Dual-bearing reel centrifugal braking device

A centrifugal braking mechanism of a dual-bearing reel for braking under centrifugal force the reel spool fitted rotatively in the body of the reel. The centrifugal braking mechanism achieves simple adjustment of braking force, by which adjustment distinctly perceptible differences in braking force are gained. The centrifugal braking mechanism includes shifting members (52), a brake element (53), an urging member (54), a restricting member (55), and an urging force adjusting mechanism (56). The shifting members are provided on a rotary member (51) that rotates with the spool, and are shifted under centrifugal force arising from rotation of the spool. The brake element is non-rotatably provided on, and permitted to shift axially with respect to, the reel body. The brake element comes into contact with the shifting members shifted under centrifugal force. The urging member urges the brake element towards the shifting members, which movement is controlled by the restricting member. The urging force adjusting mechanism adjusts the urging force of the urging member.

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 the spool
 rotatively provided in the reel body.
 2. Description of Related Art
 In dual-bearing reels referred to as a bait reels, utilized mainly for lure
 fishing, generally braking force is made to act on the spool so that
 backlash, wherein the rotational speed of the spool when casting is faster
 than the line wind-out speed, does not occur. Centrifugal braking devices
 that employ centrifugal force developing from spool rotation to brake the
 spool are an example of this type of braking mechanism.
 Centrifugal braking devices of this class are in general provided with: a
 plurality of shifting members fitted to permit radial shifting at
 circumferentially spaced intervals on the spool, or on a rotary member
 that rotates linked with the spool; and a cylindrical brake element fixed
 to the body of the reel, disposed at the outer peripheral ends of the
 shifting members, enabling contact with the shifting members.
 In this centrifugal braking device, when the spool rotates, the shifting
 members travel radially outward under centrifugal force and contact on the
 braking surface to brake the spool. Since the centrifugal force increases
 in proportion to the square of the rotational speed of the spool, the
 spool rotating at low speeds when reeling-in line does not make the
 braking force very large; the spool rotating at high speeds when casting
 does make it large. Therefore, the centrifugal braking device
 characteristically has small resistance while line is reeled in, and large
 braking force with which backlash is prevented when casting.
 In these centrifugal braking devices, the number of shifting members that
 travel radially is varied in order to adjust the braking force. Each of
 the shifting members therefore is provided with a lock mechanism that
 switches the shifting members into an operating position in which they can
 come into contact with the brake element, and into a non-operating
 position in which they cannot make contact.
 When lure fishing, for instance, with a bait reel having this type of
 centrifugal braking device, wherein lures of different weights such as
 plugs and worms are used, if the braking force is constant the flight
 distance when casting fluctuates depending on the lure weight. Thus,
 adjusting the braking force according to weight is desirable wherein lures
 of differing weights are used.
 With the conventional centrifugal braking devices noted above, since the
 shifting members travel radially, in the same direction as the centrifugal
 force acts, large braking forces are gained. Nevertheless, the braking
 force has to be adjusted by increasing/decreasing the number of shifting
 members that can contact the brake element by means of the lock mechanisms
 with which the shifting members are equipped. Instances therefore arise in
 which to adjust the braking force it is necessary to operate a number of
 the lock mechanisms, which complicates braking force adjustment.
 Therein, Japanese Laid-Open Pat. App. No. 10-304798 discloses a centrifugal
 braking device in which braking force adjustment can be
 single-operation-regulated by a dial exposed on the exterior of the body
 of the reel.
 The centrifugal braking device is provided with: a rotary member that
 rotates linked with the spool; a plurality of shifting members disposed
 radially on the rotary member and fitted to permit pivoting on the rotary
 member; a brake element provided on the body of the reel to allow it
 reciprocating travel in the spool axle direction to enable it to abut on
 the tips of the shifting members; and a shifting mechanism having a dial
 that is turned to reciprocatingly shift the brake element. Contact
 portions are provided on the tips of the shifting members for contact with
 the brake element. A ring-shaped brake shoe that comes into contact with
 the contact portions is provided on the side face of the outer
 circumferential side of the brake element, which is a disk-shaped member.
 Turning the dial on the shifting mechanism shift s the brake element
 reciprocatingly in the spool axle direction.
 When the spool rotates in the above-noted conventional centrifugal braking
 device, centrifugal force acts on the shifting members, which pivots the
 shifting members turning outward in the spool axial direction. They then
 come into contact with the brake shoe, which brakes the spool. Braking
 force can be single-operation adjusted by turning the dial to shift the
 brake element in the spool axle direction, which changes the pivoting
 angle of the shifting members when they contact the brake shoe.
 With the above-noted conventional centrifugal braking device, braking force
 adjustment is simply carried out by turning the dial. Nevertheless, large
 braking forces are hard to gain, since the braking force obtained by
 contact with the brake shoe is gained depending on the force from the
 shifting members pivoting axially outward.
