Rear derailer for bicycle gears

A rear derailleur for bicycle gears comprises an upper body which can be fixed to the bicycle frame, a lower body carrying a chain tensioning wheel for the bicycle chain and being movable relative to the upper body to bring the chain into selective engagement with a series of sprockets carried by the hub of the rear wheel of the bicycle, and a flexible cable for causing movement of the lower body. This lower body is carried by a control lever which is supported for rotation and axial sliding on a cylindrical guide element fixed to the upper body. Transmission device is interposed between the flexible cable and the control lever and is adapted simultaneously to impart rotation and axial sliding to the control lever, relative to the cylindrical guide element, as a result of operation of the flexible cable.

DESCRIPTION 
FIELD OF THE INVENTION 
The present invention relates to rear derailleurs for bicycle gears, of the 
known type comprising: 
an upper body which can be fixed to the bicycle frame, 
a lower body carrying transmission means for the bicycle chain and being 
connected to the upper body so as to be movable relative thereto to bring 
the chain into selective engagement with a series of sprockets carried by 
the hub of the rear wheel of the bicycle, and 
flexible cable means for causing movement of the lower body. 
In rear derailleurs of the type indicated above, for efficient functioning 
of the derailleur, it is desirable that the distance between the chain 
transmission means and the teeth of the sprocket engaged with the chain 
which are nearest to the transmission means is kept as uniform as 
possible, whichever sprocket is selected. In other words, it is desirable 
that, when the chain is derailed from one particular sprocket to another 
sprocket of different diameter, the movement of the chain transmission 
means should have both a component parallel to the axis of the rear wheel 
of the bicycle (so as to cause derailing of the chain from one sprocket to 
another) and a component radial to that axis to allow for the different 
diameters of the sprockets. 
SUMMARY OF THE INVENTION 
The object of the present invention to produce a derailleur which is able 
to achieve the above result and has a compact and functional structure. 
In order to achieve this object, the subject of the present invention is a 
rear derailleur of the type specified at the beginning of the present 
description, characterised in that the lower body of the derailleur is 
carried by a control lever which is supported for rotation and axial 
sliding on a cylindrical guide element fixed to the upper body, and in 
that transmission means are interposed between the flexible cable means 
and the control lever for simultaneously imparting rotation and axial 
sliding to the control lever - relative to the cylindrical guide member - 
as a result of operation of the flexible cable means, means also being 
provided for keeping the orientation of the lower body unchanged upon a 
variation of the control lever. 
By virtue of the aforementioned characteristics, various advantages are 
obtained. In the first place, the device according to the invention is 
able to achieve quite considerable movement of the control lever along the 
axis of the cylindrical guide element. It is therefore possible to allow 
for very considerable differences in diameter between the sprockets, 
whilst at the same time keeping the dimensions of the derailer relatively 
small. This advantage is particularly marked in comparison with 
conventional solutions, in which the lower body of the derailleur is 
connected to the upper body by means of an articulated parallelogram joint 
pivoting in a plane parallel to the plane tangential to the lower part of 
the imaginary cone circumscribing the sprockets. In the second place, the 
particular structure described above enables the adoption of structural 
solutions which are more functional and reliable than known solutions.

DETAILED DESCRIPTION OF THE INVENTION 
With reference to FIGS. 1 to 6, a rear derailleur for bicycles is generally 
indicated 1 and has an upper body 2 (see particularly FIGS. 1, 6) fixed by 
means of a screw 3 to an appendage 4 of the frame 5 of a bicycle, adjacent 
the hub 6 (FIG. 2) of the rear wheel of the bicycle. The hub 6 carries a 
series of sprockets 7, indicated only schematically in the drawings. 
The derailleur 1 includes a lower body 8 connected to the upper body 2 in a 
manner which will be described in detail below and supporting a 
transmission wheel 11 for the chain (shown schematically by the line 12 in 
FIG. 1) for rotation about an axis 9 parallel to the axis 10 of the hub 6. 
