Brake disc for a bicycle

A bicycle brake disc having a braking track with brake pads and a plurality of first connection portions that extend towards the inside and that comprise respective first connection areas; a second component having (i) a radially inner annular coupling portion for coupling with a hub of a wheel of the bicycle and (ii) a plurality of second connection portions. The second connection portions extending outwards from the radially inner annular coupling portion towards the first component and comprising respective second connection areas; connecting members active between the first connection areas and the corresponding second connection areas. The second connection portions comprise at least one respective pair of arms that extend between the respective second connection area and the radially inner annular coupling portion, the pair of arms defining a through opening between them.

CROSS REFERENCE TO RELATED APPLICATION

This application claims the benefit of Italian Application No. 102017000013990, filed on Feb. 9, 2017, which is incorporated herein by reference as if fully set forth.

FIELD OF INVENTION

The present invention relates to a brake disc for a bicycle.

BACKGROUND

In particular, the brake disc is configured to be mounted on a hub of a wheel of the bicycle.

Preferably, said bicycle is a racing bicycle.

As known, it is now common in bicycles to use disc brakes. Such brakes are indeed often preferred to conventional brakes of a different type in that they ensure a high braking force and better modularity that allows a marked braking sensitivity, as well as being less subject to problems caused by mud or water.

Typically, a disc brake comprises a caliper fixed onto the frame of the bicycle and a brake disc mounted on the hub of the wheel. Inside the caliper there are two or four opposite brake pads. The brake disc rotates inside the space defined between the opposite pads. By actuating the brake lever, the pads are brought towards the brake disc, generating friction on the brake disc and, consequently, braking the wheel.

The brake disc comprises a braking track configured to cooperate with pads and a radially inner annular coupling portion for coupling with the hub.

The brake disc can be made in a single piece or in two components.

In this last case, the brake disc comprises a first component having the braking track and a second component having the radially inner annular coupling portion for coupling with the hub.

The first component is typically made of a first material that ensures good braking properties, like for example steel, whereas the second component is typically made of a second lighter material, like for example aluminum or light alloys.

The second component has a plurality of radially outer connection portions for connecting to the first component at a respective plurality of radially inner connection portions of the first component.

In the technical field, the second component is called “spider” or “carrier”, whereas the first component is called “rotor” or is simply indicated with the expression “braking track”.

The connection between the radially outer connection portions of the second component and the radially inner connection portions of the first component can be carried out so that the first component and the second component are substantially coplanar but not in direct contact, to avoid the occurrence of mechanical tensions in the radial direction due to different heat expansion coefficients of the two materials of the first and the second component. The two components of the brake disc are joined together by rivets or similar which also keep the rotor and the spider coplanar and slightly spaced apart in the radial direction. The brake disc with this type of coupling, known as floating rotor brake disc, has the drawback of having potential twisting, since the planarity of the brake disc is, basically, entrusted only to the rivers.

Alternatively, the two components of the brake disc are coupled together so that regions between portions of the rotor and portions of the spider overlap, making a so-called “non floating rotor”. Also in this case, rivets or similar stably join the two components of the brake disc, but the structural continuity of the entire brake disc is also ensured by the overlapping region between rotor and spider.

As far as the coupling with the hub is concerned, the radially inner annular portion of the brake disc is provided with a grooved radially inner surface (in other words a radially inner surface that extends longitudinally and is provided with longitudinal grooves), which is mounted on a matching grooved radially outer surface (in other words a radially outer surface that extends longitudinally and is provided with longitudinal grooves matching those of the radially inner surface) of a portion of the hub, as disclosed in patent application EP 1932753 to the same Applicant.

EP 1932753 also discloses a lock nut, which is screwed onto the hub until it abuts axially on the radially inner annular portion of the brake disc, so as to define a stable axial position of the brake disc on the hub.

The radially outer connection portions of the second component typically consist of a plurality of arms arranged equally circumferentially spaced and extending from the radially inner annular coupling portion. Such arms can have a substantially radial arrangement or, preferably, are inclined with respect to the radial direction, typically with the same inclination for every arm. The number of arms is variable: for example brake discs with five or six arms are well known.

The aforementioned arms are typically made in one piece with the radially inner annular coupling portion.

