JPH10117648A - Transmission mechanism for double bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a double bearing reel which easily adjusts the energizing force of a spring at the time of switching fast/low, smoothly engages a clutch and gears and prevents the damage of the clutch and the gears. SOLUTION: A spring for sliding a switching shaft 12 and a spring 14 for sliding the clutch 11 are made respectively different. Thereby, concerning the engaging of the clutch 11 and the main gears 2 and 3 in switching operation, when inner teeth at the main gears 2 and 3 and outer teeth 11A at the clutch 11 match with each other, the clutch 11 is engaged with the main gears 2 and 3 by sliding with the shaft 12 and when the inner teeth and the outer teeth 11A do not match with each other, the clutch 11 collides with the gears 2 and 3 and only the switching shaft completes sliding. At the time of rotating the clutch 11 to match the inner teeth and outer teeth after then, the clutch 11 is engaged with the gears 2 and 3 by sliding.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change mechanism of a spool in a dual bearing reel.

[0002]

2. Description of the Related Art Conventionally, there has been known a reel in which the rotation of a spool can be changed at a high speed and a low speed in this kind of reel. The conventional transmission mechanism includes a set of first and second low-speed gears for rotating the spool at low speed, and a set of first and second gears for rotating at high speed around the handle shaft and around the rotation center line of the spool. A high-speed gear, a first low-speed gear provided around a handle shaft, and a first low-speed gear.
A clutch for selectively transmitting rotation of the handle shaft to one of the first low-speed gear and the first high-speed gear between the high-speed gear and a spring disposed on both sides of the clutch; A holding lever for maintaining a pushing operation position of the operating body is disposed on a protruding portion of the operating body, and a neutral portion is provided between the first high-speed gear and the first low-speed gear. According to the above configuration, when the operation for switching from the high-speed rotation to the low-speed rotation is performed by pushing the operating body in the axial direction, the pushing spring pushes the clutch. At this time, the spring on the return side contracts until it engages with the sliding of the clutch. When the holding lever is released, the clutch is moved to the first position by the repulsion of the opposite spring.
Engage with high speed gear.

[0003]

In the above-mentioned conventional speed change mechanism, since the moving engagement of the clutch is performed by the repulsive force of the spring, the urging force of the return side spring is lower than the urging force of the pushing side spring. But
When the spring contracts, its repulsive force increases. Therefore, the pushing-side spring withstands the repulsive force and requires an urging force capable of contracting the return-side spring until the clutch is completely engaged. Further, the spring on the return side contracts until the clutch is engaged as described above, and also requires an urging force for returning the clutch and the operating body. Further, a neutral portion is provided to prevent damage due to collision between the clutch and the gear when the engagement position between the clutch and the gear is displaced when switching between the first high-speed gear and the first low-speed gear. For example, if the urging force of the pushing-side spring is too strong, the pressing force against the gear of the clutch will be strong, and the frictional force between the two due to this pressing force will eventually damage the gear and the clutch. In other words, merely making the biasing force of the return side spring lower than the biasing force of the pushing side spring causes the above-described problem, and the biasing force of the spring is reduced to eliminate such a problem. It is very troublesome to adjust.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to make it easy to adjust the biasing force of a spring at the time of switching between high speed and low speed, and to improve the clutch and gear. To ensure smooth engagement of clutches and prevent damage to clutches and gears.

[0005]

In order to attain the above object, the present invention provides a technical means in which two main gears for high speed and low speed are provided at the tip of a hollow main shaft rotated by a handle. At the same time as free-fitting in parallel,
Two high-speed and low-speed pinion gears respectively meshing with these main gears are mounted on a spool shaft on which a spool is rotatably supported, and the main gear can be freely engaged and disengaged between the two main gears. A hollow clutch that transmits the rotation of the handle to the main gear by engaging with the main shaft is provided so as to be slidable along the axis of the main shaft and to rotate integrally with the main shaft, and the clutch is provided inside the main shaft. A switching shaft to be engaged and disengaged is slidably inserted in the axial direction, an end of the switching shaft on the main gear side is slidably inserted into the clutch, and the periphery of the switching shaft is engaged with the clutch. When the two pusher rings that slide in the axial direction are urged in the direction away from each other, The two pusher rings are slid in the axial direction, and the two stopper rings for retaining are positioned outside the pusher ring and fixed, while the end protruding from the handle side of the main shaft is switched. An operation unit for pushing and returning the shaft is provided, and a spring having an urging force exceeding the urging force applied to the pusher ring is elastically mounted between the operation unit and the switching shaft, and the switching shaft is constantly attached in the handle direction. And a locking mechanism for locking and holding the switching shaft over the main shaft and the switching shaft.