The lower body 8 supports a chain-tensioning arm 13 which is also 
rotatable about the axis 9. The arm 13 terminates in an end 14 which 
supports a chain-tensioning wheel 16 for rotation about an axis 15 
parallel to the axis 9. According to conventional techniques, resilient 
means (not illustrated) are provided between the lower body 8 and the arm 
13 which tend to keep the arm rotated in a clockwise sense (with reference 
to FIG. 1) so as to keep the chain 12 tensioned. 
The lower body 8 is articulated by means of an articulation pin with a 
vertical axis 18 to an end appendage 19 of a control lever 20 for 
controlling the movement of the lower body 8. The control lever 20 
incorporates a hub 21 (see particularly FIG. 5) which is mounted for 
rotation and axial sliding on a cylindrical guide element 22. The latter 
is carried by the upper body 2 of the derailer and has an axis 23 parallel 
to the axis 18 of the articulation pin 17. The cylindrical guide element 
22 has a hollow body with an upper end 24 which is internally threaded and 
is provided with a collar 25 at a certain distance from its head surface. 
The end 24 is housed in a cavity 26 formed in the lower surface of a 
cylindrical portion 2a of the upper body 2, with the collar 25 abutting 
this lower surface. The cylindrical guide element 22 is clamped axially 
against the upper body 2 by means of a threaded ring 27 which passes 
through a through-hole 28 formed in the upper body 2 and engages the 
internally threaded portion of the end 24. The ring 27 has an 
enlarged-diameter head 29 which bears on the upper surface of the part 2a 
with the interposition of a washer 30. The body 22 is prevented from 
rotation relative to the body 2 by a tooth 22b. In its turn, the ring 27 
has an axial through-hole 31 in which is slidably mounted a tubular shank 
32 ending at its lower end in a cylindrical body 32. The body 32 is 
mounted slidably within the cylindrical guide element 22 and has a 
transverse through-hole 33 in which the ends of two transverse pins 34 are 
fitted with interference from opposite sides. The pins 34 project 
outwardly of the cylindrical guide element 22 through two helical slots 35 
(see FIG. 1). Axial movement of the body 32 within the cylindrical guide 
element 22 thus also causes rotation of the body about the axis 23, due to 
the engagement of the pins 34 in the two helical slots 35. The outer ends 
of the pins 34 are engaged in corresponding holes formed in the hub 21 of 
the control lever 20 and each terminates with a head 36. The hub 21 of the 
control lever 20 is thus rigidly connected to the slidable body 32 and 
follows the rotations and axial movements thereof. A helical spring, 
indicated 37, is interposed between the base wall 22a of the cylindrical 
guide element 22 and the lower surface of the slidable body 32. A washer 
28 of plastics material with a low coefficient of friction is interposed 
between the lower surfaces of the body 32 and a metal ring 39 on which the 
upper end of the spring 37 bears. The washer 38 is provided since, in use, 
the body 32 can rotate relative to the cylindrical guide element 22 and 
consequently relative to the metal ring 39, as will become clear below. 
The end of the flexible metal cable 42 used for operating the derailer is 
fixed to the base wall 22a of the cylindrical guide element 22 by means of 
a tubular connector 40 provided with a stop screw 41. The opposite end of 
the cable 42 is connected to the usual gear-change lever (not visible in 
the drawings). The flexible cable 42 is also provided with a sheath 43 
having an end 44 (FIG. 1) bearing against an appendage 45 of the bicycle 
frame 5, and an end 46 ((FIG. 5) bearing on a base wall of the tubular 
shank 32. 
The lower body 8 of the derailer is also articulated by means of a pin 47 
(FIG. 6) parallel to the pin 17 to one end of an auxiliary connecting rod 
48 whose opposite end 49 (FIG. 6) is provided with a pin 50 (FIG. 4) which 
is mounted slidably and rotatably in an appendage 51 of the upper body 2. 
The operation of the above-described derailer is as follows: 
The spring 37 FIG. 5) housed within the cylindrical guide element 22 tends 
to keep the lever 20 controlling the transmission wheel 11 of the derailer 
in the position illustrated in FIGS. 1 and 2, which corresponds to 
engagement of the chain 12 with the smallest-diameter sprocket 7. 
