JPH09104388A - Shifting device for bicycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform the shifting process smoothly by installing a can means between a slide element and an idler, and thereby converting the displacement in axial direction of the slide element into a displacement round the axis of the idler while it lies in the second position. SOLUTION: An operating means is composed of a slide element 20 slided along the axis and an idler 30 which can be enaged by and disengaged from a bobbin 10 through an engaging means 40. The idler 30 having moved to the second position with displacement along the axis by the slide element 20 will separate from the bobbin 10 and is rotated round the axis into the engagement region with the bobbin 10 corresponding to the next displacement position through the action of a cam means 50 to convert the axial direction displacement of the slide element 20 into a rotational displacement of the idler 30. Then the bobbin 10 and idler 30 make relative rotation until complete engagement is established, and thus the bobbin 10 takes new shift position.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bicycle gear shift operation device for operating a gear shift device through a gear shift cable,
This speed change operation device includes a winding body rotatable around an axis for winding up the speed change cable, and an operating means for displacement operation in the axis direction for rotating the winding body in one direction. Is equipped with.

[0002]

2. Description of the Related Art As a bicycle gear shift operation device similar to the above-mentioned form, for example, as shown in Japanese Unexamined Patent Publication No. Hei 2-270693, a take-up body is rotated by an operating lever which is rotated around a rotation axis of the take-up body. Some have a structure that rotates. In this device, both speed-up and speed-down operations are performed by a rocking type operation lever. In contrast to this, there is also one that employs a structure in which the winding body is rotated in one direction by operating means that is slid along the axis of rotation of the winding body. A gear shift operation device having such a structure is disclosed in Japanese Patent Application Laid-Open No. 61-61160.
No. 222889, according to which the ratchet teeth, which determine the gear shift position, are temporarily held in the outer edge regions of both end faces of the winding body formed as a ring body. The notch is formed, and the operating means with the upper ratchet and the lower ratchet arranged so as to sandwich this ratchet tooth and part of the notch can slide along the axis of rotation of the winding body. Is equipped with. Rotation of the winding body in one direction at the time of gear shifting is performed by an oscillating operation lever, but rotation of the winding body in the other direction at the time of gear shifting is performed by pushing down the operating means to move the upper ratchet into the cutout portion. The lower ratchet from the gearshift positioning ratchet, and the return spring causes the upper ratchet to rotate back until the upper ratchet contacts the stopper wall of the notch, and then the operating mechanism moves upward to lower the ratchet. This is achieved by allowing the side ratchet to enter the gearshift positioning ratchet teeth and retracting the upper ratchet from the notch.

In such a conventional gear shift operating device, since the upper ratchet and the lower ratchet of the operating means are provided on the same member, the positional relationship between them is fixed, and the temporary winding body is temporarily wound. The engagement for holding the position of and the release thereof and the timing of the engagement for shifting positioning and the timing of the release are not always satisfactory, which is a negative factor for the smooth shift operation process.

Furthermore, since the above-mentioned operating means adopts a form in which the upper ratchet and the lower ratchet are sandwiched from the outside in the radial direction of the winding body, the structure of the entire speed change operation device is as follows. It has a shape that locally protrudes laterally from the axis of rotation, which poses a problem in terms of design and mounting flexibility.

[0005]

SUMMARY OF THE INVENTION An object of the present invention is to provide a gear shift operating device having a structure in which at least one direction of rotation of the winding body is realized by operating displacement of the winding body in the direction of the axis of rotation of the winding body. It is an object of the present invention to provide a structure in which a series of gear shift operation processes of rotating a winding body to a position corresponding to the next gear position while smoothly holding the body position is smoothly performed.

Another object of the present invention is to provide a structure in which there is no locally protruding member on the side of the winding body.