 This is because it is difficult efficiently to retrieve as a braking force
 radially acting centrifugal force, since the shifting members pivot
 axially outward, and do not travel in the radial outward direction. What
 is more, since braking force is adjusted by varying the pivoting angle of
 the shifting members, the change in braking force when the brake element
 is shifted in the spool axle direction is small; a distinct change in
 braking force can hardly be sensed.
 SUMMARY OF THE INVENTION
 An object of the present invention is in a centrifugal braking device for a
 dual-bearing reel to make braking force adjustment simple, and moreover to
 enable a distinct difference in braking force to be gained by the
 adjustment.
 The centrifugal braking device for a dual-bearing reel according to a first
 aspect of the present invention is a device for braking a spool which is
 rotatably adapted to a reel body by using centrifugal force and includes
 shifting members, a brake element, a first urging member, a restricting
 member, and an urging force adjusting mechanism. The shifting members are
 provided on the spool or a rotary member which rotates together with the
 spool. The shifting members are moved by centrifugal force generated by a
 rotation of the spool. The brake element is non-rotatably provided on the
 reel body in a movable manner in an axial direction of the spool. The
 brake element is capable of making contact with the shifting members that
 are moved by the centrifugal force. The first urging member urges the
 brake element in a direction towards the shifting member side. The
 restricting member restricts a movement of the brake element in a
 direction towards the shifting member side. The urging force adjusting
 mechanism is a mechanism for adjusting an urging force of the first urging
 member.
 In this centrifugal braking device, when the spool rotates, the shifting
 members are moved towards the brake element side by the centrifugal force
 to make contact with the brake element and press the brake element. Since
 the brake element is non-rotatably provided on the reel body, the spool is
 braked by the friction between the shifting members and the brake element.
 The brake element is urged towards the shifting member side by he first
 urging member. Accordingly, when the urging force of the first urging
 member is adjusted, the frictional force changes since the reaction force
 generated when the shifting members push the brake element changes, and
 the braking force varies in proportion to the frictional force. In this
 case, since the braking force is adjusted by changing the urging force of
 the first urging member, the braking force may be easily adjusted and a
 distinctive difference in the braking force may be obtained by the
 adjustment of the urging force.
 The centrifugal braking device for a dual-bearing reel in a second aspect
 is a device according to the invention in its first aspect, but further
 including a second urging member for urging the brake element in a
 direction away from the shifting members. The urging force of the second
 urging member is weaker than the urging force of the first urging member.
 In this case, when it is desired to brake the spool, the urging force of
 the first urging member is adjusted by using the urging force adjusting
 mechanism so that it becomes stronger than the urging force of the second
 urging member. Also, if it is desired to freely rotate the spool, the
 urging force of the first urging member is adjusted so that it becomes
 weaker than the urging force of the second urging member. In this way, it
 is possible to securely separate the brake element from the shifting
 members by using the urging force of the second urging member. As a
 result, the braking force is not applied to the spool and the spool surely
 rotate freely.
 In a third aspect of the present invention, the centrifugal braking device
 for a dual-bearing reel is a device in accordance with the either of the
 first and second aspects, but further wherein the shifting members are
 moved in the axial direction by the centrifugal force to press the brake
 element towards the axial direction. In this case, although it is
 necessary to think out a structure for attaching the shifting members
 since the shifting members are to be moved in the axial direction by using
 the centrifugal force which exerts in the radius direction, any structures
 in which the brake element makes contact with the shifting members which
 are moved in the axial direction may be acceptable. Accordingly, the
 structure of the brake element may be simplified.
 The dual-bearing reel centrifugal braking device in a fourth aspect is a
 device according to the third aspect, yet further wherein each of the
 shifting members is attached to a respective guide shaft having an end
 portion inclined towards the brake element in a movable manner in an axial
 direction of the guide shaft. The guide shafts are radially attached to
 the spool or the rotary member, and each of the shifting members has a
 contacting portion at its end, which is parallel to a plane crossing a
 rotary axis of the spool at right angle. In this case, since the guide
 shafts are disposed radially in a slant manner, the shifting members move
 towards the brake element outwardly in the axial direction and the radius
 direction along the guide shaft in a slant manner when the centrifugal
 force acts on the shifting members, and make contact with the brake
 element at the contacting portion. Since the contacting portion is formed
 parallel to a plane crossing a rotary axis of the spool at right angle,
 the brake element may be made of a disc shaped member which crosses the
 rotary axis of the spool at right angle. For this reason, a structure for
 attaching the shifting members may be simplified as it is only necessary
 to construct so that the shifting members can move along the guide shaft.
 Also, the structure of the brake element may be simplified since a disc
 shaped member may be used as the brake element.
 In a fifth aspect of the invention, the centrifugal braking device for a
 dual-bearing reel is a device in accordance with the either of the first
 and second aspects, but further wherein the shifting members are moved in
 the radius direction of the spool by centrifugal force, and the brake
 element is pressed towards the axial direction when the shifting members
 make contact with the brake element. In this centrifugal braking device,
 although a structure is required for the brake element, which is capable
 of converting a pressing force of the shifting members that are moved in
 the radius direction by centrifugal force to a force in the axial
 direction, the structure for attaching the shifting members may be
 simplified as the shifting members may be moved in the radius direction by
 using the centrifugal force.