According to the above-described means, the engagement between the clutch and the main gear in the above-described switching operation is such that when the external teeth of the clutch are in a position where the external teeth of the clutch are in conformity with the internal teeth of the main gear, the clutch slides together with the switching shaft. Engage. If the clutch is out of alignment, the external teeth of the clutch collide with the internal teeth of the main gear.However, since the spring for sliding the switching shaft and the spring for sliding the clutch are separate, only the switching shaft with the clutch left is used. When the sliding is completed and the clutch is slightly rotated in the circumferential direction thereafter, the clutch mounted on the switching shaft slides by a pusher ring biased by a spring and engages with the main gear. At this time, the spring that slides the clutch buffers the collision between the external teeth and the internal teeth, and more smoothly engages the clutch with the main gear. According to the above, the repulsive force of the spring is only required that the biasing force of the spring that slides the switching shaft is greater than the biasing force of the spring that slides the clutch, and the spring that slides the clutch can slide only the clutch. Since there is only a certain urging force, it is easy to adjust the spring.

[0007]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a partially cutaway front view of a reel body equipped with a transmission mechanism according to the present invention, showing a state where the reel body is set to low-speed rotation. A hollow main shaft 1 has a main gear 2 for high speed and a main gear 2 for low speed. A gear 3 is provided, and a pinion gear 5 meshing with the main gear 2 for high speed and a pinion gear 6 meshing with the main gear 3 for low speed are integrally provided on the spool shaft 4.

The main shaft 1 is rotatably inserted into a bearing sleeve 7 inserted into the side plate A of the reel body. An end of the main shaft protruding inside the side plate A has a cross formed by a predetermined length from its side end. The high-speed main gear 2 and the low-speed main gear 3 are rotatably fitted on the outer side of the shaft portion where the split groove 8 is cut out.

The high-speed and low-speed main gears 2 and 3 have different numbers of teeth, respectively, and have recesses 2A and 3A formed on the surface facing the opposing main gear.
The inner teeth 2B and 3B are formed on the inner periphery of the main gear 2, and a spacer 9 is mounted between the gears arranged in parallel, so that the two main gears 2 and 3B are formed.
The distance between the three is maintained. A retaining ring 10 is fitted and attached to the end of the main shaft 1 in which the split groove 8 is formed to prevent the two main gears 2 and 3 from falling off, and to form the concave portions 2A of the two main gears 2 and 3 arranged in parallel. , 3A, a clutch 11 capable of switching between the two main gears 2, 3 and being disengageable is accommodated.

The clutch 11 has outer teeth 11A meshing with the inner teeth 2B, 3B on the outer circumference, and a disk having an engaging piece 11B engaging the split groove 8 on the inner circumference.
E is integrally formed concentrically on the outer periphery of E, so that it is slidable in the axial direction with respect to the main shaft 1 and rotates integrally therewith.

A handle 16 is fitted to an end of the main shaft 1 protruding outside the side plate A, and is fastened and fixed with a nut 17. A switching shaft 12 is slidable in the main shaft 1 in the axial direction. It is inserted in.

The switching shaft 12 has its end on the main gear side slidably inserted into the clutch 11, and engages with the clutch 11 at a position surrounded by the inner periphery of the clutch 11 to slide in the axial direction. The two pusher rings 13, 13 ′ are slidably fitted in the axial direction with the two pusher rings 13, 13 ′ facing each other.
The springs 14 are resiliently mounted between them and are urged in directions away from each other. Further, the two pusher rings 13, 13 are slid in the axial direction and are prevented from slipping.
The stopper rings 15, 15 'are positioned outside the pusher rings 13, 13' and fixed.

The pusher rings 13, 13 ′ have a smaller diameter than the inner circumference of the clutch 11.
13 ′ is formed to have a diameter larger than that of the clutch 13 ′ and a concave portion for accommodating both ends of the spring 14.
1 is slidable. A pusher ring 13 ′ on the handle 16 side is provided on an engagement protrusion 11 C integrally provided at a handle side peripheral end of the inner periphery of the clutch 11, and the other pusher ring 13 is provided on the opposite side. Ring 11 mounted on the inner peripheral surface near the peripheral end
The clutch 11 is slid by contacting each of the clutches D.

On the other hand, at an end of the switching shaft 12 protruding outward from the main shaft 1 on the handle 16 side, an operating mechanism B for pushing and returning the switching shaft 12 in the axial direction is provided. In the operation mechanism B, a push button B1 is integrally fixed to an end of the switching shaft 12 by press-fitting, and the push button B1 is located outside a nut 17 for fixing the handle arm 16 to the main shaft 1, and is rotatable. It is engaged so as to rotate integrally with the knob B2 attached to the knob.