[0007]

In order to solve the above problems, a bicycle gear shift operating device according to the present invention rotates a winding body rotatable around an axis in one direction to wind a shift cable. An operating means for displacement operation in the axial direction, an idler displaceable in the axial direction between a first position and a second position and displaceable around the axial center, and interlocking with the idler. And a slide operation body displaceable in the axial direction, and

A meshing means is formed between the winding body and the idler for engaging the idler and the winding body at the first position of the idler and disengaging the winding body at the second position, and the meshing means is formed between the winding body and the idler. A cam means is formed between the slide operation body and the idler for converting the displacement of the slide operation body in the axial direction in the position into the displacement around the axis center of the idler.

[Operation] According to the above gear shift operation device, the operation means includes the slide operation body that is slid along the shaft center and the idler that can be engaged / disengaged with the winding body via the meshing means. A cam configured to be divided, and the idler moved to the second position by the displacement along the axial direction by the slide operating body is separated from the winding body, and further the axial displacement of the slide operating body is converted into the rotational displacement of the idler. Due to the action of the means, the idler is rotated around the axis in the meshing region with the winding body corresponding to the next gear shift position, and then the idler is relatively rotated until the winding body and the idler are completely meshed and coupled. As a result, the winding body comes to a new gear position.

[Effect] Due to the above-mentioned two-part construction of the operating means, axial displacement for disengagement from engagement with the winding body,
Accurate and smooth gear shifting operation processes are performed, such as rotational displacement to the region corresponding to the next gear and reverse axial displacement for reengagement with the winding body.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS As one of the preferred embodiments of the present invention, as is apparent from FIG. 1, the winding body 10, the slide operating body 20, and the idler 30 are configured as ring bodies. In some cases, the winding body 10, the slide operating body 20, and the idler 30 are arranged concentrically with respect to the axis X. According to this configuration, the winding body 10, the slide operation body 20, and the idler 30 can be externally fitted and supported by a common cylinder shaft body 70, for example, and the overall structure of the gear shift operation device is simple and easy to assemble. Will be things.

When the winding body 10 and the idler 30 are separated, the winding body 10 is prevented from rotating all at once due to the action of a return spring or the like of a target transmission, for example. It is preferable to provide a body holding means 60, which is shown in FIGS.
As shown in FIG. 3, the winding body 10 may be composed of an inner spline portion 11 formed on the inner peripheral surface and an outer spline portion 21 formed on the outer peripheral surface of the slide operation body 20. In the form of the slide operation body 20 shown in FIG. 9, the outer spline portion 21 has eight teeth and is distributed at a pitch of 45 degrees in the circumferential direction. FIG.
In the form of the winding body 10 shown by, the inner spline portion 11 is provided with 24 teeth or concave portions and is distributed at a pitch of 15 degrees in the circumferential direction. The slide operating body 20 is provided with a spline portion 7 provided on the outer peripheral surface of the cylindrical shaft body 70.
1 (FIG. 11) is provided with a groove that meshes with 1 (FIG. 11), that is, the inner spline portion 23 is movable, but is not rotatable around the cylindrical shaft body 70, although it is movable in the axial direction. Further winding body 30
The rotation around the cylindrical shaft body 70 of the idler 3 will be described later.
By the action of 0, the pitch is limited to a predetermined pitch, here 15 degrees. Therefore, the inner spline portion 11 of the winding body 10 and the outer spline portion 21 of the slide operating body 20 have the slide operating body 20 disengage the winding body 10 and the idler 30 from each other. When moving in the axial direction toward the inner spline portion 11, they are always in mesh with each other.

As shown in FIG. 8, the meshing means 40 has 24 engaging tooth portions 12 which are formed side by side in the circumferential direction on a surface perpendicular to the axis X of the winding body 10, and FIG. As shown, it is composed of 24 engaged tooth portions 31 formed side by side in the circumferential direction on a surface perpendicular to the axis X of the idler 30, and the engaging / engaged tooth portions are As can be better understood from the combination of FIG. 2B, FIG. 8 and FIG. 10, the rotational displacement in the winding direction of the speed change cable of the winding body 10 given by the manual operation body causes the idler 30 in the first position to move. Inclined surface 1 which is displaced toward the second position
2a and 31a are formed. That is, when the winding body 10 is rotated in the winding direction, its rotational force is transmitted from the inclined surface 12a of the engaging tooth portion 12 to the inclined surface 31a of the engaged tooth portion of the idler 30 to move the idler 30 to the first direction. It is pushed toward the 2 position and the connection is released by the meshing means 40. When the idler 30 is preferably configured to be biased to the first position by the ring spring 4, the rotating operation of the winding body 10 in the winding direction is performed with a click feeling in units of 15 degrees.

