Bicycle speed change operation assembly

A bicycle speed change operation assembly (A) of the present invention has a rotatable operation member (2) and is connected to a speed change device of the bicycle via a control cable (C), wherein the assembly includes a first link (3) and a second link (4). An end (3b) of the first link (3) and an end (4b) of the second link are connected for relative pivotal movement. The other end (3a) of the first link 3 is supported so as to be moved circumferentially of the operation member (2) upon rotation thereof. The other end (4a) of the second link (4) is pivotally supported at a fixed point, and an end of the control cable (C) is connected to the second link (4).

This application is a U.S. National Stage filing of PCT/JP96/00907 filed 
Mar. 29, 1996 and claiming priority from Japanese Application Nos. 
7-100491 and 7-212807, filed Mar. 31, 1995 and Jul. 27, 1995, 
respectively. 
TECHNICAL FIELD 
The present invention relates to a bicycle speed change operation assembly 
used for remotely operating a bicycle speed change device such as a rear 
derailleur, a front derailleur and the like via a control cable. 
BACKGROUND ART 
An example of conventional bicycle speed change operation assemblies of the 
above type is disclosed in U.S. Pat. No. 5,102,372. The bicycle speed 
change operation assembly of the patent includes an operation member 3e 
mounted around a handlebar 1E of the bicycle for rotational movement and a 
cam plate 130 attached to the outer surface of the operation member 3e, as 
shown in FIG. 41a of the application. The outer surface of the cam plate 
130 is brought into contact with a control cable C2 connected to a speed 
change device of the bicycle. The control cable C2 has a nipple 14 
attached to a suitable portion of a housing case 131. 
With such a bicycle speed change operation assembly, upon rotation of the 
cam plate 130 in the direction of arrow N30 by rotating the operation 
member 3e, the length of the outer surface portion of the cam plate 130 
coming into contact with the control cable C2 increases from Sc to Sd as 
shown in FIG. 41b. Thus, the control cable C2 can be pulled by the cam 
plate 130 in the direction of arrow N30 by an amount of (Sd-Sc). Further, 
the actual pulled length (Sd-Sc) of the control cable C2 can be smaller 
than the rotational displacement of the operation member 3e. Thus, 
according to the above bicycle speed change operation assembly, the 
operation cable C2 can be pulled by small pitches upon rotation of the 
operation member 3e by rather large rotational angles. 
Where a large amount of the control cable C2 is pulled due to a small 
amount of rotational angle of the operation member 3e, even if the cyclist 
slightly rotates the operation member 3e, the speed change device is 
inadvertently caused to perform a speed change operation. Further, when 
causing the speed change device to shift from the first speed level to the 
second speed level for example, an operational error is likely to occur 
with a result that the shifting is performed to the third speed level due 
to too much rotation of the operation member 3e. On the other hand, the 
bicycle speed change operation assembly described above can overcome such 
an inconvenience. 
However, the conventional assembly described above is not arranged to 
directly pull the control cable C2 by the rotational operation of the 
operation member 3e but designed to pull the control cable C2 forcefully 
along the outer circumferential surface of the cam plate 130 in contact 
with the control cable C2. 
Further, the speed change device always exerts a spring force on the 
control cable C2, thereby constantly giving the control cable C2 a tension 
T toward the speed change device. Thus, rather large frictional resistance 
will act on the control cable C2 for pulling the control cable C2 by the 
rotational operation of the cam plate 130. 
Thus, conventionally, a large rotational operation torque is needed to pull 
the control cable C2 for rotating the operation member 3e. In the above 
conventional bicycle speed change operation assembly, the actual pulling 
amount for the control cable C2 is rendered small for the rotational angle 
of the operation member 3e. Therefore, theoretically, the rotational 
operation torque for the operation member 3e should be small due to the 
function of a force-magnifying mechanism. However, in reality, it is 
disadvantageously difficult to handle the operation member 3e due to the 
frictional resistance between the control cable C2 and the cam plate 130. 
Especially, after the conventional assembly has been used for a long 
period, the outer circumferential surface of the cam plate 130 will be 
formed with a groove due to the frictional contact with the control cable 
C2. As a result, the control cable C2 is fitted into the groove, thereby 
making it more difficult to handle the operation member 3e. 
DISCLOSURE OF THE INVENTION 
An object of the present invention is to make it possible to cause the 
control cable to be slightly displaced by a large rotational angle of the 
operation member of the bicycle speed change operation assembly without 
deteriorating the handling performance of the bicycle speed change 
operation assembly. 
According to the present invention, there is provided a bicycle speed 
change operation assembly which has a rotatable operation member and is 
connected to a speed change device of the bicycle via a control cable, 
wherein the assembly includes a first link and a second link, an end of 
the first link and an end of the second link are connected for relative 
pivotal movement, another end of the first link is supported so as to be 
moved circumferentially of the operation member upon rotation thereof, 
another end of the second link is pivotally supported at a fixed point, 
and an end of the control cable is connected to the second link. 
According to the present invention, the operation member may be generally 
cylindrical for rotational operation around a handlebar of the bicycle. 
Further, said another end of the first link may be connected to the 
operation member or a member rotating with the the operation member. Said 
another end of the second link may be connected to a fixed shaft supported 
by a member which is fixed to the handlebar of the bicycle. 
In the present invention, upon rotation of the operation member said one 
end of the first link is displaced circumferentially of the operation 
member with the rotation of the operation member. Thus, the second link 
pivots to pull or pay out the control cable, thereby causing the speed 
change device of the bicycle to perform a speed change operation. 
The link mechanism constituted by the first link and the second link is a 
force-magnifying mechanism wherein the displacement of each portion of the 
second link is made smaller than that of the displacement of said one end 
of the first link circumferentially of the operation member. Thus, it is 
possible to make the pulling or paying-out amount for the control cable 
smaller than the rotational operation amount of the operation member to 
move said one end of the first link, thereby enabling a small amount of 
pulling or paying-out of the control cable by rotating the operation 
member by a large angle. As a result, it is possible to ensure a reliable 
speed change operation for one stage after another for the speed change 
device of the bicycle, thereby improving the handling performance of the 
speed change device. 
According to the present invention, unlike the prior art, the control cable 
is pulled or paid out directly by the second link, thereby avoiding a 
large frictional resistance in operating the control cable. The link 
mechanism constituted by the first link and the second link works to 
convey the magnified rotational operation torque of the operation member 
to the control cable. Therefore, it is possible to advantageously make the 
rotational torque needed to operate the operation member smaller than that 
of the prior art, thereby improving the handling performance. 
According to a preferred embodiment of the present invention, the first 
link has a concave surface fitting on an outer surface of a member which 
faces a movable portion of the first link. 
With such an arrangement, in shifting the first link circumferentially of 
the operation member by rotating the operation member, the concave surface 
of the first link can be fitted on the outer surface of the member which 
faces the movable portion of the first link, thereby preventing 
interference between the member and the first link. As a result, the 
displacement of the first link can be made large, while the bulging of the 
first link around the member is reduced as much as possible. 
According to another preferred embodiment of the present invention, the 
second link has a concave surface fitting on an outer surface of a member 
which faces a movable portion of the second link. 
With such an arrangement, in pivoting of the second link, the concave 
surface of the second link can be fitted on the outer surface of the 
member which faces a movable portion of the second link, thereby 
preventing interference between the member and the second link. As a 
result, a large bulging of the second link around the member can be 
prevented as much as possible, thereby advantageously reducing the bicycle 
speed change operation assembly as a whole in size. 
According to another preferred embodiment of the present invention, where 
the operation member is generally cylindrical for rotational operation 
around the handlebar of the bicycle, the second link may be arranged to be 
vertically pivotable below the handlebar of the bicycle. 
With such an arrangement, the second link can be prevented as much as 
possible from largely bulging around the handlebar forward and backward of 
the bicycle. Further, the first link connected to the second link can be 
arranged to take a position in which the longitudinal direction of the 
first link coincides the vertical direction, so that the first link is 
prevented as much as possible from largely bulging relative to the 
handlebar forward and backward of the bicycle. In this way, it is possible 
to prevent the entirety of the link mechanism constituted by the first 
link and the second link from bulging relative to the handlebar forward 
and backward of the bicycle. Thus, advantageously, size reduction and 
improved outer appearance for the assembly as a whole are obtainable. 
According to another preferred embodiment of the present invention, the 
assembly may comprise a positioning mechanism which is capable of holding 
the operation member at a plurality of predetermined rotational angular 
positions. 
With such an arrangement, the holding of the operation member at a desired 
rotational angular position allows the pulling amount for the control 
cable to be maintained at a constant value. Thus, it is possible to 
properly keep the speed change level for the speed change device at a 
desired value. 
According to another preferred embodiment of the present invention, the 
positioning mechanism may comprise an engaging member movable with the 
operation member, a positioning plate having a plurality of engaging 
bores, and a spring member for elastically urging the engaging member 
toward the positioning plate to bring the engaging member into releasable 
engagement with each of the plurality of engaging bores. 
According to such an arrangement, rotation of the operation member can be 
prevented by bringing the engaging member into engagement with one of the 
plurality of engaging bores of the positioning plate, so that the 
operation angle of the operation member is maintained at a constant level. 
Thus, whenever the speed change device is caused to perform a desired 
speed change operation, the speed change device can be properly held at a 
desired speed change level. 
According to another preferred embodiment of the present invention, the 
positioning plate may be rotatable by a predetermined angle in a rotating 
direction of the engaging member to enable an overshift of the speed 
change device of the bicycle. 
With such an arrangement, in causing the speed change device to perform a 
speed change operation by pulling the control cable, the operation member 
can be rotated additionally by a predetermined angle with the positioning 
plate to pull the control cable in an amount greater than needed for the 
speed change operation of the speed change device for performing overshift 
operation. Such an overshift function makes it possible to reliably 
perform a speed change operation of the speed change device. 
According to another preferred embodiment of the present invention, the 
positioning mechanism may comprise a plurality of engaging recesses 
rotatable with the operation member, an engaging member arranged to face 
the plurality of engaging recesses, and a spring member for elastically 
urging the engaging member in facing relation to the plurality of engaging 
recesses to bring the engaging member into releasable engagement with each 
of the plurality of engaging recesses. 
With such an arrangement, by bringing the engaging member into engagement 
with one of the plurality of engaging recesses, the operation member is 
prevented from rotating and the operational angle of the operation member 
is maintained at a desired operational angle and the speed change device 
can be held at a desired value of the speed change levels. Since the above 
positioning plate is not necessarily required, the over all structure can 
be simplified. 
