  71 . As a result, the shifter  67  enters the operative state and this state is maintained. Also, when the second shifter projection  67   c  is directed to the second linear projection  72 , the second shifter projection  67   c  is elastically deformed and engaged with the second linear projection  72 . As a result, the shifter  67  enters the inoperative state and this state is maintained. 
     When the adjustment of the braking force is completed, the first side-cover  6   a  is closed. At that time, the first side-cover  6   a  is manually rotated to a closing side and then the operation knob  37   b  is pushed to insert the brake case  65  in the opening  5   d.  The operation knob  37   b  is rotated in the tightening direction which is opposite to the releasing direction in a state in which the end portion of the brake case  65  is in contact so that the screw portions  25  and  26  are engaged. Then, the brake case  65  is coupled to the opening  5   d.  After that, the operation knob  37   b  is pivoted from the unlocking position to the locking position and the locking member is engaged with the recess  33   b.  In this manner, the first side-cover  6   a  is maintained in its closing state. 
     In this embodiment, since the state of the shifters  67  are switched by rotating the shifters  67 , the state of the shifters  67  can be confirmed immediately. For this reason, the two states of the shifters  67  is easily determined and the braking force may be adjusted quickly. Also, since the state of the shifters  67  may be switched by using a direction different from the moving direction of the shifters  67  during a braking operation, a large force is not required for a switching operation in the rotary direction and the switching operation may be carried out with a small force. 
     Second Embodiment 
     In the embodiment just described the two states are switched between by manually pressing on the shifters  67  one by one. But a dual-bearing reel centrifugal braking device according to the present invention may be configured providing a shifter control mechanism  80  as shown in FIG. 8 that one by one enables shifters  167  to be switched in sets. 
     In FIGS. 7 and 8, guide recesses  170  are arranged circumferentially spaced in the outer periphery of disk  166   c  on rotor  166 , but are not as in the first embodiment arranged at even spacing. That is, from the guide recess  170  uppermost in the FIG. 7 rotor  166  clockwise among the total of six guide recesses  170  disposed, to the third guide recess  170 , the recesses are arranged at a 60-degree spacing, for example; and the third guide recess  170  and fourth guide recess  170  are arranged at a 90-degree spacing. Further, the fourth through sixth guide recesses  170  are arranged at a 60-degree spacing. Arranging the guide recesses  170  to differ the spacing makes the timing at which the shifters  167  switch constant. 
     First channel notches  171   a  are formed in the corner of the clockwise, downstream-ward lateral wall of the guide recesses  170  and the outward face (lateral surface facing the brake case  65 ), and second channel notches  172   a  are formed in the upstream-ward corner. The first channel notches  171   a  are formed from the base of the guide recesses  170  to the ends opening on the rotor  166 , and guide the shifters  167  for contact with the brake element  68 . The second channel notches  172   a  are not formed as far as the open ends but are midway to them in length. Also, the length of the first through the third of the second channel notches  172  is shorter than that of the fourth through the sixth of the second channel notches  172 . The reason for this will be explained in detail later. 
     The shifters  167  are members of substantially a cylindrical shape made of a synthetic resin. The shifters  167  are attached to the guide shafts  173  in a slidable manner in the radius direction and make contact with the brake element  68  by a centrifugal force generated by the rotation of the spool  12 . Each of the shifters  167  includes a main portion  167   a  of a cylindrical shape, a first shifter projection  167   b,  and the second shifter projection  167   c.  The main portion  167   a  is guided by the guide shaft  173 . The first shifter projection  167   b  is integrally formed with the main portion  167   a  at a middle portion thereof in the axial direction. The second shifter projection  167   c  is integrally formed with the main portion  167   a  at an inner side of its end portion in the axial direction. The shape of the first shifter projection  167   b  and that of the second shifter projection  167   c  are the same and they are disposed with an interval between each other in the axial and the circumferential directions. In addition, as shown in FIG. 9B there is a small interval between the first channel notch  171   a  and the shifter projections  167   b  and  167   c  so that the movement of the shifter  167  in the spool radius direction is made smooth when the shifter projections  167   b  and  167   c  are engaged with the first channel notch  171   a.    