 The dual-bearing reel centrifugal braking device according to a sixth
 aspect is a device as set forth in the foregoing first aspect of the
 present invention, yet further wherein each of the shifting members
 includes a first member non-rotatably provided on the spool or the rotary
 member in a movable manner in the axial direction, the first member being
 capable of making contact with the brake element, a second member provided
 on the first member in a movable manner in the radius direction, the
 second member, when moved in the radius direction, being capable of moving
 the first member towards the brake element side, and a third urging member
 urging the first member in a direction away from the brake element. In
 this centrifugal braking device, when the spool rotates and the force in
 the axial direction applied to the second member by the centrifugal force
 becomes stronger than the urging force of the third urging member, the
 second member is moved outwardly in the radius direction and this movement
 of the second member in the radius direction causes the first member to
 move towards the brake element side to make contact with the brake
 element. As a result, the spool is braked. Also, when the force in the
 axial direction by the centrifugal force becomes weaker than the urging
 force of the second urging member, the second member is moved inwardly in
 the axial direction and the brake of the spool is released. In this
 device, the application of the braking force may be selectively carried
 out so that, for instance, the braking force is not applied during a line
 reeling-in operation when the spool is rotated at a low speed and is
 applied during a casting operation when the spool is rotated at a high
 speed by adjusting the urging force of the third urging member.
 The dual-bearing reel centrifugal braking device according to a seventh
 aspect is a device as set forth in the foregoing first aspect of the
 present invention, yet further wherein each of the shifting members
 includes a first member non-rotatably provided on the spool or the rotary
 member in a movable manner in the axial direction, a second member
 provided on the first member in a movable manner in the radius direction,
 the second member, after being moved in the radius direction, being moved
 together with the first member in the axial direction to make contact with
 the brake element; and a third urging member urging the first member in a
 direction away from the brake element. In this centrifugal braking device,
 when the spool rotates and the force in the axial direction applied to the
 second member by the centrifugal force becomes stronger than the urging
 force of the third urging member, the second member is moved outwardly in
 the radius direction and this movement of the second member in the radius
 direction causes the first member to move towards the brake element side
 and the second member makes contact with the brake element. As a result,
 the spool is braked. Also, when the force in the axial direction by the
 centrifugal force becomes weaker than the urging force of the second
 urging member, the second member is moved inwardly in the axial direction
 and the brake of the spool is released. In this device, the application of
 the braking force may be selectively carried out so that, for instance,
 the braking force is not applied during a line reeling-in operation when
 the spool is rotated at a low speed and is applied during a casting
 operation when the spool is rotated at a high speed by adjusting the
 urging force of the third urging member.
 In an eighth aspect of the invention, the centrifugal braking device for a
 dual-bearing reel is a device in accordance with any of the foregoing
 aspects, but further wherein the first urging member includes a plurality
 of coil springs having a different free length and a diameter, each of the
 plurality being disposed so as to be concentric to each other. In this
 centrifugal braking device, since the brake element makes contact with
 each of the coil springs of the first urging member stepwise, the urging
 force is changed stepwise, not continuously, and, accordingly, the braking
 force is varied stepwise. For this reason, a distinctive difference in the
 braking force may be obtained by the adjustment of the urging force.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
 Embodiments
 Overall Structure
 Reference is made to FIG. 1, the plan view of a dual-bearing reel in which
 an embodiment according to the present invention is adapted.
 The dual-bearing reel shown in the figure is a bait reel used mainly for
 lure fishing and includes a reel body 1, a handle 2, and a star drag 3.
 The handle 2 is provided for rotating the spool and is disposed on one
 side of the reel body 1. The star drag 3 is disposed on the reel-body side
 of the handle 2. The handle 2 is a dual-handle type that includes a
 plate-type arm portion 2a and holding portions 2b, each of which is
 rotatably fitted to a respective end of the arm portion 2a. The outer
 surface of the arm portion 2a of the handle 2 is a smooth seamless surface
 to keep fishing line from getting tangled on it.
 As shown in FIG. 2, the reel body 1 includes a frame 5, a first side-cover
 6, a second side-cover 7, and a front cover 10. The first side cover 6 and
 the second side cover 7 are disposed on respective sides of the reel frame
 5. The front cover 10 is disposed to be open/closable on a front portion
 of the frame 5. The frame 5 includes a pair of side plates 8 and 9, which
 are disposed opposite each other at a predetermined spacing, and a
 plurality of (not shown) connecting members, each of which connects the
 side plates 8 and 9.
 The second side cover 7, which is located on the handle 2 end, is
 detachably fastened to the side plate 9 by screws. The first side cover 6,
 which is located on the opposite end of the handle 2, is detachably fitted
 to the side plate 8 by a bayonet coupling 14. An opening 8a, through which
 the spool 12 penetrates, is formed in the side plate 8 located on the
 opposite end of the handle 2.