According to another preferred embodiment of the present invention, the 
engaging member may be reciprocally movable within a predetermined range 
in a rotating direction of the plurality of engaging recesses to enable an 
overshift of the speed change device of the bicycle. 
With such an arrangement, in causing the speed change device to perform a 
speed change operation by pulling the control cable, the operation member 
can be additionally rotated beyond a predetermined angle by shifting the 
engaging member in engagement with an engaging recess in the rotating 
direction of the plurality of engaging recesses to realize an overshift 
wherein the control cable is pulled in an amount greater than needed for a 
speed change operation of the speed change device. Such an overshift 
function makes it possible to reliably perform the speed change operation 
of the speed change device. 
According to another preferred embodiment of the present invention, the 
spring member may be arranged not to urge the engaging member toward an 
inner wall of any one of the plurality of engaging recesses when the 
engaging member comes into engagement with said any one of the plurality 
of engaging recesses. 
With such an arrangement, when the engaging member is held in engagement 
with one of the engaging recesses, the engaging member is not urged toward 
the inner wall of the engaging recess by the spring member. Thus, it is 
possible to prevent the operation member from suffering deterioration of 
the handling performance, which would otherwise be caused due to large 
contact friction between the engaging member and the inner wall of the 
engaging recess. Particularly, in performing an overshift operation 
wherein the operation member is rotated in an amount greater than needed 
for a desired speed change operation of the speed change device, the 
operation member can be advantageously brought back to the actual angular 
position by the tension acting on the control cable after the overshift. 
According to another preferred embodiment of the present invention, the 
assembly may comprise a positioning ring which releasably engages the 
operation member and the plurality of engaging recesses are formed in the 
positioning ring. 
With such an arrangement, when the plurality of engaging recesses are 
intended to be modified correspondingly to the specifications of the 
bicycle speed change device, the modification can only be made to the 
positioning ring. Specifically, when modifying the bicycle speed change 
device having a six-speed function to that having a seven-speed function, 
the number of the engaging recesses is needed to vary accordingly. Such a 
modification is possible only by altering the positioning ring. Thus, 
design specifications can be easily changed correspondingly to the speed 
change device. 
According to another preferred embodiment of the present invention, the 
positioning ring may be rotatable within a predetermined angular range 
relative to the operation member to enable an overshift of the speed 
change device of the bicycle. 
With such an arrangement, in causing the speed change device to perform a 
speed change operation by pulling the control cable, it is possible to 
provide an overshift function wherein the control cable is pulled in an 
amount greater than needed for the speed change operation by rotating the 
operation member with the positioning ring more beyond a predetermined 
angle. 
According to another preferred embodiment of the present invention, the 
assembly may comprise a cable supporting guide pivotable with the second 
link about a fixed shaft which is concentric with a pivot center of the 
second link. The cable supporting guide has a guide surface for supporting 
the control cable in contact therewith, and the guide surface is 
configured in an arcuate form which is concentric with a pivot center of 
the cable supporting guide. 
With such an arrangement, in pulling the control cable by the second link, 
the control cable can be guided along the arcuate guide surface of the 
cable supporting guide, so that the control cable is prevented from unduly 
bending. Thus, it is possible to prevent the control cable from suffering 
damages which would otherwise be caused by the bending of the control 
cable. 
The control cable is not guided by the guide surface of the cable 
supporting guide in sliding contact therewith, but guided by the cable 
supporting guide which pivots in the pulling direction for the control 
cable. Therefore, no large frictional force is generated between the 
control cable and the cable supporting guide for pulling the control 
cable, thereby requiring less rotational operation torque for the 
operation member to pull the control cable. 
Further, the control cable is guided by the arcuate guide surface which is 
concentric with the pivot center of the second link. Therefore, the actual 
pulling or paying-out length of the control cable connected to the second 
link can be rendered to exactly correspond to the pivot angle of the 
second link. As a result, the setting of the pulling or paying-out amount 
for the control cable is facilitated. If the displaced length of the 
control cable does not exactly correspond to the pivot angle of the second 
link, it becomes difficult to determine a desired displaced length of the 
control relative to the rotational operation angle of the operation 
member. However, the above arrangement makes it possible to avoid such an 
inconvenience. 
According to another preferred embodiment of the present invention, said 
end of the control cable may be connected to the second link so that said 
end of the control cable is pulled along a straight path from an upper 
portion of a cable guide when the second link pivots. 
With such an arrangement, the control cable can be properly pulled by the 
second link without using the cable supporting guide described above, 
thereby requiring less parts. Since the control cable pulled by the second 
link follows a straight path, the control cable is prevented from 
disadvantageously suffering an inconvenience such as bending. Further, in 
pulling the control cable, it is possible to prevent the control cable 
from suffering a frictional force which would otherwise occur on the 
control cable due to contacting other members. Sill further, the pulling 
length of the control cable can be arranged to properly correspond to the 
rotational operation angle of the operation member.

BEST MODE FOR CARRYING OUT THE INVENTION 
A first embodiment of the present invention will be described with 
reference to FIGS. 1-14. 
In FIGS. 1 and 2, a bicycle speed change operation assembly A for causing a 
bicycle rear derailleur (not shown) to perform a speed change operation is 
mounted adjacent to a right-hand grip 10 of a handlebar 1 made of a metal 
pipe. The rear derailleur is used for shifting a chain 13 among rear gears 
including 6-speed freewheels 12a-12f mounted on a hub 11 of the rear wheel 
of the bicycle as shown in FIG. 4 for example and includes a guide pulley 
for pushing the chain 13 for lateral movement, a tension pulley located 
therebelow for taking up the slack of the chain, and the like. A bicycle 
front derailleur described hereinafter is used for shifting the chain 13 
among 3-speed front gears 15a-15c. 
The above-described rear derailleur is designed as a top-normal type and 
performs sequential shifting events of the chain 13 from a top gear 12a 
for the sixth speed level to a low gear 12f for the first speed level when 
a control cable C (inner wire) connected to the rear derailleur is pulled 
in the direction of the bicycle speed change operation assembly A. 
Conversely, when the control cable C is paid out from the bicycle speed 
change operation assembly A toward the rear derailleur, the chain 13 is 
shifted in the direction opposite to the above-mentioned direction. The 
derailleur includes a pantograph mechanism with a spring (not shown), and 
the spring force is always exerted on the control cable C to cause the 
chain 13 to engage the diametrically smallest top gear 12a when the 
control cable C is not pulled toward the bicycle speed change operation 
assembly A. 
The bicycle speed change operation assembly A is constituted by an 
operation member 2 externally fitted about the handlebar 1 for rotational 
movement, a first link 3 and a second link 4 which constitute a link 
mechanism, a positioning plate 5 for positioning the second link 4, a 
spring member 6, a cable support guide 7 for supporting and guiding the 
control cable C, a fixing ring 8 attached externally about the handlebar 
1, and a housing case 9 accommodating the above elements for protection 
thereof. 
As shown in FIGS. 5a and 5b, the operation member 2 is generally 
cylindrical having a through-hole 20 and a flange 21 and can be externally 
fitted about the bicycle handlebar 1. The operation member 2 has an end 
surface formed with bores 23, 23a as well as with grooves 22, 22a, each of 
which has a generally circular front view, at the locations of the bores 
23, 23a. Of these, the groove 22 and the bore 23 are used for pivotally 
connecting a first end 3a of the first link 3 to the operation member 2. 
Specifically, as shown by single-dot chain lines in FIG. 5b, the first end 
3a of the first link 3 is inserted into the groove 22 and thereafter a pin 
31 is inserted through the bore 23 of the operation member 2 and the 
through-hole 30a of the first link 3, thereby connecting the first link to 
the operation member 2 for pivotal movement about the pin 31. Thus, upon 
rotation of the operation member 2 externally fitted about the handlebar 
1, the first end 3a of the first link 3 is moved around the handlebar with 
the rotation of the operation member 2. In the arrangement of a speed 
change operation assembly Aa (FIG. 15) mounted on the left-hand end of the 
handlebar 1 for the below-described front derailleur, the other groove 22a 
and bore 23a are used for fixation of a first link 3 of the speed change 
operation assembly Aa. 
The operation member 2 includes at one end surface thereof a stepped 
portion 24 providing an arcuate front view. When the operation member 2 is 
rotated as shown in FIG. 13, the stepped portion 24 functions as a stopper 
by causing an end surface 24a of the stepped portion 24 to come into 
engagement with a first fixed shaft 80 attached to a fixing ring 8, 
thereby preventing any further rotational movement of the operation member 
2. The other end surface 24b of the stepped portion 24 will be used for 
engagement with the first fixed shaft 80 of the speed change operation 
assembly Aa in application of the operation member 2 for the speed change 
operation assembly Aa described hereinafter. 
As shown in FIG. 5b, the operation member 2 is formed with projections 25 
on the external surface located on a side of the flange 21, wherein the 
projections extend longitudinally of the operation member 2. As shown in 
FIG. 2, for external fitting of a tubular operation grip 28 of synthetic 
rubber on the operation member 2, the projections 25 fittingly engage 
spline grooves 27 formed in the internal surface of the operation grip 28. 
This renders the operation member 2 and the operation grip 28 mutually 
engaged, unable to perform a relative rotational movement. Thus, the 
operation member 2 will rotate about the handlebar with the rotational 
operation of the operation grip 28. 
The operation member 2 may be formed with a plurality of radially extending 
projections 21A, as shown in FIGS. 6a and 6b for example, instead of the 
flange 21 shown in FIG. 5b. With the operation member 2 having such an 
arrangement, the cyclist can rotate the operation member 2 by engaging a 
finger with the plurality of projections 21A, thereby facilitating the 
rotational operation of the operation member 2. 
As shown in FIG. 3, the first link 3 is made in a form of a thin plate. The 
first link 3 has a curved configuration and includes a concave surface 30 
whose radius of curvature is equal or generally equal to the radius Ra of 
the handlebar 1. Therefore, upon rotation of the operation member 2 as 
shown in FIG. 13 for example, the concave surface 30 of the first link 3 
is brought into fitting engagement with the outer surface of the handlebar 
1. Thus, the first link 3 can rotate around the handlebar without bulging. 
The second link 4 is constituted by a pair of plates 47A, 47B, as shown in 
FIG. 3. These two plates 47A, 47B are similar in appearance for example. 