     In this embodiment, the shifters  167  attached to the first to the third guide recesses  170  and the shifters  167  attached to the fourth to the sixth guide recesses  170  have a structure in which the two shifter projections  167   b  and  167   c  are disposed as a mirror image relationship. The shifter projections  167   b  and  167   c  of the first to third shifters  167  project outwardly in the radius direction from the main portion  167   a  so that they may be engaged with the first and the second channel notches  171   a  and  172   a,  respectively. The shifter projections  167   b  and  167   c  of the fourth to sixth shifters  167  project outwardly in the radius direction from the main portion  167   a  so that they may be engaged with the second and the first channel notches  172   a  and  171   a,  respectively. 
     The reason why the length of the first to third second channel notches  172   a  is different from that of the fourth to six channel notches  172   a  is because the second shifter projection  167   c  which projects from an inside end portion of the main portion  167   a  in the axial direction engages with the first to third second channel notches  172   a  and the first shifter projection  167   b  which projects from a middle portion of the main portion  167   a  in the axial direction engages with the fourth to sixth second channel notches  172   a.  That is, since the first shifter projection  167   b  is disposed more outwardly in the radius direction with respect to the second shifter projection  167   c,  it is necessary to increase the length of the second channel notches  172   a.  In other words, the lengths are different so that the second shifter projection  167   c  is engaged with the first to third second channel notches  172   a  to prohibit a contact of the shifters  167  with the brake element  68  and that the first shifter projection  167   b  is engaged with the fourth to sixth second channel notches  172   a  to prohibit a contact of the shifters  167  with the brake element  68 . The switching mechanism  169  is formed by the channel notches  171   a  and  172   a  and shifter projections  167   b  and  167   c.  In this embodiment, if one of the shifter projections  167   b  and  167   c  is engaged with one of the channel notches  171   a  and  172   a,  the state thereof is not maintained. 
     As shown in FIG. 8, the shifter controlling mechanism  80  includes an adjustment member  81 , a first arc projection  82 , and a second arc projection  83 . The adjustment member  81  has a circular plate shape and is attached to the boss portion  66   a  of the rotor  166 . The first arc projection  82  has a half arc shape and is formed at a side surface of the adjustment member  81  at a position capable of opposing to the first shifter projection  167   b.  The second arc projection  83  has a half arc shape and is formed at a position that is opposite to the first arc projection  82  and capable of opposing to the first shifter projection  167   b.    
     The adjustment member  81  may relatively rotate around the spool shaft with respect to the rotor  166  and may rotate together with it while maintaining a relative rotary position. The adjustment member  81  is rotatably attached to the boss portion  166   a  and pressed against the cylindrical portion  166   b  by a snap ring  85  attached to the boss portion  166   a  via an O-ring  84 . In this manner, the adjustment member  81  and the rotor  166  may rotate together as well as relatively rotate with respect to each other. The adjustment member  81  includes a tubular portion  81   a  and a circular plate portion  81   b.  The tubular portion  81   a  extends outwardly in the spool axis direction from the boss portion  166   a  along the cylindrical portion  166   b.  The circular plate portion  81   b  is disposed as to be opposed to the disk  166   c  from an outer periphery surface of an end portion of the tubular portion  81   a.  First and second arc projections  82  and  83  are formed on a side surface opposed to the disk  166   c  of the circular plate portion  81   b  so as to project towards the disk  166   c.    
     As shown in FIG. 9A, the first arc projection  82 , when the shifters  167  are in their inoperative state, presses the three first shifter projections  167   b  of the first to the third guide recesses  170  in that order by an end portion thereof by the rotation of the adjustment member  81  in a clockwise direction in FIG. 7 so that the first shifter projections  167   b  are engaged, in that order, with the first channel notches  171   a  which are guides. In this manner, the state of the shifters  167  is switched from the inoperative state to the operative state and the operative state of the switched shifters  167  is maintained by restricting the first shifter projection  167   b  by an opposing surface  82   a  of the first arc projection  82 . 
     Also, the first arc projection  82 , when the shifters  167  are in their operative state, presses the three first shifter projections  167   b  of the sixth to the fourth guide recesses  170  in that order by another end portion thereof by the rotation of the adjustment member  81  in a counterclockwise direction in FIG. 7 so that the first shifter projections  167   b  are engaged, in that order, with the second channel notches  172   a  which are restricting portions. In this manner, the state of the shifters  167  is switched from the operative state to the inoperative state and the inoperative state of the switched shifters  167  is maintained by restricting the first shifter projection  167   b  by the opposing surface  82   a.    