Supposing that the derailer is in this position when the cyclist wishes to 
derail the chain onto another gear, he operates the gear-change lever (not 
illustrated) to tension the flexible metal cable 42. As already stated, 
the opposite end of the cable 42 is fixed to the base wall 22a of the 
cylindrical guide element 22 (FIG. 5) which is in turn fixed to the 
bicycle frame by means of the upper body 2. However, as is clear from FIG. 
1, the section of cable between the two ends of the sheath 43 forms a 
large loop. When the cable 42 is tensioned, it tends to straighten in this 
section. As a result, the end 46 (FIG. 5) of the sheath 43 is urged 
downwardly against the base wall of the tubular shank 32a and thus causes 
a downward axial movement of the slidable member 32 within the cylindrical 
guide element 22, against the action of the spring 37. The engagement of 
the transverse pins 34 in the helical slots 35 means that the downward 
movement of the slidable body 32 is accompanied by a corresponding 
rotation of this body about the axis 23. Since the hub 21 of the control 
lever 20 is connected to the body 32 by means of the pins 34, the 
operation of the flexible cable 42 consequently imparts rotation and 
simultaneous axial movement to the control lever 20. During this movement, 
the orientation of the axis 9 of the lower body 8 does not change, by 
virtue of the further connection existing between the lower body 8 and the 
upper body 2, constituted by the connecting rod 48 (FIG. 6). The 
conformation of the helical slots 35 is selected so as to obtain the 
desired path of movement of the transmission wheel 11. The resulting 
movement of the wheel therefore has both a component parallel to the axis 
10 of the rear wheel of the bicycle, which is necessary to cause derailing 
of the chain from one sprocket to another, and a component radial to that 
axis, to allow for the different diameters of the various sprockets. 
FIGS. 3 and 4 illustrate the position of the derailleur in the condition 
which corresponds to the engagement of the chain with the sprocket of 
largest diameter. 
As can be seen, it is possible to obtain efficient operation of the 
derailleur even with sprockets of greatly differing diameters, whilst at 
the same time keeping the dimensions of the derailleur, and in particular 
of the operating lever 20, relatively small. 
When the tension in the flexible metal cable is relaxed, the spring 37 
causes the derailleur to return towards the position which corresponds to 
engagement with the smaller-diameter sprockets. The arrangement of the 
biassing spring within the cylindrical guide element affords the further 
advantage of the protection of this spring from operating problems due to 
the deposition of dirt. 
Naturally, the configuration of the helical slots 35 can be varied at the 
design stage to obtain whatever laws are required for the movement of the 
transmission wheel 11. Moreover, it is also possible to use some other 
type of cam device for rotating the control lever 20 as a result of the 
axial movement of the slidable body 32 caused by operation of the flexible 
cable, instead of the helical slots 35. 
Finally, it is possible to provide on the same device various (for example, 
two) helical slots with different configurations and to provide a system 
for selecting engagement of the corresponding transverse pins in one or 
other of the slots. This solution enables the cyclist to adapt the 
derailleur easily to different possible requirements resulting from 
different selections of sprockets. 
FIG. 7 is a variant of FIG. 5 which relates to a second embodiment of the 
invention. In FIG. 7, the parts in common with FIG. 5 are indicated by the 
same reference numerals. In the case of FIG. 7, the body 32 mounted 
slidably within the cylindrical guide element 22 is made fast with the hub 
21 of the control lever 20 by means of a single transverse pin 34a. The 
spring 37 bears directly against the transverse pin 34a through an element 
39a having an upper saddle-shaped surface and bearing at its bottom 
against a nut 150 screwed into a threaded hole 151 of an appendage 52 
projecting from a reinforcing brace 53 formed in a single piece with the 
upper body 2. The cylindrical guide element 22 is inserted at its lower 
end in a hole 54 in the appendage 52. A cup 55 is interposed between the 
lower end of the spring 37 and the surface of the nut 50 and is supported 
by a ball 56 or by some other type of anti-slip device, for example, a 
thrust bearing. The shank 32a of the slidable body 32 has an end which 
projects from the top of the upper body 2 and to which a body 58 having 
the function of a crank for rotating the member 32 is fixed by a screw 57. 