As can be understood from the combination of FIG. 2B, FIG. 8 and FIG. 10, the cam means 50 are arranged in the circumferential direction on the outer peripheral surface of the end portion of the slide operation body 20 on the idler 30 side. 12 slanting cam surfaces 22 are formed here, and 12 slanting cam surfaces 22 are formed side by side in the circumferential direction on the inner peripheral surface of the idler 30 on the side of the slide operation body 20 so as to fit the slanting cam surfaces 22. And the inclined cam follower surface 32 of. The shape of the both inclined surfaces is such that the inclined cam follower surface 32 is in contact with the inclined cam surface 22 by moving the idler 30 toward the second position.
The idler 30 is further moved to the second position via the, and further movement operation of the slide operation body 20 is set to rotate the idler 30 in the axial stop position in the winding direction. By this rotation of the idler 30, the engaging tooth portion 12 of the winding body 10 comes to a position corresponding to the area of the next engaged tooth portion 32 of the idler 30. Next, when the slide operating body 20 is returned to the first position, the winding body 30 moves in the rewinding direction and the engaging tooth portion 12
And the next engaged tooth portion 32 rotate until they mesh with each other. The winding body 30 This rotation in the rewinding direction can be reliably performed by one pitch of the meshing means 40 by the function of the winding body holding means 60 described above. In order to allow the idler 30 to rotate a predetermined amount, as shown in FIG. 10, an inner spline portion 71 formed on the inner peripheral surface of the idler 30.
Each recessed portion has a rotational play of about 5 degrees in the circumferential direction with respect to the width of one tooth of the spline portion 71 provided on the outer peripheral surface of the cylindrical shaft body 70.