However, of the two, the plate 47A is formed with a control cable 
connecting portion 41 for inserting the control cable C and fixing a 
nipple 14 attached at an end of the control cable C. 
The pair of plates 47A, 47B are formed with through-holes 40a, 40a at their 
respective first ends 4a, 4a. A second fixed shaft 49 is inserted through 
the respective through-holes 40a, 40a of the two plates 47A, 47B in 
series. The second fixed shaft 49 is attached to the fixing ring 8 like 
the first fixed shaft 80. A second end 3b of the first link 3 is inserted 
between respective second ends 4b, 4b of the plates 47A, 47B, and a 
connecting pin 48 is inserted in series through the through-holes 40b, 40b 
of the plates 47A, 47B and the through-hole 30b in the second end 3b of 
the first link 3. The second end 3b of the first link 3 and the second end 
4b of the second link 4 are connected via the connecting pin 48 for 
relative pivotal movement. 
As shown in FIGS. 7a and 7b, the positioning plate 5 includes a bore 50 and 
six engaging bores 51a-51f arranged along a circle cocentric with the bore 
50 and having a predetermined radius R4. As shown in FIG. 3, an upper part 
of the positioning plate 5 will be located between the respective first 
ends 4a, 4a of the pair of plates 47A, 47B constituting the second link 4. 
The bore 50 receives the second fixed shaft 49 extending therethrough. 
Thus, the positioning plate 5 can pivot around the second fixed shaft 49 
in the same direction as the pivotal direction of the second link 4. 
However, the first fixed shaft 80 is arranged to extend through a 
semicircular cutout 52 formed in an edge of the positioning plate 5. The 
outside diameter of the first fixed shaft 80 is smaller than the inside 
diameter of the cutout 52. Thus, as shown in FIG. 7a, the positioning 
plate 5 can pivot around the fixed shaft 49 extending through the bore 50 
by a small angular range of clearance A formed between the inner surface 
end of the cutout 52 and the outer surface of the first fixed shaft 80. 
The maximum pivotal angle of the positioning plate 5 is smaller than 
respective pitch angles .theta.1-.theta.5 defined between the engaging 
bores 51a-51f. 
As shown in FIG. 3, the spring member 6 has an overall configuration 
similar to tweezers providing a U-shaped front view and includes a pair of 
opposite pieces 60, 60. The pair of opposite pieces 60, 60 are designed to 
provide an urging toward each other, and therebetween are provided two 
metal balls 61, 61, which are an example of engaging members of the 
present invention, thus constituting a positioning mechanism shown in FIG. 
8. 
Specifically, in the positioning mechanism shown in FIG. 8, the balls 61, 
61 are fitted into respective bores 42, 42 formed in the pair of plates 
47A, 47B constituting the second link 4. The spring member 6 is mounted on 
the pair of plates 47A, 47B, and their opposite pieces 60, 60 elastically 
urge the balls 61, 61 in an approaching direction to each other. With such 
an arrangement, the balls 61, 61 can be brought into releasable engagement 
with the engaging bore 51a as well as each of the other engaging bores 
51b-51f of the positioning plate 5. Specifically, supposing that the balls 
61, 61 are fitted into the engaging bore 51a of the positioning plate 5 at 
first, when the second link 4 is caused to pivot about the second fixed 
shaft 49, the balls 61, 61 can be moved out of the engaging bore 51a to 
engage the neighboring engaging bore 51b. Similarly thereafter, the balls 
61, 61 can be brought into releasable engagement with the other engaging 
bores 51c-51f one after another. 
The spring member 6 should be secured to the second link 4. For this 
purpose, as shown in FIG. 3 for example, the spring member 6 and the 
second link 4 are connected via a pin 63 extending in series through a pin 
bore 62 of the spring member 6 and respective pin bores 43, 43 formed in 
the plates 47A, 47B. 
The cable supporting guide 7 is made in a form of a generally sectorial 
plate as a whole and has two through-holes 70, 71. The through-hole 70 
receives the second fixed shaft 49 extending therethrough. The other 
through-hole 71 is provided for fixing the cable supporting guide 7 to the 
plate 47A via e.g. a rivet 73 as shown in FIG. 1. Thus, the cable 
supporting guide 7 pivots with the second link 4 about the second fixed 
shaft 49 extending through the through-hole 70. 
The cable supporting guide 7 also has an arcuate guide surface 72 
concentric with the second fixed shaft 49 and the through-hole 70, which 
are the pivot center of the cable supporting guide 7. As shown in FIG. 1, 
the control cable C is supported by the guide surface 72 in contact 
therewith. Therefore, the guide surface 72 is preferably provided with a 
groove or projections for example to prevent the control cable C from 
coming off the guide surface 72. The radius of curvature of the guide 
surface 72 corresponds to the winding radius for the control cable C and 
is smaller than the radius R4 of the circle shown in FIG. 7, along which 
the engaging bores 51a-51f of the positioning plate 5 are provided. 
As shown in FIGS. 9a and 9b, the fixing ring 8 has a through-hole 81 by 
which the fixing ring 8 is externally fitted around the handlebar 1 of the 
bicycle. The fixing ring 8 has an outer surface formed with threaded bores 
83, 83 each for engaging a set screw 82. The fixing ring 8 can be 
non-rotatably positioned on the handlebar 1 by pressing the front end of 
each set screw 82 onto the outer surface of the handlebar 1. Further, the 
fixing ring 8 has a side surface formed with two bores 84 for attaching 
the second fixed shaft 49 extending therethrough and a bore 85 for 
attaching the first fixed shaft 80 extending therethrough. Two of the 
bores 84 are formed so that the fixing ring 8 can be also applied to the 
front derailleur speed change operation assembly Aa mounted on the 
left-hand end of the handlebar 1. 
As shown in FIG. 1, the housing case 9 is formed by two separate members, 
an upper member 90A and a lower member 90B. The upper member 90A and the 
lower member 90B are connected at respective ends thereof via a shaft 90 
for relative pivotal movement. The other ends of the respective upper 
member 90A and lower member 90B are bolted by a bolt 91 and a nut 91a. 
Thus, the housing case 9 can be fixed by clamping part of the outer edge 
of the fixing ring 8 secured on the handlebar 1. 
The lower member 90B is provided with a bore (not shown) through which the 
first fixed shaft 80 secured to the fixing ring 8 is inserted, thereby 
preventing the housing case 9 as a whole from rotating around the 
handlebar. As shown in FIG. 2, side walls 93a, 93b of the housing case 9 
are brought into engagement with the flange 86 of the fixing ring 8 and 
the flange 21 of the operation member 2, thereby enabling longitudinal 
positioning along the handlebar 1. Members such as the first link 3 and 
the second link 4 for example are accommodated within the housing case 9. 
The housing case 9 may be made of opaque synthetic resin or alternatively 
of transparent resin. In using transparent resin for the housing case 9, a 
pointer K as an indicator can be provided at a suitable portion of the 
first link 3 shown in FIG. 1, and the cyclist can see the pointer K 
through the housing case 9 from above. Therefore, by providing the outer 
surface of the housing case 9 with a scale or the like to indicate what 
speed level the rear derailleur is aligned with, the cyclist can know the 
position of the first link 3 and consequently the speed level of the rear 
derailleur by looking at the scale and the pointer K. 
In the bicycle speed change operation assembly A, the upper member 90A of 
the housing case 9 has a curved cross section. Therefore, when the pointer 
K is seen from outside, the pointer K is seen refracted, thereby giving an 
neater appearance to the pointer K and the housing case 9 as well as to 
the assembly as a whole. Means to make the pointer K at the first link 3 
recognizable from outside is not limited to the arrangement where the 
entirety of the housing case 9 is made of transparent resin. 
Alternatively, transparent resin may be used only for a portion 
corresponding to the pointer K. 
A cable guide 94 for guiding the control cable C is connected to the lower 
member 90B of the housing case 9. The cable guide 94 is made in a form of 
a curved tube for example to allow passage of the control cable C 
therethrough. The connection of the cable guide 94 to the lower member 90B 
may be arranged as in FIG. 10. Specifically, in the illustrated 
arrangement, an end of the cable guide 94 is inserted into a through-hole 
95 formed in the bottom surface of the lower member 90B. However, the 
above-mentioned end of the cable guide 94 is provided with a thin flange 
94a, and the through-hole 95 is formed with an inward projection 95a for 
fixing the flange 94a. According to such an arrangement, the cable guide 
94 is rotatably connected to the lower member 90B by the engagement 
between the flange 94a and the projection 95a. Thus, it is possible to pay 
out the control cable C in a suitable direction by properly rotating the 
cable guide 94. 
The outside diameter of the flange 94a is rendered larger than the inside 
diameter of the projection 95a. However, if the lower member 90B is made 
of synthetic resin, the insertion of the above-mentioned end of the cable 
guide 94 into the through-hole 95 is performed by forcing the projection 
95a to be elastically deformed into the through-hole 95. Thus, the 
connection of the cable guide 94 does not require any screws and the like, 
thereby simplifying the connecting process. 
As shown in FIG. 11, an outer cable 96 for guiding and protecting the 
control cable C is connected to the other end of the cable guide 94. The 
connection of the outer cable 96 can be accomplished by bringing a 
threaded portion 96 connected to the end of the outer cable 94 into 
engagement with a threaded portion 94b formed in the inner surface of the 
other end of the cable guide 94. 
With such a connecting arrangement, it is necessary to prevent the threaded 
portion 96a from becoming loose. According to the illustrated embodiment, 
the following means is adopted. Specifically, the cable guide 94 is 
externally provided with a ring 97 made of resilient synthetic resin which 
is capable of stretching. The inner surface of the ring 97 is formed with 
a plurality of projections 97a, 97a to fit into two bores 94c, 94c formed 
in the outer wall of the cable guide 94. According to such means, the 
projections 97a, 97a of the ring 97 pressed into engagement with the 
threaded portion 96a makes it possible to suitably overcome the problem of 
loosening of the threaded portion 96a due to an inadvertent rotation 
thereof. 
In assembling the bicycle speed change operation assembly A, first the 
fixing ring 8 is externally fitted on the handlebar 1. Then, the 
positioning plate 5, the second link 4, the cable supporting guide 7 and 
the like are put together. The one end of the control cable C is connected 
to the control cable connecting portion 41 of the second link 4. Then, 
after externally fixing the operation member 2 on the handlebar 1, the 
first link 3 is assembled, and then the housing case 9 is attached. The 
externally fitting step of an operation grip 28 on the operation member 2 
or the externally fitting step of the hand grip 10 may be performed at a 
proper timing thereafter. 