     Similar to the first arc projection  82 , the second arc projection  83 , when the shifters  167  are in their inoperative state, presses the three second shifter projections  167   c  of the fourth to the sixth guide recesses  170  in that order by an end portion thereof by the rotation of the adjustment member  81  in a clockwise direction in FIG. 7 so that the second shifter projections  167   c  are engaged, in that order, with the first channel notches  171   a  which are guides. In this manner, the state of the shifters  167  is switched from the inoperative state to the operative state and the operative state of the switched shifters  167  is maintained by restricting the second shifter projection  167   c  by an opposing surface  83   a  of the second arc projection  83 . 
     Also, as shown in FIG. 9B, the second arc projection  82 , when the shifters  167  are in their operative state, presses the three second shifter projections  167   c  of the third to the first guide recesses  170  in that order by another end portion thereof by the rotation of the adjustment member  81  in a counterclockwise direction in FIG. 7 so that the second shifter projections  167   c  are engaged, in that order, with the second channel notches  172   a  which are restricting portions. In this manner, the state of the shifters  167  is switched from the operative state to the inoperative state and the inoperative state of the switched shifters  167  is maintained by restricting the second shifter projection  167   b  by the opposing surface  83   a.    
     In addition, the guide recesses  170  are disposed with different space between each other as mentioned above so that the timing of the first arc projection  82  presses the first shifter projections  167   b  of the first to the third shifters  167  is shifted about 30 degrees in phase angle from the timing of the second arc projection  82  presses the second shifter projections  167   c  of the fourth to the sixth shifters  167 . As a result, the switching order from the inoperative state to the operative state becomes 1-4-2-5-3-6 and the switching order from the operative state to the inoperative state becomes 6-3-5-3-4-1 to achieve a switching operation of the shifters  167  while maintaining an excellent balance in a stepwise manner. 
     In the centrifugal braking mechanism  123  having the above mentioned structure, the state of the shifters  167  may be switched at once by, for instance, holding the spool  12  by his/her left hand while the first side-cover  6   a  is opened and rotating the adjustment member  81  by his/her right hand. After the switching operation, if the fist side-cover  6   a  is closed and cast, the adjustment member  81  rotates together with the spool  12  and the rotor  166 , and the phase of the rotor  166  does not change. Accordingly, the state achieved after the switching operation is maintained. When the shifters  167  make contact with the brake element  68  by a centrifugal force, the spool  12  is braked by a braking force which corresponds to the number of the shifters  167  that make contact and, hence, backlash is unlikely to arise. 
     Third Embodiment 
     Although the switching operation of the shifters  167  and the maintenance of the state thereof are carried out by using the two arc projections  82  and  83  in the above second embodiment, the maintenance of the state is performed by the engagement of shifter projections with channel notches in the third embodiment. Since there is no need to maintain the state by using a side surface of the projection, scattered four control nubs are provided instead of the arc projections and only the switching operation of the state of the shifters  267  is carried out by the control nubs. 
     In FIGS. 10,  11 A and  11 B, the guide recesses  270  are disposed at an outer periphery portion of the circular plate portion  266   c  of the rotor  266  with an equal interval between each other. That is, a total of six guide recesses  270  are provided from the top of the rotor  66  in a clockwise direction, for instance, at a 60 degree angle for each other. 
     A first channel notch  271   a  is formed at a corner of a side wall of the guide recess  270  at a downstream side in a clockwise direction and an outer side surface (a side surface facing the brake case  65 ), and a second channel notch  272   a  is formed at a corner at an upstream side. The first channel notch  271   a  is formed from a bottom of the guide recess  270  to an opening end of the rotor  266  and guides the shifter  267  to the brake element  68  in a manner capable of making contact with it. The second channel notch  272   a  is not formed to the opening end and has a length of about half size. Also, the length of each of the first to the third second channel notches  272  is shorter than that of the fourth to the sixth second channel notches  272 . The reason for this is the same as that described in the second embodiment. Contacting surfaces  271   b  and  272   b  of the channel notches  271   a  and  272   a  are slightly hollowed in order to maintain the states of the shifter projections  267   b  and  267   c  of the shifters  267 . 