The end 46 of the sheath 43 of the flexible cable is fixed to an appendage 
59 of the upper body 2, situated in the rear region of the upper body 
(with refernece to the direction of travel of the bicycle). The end of the 
flexible cable 42, however, is fixed by a screw 69 to the crank body 58 at 
a point which is spaced from the axis 23. 
As in the solution already described, the spring 37 tends to keep the 
control lever 20 in its highest position. When the flexible cable 42 is 
tensioned, it causes the rotation of the member 34, and consequently of 
the control lever 20, through the crank 58. The engagement of the 
transverse pin 34a in the helical slots 35 causes simultaneous lowering of 
the control lever 20 against the action of the helical spring 37. When the 
tension in the cable is relaxed, the spring 37 tends to return the body 34 
upwards, together with the control lever 20, causing an opposite rotation 
of this lever, again as a result of engagement of the transverse pin 34a 
in the helical slots 35. 
FIG. 8 illustrates a further variant of FIG. 5 which relates to a third 
embodiment of the invention. In this Figure also, the parts in common with 
FIG. 5 are indicated by the same reference numerals. 
In the case of FIG. 8, an auxiliary tubular element 70 is slidably mounted 
within the cylindrical guide element 22 carried by the upper body 2, and 
its lower end is fixed to the hub 21 of the control lever 20 by means of a 
nut 71. The nut 71 presses an annular end flange 72 of the auxiliary 
tubular element 70 against the base wall of a threaded hole 73 formed 
axially in the lower end of the hub 21. The transverse pins 34 are carried 
by the hub 21 and engage the two helical slots 35 provided in the 
cylindrical guide element 22 from the outside. The helical spring 37 is 
situated within the auxiliary tubular element 70 and is interposed between 
the nut 71 and the lower end surface of the ring 29 used for the axial 
clamping of the various elements. A washer of plastics material with a low 
coefficient of friction, indicated 74, is interposed between the upper 
surface of the spring 37 and the lower surface of the ring 29. The end 46 
of the sheath 43 of the flexible cable bears on the base surface of a seat 
46a formed in the head of the ring 29, whilst the end of the flexible 
metal cable 42 is anchored by means of a bolt 75 to an appendage 76 of the 
nut 71. The metal cable 42 passes through the axial hole 31 of the ring 
29, through a tubular bush 77 joined to the nut 71, and through an axial 
through-hole 78 formed in this nut. 
In the case of FIG. 8, the control lever 20 is in its highest position 
(illustrated in the drawing) when the cable is in the condition of maximum 
tension. When the tension in the cable is relaxed, the lever 20 moves 
downwards under the biassing action of the helical spring 37. Supposing 
that the control lever 20 is in the position illustrated in FIG. 8 and 
that the tension in the cable is relaxed, the biassing spring 37 causes 
lowering of the auxiliary tubular element 70 together with control lever 
20. The engagement of the pins 34 in the helical slots 35 causes 
simultaneous rotation of the control lever 20, together with the tubular 
auxiliary element 70, about the axis 23. 
Naturally, the principle of the invention remaining the same, the forms of 
embodiment and details of construction may be varied widely with respect 
to those described and illustrated purely by way of example. 
In the case of the variant illustrated in FIG. 7, for example, the 
appendage 59 for supporting the sheath 43 could be provided in the front 
region of the upper body 2 - with reference to the direction of travel of 
the bicycle - with the advantage that a shorter sheath 43 can be used. 
A further possible variant consists of the arrangement of the axis 23 of 
rotation of the lever 20 so that it is inclined to a plane perpendicular 
to the axes 9 and 10. Furthermore, a structural solution could be produced 
in which the spring 37 is not arranged within the hub 21 of the lever 20. 
Finally, it is clear that the cam means, constituted by the helical slots 
35 and the pins 34 in the examples illustrated, could be replaced by some 
other type of mechanism adapted to cause simultaneous rotation and axial 
movement of the lever 20 when a simple axial movement or a simple rotation 
is transmitted thereto.