In the bicycle speed change operation assembly A having the construction 
described above, the link mechanism constituted by the operation member 2, 
the first link 3 and the second link 4 functions according to the same 
principle as in a link mechanism shown in FIG. 12. 
Specifically, in the link mechanism illustrated in FIG. 12, a first link 3' 
and a second link 4' are connected for relative pivotal movement, and an 
end 4a' of the second link 4' is supported by a second fixed shaft 49'. In 
such a mechanism, upon movement of an end 3a' of the first link 3' in the 
direction indicated by arrow N1, the second link 4' pivots about the 
second fixed shaft 49'. The displaced distance La of the end 4b' of the 
second link 4' is inevitably rendered smaller than the displacement L of 
the first link 3'. In the second link 4', the displacement of a portion 
thereof becomes smaller, as the portion comes closer to the end 4a' than 
the end 4b'. In other words, the link mechanism is arranged as a 
force-magnifying mechanism. Therefore, the control cable C connected to 
the second link 4' is pulled by an amount smaller than the displacement L 
of the first link 3', while the pulling of the the control cable C 
requires less force. 
The bicycle speed change operation assembly A differs from the link 
mechanism illustrated in FIG. 12 in that the first end 3a of the first 
link 3 is moved not in a straight path but along a curved path with the 
rotational operation of the operation member 2. However, the pulling and 
paying-out amounts of the control cable C connected to the second link 4 
of the bicycle speed change operation assembly A can be made smaller than 
the displacement of the first end 3a of the first link 3. 
Specifically, upon rotation of the operation member 2 in the direction of 
arrow N2, starting from the state shown in FIG. 1 toward the angular 
position illustrated in FIG. 13, the first end 3a of the first link 3 
connected to the operation member 2 moves by an amount L1. On the other 
hand, the displacement of each portion of the second link 4 is smaller 
than the amount L1, and the pulled displacement L2 of the control cable C 
connected to the second link 4 is much smaller than the amount L1. 
Further, the rotation angle of the second link 4 is smaller than the 
operation angle of the operation member 2. 
Thus, in operation of the rear derailleur to perform speed changes by 
sequentially pulling the control cable C, even if only small amounts of 
pulling of the control cable C cause the rear derailleur to perform 
sequential speed change operations, the cyclist can rotate the operation 
member 2 by a large amount of rotational angle to cause the rear 
derailleur to properly perform the speed change operations one after 
another. As a result, the cyclist can reliably operate the rear derailleur 
for selection of a desired speed level of the rear derailleur. 
Further, since the link mechanism constituted by the first link 3, the 
second link 4 and the like is a force-magnifying mechanism, the operation 
torque can be smaller for rotating the operation member 2 while the 
control cable C is pulled against the spring force of the rear derailleur. 
The control cable C pulled by the second link 4 is guided by the arcuate 
guide surface 72 of the cable supporting guide 7, as shown in FIG. 13. The 
cable supporting guide 7 pivots about the second fixed shaft 49 in the 
same direction and by the same amount of angle as the second link 4 does. 
Thus, every portion of the guide surface 72 will brought into engagement 
with the same point of the control cable C or in other words the control 
cable C is not pulled in sliding contact with the cable supporting guide 7 
for example. Therefore, it is possible to minimize the frictional force 
between the control cable C and the cable supporting guide 7, thereby 
preventing the pulling performance for the control cable C from 
deteriorating due to the frictional force between them. 
Further, since the guide surface 72 is made in an arcuate form which is 
concentric with the pivot center of the second link 4, the control cable C 
is always guided by a constant angle from the upper end of the cable guide 
94 toward the cable supporting guide 7, no matter how much the second link 
4 may pivot. As a result, the control cable C is not unduly bent in 
pulling the control cable C by the second link 4. Further, with the 
guiding arrangement of the control cable C by the arcuate guide surface 
72, the pivotal angle of the second link 4 can be rendered to accurately 
correspond to the actual pulling and paying-out amounts of the control 
cable C. As a result, it is easy to exactly determine the pulling and 
paying-out amounts of the control cable C in use with reference to the 
pivotal angle of the second link 4 and consequently the rotation angle of 
the operation member 2. 
As the operation member 2 is sequentially rotated, the balls 61, 61 
retained by the second link 4 are moved relative to the positioning plate 
5, caused to leave the engaging bore 51a of the positioning plate 5 and 
brought into releasable engagement with each of the other engaging bores 
51b-51f. The engaging bores 51a-51f of the positioning plate 5 are 
positioned to correspond to the speed change operations of the rear 
derailleur. The balls 61, 61 will engage the engaging bore 51a when the 
rear derailleur is shifted for the the sixth speed, whereas they will 
engage the engaging bore 51b when the derailleur is shifted for the fifth 
speed. Similarly thereafter, the balls will engage the respective engaging 
bores 51c-51f when the rear derailleur is sifted for the fourth speed to 
the first speed. In this way, it is possible to positionally retain the 
second link 4 at an intended pivotal angle by the engagement between the 
balls 61, 61 and the engaging bores 51a-51f, thereby retaining the rear 
derailleur for a desired speed level. 
Next, the operational relation between the positioning plate 5 and the ball 
61 in rotating the operation member 2 will be described. A spring force 
pulling the control cable C toward the rear derailleur always acts on the 
second link 4 and the positioning plate 5 engaging the second link 4. 
Thus, in a normal state where the cyclist keeps his hand off the operation 
grip 28, the spring force exerts a rotational force on the positioning 
plate 5 in the direction of arrow N3 so that an end 52a of the inner 
surface of the cutout 52 is held in a stabilized condition, resting on the 
first fixed shaft 80, as shown in FIG. 14a. The ball 61 is in engagement 
with the engaging bore 51a for example, thereby properly maintaining the 
rear derailleur at the position for the sixth speed. 
Then, in rotating the operation member 2 in the direction of arrow N4 shown 
in FIG. 14b to cause the ball 61 to leave the engaging bore 51a and engage 
the next engaging bore 51b, the positioning plate 5 can be rotated in the 
direction of arrow N4 until the other end 52b of the inner surface of the 
cutout 52 comes into contact with the first fixed shaft 80. Therefore, in 
shifting the rear derailleur from the position for the sixth speed to that 
for the fifth speed, the positioning plate 5 and the second link 4 
engaging the positioning plate 5 can be rotated in the direction of arrow 
N4 additionally by an amount of the clearance between the cutout 52 and 
the first fixed shaft 80. Thus, the control cable C can be pulled by an 
amount slightly greater than needed to cause the rear derailleur to 
perform a speed change operation. 
As a result, in shifting the chain 13 by pulling the control cable C, 
so-called overshift function is provided wherein the chain 13 is firstly 
displaced to a position beyond the free wheel 12b of the fifth speed by 
pulling the control cable C by an amount greater than needed to perform 
the shifting of the chain 13, and then the chain 13 is brought into 
engagement with the free wheel 12b of the fifth speed. According to this 
function, the shifting of the chain 13 can be accurately performed. 
When the cyclist removes the hand from the operation grip 28 after the ball 
61 is brought into engagement with the engaging bore 51b, the positioning 
plate 5 rotates slightly in the direction of arrow N3 again due to the 
tension of the control cable C (the spring force of the rear derailleur), 
as shown in FIG. 14c. Upon such an rotation of the positioning plate 5, 
the end 52a of the inner surface of the cutout 52 comes into contact with 
the first fixed shaft 80, thereby stabilizing the positioning plate 5. As 
a result, the chain 13 can be accurately retained at a position 
corresponding to the free wheel 12b. Such overshift function is obtainable 
not exclusively in performing the speed change operation from the sixth 
speed level to the fifth speed level but also in each of the speed change 
operations sequentially performed from the fifth speed level to the first 
speed level. 
Further, the distance R4 from the second fixed shaft 49 as the pivot center 
of the second link 4 to the respective engaging bores 51a-51f of the 
positioning plate 5 is greater than the winding radius R3 for the control 
cable C. The spacing between the respective engaging bores 51a-51f of the 
positioning plate 5 is rendered greater than the pulling amount of the 
control cable C which is needed to cause the rear derailleur to perform 
one-step speed change operation. Therefore, for formation of the engaging 
bores 51a-51f in the positioning plate 5, there is no need to precisely 
machine the engaging bores 51a-51f to leave minute spacings therebetween, 
thereby facilitating production of the positioning plate 5. 
In the rear derailleur, as the chain 13 is shifted from the top gear 12a to 
the low gear 12f due to the pulling of the control cable C by the speed 
change operation assembly A, the spring force urging the chain 13 back 
toward the diametrically small top gear 12a becomes stronger. In other 
words, as the speed change operation of the rear derailleur is performed 
from the sixth speed or top gear to the first speed or low gear, the force 
to pull the control cable C toward the rear derailleur will increase. 
On the other hand, in the link mechanism constituted by the first link 3, 
the second link 4, the displacement of the first end 3a of the first link 
3 is not proportional to the displacement of the second link 4. In other 
words, in the link mechanism, the displacements of the first end 3a of the 
first link 3 (the rotation angles of the operation member 2) necessary to 
cause the control cable C to be pulled sequentially by a constant amount 
through a constant pivot angle of the second link 4 are not the same. In 
the link mechanism, it can be so arranged by properly modifying each 
portion of the first link 3 and second link 4 in terms of size and 
connecting angle for example that the operation member 2 need be operated 
by a greater angle to pull a constant amount of the control cable C when 
the operation member 2 rotates further in the direction of arrow N2. 
Specifically, it may be arranged that the spacings .theta.1-.theta.5 
between the engaging bores 51a-51f of the positioning plate 5 illustrated 
in FIG. 7 are not equal. Of these, .theta.2-.theta.5 may be determined 
such that .theta.2&lt;.theta.3&lt;.theta.4&lt;.theta.5 for example. According to 
the arrangement where the rotation angles of the operation member 2 for 
pulling a constant amount of the control cable C gradually increase, it is 
possible to increase the magnifying proportion of torque for rotation of 
the operation member 2, while the operation torque needed to rotate the 
operation member 2 can be reduced. 
As a result, though the resisting spring force of the rear derailleur in 
pulling the control cable C increases as the rear derailleur shifts from 
the fifth speed gear to the first speed gear, the magnifying proportion of 
the rotation torque of the operation member 2 can be increased. Thus, 
totally, the operation torque of the operation member 2 needed to pull the 
control cable C can be equalized, thereby further facilitating the 
operation of the operation member 2. 