     The shifters  267  are members of substantially a cylindrical shape made of a synthetic resin and includes a main portion  267   a  of a cylindrical shape, a first shifter projection  267   b,  and the second shifter projection  267   c,  each of which has the same structure as described in the second embodiment. An end portion of each of the shifter projections  267   b  and  267   c  is rounded so as to fit to a hollow of the channel notches  271   a  and  272   a.  Due to the engagement of the round shape with the hollow and the fact that the shape of the end portion of the shifter projections  267   b  and  267   c  is not concentric with the pivoting axis of the shifters  267 , the shifter projections  267   b  and  267   c  are engaged with the channel notches  271   a  and  272   a  by utilizing the difference in the diameter and the elasticity thereof when pivoted and the state thereof is maintained. In this embodiment, also, the shifters  267  attached to the first to the third guide recesses  270  and the shifters  267  attached to the fourth to the sixth guide recesses  270  have a structure in which the two shifter projections  267   b  and  267   c  are disposed as a mirror image relationship. The shifter projections  67   b  and  67   c  of the first to the third shifters  267  protrude outwardly in the radius direction from the main portion  267   a  so that they may be engaged with the first and the second channel notches  271   a  and  272   a,  respectively. The shifter projections  267   b  and  267   c  of the fourth to the sixth shifters  267  protrude outwardly in the radius direction from the main portion  267   a  so that they may be engaged with the second and the first channel notches  272   a  and  271   a,  respectively. In addition, as shown in FIG. 11B, there is a small interval between the first channel notch  271   a  and the shifter projections  67   b  and  67   c  so that the movement of the shifter  267  in the spool radius direction is made smooth when the shifter projections  267   b  and  267   c  are engaged with the first channel notch  271   a.    
     The shifter controlling mechanism  280  includes an adjustment member  81  which has the same structure as in the second embodiment shown in FIG.  8  and first to fourth control nubs  91  to  94  which are formed on a side surface of the adjustment member  81 . 
     The first control nub  91  is formed at a position at which it may oppose to the first shifter projection  267   b.  As shown in FIG. 11A, the first control nub  91 , when the shifters  267  are in their inoperative state, presses the first shifter projections  267   b  of the first to the third guide recesses  270  in that order by the rotation of the adjustment member  81  in a clockwise direction so that the first shifter projections  267   b  are engaged, in that order, with the first channel notches  271   a  which are guides. In this manner, the state of the shifters  267  is switched from the inoperative state to the operative state. The operative state of the switched shifters  267  is maintained by engaging the first shifter projection  67   b  with the first channel notch  271   a.    
     The second control nub  92  is disposed at a side surface of the adjustment member  81  at a position at which it may oppose to the second shifter projection  267   c  and which is located at an upper stream side in a clockwise direction with respect to a symmetrical position formed by the first control nub  91  and the spool shaft center. More specifically, the second control nub  92  is disposed at a 150 degrees angle with respect to the first control nub  91 . The second control nub  92  presses the second shifter projections  267   c  of the fourth to the sixth guide recesses  270  in that order by the rotation of the adjustment member  81  in a clockwise direction so that the second shifter projections  267   c  are engaged, in that order, with the first channel notches  271   a.  In this manner, the state of the shifters  267  is switched from the inoperative state to the operative state. The operative state of the switched shifters  267  is maintained by engaging the second shifter projection  267   c  with the first channel notch  271   a.    
     The third control nub  93  is disposed at a position located at a downstream side in a clockwise direction with respect to the second control nub  92  with the same radius position as the first control nub  91 . The third control nub  93 , when the shifters  267  are in their operative state, presses the first shifter projections  267   b  of the sixth to the fourth guide recesses  270  in that order by the rotation of the adjustment member  81  in a counterclockwise direction so that the first shifter projections  267   b  are engaged, in that order, with the second channel notches  272   a.  In this manner, the state of the shifters  267  is switched from the operative state to the inoperative state. The inoperative state of the switched shifters  267  is maintained by engaging the first shifter projection  267   b  with the second channel notch  272   a.    