The structure will be described in more detail with reference to FIGS. 2 and 4. A cylindrical body B3 having split grooves B4 spaced apart in the circumferential direction is rotatably mounted at a fixed position on the outside of the nut 17, and Push button B on split groove B4 of cylinder B3
The push button B1 is slidable in the axial direction and rotatable integrally with the cylinder B3 by fitting and engaging a projection B5 protruding from the outer peripheral surface of the cylinder 1, and a knob B2 is provided on the outer periphery of the cylinder B3. The knob B2 and the cylindrical body B3 are integrated by screwing, and a coil spring B is provided between the step of the nut 17 and the inner bottom surface of the push button B1.
6, the switching shaft 12 is attached to the handle arm 1
6 is always energized. The biasing force of the coil spring B6 is stronger than the biasing force of the spring 14 mounted on the switching shaft 12.

Further, a locking mechanism C for locking and holding the switching shaft 12 over the main shaft 1 and the switching shaft 12 is provided. The locking mechanism C includes a notch engaging portion C1 formed in the middle small-diameter portion 12A of the switching shaft 12 and a switching shaft 12 that engages with the notching engaging portion C1.
And an elastic piece C2 that latches and holds the pushed state, and a holding cylinder C3 that holds the elastic piece C2. More specifically, the structure of the locking mechanism C will be described in detail. The notch engaging portion C1 is formed by cutting the outer peripheral surface of the small-diameter portion 12A flat at two places. The elastic piece C2 which engages with the notch engaging portion C1 and latches and retains the spring plate substantially D
The elastic piece C2 is accommodated in a holding cylinder C3 screwed inside the main shaft 1 so as to cover the small diameter portion. Further, a groove C4 into which the elastic piece C2 is fitted is formed in an annular shape on the outer peripheral surface of the holding cylinder C3, and a part of the groove C4 reaches the inner surface of the holding cylinder C3 and is cut out in a substantially crescent shape to form an opening. C5 is formed so that the outer peripheral surface of the switching shaft 12 faces the opening C5. The position where the groove C4 is formed is a position facing the notch engaging portion C1 when the switching shaft 12 is slid by pressing the push button B1. Therefore, the arc portion of the elastic piece C2 bent into a substantially D shape fits into the groove C4, and the linear portion continuously provided on one side of the arc portion is accommodated so as to cross the opening C4. The number of the notch engaging portions C1 may be one or three or more in addition to the two shown. If the number of the notch engaging portions C1 is large, the knob B2 for switching from low speed to high speed is used. The amount of rotation is small.

Hereinafter, the shifting operation of the transmission mechanism will be described with reference to the drawings. FIG. 2 shows a state in which the switching button 12 of the operating mechanism B is pushed against the elastic force of the coil spring B6 to slide the switching shaft 12 toward the low speed main gear 3 side. ing. In this state, the notch engaging portion C1 of the locking mechanism C faces the groove C5, so that the linear portion of the elastic piece C2 engages with the notching engaging portion C1 to stop the switching shaft 12 from being pushed. Hold. Then, the clutch 11 is engaged with the low speed main gear 3, and in this state, the rotation of the handle 16 is performed from the main shaft 1, the clutch plate 11, and the low speed main gear 3 via the low speed pinion gear 6 meshing with the gear. Propagated to the spool shaft 6, the spool D obtains a high torque winding force at a low speed rotation suitable for large fish. At this time, the high-speed main gear 2 freely rotates outside the main shaft 1 with the rotation of the high-speed pinion gear 5.

Next, when the knob B1 is rotated in the low-speed rotation state, the switching shaft 12 is rotated via the push button B1. The rotation of the switching shaft 12 causes the notch engagement portion C1 to rotate in the circumferential direction, and the linear portion of the elastic piece C2 elastically engaged with the notch engagement portion C1 is pushed open to form the notch. The switching member 12 rides on the outer peripheral surface of the switching shaft 12 between the engaging portions C1, thereby the elastic piece C2 and the notch engaging portion C
1 is released, and the switching shaft 12 slides toward the side plate high-speed main gear 2 by the elastic force of the coil spring B6. Then, the clutch 11 slides following the switching shaft 12 and engages with the high-speed main gear 2 to switch to the high-speed rotation connection state. (See FIGS. 6 and 7)