The braking force exerted by the pads of the brake on the braking track is transmitted to the radially inner annular coupling portion of the brake disc and discharged on the hub of the wheel. Therefore, the braking force exerted by the pads of the brake creates a torque at the radially inner annular coupling portion of the brake disc that is compensated by a pair of resistant forces of equal intensity and opposite direction at the coupling between brake disc and hub of the wheel.

The Applicant has observed that at the connection between arm and radially inner annular coupling portion there are areas with high concentration of stresses, since in these areas the distance from the pad of the brake is substantially maximum and, therefore, the torque transmitted is also maximum. For this reason, as stated above, the cited arms are preferably inclined with respect to the perfectly radial direction, to try to decrease the component of the braking force perpendicular to the arm itself (and therefore the torque transferred to the radially inner annular coupling portion).

The Applicant has however noted that the inclination of the arms with respect to the radial direction cannot be increased beyond a certain limit, since the arms must effectively reach the radially inner annular coupling portion.

The Applicant has also noted that increasing the inclination of the arms and, at the same time, ensuring that they effectively reach the radially inner annular coupling portion means an increase in the size of the arms, with consequent increase in the weight of the brake disc.

The Applicant has perceived that it would be advantageous to ensure an effective and safe transmission of forces between braking track and radially inner annular coupling portion, at the same time keeping down the weight of the brake disc.

SUMMARY

In the present description and in the following claims, the terms “axial”, “axially”, “longitudinal”, “longitudinally” and the like are meant to refer to a direction substantially coinciding with or substantially parallel to a rotation axis of the brake disc, which substantially coincides with a longitudinal axis of the hub, whereas the terms “radial”, “radially” and similar are meant to refer to a direction that lies in a plane substantially orthogonal to the rotation axis of the brake disc and that passes through such a rotation axis.

The present invention therefore relates to a brake disc for a bicycle comprising:

a first component having a braking track configured to cooperate with brake pads and a plurality of first connection portions that extend towards the inside and that comprise respective first connection areas;

a second component having (i) a radially inner annular coupling portion for coupling with a hub of a wheel of the bicycle and (ii) a plurality of second connection portions, in a number corresponding to said plurality of said first connection portions, the second connection portions extending outwards from the radially inner annular coupling portion towards said first component and comprising respective second connection areas;

connecting members active between the first connection areas and the corresponding second connection areas;

characterized in that said second connection portions comprise at least one respective pair of arms that extend between the respective second connection area and the radially inner annular coupling portion, said pair of arms defining a through opening between them.

The Applicant has perceived that, by connecting the second connection area and the radially inner annular coupling portion with a pair of arms, it is possible to at the same time ensure both an effective mechanical coupling between the second connection area and the radially inner annular coupling portion, and an effective transmission of loads from the braking track to the radially inner annular coupling portion.

The Applicant has indeed perceived that each arm of the pair of arms can be oriented, in other words can extend, along mutually different directions so that the two arms can cooperate in transferring the loads coming from the braking track.

Moreover, thanks to the provision of the through openings defined between the pairs of arms, it is also ensured that the weight of the brake disc is kept down.

Hereinbelow preferred features of the brake disc for a bicycle according to the present invention are described, which can be provided for individually or in combination.

Preferably, the arms of said pair of arms extend along an arched line.

Such an arched line, predetermined during the design step, defines a concavity for each arm of the pair of arms. In this way, during braking, the compression force that said arms are subjected to tends to accentuate the concavity thereof, ensuring that they always bend in the same direction, avoiding breaking or yielding of the arms.

Preferably, said pair of arms has divergent arrangement from the respective second connection area towards the radially inner annular coupling portion, making divergent arms that extend in different directions.

The two divergent arms, extending in different directions, ensure that the load coming from the braking track is transmitted in points of the radially inner annular coupling portion that are circumferentially distant from one another. In this way, the load coming from the braking track can be distributed on the radially inner annular coupling portion along a large circular sector, decreasing the possibility of concentration of loads on very limited areas of the radially inner annular coupling portion.

Preferably, each second connection portion comprises a reinforcing arm that extends from the second connection area and reaches another second connection portion that is located circumferentially adjacent to said second connection portion.