In the preferred embodiment of the present invention, on the one hand, the inclined cam surface 22 for the cam means 50 formed on the slide operating body 20 and the spline portion 71 of the cylindrical shaft body 70.
The inner spline portion 23 that meshes with is located on substantially the same plane perpendicular to the axis X, and on the other hand, for the engaged tooth portion 31 for the meshing means 40 formed on the idler 30 and the cam means 50. The formed inclined cam surfaces 32 are located on substantially the same plane perpendicular to the axis X, which contributes to reducing the axial dimensions of the slide operation body 20 and the idler 30. Further, when the inner spline portion 11 for the winding body holding means 60 and the engaging tooth portion 12 for the meshing means 40 are also provided on the inner peripheral side of the winding body 10 formed in a tubular shape, As is clear from FIG. 1, the entire idler 30 and the slide body are slidable in the ring space formed by the cylindrical shaft body 70 serving as a common support shaft of the winding body 10, the slide operating body 20, and the idler 30 and the winding body 10. At least a part of the operating body 20 can be stored. For this purpose, as shown in FIG. 11, one end of the cylindrical shaft body 70 has a collar portion 7 extending outward in the radial direction.
2 are provided, and through holes 73 for inserting the extension portions 24 of the slide operating body 20 extending in the axial direction are formed in the collar portion 72 in a circumferentially distributed manner at a pitch of 90 degrees. . Further, the winding body 10 is also provided with a bottom wall 13 extending inward in the radial direction at an end portion thereof away from the slide operation body 20, and the bottom wall 13 has a central portion through which the cylindrical shaft body 70 is inserted. A through hole 14 is provided. In addition, this winding body 1
0 is a second member 10a including a connecting portion 15 between the bottom wall 13 and the operation cable 10 and a second member 10b forming the inner spline portion 11 and the meshing means 40 for assembly reasons. The first member 1 is configured to be divided.
0a and the second member 10b for connecting the spline 16
Is provided. As a result, this gear shift operating device
The first member 1 of the operating body 10 with respect to the cylindrical shaft body 70 serving as a base body
0a, the second member 10b, the slide operation body 20, and the idler 30 can be easily assembled by sequentially inserting them in the axial direction.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a bicycle gear shift operation device 1 according to the present invention.
Is shown, and is fastened and fixed using the band body 2 to the handlebar 100 of the bicycle whose cross section is shown by the alternate long and short dash line. The gear shift operating device 1 basically includes a winding body 10, a slide operating body 20, and an idler 3.
0, the cylinder shaft body 70. The cylindrical shaft body 70 has an inner peripheral surface having an axis X so that the cylindrical shaft body 70 engages with a radial stepped hole provided in the band body 2 and is externally fitted and mounted on the shaft 2a extending outward in the engaging direction. Is fixed by the tightening nut 2b, and the slide operation body 20 and the idler 3 are attached to the outer peripheral surface of the cylindrical shaft body 70 having the axis X.
0, the cylinder shaft body 70 is externally fitted and mounted. At that time, the slide operating body 20 and the cylindrical shaft body 70 cannot rotate relative to each other due to the engagement of the inner spline part 23 provided on the slide operating body 20 and the outer spline part 71 provided on the cylindrical shaft body 70, and thus the relative rotation is impossible. Is displaceably connected to. On the other hand, as can be understood from FIG. 10, the idler 30 and the tubular shaft body 70 are connected by the engagement of the inner spline portion 33 provided on the idler 30 and the outer spline portion 71 provided on the tubular shaft body 70. However, since the engagement is provided with a play of about 5 degrees in the circumferential direction, the idler 30 is allowed to rotate about 5 degrees around the cylindrical axis X with respect to the cylindrical shaft body 70, and the idler 30 is rotated. It can be displaced in any direction.
The winding body 10 is rotatable along the outer peripheral surface of the cylindrical shaft body 70, that is, about the axis X. The winding body 10 is connected to a derailleur (not shown here) by the operation cable 3, and by rotating the operation body 10 in the winding direction of the operation cable 3, the operation cable 3 is pulled, and the derailleur increases, for example. The speed can be switched. On the contrary, the operation cable 3 is loosened by rotating the operation body 10 in the rewinding direction of the operation cable 3, and the derailleur is switched to the deceleration direction by the action of the return spring or the like.

The winding body 10 is rotated in the winding direction by rotating a disk-shaped dial 5 rotatably supported by a pin 2c protruding from the side of the band body 2 at a right angle to the shaft 2a. Done by For this purpose, a bevel gear mechanism 8 is provided between the dial 5 and the cylinder shaft body 10.
0 is provided.

Although the rotation of the winding body 10 in the rewinding direction will be described in detail later, it is carried out by pushing down the slide operating body 20 with the cap 6 attached to the tip portion thereof. At that time, the axial displacement of the slide operating body 20 is converted into rotational displacement via the idler 30 and transmitted to the winding body 10. For this purpose, a cam means 50 is provided between the slide operating body 20 and the idler 30.
Is provided. Further, as a so-called single shift preventing mechanism, which prevents the winding body 10 from rotating to the end position at once due to the action of a return spring or the like during a shift operation,
A winding body holding means 60 for temporarily holding the winding body 10 is provided between the slide operation body 20 and the winding body 10.

The cylindrical shaft body 7 of the winding body 10 at a desired gear shift position.
Fixing with respect to 0 is effected via the idler 30, for which purpose meshing means 40 are provided between the winding body 10 and the idler 30.

As is apparent from FIG. 1, the meshing means 40, the cam means 50, and the winding body holding means 60 described above have a winding body 10 having a bottom wall 13 extending radially inward, and a winding body 10. The structure is located in a substantially closed ring space resulting from the assembling structure of the cylindrical shaft body 70 provided with the flange portion 72 extending outward in the direction, which is a structure that is convenient from the viewpoint of dust prevention.