In the state set to the high-speed rotation, the rotation of the handle 16 is transmitted to the spool shaft 4 via the clutch plate 11 engaged with the main shaft 1 and the high-speed pinion gear 5 meshing with the high-speed main gear 2, The spool D can obtain high-speed rotation suitable for small fish. At this time, the low speed main gear 3 is freely rotating outside the main shaft 1 with the rotation of the low speed pinion gear 5. The elastic piece C1 housed in the holding cylinder C3
Is in elastic contact with the outer peripheral surface of the switching shaft 12. (See Fig. 8)

The engagement of the clutch 11 with the main gears 2 and 3 in the above-described switching operation depends on the external teeth 1 of the clutch 11.
When the gear 1A is at a position where the gears match the internal teeth 2B and 3B of the main gears 2 and 3, the clutch 11 slides and engages with the switching shaft 12 as it is. In the case of deviation, the outer teeth 11A of the clutch 11 collide with the inner teeth 2B, 3B of the main gears 2, 3 as shown in FIGS. Since the urging force of the spring 14 mounted on the switching shaft 12 is weaker than the urging force of the switching shaft 12, only the switching shaft 12 completes sliding with the clutch 11 left.
Thereafter, when the clutch 11 is slightly rotated in the circumferential direction, the clutch 11 mounted on the switching shaft 12
Slidably engage with the main gears 2 and 3 by the pusher rings 13 and 13 'which are biased by. At this time, the spring 14 buffers the collision between the external teeth 11A and the internal teeth 2B and 3B, and more smoothly engages the clutch 11 with the main gears 2 and 3.

[0021]

According to the first aspect of the present invention, the repulsive force of the spring simply exceeds the urging force of the spring that slides the switching shaft when the repulsive force of the spring exceeds the urging force of the spring that slides the clutch. Also, since the spring for sliding the clutch only needs to have an urging force enough to slide only the clutch, it is easy to adjust the repulsive force of the spring. When the clutch collides with the main gear, only the switching shaft completes sliding while leaving the clutch,
At this time, the spring buffers the collision between the clutch and the main gear, and can more smoothly engage the clutch with the main gear. Therefore, it is possible to provide a transmission mechanism that can solve the conventional problems.

[Brief description of the drawings]

FIG. 1 is a partially cutaway front view showing a dual bearing reel equipped with a transmission mechanism of the present invention, in a state where it is set to low-speed rotation.

FIG. 2 is an enlarged view of a main part in FIG.

FIG. 3 is a sectional view taken along (3)-(3) of FIG. 2;

FIG. 4 is a sectional view taken along (4)-(4) of FIG. 2;

FIG. 5 is a sectional view taken along (5)-(5) of FIG. 2;

FIG. 6 is a longitudinal sectional view showing a state in which the switching shaft is rotated to shift from low-speed rotation to high-speed rotation.

FIG. 7 is an enlarged sectional view of a main part showing a state set to high-speed rotation.

FIG. 8 is a cross-sectional view along (8)-(8) in FIG. 7;

FIG. 9 is an enlarged sectional view of a main part in a state where the clutch collides with a low-speed main gear.

FIG. 10 is an enlarged sectional view of a main part in a state where the clutch collides with a high-speed main gear.

[Explanation of symbols]

1 ... Main shaft 2 ... High-speed main gear 3
… Main gear for low speed 4… Spool shaft 5… Pinion gear for high speed 6… Pinion gear for low speed 11… Clutch 12…
Switching shaft 13, 13 '... Pusher ring 14 ... Spring 15, 15' ... Stopper ring 16 ... Handle B ... Operating mechanism C ... Locking mechanism B6 ... Coil spring

Claims (1)

[Claims] 1. A high-speed and low-speed two main gears are idle-fitted in parallel at the tip of a hollow main shaft rotated by a handle, and are engaged with these main gears, respectively. The two pinion gears are mounted on a spool shaft on which the spool is rotatably supported, and the main gear is engaged with and disengaged between the two main gears. A hollow clutch is provided so as to be slidable along the axis of the main shaft and to rotate integrally with the main shaft, and a switching shaft for engaging and disengaging the clutch in the main shaft is slidable in the axial direction. And an end of the switching shaft on the main gear side is slidably inserted into the clutch, and the periphery of the clutch is And pushes the two pusher rings that slide the clutch in the axial direction in a direction away from each other so as to be slidably fitted in the axial direction, and to push the two pusher rings in the axial direction. An operation unit for pushing and returning the switching shaft is provided at the end of the main shaft protruding from the handle side, while the two stopper rings to be slid and stopped are positioned outside the pusher ring and fixed. A spring having an urging force exceeding the urging force applied to the pusher ring is elastically mounted between the operation unit and the switching shaft to constantly urge the switching shaft in the handle direction, thereby engaging the switching shaft in the main shaft. A double-bearing reel transmission mechanism provided with a locking mechanism for stopping and holding.