 Inside the frame 5, are the spool 12, a level wind mechanism 15, and a
 thumb rest 17. The level wind mechanism 15 is provided for uniformly
 winding on fishing line around the spool 12. The thumb rest 17 on which
 the thumb is rested during a thumb-actuated operation is also used as a
 clutch lever. A gear mechanism 18, a clutch mechanism 13, a clutch
 engage/disengage mechanism 19, a drag mechanism 21, and a casting control
 mechanism 22 are provided in the space between the frame 5 and the second
 side-cover 7. The gear mechanism 18 transmits rotational force from the
 handle 2 to the spool 12 and the level wind mechanism 15. The clutch
 engage/disengage mechanism 19 engages/disengages the clutch mechanism 13
 in accordance with operation of the thumb rest 17. The drag mechanism 21
 brakes the spool 12 when fishing line is released. The casting control
 mechanism 22 brakes the spool 12 by grasping the spool's spindle 16 at
 either end. Also, a centrifugal braking mechanism 23 for preventing
 backlash during casting is provided between the frame 5 and the first
 side-cover 6.
 The spool 12 on either side has saucer-shaped flange portions 12a, and
 between the flange portions 12a has tubular line-winding trunk 12b. Also,
 the spool 12 has a tubular boss portion 12c that is formed integral with
 the inner peripheral side of the line-winding trunk 12b in the middle. By
 for example, a serration engagement the spool 12 is non-rotatably fixed to
 the spool spindle 16, which penetrates through the boss portion 12c.
 The spool spindle 16 penetrates the side plate 9 and extends outside the
 second side-cover 7. The extended end of the spool spindle 16 is rotatably
 supported on a bearing 35b in a boss 29 that is formed in the second side
 cover 7. Also, bearing 35a in the centrifugal braking mechanism 23
 rotatably supports the other end of the spool spindle 16.
 The level wind mechanism 15 includes a guide tube 25, a worm shaft 26, and
 a line guide 27. The guide tube 25 is fixed between the pair of side
 plates 8 and 9. The worm shaft 26 is rotatably supported in the guide tube
 25. A gear 28a, which forms a part of the gear mechanism 18, is fixed to
 one end of the worm shaft 26. Also, a spiral groove 26a is formed on the
 worm shaft 26, and the line guide 27 is meshed with the spiral groove 26a.
 The line guide 27 therefore reciprocates along the guide tube 25 by the
 worm shaft 26 being rotated via the gear mechanism 18. A fishing line is
 inserted in the line guide 27 and uniformly wound onto the spool 12.
 The gear mechanism 18 includes a main gear 31, a pinion gear 32, the
 above-mentioned gear 28a, and a gear 28b. The main gear 31 is coupled to a
 handle shaft 30. The pinion gear 32 is cylindrical and is engaged with the
 main gear 31. The gear 28a is fixed to one end of the worm shaft 26. The
 gear 28b is non-rotatably fixed to the handle shaft 30 and engaged with
 the gear 28a.
 The pinion gear 32, a cylindrical member disposed outward of the side plate
 9, is centrally penetrated by the spool spindle 16. The pinion gear 32 is
 fitted to be axially shiftable on the spool spindle 16. The pinion gear 32
 includes a toothed portion 32a and an meshing portion 32b. The toothed
 portion 32a is located on the right side of the reel body 1 shown in FIG.
 2 and engages with the main gear 31. The meshing portion 32b is formed at
 the other of the pinion gear 32. A constricted portion 32c is established
 between the toothed portion 32a and the meshing portion 32b. The meshing
 portion 32b is constituted by a recessed groove formed on the end face of
 the pinion gear 32, and a clutch pin 16a, which radially penetrates the
 spool spindle 16, engages in the meshing portion 32b. Shifting the pinion
 gear 32 outward detaches the clutch pin 16a on the spool spindle 16 from
 the recessed groove in the meshing portion 32b, such that rotation from
 the handle shaft 30 is not transmitted to the spool 12. The clutch
 mechanism 13 is constituted by the recessed groove of the meshing portion
 32b and the clutch pin 16a.
 As shown in FIG. 2, the thumb rest 17 is disposed at the back of the spool
 12 in the rear part between the pair of side plates 8 and 9. The thumb
 rest 17 is also used as a clutch operation lever. An oblong hole (not
 shown) is formed in the side plates 8 and 9 of the frame 5, and a clutch
 cam (not shown) that fixes the thumb rest 17 penetrates the oblong hole.
 Thus, the thumb rest 17 slides up and down along the oblong hole. The
 clutch engage/disengage mechanism 19 includes a clutch yoke 40. By turning
 movement of the thumb rest 17, the clutch engage/disengage mechanism 19
 shifts the clutch yoke 40 parallel to the axis of the spool spindle 16.
 Further, when the handle shaft 30 is rotated in the line reeling-in
 direction, the clutch engage/disengage mechanism 19 shifts the clutch yoke
 40 whereby the clutch mechanism 13 is automatically put on.