2 to 6, the operation of the gear shifting operation device 1 during the gear shifting operation will be described; (a) in each of FIGS. The states of the body 10, the slide operation body 20, and the idler 30 in respective operating stages are shown in cross-sectional views, and (B) shows the meshing means 40, the cam means 50, and the winding body holding means 60.
The state in each action stage of is shown in a developed schematic diagram.

FIG. 2 shows the stage before the gear shifting operation,
The winding body 10 is positioned at a predetermined position by the idler 30 via the meshing means 40 against the rotational force in the arrow R direction by the return spring or the like. The slide operating body 20 is located at the first position as the home position by the biasing force of the spring 7.

In FIG. 3, the slide operating body 20 is moved in the axial direction (to the right in the drawing) by pushing in the cap 6, and the inner spline portion 11 and the outer spline portion 21 of the position holding means 60 start to mesh with each other. The stage where the inclined cam surface 22a of the cam means 50 and the inclined cam follower surface 31a contact each other is shown.

In FIG. 4, the slide operating body 20 is further moved in the axial direction by further pushing in the cap 6, and the idler 30 and the inclined cam follower surface 32 are brought into contact with each other, and the idler 30 and the spring 4 are moved. It is moved axially (to the right in the drawing) to the end position (second position) against the urging force of the engaging tooth portion 1 of the meshing means 40.
2 shows a stage where the engagement between the engaged tooth portion 31 and the engaged tooth portion 31 is released. At this stage, that is, even though the engagement tooth portion 12 of the meshing means 40 and the engaged tooth portion 31 are disengaged from each other, the inner spline portion 11 and the outer spline portion 21 of the position holding means 60 are The winding body 10 is temporarily held by the slide operating body 20 through the meshing of.

In FIG. 5, a part of the axial displacement force transmitted to the slide operating body 20 by further pushing the cap 6 is caused by the inclined cam surface 22 and the inclined cam follower surface 31 of the cam means 50 so that the axial center of the idler 30 is moved. The idler 30 is converted by being converted into a rotational force in the direction of arrow F around X.
Indicates the stage of rotation in the direction of arrow F. By the rotation of the idler 30, the engaging tooth portion 12 and the engaged tooth portion 31 of the meshing means 40 are displaced to the next tooth area.

FIG. 6 shows that the slide operating body 20 is moved toward the first position by releasing the pushing on the cap 6, whereby the inner spline portion 11 and the outer spline portion 21 of the position holding means 60 mesh with each other. When the idler 30 is disengaged, the idler 30 is axially moved toward the slide operation body 20 (to the left in the drawing) by the spring 4. At this stage, the engagement of the position holding means 60 is disengaged, the winding body 10 rotates in the direction of arrow R, and the idler 30 moves to the left in the axial direction. By the engagement tooth portion 31 meshingly entering, the winding body 10 finally completes one-step gear shifting in the arrow R direction, for example, decelerating gear shifting.

The reverse gear shift, for example, the speed-up gear shift, is performed by rotating the dial 5 to rotate the winding body 10 in the arrow F direction. At this time, the idler 30 is axially rightward, that is, meshed. Since the means 40 moves in the disengagement direction of the means 40 against the biasing force of the spring 4, the stepwise rotation of the winding body 10 is realized for each tooth like a ratchet mechanism. For this purpose, the engaging teeth 12 and the engaged teeth 32 of the meshing means 40 are inclined surfaces so as to cause the rotation of the winding body 10 in the direction of arrow F to cause an axial displacement that disengages the idler 30. And vertical surfaces are formed in an alternating repeating shape.

[Brief description of the drawings]

FIG. 1 is a partial sectional side view showing an embodiment of a shift operating device according to the present invention.

2 shows an operating state of the gear shift operating device according to FIG.
(A) is a cross-sectional side view, and (b) is a developed schematic view of meshing means, cam means, and winding body holding means.

3 shows an operating state of the gear shift operating device according to FIG.
(A) is a cross-sectional side view, and (b) is a developed schematic view of meshing means, cam means, and winding body holding means.