Next, a second embodiment of the present invention will be described below 
with reference to FIGS. 15-17. Throughout FIG. 15 and the following 
figures, portions similar to those of the above described first embodiment 
are indicated by the same references. 
A bicycle speed change operation assembly Aa according to the second 
embodiment is provided for causing a front derailleur (not shown) of the 
bicycle to perform speed change operations and mounted adjacent to a 
left-hand grip 10a on the handlebar 1 used for carrying the already 
described bicycle speed change operation assembly A according to the first 
embodiment. 
As already described with reference to FIG. 4, the front derailleur of the 
bicycle is provided for shifting the chain 13 among three front gears 
15a-15c rotated by the crank arm 16 and includes a shifter (not shown) for 
pushing the chain 13 laterally (widthwise of the bicycle). 
The above front derailleur is designed as a low-normal type. When the 
control cable C1 connected to the front derailleur is pulled toward the 
bicycle speed change operation assembly Aa, the derailleur performs 
sequentially shifting of the chain 13 from the chain wheel 15a as the 
first speed gear to the chain wheel 15c as the third speed gear. 
Conversely, when the control cable C1 is paid out from the bicycle speed 
change operation assembly Aa toward the front derailleur, the chain 13 is 
shifted in the direction opposite to the above mentioned direction. The 
front derailleur carries a spring (not shown) similarly to the rear 
derailleur. When the control cable C1 is not pulled toward the bicycle 
speed change operation assembly Aa, the spring force always acts on the 
control cable C1 so as to cause the chain 13 to be held in engagement with 
the diametrically smallest chain wheel 15a. 
The structure of the bicycle speed change operation assembly Aa is 
basically similar to that of the bicycle speed change operation assembly A 
according to the first embodiment. Thus, the operation member 2, the first 
link 3, the second link 4, the spring member 6, the ball 61, the cable 
supporting guide 7, the fixing ring 8, the housing case 9 and the like are 
the same elements as those used for the first embodiment. The arrangement 
for attaching and assembling these elements and that of the first 
embodiment are laterally symmetrical and basically the same. 
Therefore, in the bicycle speed change operation assembly Aa again, it is 
possible to cause the front derailleur to perform sequentially speed 
change operations one step after another by rotating the operation member 
2 to pull or pay out the control cable C1. Further, in this operation, the 
operation angle of the operation member 2 can be large due to the 
principle of the link mechanism as a force-magnifying mechanism 
constituted by the first link 3, the second link 4 and the like. In 
addition, it is also possible to reduce the operation torque needed to 
rotate the operation member 2. 
However, in the bicycle speed change operation assembly Aa, the positioning 
plate 5A differs constructionally from the positioning plate 5 of the 
above bicycle speed change operation assembly A. 
Specifically, as shown in FIG. 17a, the positioning plate 5A includes a 
bore 50 for insertion of a second fixed shaft 49 and a semicircular cutout 
52 for insertion of a first fixed shaft 80 similarly to the positioning 
plate 5 illustrated in FIG. 7. However, the plate differs from the 
positioning plate 5 in that it has a cutout portion 54 to accommodate a 
movable plate 53 and three engaging bores 51g-51i. 
Though the movable plate 53 has a configuration generally similar to that 
of the cutout portion 54, the length S of the movable plate 53 is smaller 
than the length Sa of the cutout 51. Thus, the movable plate 53 is capable 
of moving by an amount of predetermined size within the cutout 51. Of the 
three engaging bores 51g-51i, the engaging bore 51h is formed in the 
movable plate 53 and corresponds to the chain wheel 15b of the front 
gears. The other engaging bores 51g, 51i, which are formed in the 
positioning plate 5A, correspond to the chain wheels 15a, 15c of the front 
gears, respectively. 
According to the positioning plate 5A having the above movable plate 53, 
the following operation is performed. Suppose that the speed level of the 
front derailleur is set at the first speed and the ball 61 retained by the 
second link 4 engages the engaging bore 51g. When the second link 4 is 
rotated in the direction of arrow N5 upon rotation of the operation member 
2, the ball 61 leaves the engaging bore 51g and comes into engagement with 
the engaging bore 51h of the movable plate 53, as shown in FIG. 17b. With 
the ball 61 being retained by the engaging bore 51h, the movable plate 53 
can be rotated with second link 4 in the direction of arrow N5 until the 
end 53a of the movable plate 53 comes into contact with an inner wall 55a 
of the positioning plate 5A. In this way, with the movable plate 53 held 
in contact with the inner wall 55a of the positioning plate 5A, it is also 
possible to further rotate the positioning plate 5A about the second fixed 
shaft 49 in the direction of arrow N5 until an end 52c of the inner 
surface of the cutout 52 comes into contact with the first fixed shaft 80. 
Thus, the second link 4 can be additionally rotated by the total amount of 
the displacement of the movable plate 53 and the rotational angle of the 
positioning plate 5A, thereby making it possible to additionally pull the 
control cable C1 in an amount greater than needed to perform an intended 
speed change operation of the front derailleur. In this way, in performing 
the speed change operation from the first speed to the second speed, it is 
possible to perform a large amount of overshift. 
In the multi-stage front gears of the bicycle, generally the chain wheel 
15a as the low gear is formed to have a diameter much smaller than those 
of the other chain wheel 15b as the second speed and 15c as the third 
speed. With such front gears, it is more difficult to perform the speed 
change operation from the first speed to the second speed than that from 
the second speed to the third speed. However, it is possible to perform 
the speed change operation properly and reliably from the first speed to 
the second speed by accomplishing a large amount of overshift for the 
operation, as described above. 
When the hand is removed from the operation grip 28 externally fitted on 
the operation member 2 upon completion of the speed change operation to 
the second speed by the front derailleur, the spring force of the front 
derailleur acting on the control cable C causes the movable plate 53 and 
the positioning plate 5A to move backward in the direction of arrow N6 and 
stabilize, as shown in FIG. 17c. Thus, the chain 13 is retained at a 
position exactly corresponding to the chain wheel 12b. 
When the ball 61 engaging the engaging bore 51h is moved for engagement 
with the next engaging bore 51i, or in other words when the front 
derailleur is shifted from the second speed gear to the third speed gear, 
there is no need for so great an overshift as in the speed change 
operation from the first speed to the second speed, and the overshifting 
function by the movable plate 53 is not provided. However, even for the 
speed change operation from the second to the third speed, an appropriate 
overshift is obtainable since the positioning plate 5A can pivot within a 
range of the clearance .lambda.1 between the cutout 52 and the first fixed 
shaft 80. Thus, the speed change operation is properly performed from the 
second to the third speed. 
Next, a third embodiment of the present invention will be described with 
reference to FIGS. 18-28. 
Similarly to the already-described bicycle speed change operation assembly 
A according to the first embodiment, a bicycle speed change operation 
assembly Ab according to the third embodiment is provided for causing the 
rear derailleur to perform speed change operations by shifting the chain 
13 among the six-speed rear gears 12a-12f illustrated in FIG. 4. The 
bicycle speed change operation assembly Ab is mounted adjacent to the 
right grip 10 externally fitted on the right end of the handlebar 1, as 
shown in FIG. 19 for example. 
As shown in FIG. 18, the bicycle speed change operation assembly Ab 
includes a first link 3B and a second link 4B, and these links constitute 
a link mechanism enabling the pulling and paying-out of the control cable 
C connected to the rear derailleur. However, the specific arrangements of 
other elements for operating the link mechanism constituted by the first 
link 3B and the second link 4B are different from those of the 
already-described bicycle speed change operation assemblies A, Aa as 
follows. 
Specifically, as shown in FIG. 21, in addition to the first link 3B and the 
second link 4B, the bicycle speed change operation assembly Ab includes an 
operation member 2B externally fitted on the handlebar 1A for rotational 
movement, two ring members 17A, 17B externally fitted on the operation 
member 2B, a positioning plate 5B positioned between the two ring members 
17A, 17B and externally fitted on the operation member 2B, a spring member 
6B for bringing the positioning plate 5B and the ring members 17A, 17B 
into engagement with each other via two balls 61, 61 and a housing case 
9B. The housing case 9B includes an upper member 91A and a lower member 
91B, which are separate. 
As shown in FIGS. 22a and 22b, the operation member 2B is generally 
cylindrical having a through-hole 20 and a flange 21B and can be 
externally fitted on the handlebar 1A of the bicycle. The operation member 
2B has an outer surface formed with projections 25 for fitting into spline 
grooves 29 of the operation grip 28 shown in FIG. 19. 
The flange 21B is formed with a projection 26 at a portion of the periphery 
thereof. The projection 26 is caused to move externally and 
circumferentially of the upper member 91A of the housing case 9B upon 
rotation of the operation member 2B due to the rotation of the operation 
grip 28 by the cyclist. The outer surface of the upper member 91A may be 
provided with a label 92 attached thereon which carries numbers one to six 
for indication of the positioning of the rear derailleur in the speed 
change operation. The projection 26 serves as an indicator pointing to the 
speed level of the rear derailleur. 
The operation member 2B has a tubular portion 29 projecting in a direction 
from the flange 21 and includes a plurality of recesses 29a externally 
formed on the end of the tubular portion 29, a plurality of projections 
29c intermittently formed on the end of the tubular portion 29 so that 
they provide clearances 29b therebetween and grooves 29d for a snap ring 
SR which are externally formed on the plurality of projections 29c. These 
elements serve to cause the positioning plate 5B and the ring members 17A, 
17B to be externally retained on the operation member 2B, as described 
below. 
As shown in FIGS. 23a-23c, the ring member 17B has a bore 18a for 
externally fitting on the tubular portion 29 of the operation member 2B. 
The inner edge of the bore 18a is provided with a plurality of projections 
18. These projections 18 come into engagement with the recesses 29a or the 
clearances 29b between the projections 29c, 29c of the operation member 2B 
when the ring member 17B is externally fitted on the tubular portion 29 of 
the operation member 2B. Thus, the ring member 17B is prevented from 
rotating relatively to the operation member 2B. The ring member 17B is 
externally fitted on the operation member 2B for rotation with the 
operation member 2B. 
The ring member 17B further includes a bore 42B for receiving the ball 61, 
a projection 19b for engagement with the spring member 6B, a bore 23B for 
fixation of a pin 31B supporting the first end 3a of the first link 3B as 
shown in FIG. 21 and the like. As shown in FIG. 23c, of portions of the 
ring member 17B, the portion at the location of the bore 23B is formed 
offset from the other portions by a predetermined amount t. With such an 
arrangement, an end of the pin 31B inserted through the bore 23B can be 
caulked within a range of the amount t. 