 In the configuration thus, the pinion gear 32 is normally located at a
 clutch engaging position and the meshing portion 32b is engaged with the
 clutch pin 16a for the spool spindle 16 to achieve a clutch-on state. On
 the other hand, when the pinion gear 32 is moved outwardly by the clutch
 yoke 40, the meshing portion 32b is disengaged from th e clutch pin 16a to
 achieve a clutch-off state.
 In the configuration thus, the pinion gear 32 is the usual state is
 situated in the inward clutch-engaging position wherein the meshing
 portion 32b is engaged with the clutch pin 16a in the spool spindle 16,
 which is the clutch-on state. On the other hand, when the clutch yoke 40
 shifts the pinion gear 32 outward, engagement of the meshing portion 32b
 and the clutch pin 16a is released, which is the clutch-off state.
 Centrifugal Braking Mechanism Configuration
 As shown in FIG. 3, the centrifugal braking mechanism 23 includes shifting
 members 52, a brake element 53, an urging member 54, a restricting member
 55, and an urging force adjusting mechanism 56. The shifting members 52
 are provided on a rotary member 51 that rotates linked with the spool 12.
 The brake element 53 is capable of coming into contact with the shifting
 members 52. The urging member 54 urges the brake element 53 towards the
 shifting members 52. The restricting member 55 restricts travel of the
 brake element 53 towards the shifting members 52. The urging force
 adjusting mechanism 56 adjusts the urging force of the adjusting member
 54.
 The shifting members 52, members fitted to permit shifting on the rotary
 member 51, travel radially and axially outward under centrifugal force
 from rotation of the spool 12. The rotary member 51 is a cylindrical
 component non-rotatably coupled to the spool spindle 16 by, for instance,
 a serration coupling. Guide shafts 57, which may number six for example,
 are disposed circumferentially spaced on the outer peripheral surface of
 the rotary member 51. The radially fitted guide shafts 57 incline towards
 the brake element 53. Each shifting member 52 is provided in a respective
 guide shaft 57 and permitted axial travel therein. By thus disposing the
 guide shafts 57 radially, at an incline, the shifting members 52 shift
 diagonally-radially and axially outward--along the guide shafts 57 under
 centrifugal force, when centrifugal force acts on the shifting members 52.
 A flange portion 51a for preventing the shifting members 52 from coming
 off is disposed at an end (the left end in FIG. 3) of the rotary member
 51.
 The shifting members 52 are approximately rod-shaped components that bend
 towards the brake element 53. Guide holes 52a in which the guide shafts 57
 are guided are formed in the shifting members 52. Contact surfaces 52b
 lying in a plane orthogonal to the spool spindle 16 are formed on the ends
 of the shifting members 52 on the brake element 53 side. The shifting
 members 52 are non-rotatable with respect to the guide shafts 57 in order
 that the contacting surfaces 52b stay lying in the just-mentioned
 orthogonal plane.
 As shown in FIGS. 3 and 4, the brake element 53 is provided non-rotatably
 on the reel body 1, yet allowed axial travel with respect to the spool 12.
 The brake element 53 is a washer-shaped component able to come into
 contact with the shifting members 52 shifted under centrifugal force. In
 practice, the brake element 53 is fitted non-rotatably yet permitted to
 shift axially in a brake case 50 that forms part of the reel body 1. The
 brake case 50, a short cylindrical component having base, is formed with a
 cylindrical bearing-accommodation portion 50a that projects inwardly from
 the central portion of the base. The inner periphery of the bearing
 accommodating portion 50a, to which a friction plate of the casting
 control mechanism 22 is attached, accommodates the bearing 35a that
 supports the spool spindle 16. The brake element 53 is non-rotatably
 fitted to and permitted axial travel on the outer periphery of the bearing
 accommodating portion 50a.
 The brake case 50 (as shown in FIG. 2) is fixed to the first side cover 6
 by a screw 60. Namely, the brake case 50 forms a part of the reel body 1.
 Also, a pair of mortise-grooves 50b are formed running axially on the
 outer periphery of the end (right end in FIG. 3) of the bearing
 accommodating portion 50a. The mortise-grooves 50b are provided for
 non-rotatably interlocking with the brake element 53. An annular groove
 50c is formed at the end of the mortise-grooves 50b, and the restricting
 member 55 is fitted in the annular groove 50c. The restricting member 55
 is, for example, an elastic ring-shaped element made of wire with a
 portion of the circle notched and, as described above, restricts travel of
 the brake element 53 towards the shifting members 52. Being that the inner
 periphery of the brake element 53 is supported on the bearing
 accommodating portion 50a to permit its axial shift, a pair of interlock
 projections 53a that interlock with the mortise-grooves 50b is formed on
 the inner periphery.
 Three projections 14a that are components of the bayonet coupling 14 are
 formed circumferentially spaced on the outer surface of the brake case 50.
 Also, pawls 14b are formed on the opening 8a in positions opposite the
 projections 14a. The pawls are formed projecting 14b outwardly from the
 opening 8a.