     The fourth control nub  94  is disposed at a position located at a downstream side in a clockwise direction with respect to the first control nub  91  with the same radius position as the second control nub  92 . The fourth control nub  94  is disposed at a 150 degrees angle with respect to the third control nub  93 . As shown in FIG. 11B, the fourth control nub  94  presses the second shifter projections  267   c  of the third to the first guide recesses  270  in that order by another end portion thereof by the rotation of the adjustment member  81  in a counterclockwise direction so that the second shifter projections  267   c  are engaged, in that order, with the second channel notches  272   a.  In this manner, the state of the shifters  267  is switched from the operative state to the inoperative state. The inoperative state of the switched shifters  267  is maintained by engaging the second shifter projection  267   c  with the second channel notch  272   a.    
     In addition, the guide recesses  270  are disposed with equal spaces between each other as mentioned above and the first control nub  91  and the second control nub  92 , the third control nub  93  and the fourth control nub  94  are disposed at a 150 degrees angle with each other so that the timing of the first control nub  91  presses the first shifter projections  267   b  of the first to the third shifters  267  is shifted 30 degrees in phase angle from the timing of the second control nub  92  presses the second shifter projections  267   c  of the fourth to the sixth shifters  267 . As a result, the switching order from the inoperative state to the operative state becomes 1-4-2-5-3-6 and the switching order from the operative state to the inoperative state becomes 6-3-5-3-4-1 to achieve a switching operation of the shifters  267  while maintaining an excellent balance in a stepwise manner. Also, since the guide recesses  270  are disposed with the same interval between each other maintaining an excellent balance, the balance of rotation is not easily disturbed. 
     In the centrifugal braking mechanism  223  having the above mentioned structure, the state of the shifters  267  may be switched at once by, for instance, holding the spool by his/her left hand while the first side-cover  6   a  is opened and rotating the adjustment member  81  by his/her right hand. After the switching operation, if the fist side-cover  6   a  is closed and cast, the adjustment member  81  rotates together with the spool  12  and the rotor  266 , and the phase of the rotor  266  does not change. Accordingly, the state achieved after the switching operation is maintained. When the shifters  267  make contact with the brake element  68  by a centrifugal force, the spool  12  is braked by a braking force which corresponds to the number of the shifters  267  that make contact with the brake element  68  and, hence, backlash is not liable to occur. 
     Other Embodiments 
     (a) Although a projecting portion of the shifters is engaged with the guide recess which is disposed at a side wall of the rotor in the previous three embodiment, the present invention is not limited to this structure. For instance, the guide shafts may be formed by rod-shape members having different cross sectional shapes so that the shifters can move in the guide shaft direction only when a certain rotational phase appears and then, when rotates, the shifters are elastically deformed to be engaged with the guide shaft. 
     (b) Although the first and the second linear projections  71  and  72  are provided with the guide recess  70  and the recessed engaging portion  67   d  and  67   e  are provided with the first and the second shifter projections  67   b  and  67   c  of the shifters  67  in the above first embodiment, a linear channel notch may be provided in the guide recess and a protuberant portion which is engaged with the linear channel notch may be provided with the shifters. 
     (c) Although the state of the shifter  267  is maintained by the dovetailing engagement of the channel notches  271   a  and  272   a  with the shifter projections  267   b  and  267   c  in the above third embodiment, the operative state and the inoperative state may be maintained by the guide shafts  373 . For instance, as shown in FIGS. 12A and 12B, the guide shafts  373  may be formed by using a rod-shape member having a foursided figure cross section so that the shifter  367  is difficult to be pivoted but may be pivoted by being pressed by the control nubs  191 - 194 . 
     According to the present invention, a switching operation may be carried out by changing a rotational position of the shifter around the guide shaft. Since the rotational direction around the guide shaft is different from the moving direction of the shifter (i.e., the axial direction of the guide shaft), a large force is not necessary for the switching operation in the rotary direction and the operation may be carried out by using a small force. Since the switching operation may be carried out with a small force, it may be performed all at once by using another member instead of performing it one by one manually. Moreover, since the operation direction is the rotary direction, not the radius direction of the spool, the switching operation is easily performed all at once. 
     While only selected embodiments have been chosen to illustrate the present invention, to those skilled in the art it will be apparent from this disclosure that various changes and modifications can be made herein without departing from the scope of the invention as defined in the appended claims. Furthermore, the foregoing description of the embodiments according to the present invention is provided for illustration only, and not for the purpose of limiting the invention as defined by the appended claims and their equivalents.