As shown in FIG. 21, the other ring member 17A has a structure basically 
similar to that of the ring member 17B, thereby requiring no detailed 
description. However, the ring member 17A does not include a bore 23B for 
connecting the first link 3B. Further, the projection 19a for engaging the 
spring member 6B is bent in an opposite direction to the projection 19b of 
the ring member 17B. 
As shown in FIGS. 24a, 24b, the positioning plate 5B has a bore 50B for 
external fitting on the tubular portion 29 of the operation member 2B. The 
positioning plate 5B is formed with six engaging bores 51a-51f located 
along a circle having a predetermined radius R5. The engaging bores 
51a-51f are provided for bringing the ball 61 into engagement therewith 
like the engaging bores 51a-51f of the positioning plate 5 illustrated in 
FIG. 7. 
The positioning plate 5B differs from the two ring members 17A, 17B in that 
it does not engage the operation member 2B nor rotate with the operation 
member 2B. A fixed shaft 80B attached to the lower member 91B of the 
housing case 9B and a sleeve 87 externally fitted on the fixed shaft 80B 
are arranged within the cutout 52B of the positioning plate 5B to prevent 
the positioning plate 5B from pivoting due to coming into engagement with 
the sleeve 87. 
However, the outside diameter of the sleeve 87 is smaller than the width of 
the cutout 52B, thereby providing a clearance .lambda.2 therebetween. 
Thus, the positioning plate 5B can pivot slightly about the operation 
member 2B within a range of the clearance .lambda.2. When the positioning 
plate 5B for engaging the ball 61 is capable of pivoting by a small angle, 
it is possible to provide an overshift movement when the rear derailleur 
performs a speed change operation, similarly to the bicycle speed change 
operation assembly A using the positioning plate 5 illustrated in FIG. 7. 
As shown in FIG. 25, the two ring members 17A, 17B, the positioning plate 
5B, the spring member 6B and the balls 61, 61 constitute a positioning 
mechanism. In the positioning mechanism, the positioning plate 5B and the 
two ring members 17A, 17B allowing insertion of the positioning plate 5B 
therebetween are externally fitted on the tubular portion 29 of the 
operation member 2B. A snap ring SR is brought into fixed engagement with 
a groove 29d formed in the outer surface of the plurality of projections 
29c of the operation member 2B, thereby causing the positioning plate 5B 
and the two ring members 17A, 17B to be positionally retained 
longitudinally of the operation member 2B. The bores 42B, 42B of the two 
ring members 17A, 17B accommodate the balls 61, 61 fitted therein. The 
balls 61, 61 are urged in an approaching direction to each other by a pair 
of opposite pieces 60, 60 of the spring member 6B so that they are 
received in one of the engaging bores 51a-51f of the positioning plate 5B. 
As a result, in the positioning mechanism, when the operation member 2B 
rotates, though the positioning plate 5B does not rotate therewith, the 
two ring members 17A, 17B, the spring member 6B and the balls 61, 61 
rotate with the operation member 2B. 
Specifically, when the operation member 2B is rotated while the balls 61, 
61 are held in engagement with the engaging bore 51a, the balls 61, 61 
retained by the ring members 17A, 17B rotating with the operation member 
2B can be moved out of the engaging bore 51a. Thereafter, the balls 61, 61 
may be brought into engagement with the next engaging bore 51b. Similarly, 
the balls 61, 61 may be sequentially brought into engagement with one of 
the other engaging bores 51c-51f after another. 
As shown in FIG. 26, the pair of opposite pieces 60, 60 of the spring 
member 6B are arranged to come into engagement with the projections 19a, 
19b formed on the peripheries of the two ring members 17A, 17B. Thus, the 
spring member 6B is retained by the two ring members 17A, 17B in 
engagement therewith for prevention of coming off the ring members 17A, 
17B. 
As shown in FIGS. 18 and 21, the first link 3B is connected to the ring 
member 17B for rotational movement by arranging the pin 31B extending 
through the through-hole 30a in the first end 3a and the bore 23B of the 
ring member 17B. Thus, upon rotation of the ring members 17A, 17B due to 
the rotating of the operation member 2B, the first end 3a of the first 
link 3B is moved around the handlebar 1A with the rotation of the ring 
member 17B. 
The first link 3B is made in a curved configuration having a concave 
surface 30 whose radius of curvature Rb is equal or generally equal to the 
radius of the handlebar 1A. Thus, in rotating the operation member 2B as 
shown in FIG. 27, the first link 3B can come into fitting engagement with 
the outer surface of the handlebar 1A, thereby providing an increased 
maximum rotational angle of the operation member 2 while preventing the 
bulging of the first link 3B. 
As shown in FIGS. 18 and 21, the through-hole 40a formed at the first end 
4a of the second link 4B receives an end of the sleeve 87 externally 
fitted on the fixed shaft 80B. Thus, the second link 4B is vertically 
pivotable about the fixed shaft 80B and the sleeve 87. On the other hand, 
the through-hole 40b at the second end 4b of the second link 4B and the 
through-hole 30b at the second end 3b of the first link 3B receive the 
connecting pin 48B extending therethrough. Thus, the second end 4b of the 
second link 4B and the second end 3b of the first link 3B are connected 
for relative pivotal movement. 
As shown in FIG. 18, the second link 4B is located below the handlebar 1A 
of the bicycle. The first link 3B is arranged to extend generally 
vertically as viewed longitudinally of the first link 3B, when the control 
cable C is not pulled at all or pulled by a small amount. Thus, the second 
link 4B and the first link 3B are prevented from unduly bulging from the 
handlebar 1A forward or backward of the bicycle. Therefore, the width of 
the bicycle speed change operation assembly Ab as a whole can be reduced 
and give a neater appearance. 
A bracket piece 75 is pivotally connected via a pin 76 to a generally 
longitudinal center of the second link 4B. The bracket piece 75 has a 
bottom plate 75a formed with a bore 75b for insertion of the control cable 
C, and a nipple 14 provided at the end of the cable is retained by the 
bottom plate 75a. Thus, the control cable C is pulled or paid out by the 
second link 4B when the link 4B pivots about the fixed shaft 80B or the 
sleeve 87. 
The direction N7 in which the control cable C is pulled from the upper end 
of the cable guide 94B generally coincides with the pivotal direction N8 
of the pin 76 of the second link 4B. Therefore, the second link 4B pulls 
the control cable C along a straight path from the upper end of the cable 
guide 94B. The control cable C is not drawn out in a curved path which 
sways vertically or horizontally. 
As shown in FIG. 21, the upper member 91A and the lower member 91B of the 
housing case 9B have clamp portions 98a, 98b for clamping the handlebar 1A 
from above and below. The clamp portions 98a, 98b are bolted to each other 
by a bolt 91b and a nut 91c to fix the housing case 9B on the handlebar 
1A. A set screw 82a is threaded through the lower member 91B. The set 
screw 82a is brought into pressing contact with the outer surface of the 
handlebar 1A, thereby preventing the housing case 9B from unduly rotating 
around the handlebar. 
The lower member 91B further includes a through-hole 95B for insertion and 
retainment of the upper end of the cable guide 94B for the control cable C 
and a bore 85B for attaching the fixed shaft 80B. 
In the bicycle speed change operation assembly Ab having the above 
arrangement, when the operation member 2B is rotated in the direction of 
N9 shown in FIG. 18 to the angular position shown in FIG. 27, the first 
end 3a of the first link 3B is moved around the handlebar 1A by a 
predetermined length L3 with the rotation of the operation member 2B. 
Then, the second link 4B pivots upward about the fixed shaft 80B or the 
sleeve 87 with the movement of the first link 3B. As a result, the bracket 
piece 75 connected to the second link 4B is lifted to pull the control 
cable C. 
The first link 3B and the second link 4B constitute a force-magnifying 
mechanism or reduction mechanism similar to the link mechanism described 
with reference to FIG. 12. Therefore, the displacement of any portion of 
the second link 4B is rendered smaller than the displacement L3 of the 
first end 3a of the first link 3B, and the pulling amount L4 of the 
control cable C is considerably smaller than the displacement L3 of the 
first end 3a of the first link 3B. As a result, again in the speed change 
operation assembly Ab, it is possible to reliably cause the rear 
derailleur to sequentially perform a speed change operation after another 
by a large amount of rotational operation of the operation grip 28 
externally fitted on the operation member 2B. It is also possible to 
reduce the operation torque needed to rotate the operation member 2B. 
Since the control cable C pulled by the second link 4B follows a straight 
or generally straight path from the upper end of the cable guide 94B, 
there is no need for additional members such as the cable supporting guide 
7 for guiding the control cable C, unlike the already-described bicycle 
speed change operation assembly A. Thus, reduction in the number of 
elements can be accomplished. Further, since frictional resistance 
generated on the control cable C in pulling the control cable C can be 
further decreased, the speed change operation can be improved more. 
On the other hand, in sequentially rotating the operation member 2B, the 
balls 61, 61 retained by the two ring members 17A, 17B are moved relative 
to the positioning plate 5B. During the movement after leaving the 
engaging bore 51a of the positioning plate 5B, each ball 61 is 
sequentially brought into and out of engagement with the respective 
engaging bores 51b-51f. According to the above positioning mechanism where 
each ball 61 engages one of the engaging bores 51a-51f, the two ring 
members 17A, 17B and consequently the operation member 2B can be retained 
at an intended angular position, thereby retaining the rear derailleur at 
an intended speed level. 
Further, again the positioning mechanism adopted in the bicycle speed 
change operation assembly Ab can perform an overshift operation as 
described below. 
Specifically, the rear derailleur always provides a spring force urging the 
control cable C toward the rear derailleur. Thus, when the cyclist keeps 
his hand off the operation grip 28, the spring force acts on the 
positioning plate 5B as a rotating force in the direction of arrow N10, as 
shown in FIG. 28a for example. Thus, the positioning plate 5B is 
stabilized with the end 52d of the inner surface of the cutout 52B 
contacting with the sleeve 87. The ball 61 engages the engaging bore 51a 
for example, thereby properly retaining the rear derailleur for the sixth 
speed. 