 The urging member 54 is a conical spring one end of which abuts on the
 brake element 53--the larger diameter end is on the brake element 53 side.
 The urging member 54 is disposed between the brake element 53 and a
 pressing member 58, which will be described later, in a compressed state.
 It should be understood that the urging member 54 may be at its free
 length when the pressing member 58 is most retracted.
 The urging force adjusting mechanism 56 includes the pressing member 58, an
 operation member 59, and a cam mechanism 61. The pressing member 58 is
 disposed non-rotatably yet permitting axial shift in the brake case 50.
 The operation member 59 is pivotably fitted to the exterior of the brake
 case. The cam mechanism 61 converts pivoting of the operation member 59
 into axial shifting of the pressing member 58.
 The pressing member 58 includes an inner peripheral part 58a, an outer
 peripheral part 58b, and a base 58c. The inner peripheral part 58a is
 supported to permit axial shift on the bearing accommodating portion 50a.
 The outer peripheral part 58b is non-rotatably fitted yet permitted axial
 shift on inner surface of the brake case 50. The bottom portion 58c
 connects the inner peripheral part 58a and the outer peripheral part 58b.
 A pair of radially protruding interlock pins 62 is formed on the outer
 surface of the outer peripheral part 58b. The pair of interlock pins 62
 interlocks with a pair of interlock grooves 50e formed in the inner
 peripheral surface of the brake case 50 along the spool spindle direction
 to fit the pressing member 58 non-rotatably to the brake case 50. Also, a
 first cam 63 of the cam mechanism 61 is formed on the outer peripheral
 surface of the outer peripheral part 58b. The first cam 63 is roughly
 triangular. A stepped portion 58d is formed on the inner wall of the
 bottom portion 58c, and the other end of the urging member 54 is
 interlocked on the stepped portion 58d.
 The operation member 59, an approximately ring-shaped component, is
 rotatively fitted to the outer end face of the brake case 50. A knob 59a
 is formed on the outer periphery of the outer end face of the operation
 member 59. The knob 59a is formed protruding in the spool axial outward
 direction. A central projecting portion 59c running diametrically is
 further formed on the outer surface of the knob 59a so as to protrude from
 the surface of the first side cover 6. The projecting portion 59c for
 indicating a number from 0 to 5 (not depicted in the figures), for
 instance, on the surface of the first side cover 6 to signify braking
 force strength. Also, a pair of pivot-restricting recesses 59b for
 restricting pivotal range of the operation member is formed on the inner
 peripheral face thereof. A positioning mechanism 70 for positioning
 pivotal angle with respect to the brake case 50 into six positions is
 provided in the operation member 59.
 The positioning mechanism 70 includes a positioning pin 70a, a coil spring
 70b, and positioning recesses 70c. The positioning pin 70a is attached to
 the operation member 59 movably in the spool axis direction. The coil
 spring 70b urges the positioning pin 70a toward the brake case 50 side.
 The positioning recesses 73c, which number six in this embodiment, are
 formed circumferentially spaced on the outer lateral face of the brake
 case 50.
 Second cams 64, which form a part of the cam mechanism 61, are provided on
 the right hand side surface of the operation member 59 in FIG. 4. Each of
 the second cams 64 is formed at a position corresponding to the position
 of the respective first cam 63, and forms a triangular oblique side cam.
 The rotation of the operation member 59 is converted into a movement of
 the pressing member 58 in a direction approaching to the brake element 53.
 Also, a pair of cam grooves 50f having an arc shape is provided in the
 brake case 50 for the respective second cam 64 to penetrate.
 The operation member 59 is compressed against the brake case 50 by a
 pressing plate 75. The pressing plate 75 compresses the operation member
 70 by means of screws, each of which is tighten against a respective screw
 base portion 50d formed on the outer side surface of the brake case 50.
 The screw base portion 50d protrudes outwardly in the radius direction.
 The range of the rotational angle of the operation member 59 is
 predetermined by the screw base portions 50d which stops the movement of
 the operation member 59 by being engaged with the respective rotation
 controlling concave portion 59b.
 In the urging force adjusting mechanism 56 having the above-mentioned
 configuration, the pressing member 58 moves in a direction approaching the
 brake element 53 due to the function of the first and second cams 63 and
 64 when the operation member 59 is rotated, using the knob portion 59a, in
 the direction indicate by an arrow A. As a result, the braking force is
 increased since the urging force against the brake element 53 is increased
 and the reaction force generated when the shifting members 52 make contact
 with the brake element 53 is increased. On the other hand, when the
 operation member 59 is rotated in the direction indicated by an arrow B,
 the pressing member 58 is moved in a direction away from the brake element
 53 by the urging force of the urging member 54 and, hence, the urging
 force applied to the brake element 53 is reduced. Accordingly, the braking
 force is reduced. When the pressing member 58 is moved to a most receded
 position, the braking force reaches its minimal and the reaction force is
 gradually decreased from one position to the other among four intermediate
 positions. Accordingly, the braking force is decreased stepwise.