4 shows an operating state of the gear shift operating device according to FIG. 1,
(A) is a cross-sectional side view, and (b) is a developed schematic view of meshing means, cam means, and winding body holding means.

5 shows an operating state of the gear shift operating device according to FIG. 1,
(A) is a cross-sectional side view, and (b) is a developed schematic view of meshing means, cam means, and winding body holding means.

6 shows an operating state of the gear shift operating device according to FIG.
(A) is a cross-sectional side view, and (b) is a developed schematic view of meshing means, cam means, and winding body holding means.

7 is a front view of the second member of the winding body as seen from the direction of arrow A in FIG.

FIG. 8 is a front view of the second member of the winding body as seen from the arrow B of FIG.

9 is a front view of the slide operating body as viewed from the direction of arrow C in FIG.

10 is a front view of the idler including a cross section of the cylindrical shaft body as viewed from the arrow D of FIG.

FIG. 11 is a partial cross-sectional side view of the cylindrical shaft body.

[Explanation of symbols]

 10 winding body 20 slide operation body 30 idler 40 meshing means 50 cam means 60 winding body holding means

Claims (8)

[Claims] 1. A winding body (10) rotatable about an axis (X) for winding up the speed change cable for operating the transmission through the speed change cable, and the winding body (10). To rotate the shaft in one direction
A bicycle gear shift operation device comprising: an operation unit that is operated to be displaced in the (X) direction, wherein the operation unit is displaceable in the axial center (X) direction between a first position and a second position, and An idler (30) displaceable around the axis (X), and a slide operation body (20) displaceable in the axis (X) direction in conjunction with the idler (30), and Between the winding body (10) and the idler (30) for engaging the idler (30) and the winding body (10) in the first position of the idler (30) and releasing them in the second position. The meshing means (40) is formed,
The slide operating body for converting the displacement of the slide operating body (20) in the axial center (X) direction at the second position of the idler (30) into the displacement around the axial center (X) of the idler (30). A bicycle gear shifting operation device in which a cam means (50) is formed between the (20) and the idler (30). 2. The winding body (10) and the slide operating body (20)
And the idler (30) is configured as a ring body, the winding body (10), the slide operation body (20), and the idler (30) are arranged concentrically with respect to the shaft core (X). The bicycle gear shifting operation device according to claim 1. 3. A winding body holding means (60) for preventing rotation of the winding body (10) when the winding body (10) and the idler (30) are separated from each other. The gear shift operation device for a bicycle according to 1 or 2. 4. The winding body holding means (60) comprises the winding body (1).
The bicycle according to claim 3, comprising an inner spline portion (11) formed on the inner peripheral surface of (0) and an outer spline portion (21) formed on the outer peripheral surface of the slide operation body (20). Gear change operation device. 5. The slide means (2) for the cam means (50).
(0) a plurality of inclined cam surfaces (22) formed side by side in the circumferential direction and the idler (3) so as to fit the inclined cam surfaces (22).
The bicycle gear shifting operation device according to any one of claims 1 to 4, wherein the bicycle gear shifting operation device comprises a plurality of inclined cam follower surfaces (32) which are formed side by side in the circumferential direction in (0). 6. The engagement means (40) is formed in the winding body (10) in a circumferential direction and a plurality of engaging tooth portions (12) formed in the circumferential direction in the idler (30). A plurality of engaged tooth portions (31) that are engaged with each other, and the engaging / engaged tooth portions have the first rotational displacement of the winding body (10) in the speed change cable winding direction. The bicycle gear shift operating device according to any one of claims 1 to 5, which is formed so as to displace the idler (30) in the position toward the second position. 7. The winding body (10) and the slide operating body (20)
The shift operating device for a bicycle according to any one of claims 1 to 6, wherein the idler (30) and the idler (30) are supported by a common tubular shaft body (70). 8. The bicycle gear shifting operation device according to claim 1, further comprising a biasing means (4) for biasing the idler (30) to the first position.