Then, as shown in FIG. 28b, when rotating the operation member 2B in the 
direction of arrow N11, the ball 61 leaves the engaging bore 51a and then 
fitts in the next engaging bore 51b. However, even thereafter, it is 
possible to additionally rotate the positioning plate 5B and the operation 
member 2B by a small angle, until the other end 52e of the inner surface 
of the cutout 52B comes into contact with the sleeve 87. Thus, the control 
cable C can be additionally pulled more than needed for the speed change 
operation of the rear derailleur i.e., by an amount of the extra rotation 
angle of the positioning plate 5B. 
Thereafter, when the cyclist removes his hand off the operation grip 28, 
the rear derailleur spring force acting on the control cable C causes the 
positioning plate 5B to slightly rotate back in the direction of arrow N10 
as shown in FIG. 28c and to be stabilized due to the end 52d of the inner 
surface of the cutout 52B coming into contact with the sleeve 87. In this 
way, with the bicycle speed change operation assembly Ab as well, an 
overshifting of the rear derailleur can be performed to provide a reliable 
speed change performance by the rear derailleur. 
In the link mechanism of the bicycle speed change operation assembly Ab, 
similarly to the already-described link mechanisms of the bicycle speed 
change operation assemblies A, Aa, the displacement of the first end 3a of 
the first link 3B and the displacement of the second link 4B are not 
proportional. With the link mechanism of the bicycle speed change 
operation assembly Ab, the operation member 2B can be arranged to require 
a larger rotational angle to pull a constant length of the control cable 
C, as the operation member 2B is rotated further into the direction of 
arrow N9 as shown in FIG. 18. For this, the angles .theta.1'-.theta.5' 
between the engaging bores 51a-51f of the positioning plate 5B shown in 
FIG. 24 may unequally formed such that .theta.2'-.theta.5' may be 
determined to satisfy .theta.2'&lt;.theta.3'&lt;.theta.4'&lt;.theta.5'. 
In this way, by increasing the rotation angles for the operation member 2B 
to pull a constant length of the control cable C, the operation torque for 
rotating the operation member 2B can be reduced accordingly. As a result, 
even if the rear derailleur spring force working as resistance in pulling 
the control cable C increases as the speed is reduced by shifting the rear 
derailleur from the fifth speed to the first speed, the magnifying ratio 
of the rotation torque of the operation member 2B is increased 
accordingly, thereby equalizing the operation torque needed to rotate the 
operation member 2B as a whole. 
Next, a fourth embodiment of the present invention will be described with 
reference to FIGS. 29-31. 
A bicycle speed change operation assembly Ac according to the fourth 
embodiment is provided for causing the front derailleur shifting the chain 
13 among the three-speed front gears 15a-15c illustrated in FIG. 4 to 
perform speed change operations. The bicycle speed change operation 
assembly Ac is mounted adjacent to the left grip 10a of the handlebar 1A 
carrying the bicycle speed change operation assembly Ab according to the 
third embodiment already described. 
The arrangement of the bicycle speed change operation assembly Ac is 
basically similar to that of the bicycle speed change operation assembly 
Ab according to the third embodiment. The operation member 2B and others 
such as the first link 3B, the second link 4B, the two ring members 17A, 
17B, the spring member 6B, the ball 61 and the housing case 9B are the 
same as those of the third embodiment. 
Thus, again in the bicycle speed change operation assembly Ac, the pulling 
and paying-out of the control cable C1 are performed by rotating the 
operation member 2B to cause the front derailleur to sequentially perform 
a step-by-step speed change operation. Simultaneously, the link mechanism 
as a force-magnifying mechanism constituted by the first link 3B and the 
second link 4B makes it possible to rotate the operation member 2B by a 
large rotational angle, while the operation torque needed to rotate the 
operation member 2B can be reduced. Apparently, the speed change operation 
can be facilitated without generating a large frictional force on the 
control cable C1. 
However, in the bicycle speed change operation assembly Ac, the positioning 
plate 5c engaging the balls 61, 61 retained by the two ring members 17A, 
17B is different from the positioning plate 5B of the above bicycle speed 
change operation assembly Ab. 
Specifically, as shown in FIG. 31a, the positioning plate 5C includes a 
bore 50B for externally fitting on the operation member 2B and a cutout 
52B for inserting the sleeve 87 externally fitted around the fixed shaft 
80B. However, the illustrated positioning plate is different from the 
already-described positioning plate 5B in that it has a cutout portion 54 
for accommodating a movable plate 53 and three engaging bores 51g-51i. The 
movable plate 53 and the cutout portion 54 are similar to the movable 
plate 53 and the cutout portion 54 described with reference to FIG. 17. 
In the positioning mechanism including the positioning plate 5C, an 
overshifting function similar to that by the positioning plate 5A 
described with reference to FIG. 17 is obtainable as described below. 
Specifically, suppose that the speed level of the front derailleur is set 
for the first speed wherein the ball 61 retained by the second link 4B 
engages the engaging bore 51g. Upon rotation of the ring members 17A, 17B 
in the direction of arrow N12 by rotating the operation member 2B, the 
ball 61 leaves the engaging bore 51g and then comes into engagement with 
the engaging bore 51h of the movable plate 53, as shown in FIG. 31b. With 
the ball 61 engaging the engaging bore 51h, the operation member 2B can be 
rotated in the direction of arrow N13 until an end 53 of the movable plate 
53 comes into contact with an inner end wall 55a of the positioning plate 
5C. Further, with the movable plate 53 held in contact with the inner end 
wall 55a of the positioning plate 5C, the operation member 2B can be 
further rotated in the direction of arrow N13 until an end 52d of the 
inner surface of the cutout 53B comes into contact with the sleeve 87. 
As a result, it is possible to additionally rotate the operation member 2B 
by a total amount of the displaced angle of the movable plate 53 and the 
rotational angle of the positioning plate 5C, thereby pulling the control 
cable C1 by an amount greater than needed for performing an intended speed 
change. In other words, a large amount of overshift can be provided in 
performing the speed change from the first speed to the second speed. As 
already described, in multistage front gears of the bicycle, generally the 
speed change from the first speed to the second speed is more difficult 
than that from the second speed to the third speed. Therefore, when a 
large amount of overshift is possible for performing the speed change from 
the first speed to the second speed, the speed change operation can be 
performed properly and reliably. 
When the cyclist removes his hand from the operation grip 28 externally 
fitted on the operation member 2B upon completion of the shifting to the 
second speed, the movable plate and the positioning plate 5C are moved 
backward in the direction of arrow N12 as shown in FIG. 31c due to the 
tension of the control cable C1 and comes into a stabilized condition. 
Thus, the chain 13 is retained at a position exactly corresponding to the 
chain wheel 12b. 
In shifting the ball 61 engaging the engaging bore 51h to the next engaging 
bore 51i for engagement therewith, an overshifting function due to the 
displacement of the movable plate 53 is not obtainable. However, in such 
an instance, an overshift can be provided in a moderate amount, since the 
positioning plate 5C can pivot within a range of a clearance .lambda.3 
defined between the cutout 52B and the sleeve 87, thereby facilitating the 
speed change operation from the second speed to the third speed. 
Next, a fifth embodiment of the present invention will be described with 
reference to FIGS. 32-40. 
A bicycle speed change operation assembly Ad according to the fifth 
embodiment is provided for causing the rear derailleur shifting the chain 
13 among the six-speed rear gears 12a-12f described with reference to FIG. 
4 to perform a speed change operation, similarly to the already described 
bicycle speed change operation assemblies A, Ab according to the first and 
the third embodiments, respectively. The bicycle speed change operation 
assembly Ad is mounted adjacent to the right grip 10 externally fitted 
around the right end of the handlebar 1B as shown in FIG. 32 for example. 
As shown in FIG. 33, the bicycle speed change operation assembly Ad 
includes a first link 3C and a second link 4C which constitute a link 
mechanism performing the pulling and paying-out of the control cable C 
connected to the rear derailleur. However, specific arrangements of 
portions for operating the link mechanism constituted by the first link 3C 
and the second link 4C are different from those of the already described 
bicycle speed change operation assemblies A, Ab as follows. 
Specifically, as shown in FIG. 35, in addition to the first link 3C and the 
second link 4C, the bicycle speed change operation assembly Ad includes an 
operation member 2C externally fitted on a handlebar 1B for pivotal 
movement, a positioning ring 5D engaging the operation member 2C, a roller 
61A as an engaging member, a plate-like spring member 6C and a housing 
case 9C accommodating these members. 
The housing case 9C includes a case body 91C and a cover 91D, which are 
separate. The cover 91D is releasably attached to the case body 91C via 
screws 100. The respective members of the bicycle speed change operation 
assembly Ad are put together in a state where the cover 91D is removed 
from the case body 91C. 
The case body 91C has a tubular portion 102 with a through-hole 101 and a 
cable guide portion 115 for guiding the control cable C. The tubular 
portion 102 can be externally fitted on the handlebar 1B. The through-hole 
101 has an inner end surface provided with a tightening band 104 
externally covering the handlebar 1B, as shown in FIG. 34. Both ends 104a, 
104b of the tightening band 104 allow passage of a bolt 105 which is 
inserted through a bore 106 of the case body 91C. The tightening band 104 
can be fastened by rotating the bolt 105. The case body 91C is 
non-rotationally attached to the handlebar 1B by clamping the handlebar 1B 
with the use of the tightening band 104. 
The operation member 2C is generally cylindrical having a through-hole 20C 
and a flange 21C and externally fitted around the tubular portion 102 of 
the case body 91C. The outer surface of the operation member 2C is 
provided with a plurality of projections 25 for preventing the operation 
grip 28 from rotating when the grip 28 is externally fitted on the 
operation member 2C. 
The operation member 2C has a tubular portion 29C projecting on a side of 
the flange 21C, a plurality of constantly spaced projections 107 formed on 
an end of the outer surface of the tubular portion 29C, two mutually 
facing wall portions 108a, 108b and a bore 109 formed in the two wall 
portions 108a, 108b. 
The first end 3a of the first link 3C is inserted in a clearance 110 formed 
between the ball portions 108a, 108b, and a shaft 31C is inserted through 
the through-hole 30a of the first link 3C and the bore 109. Thus, the 
first end 3a of the first link 3C is connected to the operation member 2C 
via the shaft 31C and is moved about the tubular portion 29C of the 
operation member 2C upon rotation of the operation member 2C. 
The first link 3C has a curved configuration having a concave surface 30 
whose radius of curvature is equal or generally equal to the radius of the 
tubular portion 29C of the operation member 2C. Therefore, upon rotation 
of the operation member 2C as shown in FIG. 36, the first link 3C can be 
brought into fitting engagement with the outer surface of the tubular 
portion 29C of the operation member 2C, thereby making it possible to 
prevent the first link 3C from bulging while providing an increased 
maximum rotational angle of the operation member 2C. 