 In this embodiment, since the braking force is adjusted by changing the
 urging force of the urging member 54, the braking force may be easily
 adjusted and a distinctive difference in the braking force may be obtained
 by the adjustment of the urging force.
 Reel Operation
 In a normal state, the clutch yoke 40 is pressed inwardly and, hence, a
 clutch-on state is maintained. As a result, the rotational force from the
 handle 2 is transmitted to the spool 12 via the handle shaft 30, the main
 gear 31, the pinion gear 32 and the spool spindle 16 to rotate the spool
 12 in the line reeling-in direction. At that time, although centrifugal
 force acts on the shifting members 52 of the centrifugal braking mechanism
 23 to move the shifting members 52 outwardly in the radius direction and
 the axial direction, the braking force does not become so large since the
 rotation speed of the spool 12 is low and, hence, it does not interfere
 with the rotation of the handle 2. However, if it is necessary to reduce
 the braking force, the operation member 59 may be rotated in the direction
 indicated by the arrow B in FIG. 4 using the knob portion 59a so that the
 pressing member may be positioned at a receded position shown in FIG. 3.
 When a fishing line is cast, the braking force is adjusted to prevent
 backlash by the operation member 59 using the knob portion 59a. When the
 pressing member 58 is moved towards the brake element 53 by rotating the
 operation member 59 in the direction indicated by the arrow A, the urging
 force of the urging member 54 is increased and the braking force is
 enhanced.
 Then, the thumb rest 17 may be pushed down. In this embodiment, the thumb
 rest 17 is moved along the side plates 8 and 9 down to a disengaging
 position located below. Due to the movement of the thumb rest 17, the
 clutch yoke 40 and the pinion gear 32 are moved outwardly. As a result,
 the clutch enters a clutch-off state. In the clutch-off state, the
 rotation from the handle shaft 30 is not transmitted to neither the spool
 12 nor the spool spindle 16 and the spool 12 may freely rotate. When a
 fishing rod is swung in the clutch-off state so that a reel is inclined in
 the axis direction in order for the spool spindle 16 to face a vertical
 surface while thumbing the spool using a thumb on the thumb rest 17, a
 lure is cast and the spool 12 rotates vigorously in the line-releasing
 direction.
 In this state, the spool spindle 16 is rotated in the line-releasing
 direction by the rotation of the spool 12, and the rotation is transmitted
 to the rotary member 51. When the rotary member 51 is rotated, the
 shifting members 52 make contact with the brake element 53, and the spool
 12 is braked by the centrifugal braking mechanism 23 to prevent a
 generation of backlash.
 In addition, if backlash of the spool 12 is caused by any chance, the
 problem may be easily dissolved since the first side cover 6 is easily
 removed due to the presence of the bayonet coupling 14.
 Moreover, if the lure is changed to one having a different weight, the
 braking force may be adjusted in accordance with the weight of the lure,
 by rotating the operation member 59 using the knob portion 59a. In this
 embodiment, the braking force is easily adjusted by simply rotating the
 operation member 59 using the knob portion 59a which is exposed to outside
 of the reel. Further, a clear difference in the braking force may be
 obtained when the braking force is adjusted.
 Other Embodiments
 (a) Although the pressing member 58 is shifted by the cam mechanism 61 in
 the above-described embodiment, the pressing member 58 may be shifted
 through other converting mechanisms such as screws.
 (b) The brake element 53 may be urged by an urging member 154 formed by a
 plurality of coil springs 54a through 54d, as shown in FIG. 5. In this
 embodiment, the coil springs 54a through 54d are each of different free
 length and diameter, and disposed concentrically nested. The free length
 of the coil spring 54a on the outer circumferential side is the longest
 and that of the coil spring 54d on the inner circumferential side is the
 shortest. Also, the position of the tip-end of the coil spring 54d on the
 inner circumferential side located to enable contact with the brake
 element 53 when most retracted. The pressing member 158 in this embodiment
 includes inner portion 158a, outer portion 158b, and base portion 158c.
 Cylindrical interlock projections 58e for interlocking with the base ends
 of the coil springs 54a through 54d are provided on the [pressing member
 58] base portion 158c.
 In this embodiment, since the brake element 53 makes contact with each coil
 spring 54a through 54d stepwise, the urging force changes stepwise, not
 continuously, and, hence, the braking force also varies stepwise.
 Accordingly, a distinctive difference in the braking force may be obtained
 by adjusting the urging force.
 (c) As shown in FIG. 6, it is possible to dispose an urging member 71 at
 the right hand side of the brake element 53 in FIG. 6. The urging member
 71 may be a cone shaped coil spring whose diameter becomes larger towards
 the brake element 53 side. The spring constant of the urging member 71 is
 smaller than that of the urging member 54 and the urging force at a normal
 state of the urging member 71 is also smaller than that of the urging
 member 54. An end portion of the urging member 71 at the smaller diameter
 side is engaged with a spring engaging ring 73 which is controlled by a
 stop ring 72 being engaged with the annular groove 50c. In this
 embodiment, the urging force of the urging member 54 is adjusted by using
 the urging force adjusting mechanism 56 so that it becomes stronger than
 the urging force of the urging member 71. When it is desired to freely
 rotate the spool 12, the urging force of the urging member 54 is adjusted
 so that it becomes weaker than the urging force of the urging member 71.