The second link 4C is constituted by two curved plates 47C, 47D connected 
to each other with a predetermined spacing therebetween. The control cable 
C is arranged between the two plates 47C, 47D and the nipple 14 of the 
control cable C is held in engagement with edges of the respective plates 
47C, 47D. The portions engaging the nipple 14 in the plates 47C, 47D are 
recessed to prevent an undesirable positional shift of the nipple 14. 
The fixed shaft 80C attached to the housing case 9C is inserted through the 
through-hole 40a at the first end 4a of the second link 4C. The second 
link 4C is vertically pivotal about the fixed shaft 80C. The second end 4b 
of the second link 4C and the second end 3b of the first link 3C are 
connected for relative pivotal movement. Similarly to the first link 3C, 
the second link 4C has a curved configuration having a concave surface 40C 
whose radius of curvature is equal or generally equal to the radius of the 
tubular portion 29C of the operation member 2C. Therefore, as shown in 
FIG. 36, when the second link 4C is brought into contact with the tubular 
portion 29C of the operation member 2C, the second link 4C can be fitted 
around the tubular portion 29C without interfering with the operation 
member 2C. 
It is possible to bring the first link 3C and the second link 4C much 
closer to the operation member 2C by providing the tubular portion 29C of 
the operation member 2C with a recess 129 for accommodating the connected 
portion of the second end 3b of the first link 3C and the second end 4b of 
the second link 4C. 
As shown in FIG. 35, the positioning ring 5D can be externally fitted 
around the tubular portion 102 of the housing case 9C. An edge of the 
positioning ring 5D is provided with an arcuate portion 57 to partially 
increase the width of the outer surface, and the arcuate portion is 
externally formed with a plurality of engaging recesses 56. The 
positioning ring 5D is internally formed at an end thereof with a 
plurality of recesses 112. The tubular portion 29C of the operation member 
2C is inserted into the positioning ring 5D to bring the respective 
recesses 112 into engagement with the projections 107. The positioning 
ring 5D is not rotatable relatively to the operation member 2C due to the 
engagement between the recesses 112 and the projections 107 but rotatable 
around the tubular portion 102 with the operation member 2C. 
As shown in FIG. 34, the roller 61A is retained in the housing case 9C so 
that the roller can be brought into facing relation with the engaging 
recesses 56. Specifically, the inner surface of the through-hole 101 of 
the housing case 9C is formed with a bore 113 for accommodating the roller 
61A. As shown in FIG. 37, the width S5 of the bore 113 is larger than the 
outside diameter D5 of the roller 61A, so that in the bore 113 the roller 
61A is movable circumferentially of of the positioning ring 5D within a 
range of a predetermined displacement. 
The spring member 6C is fitted into a slit 114 formed in the housing case 
9C. As shown in FIG. 38, when the roller 61A is not in engagement with the 
engaging recess 56, the spring member 6C is deformed and elastically urges 
the roller 61A toward the positioning ring 5D. On the other hand, as shown 
in FIG. 37, when the roller 61A is accommodated in the engaging recess 56, 
the spring member 6C does not elastically urge the roller 61A, preventing 
the roller 61A from coming into contact with the inner wall 56A of the 
engaging recess 56. Preferably, a suitable clearance S6 is formed between 
the roller 61A and the inner wall 56A of the engaging recess 56. 
In the bicycle speed change operation assembly Ad having the above 
arrangement, upon rotation of the operation member 2C in the direction of 
arrow N14, starting from the state shown in FIG. 33, the second link 4C 
pivots vertically about the fixed shaft 80C with movement of the first 
link 3C as shown in FIG. 36, thereby pulling the control cable C. Like the 
already-described bicycle speed change operation assemblies A and Aa-Ac, 
the bicycle speed change operation assembly Ad also includes a link 
mechanism as a force-magnifying mechanism constituted by the first link 3C 
and the second link 4C. Thus, a small displacement of the control cable C 
is obtainable by rotating the operation member 2C by a large angle. 
Further, the angular operation torque of the operation member 2C can be 
reduced. Since the control cable C is pulled directly by the second link 
4C from the cable guide portion 115, there is no large frictional force 
generated on the control cable C. Thus, the operation of the operation 
member 2C is facilitated when causing the rear derailleur to perform speed 
change operations. 
The control cable C can be pulled in a straight path by the second link 4C, 
similarly to the already-described bicycle speed change operation 
assemblies Ab, Ac, thereby requiring no need to provide an additional 
guide member for the control cable C. 
As the operation member 2C is sequentially rotated, the engaging recesses 
56 of the positioning ring 5D rotates accordingly, and the roller 61A will 
come into releasable engagement with one of the respective recesses 56 
after another. Thus, the engagement between the roller 61A and the 
respective engaging recesses 56 can retain the positioning ring 5D and the 
operation member 2C at a predetermined rotational angular position, 
thereby retaining the rear derailleur for at an intended speed level. 
With the bicycle speed change operation assembly Ad again, an overshift can 
be performed as follows. 
Specifically, as shown in FIG. 37 for example, in an instance where the 
roller 61A is held in engagement with an engaging recess 56 (56a), when 
the cyclist keeps his hand off the operation grip 28, the rear derailleur 
spring force acting on the control cable C tends to rotate the positioning 
ring 5D and the operation member 2C in the direction of arrow N15. Thus, 
in a normal state where no speed change is performed, the roller 61A is in 
a stabilized state, being urged by the engaging recess 56 (56a) to come 
into contact with an end wall 113a of the bore 113. 
Then, as shown in FIG. 38, the roller 61A leaves the engaging recess 56 
(56a) upon rotation of the operation member 2C in the direction of arrow 
16 and comes into engagement with the next engaging recess 56 (56b), as 
shown in FIG. 39a. At this time, the roller 61A is movable within the bore 
113 until coming into contact with the other end wall 113b of the bore 
113. Thus, the displacement of the roller 61A within the bore 113 allows 
the operation member 2C to be additionally rotated more than needed for 
the actual angular rotation, thereby pulling the control cable C in an 
amount greater than needed for the speed change operation of the rear 
derailleur. 
Then, when the cyclist removes his hand off the operation grip 28, the rear 
derailleur spring force acting on the control cable C rotates the 
positioning ring 5D backward in the direction of arrow 17 as shown in FIG. 
39b, until the roller 61A comes into contact with a wall 113a of the bore 
113, and the positioning ring stabilizes thereafter. During the backward 
rotation of the positioning ring 5D, the inner wall 56A of the engaging 
recess 56 (56b) and the roller 61A are not pressed against each other, 
thereby preventing the roller 61A from giving a large resisting force to 
the positioning ring 5D in the backward rotation. Thus, it is possible to 
cause the positioning ring 5D and the operation member 2C to perform a 
returning movement smoothly and easily. 
The following means is also applicable for causing the bicycle speed change 
operation assembly Ad to perform an overshift function in place of the 
means where the roller 61A is rendered movable within the bore 113. 
Specifically, as shown in FIG. 40a, for mutual engagement between the 
projections 107 of the operation member 2C and the recesses 112 of the 
positioning ring 5D, the width S7 of the projection 107 may be rendered 
smaller than the width S8 of the recess 112 for example, so that the 
positioning plate 5D can move relatively to the operation member 2C within 
a predetermined angular range. 
With such an arrangement, in a normal state where one of the engaging 
recesses 56 is held in contact with the roller 61A and no speed change 
operation is performed, the projection 107 is held in contact with the 
wall 112a of the recess 112 for prevention of the rotation of the 
operation member 2C due to the rear derailleur spring force tending to 
rotate the operation member 2C in the direction of arrow N18. 
Then, when the operation member 2C is rotated in the direction of arrow N19 
as shown in FIG. 40b, the projection 107 comes into contact with the other 
wall 112b of the recess 112, thereby enabling additional rotation of the 
positioning member 2C in the direction of arrow 19 more than the 
rotational angle of the positioning ring 5D. Thus, the control cable C can 
be additionally pulled by an amount larger than necessary for the rear 
derailleur speed change operation. 
Thereafter, when the cyclist removes his hand off the operation grip 28, 
the rear derailleur spring force rotates the operation member 2C backward 
relatively to the positioning ring 5D in the direction of arrow N20 as 
shown in FIG. 40c until the projection 107 comes into contact with the 
wall 12a of the recess 112. Thus, the operation member 2C is settled at 
the actually corresponding angular position for the speed change 
operation. 
Similarly to the already-described bicycle speed change operation 
assemblies A, Ab, in the bicycle speed change operation assembly Ad, it is 
possible to arrange that the operation member 2C need be rotated by a 
larger amount to pull a constant length of the control cable C, as the 
operation member 2C is rotated further into the direction of arrow N14 as 
shown in FIG. 33. Therefore, even when the rear derailleur spring force 
becomes larger as the rear derailleur is operated for a reduced speed, the 
magnifying ratio of the rotational torque of the operation member 2B can 
be increased accordingly, thereby providing a total equalization for the 
operation torque needed for rotational operation of the operation member 
2B. 
Though the bicycle speed change operation assembly Ad described above is 
designed for a rear derailleur, the same may be designed for a front 
derailleur. When arranging the assembly for the front derailleur, it is 
necessary to modify the specifications of the speed change operation 
assembly so that the engaging recess 56 of the positioning ring 5D is made 
suitable for the front derailleur. Such a modification can be easily 
performed by replacing the positioning ring 5D with another positioning 
ring. 
In the embodiments described above, reference is made to examples of a 
speed change operation assembly used for the speed change operation of the 
rear derailleur for six-speed rear gears and the front derailleur for 
three-speed front gears. However, apparently, the present invention is not 
limited to these but may be embodied as a speed change operation assembly 
applicable to speed change devices which are of various kinds or provide a 
different number of speed levels. 
Further, though in the above embodiments the operation member is of a 
grip-type and mounted around the handlebar of a bicycle for rotational 
movement, the present invention is not limited to this, either. According 
to the present invention, the operation member may be mounted on a portion 
other than the handlebar. 
Specific arrangements for the respective elements of the bicycle speed 
change operation assembly according to the present invention may be 
modified in various ways. 
INDUSTRIAL APPLICABILITY 
The bicycle speed change operation assemblies according to the present 
invention are applicable in general to bicycles having a speed change 
device such as a rear derailleur, a front derailleur and the like.