 In this manner, the brake element 53 may be surely separated from the
 shifting members 52 by the urging force of the urging member 71. As a
 result, the braking force is not applied to the spool 12 and, hence, the
 spool 12 may surely rotate in a free state.
 (d) As shown in FIG. 7, guide shafts 157 may be radially disposed in guide
 holes 152a extending along the radius direction of rotary member 151, and
 a conical inclined braking surface 53b may be formed on brake element 153.
 Herein, shifting members 152 are movably guided in the radius direction of
 the rotary member 51. Contact faces 152b formed with sloping bent surfaces
 so as to contact the braking face are formed on the ends of the shifting
 members 152. In the embodiment thus, when the spool 12 is rotated and
 centrifugal force acts on the shifting members 152, the shifting members
 152 move outwardly in the radius direction to make contact with the
 inclined braking surface 53b. Accordingly, the spool 12 is braked.
 Therein, since the inclined braking surface 53b is inclined, the brake
 element 153 is pressed outwardly in the spool axis direction by the
 shifting members 152. The braking force in this instance is determined by
 the urging force of the urging member 54 urging the brake element 53
 towards the shifting members 152. Herein, the structure for attaching the
 shifting members 152 is simplified because the shifting members 152 need
 only shift radially.
 (e) As shown in FIG. 8, shifting members 252 may be configured with two
 elements, a first shifting member 76 allowed to shift axially, and a
 second shifting members 77 allowed to shift radially.
 The first shifting member 76 is, for instance, a circular truncated conical
 member provided non-rotatably, yet permitted axial shift, on rotary member
 151. An annular contact portion 76a is formed on the end of the first
 shifting member 76 on the large- diameter side. An extension member 74
 made out of a coil spring interlocks with the other end on the
 small-diameter side. The extension member 74 pulls the first shifting
 member 76 towards spool 112. For this purpose, the ends of the extension
 member 74 are interlocked with the first shifting member 76 as well as the
 spool 112. It should be noted that the tensile force of the extension
 member 74 is weaker than, for example, the axially outward component force
 acting under centrifugal force on the first shifting member 76 when
 centrifugal force acts on the second shifting members 77 during line
 reel-out, and larger than the axially outward component force acting
 during the line reeling-in operation.
 The second shifting members 77 are fitted to the first shifting member 76
 allowing them to shift radially. The ends of the second shifting members
 77 are faces 77a sloped for contact on a tapered surface 112d formed on
 the outer peripheral surface of the flange portion 112a of the spool 112.
 In the embodiment thus, when the spool 112 rotates and centrifugal force
 acts on the second shifting members 77, the second shifting members 77
 shift radially outward under the centrifugal force and contact the tapered
 surface 112d. When the second shifting members 77 come into contact with
 the tapered surface 112d, they shift axially outward together with the
 first shifting member 76 at the point when the axial component force
 arising due to the centrifugal force becomes larger than the tensile force
 of the extension member 74. As a result, the first shifting member 76
 comes into contact with the brake element 53 to brake the spool. When the
 component force due to the centrifugal force becomes weaker than the
 tensile force the first shifting member 76 is pulled by the extension
 member 74 and parted from the brake element 53. Further, the spool 112 is
 not braked when rotated at the speeds during line reel-in that are lower
 than during line reel-out, because when reeling in line the component
 force that arises under centrifugal force is weaker than the tensile force
 of the extension member 74. The spool 112 is therefore selectively braked
 during line reel-in and during line reel-out.
 In addition, as shown in FIG. 9, guide shafts 80 may be provided radially
 on first shifting member 78 provided non-rotatably yet permitted axial
 shift on the rotary member 51. Second shifting members 79 permitted radial
 movement may be provided on the guide shafts 80. Formed on the second
 shifting members 79 are first contact surfaces 79a that come into contact
 with the tapered surface 112d of the spool 112, and second contact
 surfaces 79b that come into contact with the brake element 53. Operation
 in this case is likewise as with the embodiment illustrated in FIG. 8;
 explanation is therefore omitted.
 (f) In the above embodiment, although the shifting members are provided on
 the rotary member in a movable manner in the radius direction and/or the
 axial direction, the shifting members may be pivotally provided on the
 rotary member so the they are pivoted by the centrifugal force.
 (g) In the above embodiment, although the shifting members are provided on
 the rotary member which rotates together with the spool 12, the shifting
 members maybe directly attached to the spool 12.
 According to the present invention, since the braking force is adjusted by
 changing the urging force of the first urging member, the braking force
 may be adjusted easily and a distinctive difference in the braking force
 may be obtained by the adjustment of the urging force.
 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.