Preferably, the reinforcing arm extends along an arched line.

Such an arched line, predetermined during the design step, defines a concavity for the reinforcing arm. In this way, during braking, the compression force that the reinforcing arm is subjected to tends to accentuate the concavity thereof, ensuring that it always bends in the same direction, avoiding breaking or yielding of the reinforcing arm.

Advantageously, the reinforcing arms ensure a more balanced distribution of the loads on the radially inner annular coupling portion.

In particular, each reinforcing arm extends from the second connection area and reaches an arm of the pair of arms, of the circumferentially successive second connection portion, at or close to a radially outer end thereof.

Such a configuration allows the creation of air vortices such as to allow a rapid dissipation of heat especially in the connection areas.

Furthermore, by extending and connecting the reinforcing arm in radially inner position with respect to the second connection area, the compression forces that passes through the reinforcing arm is allowed to be discharged far from the pivot of the connection between the first and the second component of the disc brake.

Preferably, each first connection portion comprises a radially outer end joined to the braking track and a radially inner end at the respective first connection area. More preferably, said first connection portion extends in an inclined direction with respect to a radial direction passing through the center of the radially inner annular coupling portion and through said radially inner end.

Advantageously, such an inclined direction with respect to the radial direction makes it possible to distribute the loads in a balanced manner so that the first connection portion works substantially with a compression stress and so that a radially opposite first connection portion works substantially with a traction force.

Preferably, each reinforcing arm of a second connection portion has an arrangement substantially parallel to that of the first connection portion of said first component with which the second connection portion of the second component is associated.

Advantageously, the reinforcing arm—with arrangement substantially parallel to that of the first connection portion—also works substantially with a compression stress.

Preferably, said through opening has rounded edges at joining areas of each arm of the pair of arms with the respective second connection area and with the radially inner annular coupling portion.

More preferably, said rounded edges have radii of curvature comprised in the range between 1 mm and 6 mm, including extreme values, preferably in the range between 2 mm and 4 mm, including extreme values, and more preferably in the range between 2.5 mm and 3 mm, including extreme values.

Advantageously, the rounded edges prevent the creation of areas of concentration of the stresses between the arms and the second connection area and between the arms and the radially inner annular coupling portion.

Preferably, each arm of the pair of arms has the same axial thickness.

More preferably, said reinforcing arm has smaller axial thickness than that of the arms of the pair of arms.

Advantageously, the arms of the pairs of arms and the reinforcing arms lie on two different planes. The middle plane of the arms of the pairs of arms lies between two planes of maximum thickness of the second connection portions, whereas the middle plane of the reinforcing arms lies on a plane that is located between the aforementioned planes of maximum thickness. This, as well as lightening the structure of the brake disc, creates a discontinuity of the surfaces that advantageously increases the turbulence of the air on the brake disc in operation and thus the dissipation of heat.

The connection between the second connection portions of the second component and the corresponding first connection portions of the first component takes place through the cited connecting members.

Preferably, such connecting members comprise axially perforated rivets received in respective through holes defined in the first and second connection area.

Advantageously, the use of perforated rivets ensures better damping of the vibrations with the effect of obtaining braking that is less noisy.

Preferably, said connecting members are equally spaced apart by a distance L comprised in the range between 10 mm and 80 mm, including extreme values, preferably in the range between 20 mm and 50 mm, including extreme values, and more preferably in the range between 35 mm and 40 mm, including extreme values.

Advantageously, the Applicant has found that with the distance L comprised in the aforementioned ranges the vibrations of the brake disc during braking are kept down, as is the relative noise produced.

The Applicant has also found that the preferred values of the aforementioned distance L between the connecting members are substantially unchanged irrespective of the outer diameter of the brake disc. For this reason, the number of connecting members, i.e. the number of first and second connection portions, increases as the outer diameter of the brake disc increases. For example, the Applicant has found that for a brake disc with outer diameter equal to 140 mm it is advantageous to have 6 connecting members (i.e. 6 first and second connection portions) and that for a brake disc with outer diameter equal to 160 mm it is advantageous to have 7 connecting members (i.e. 7 first and second connection portions).

Preferably, said first connection area axially overlaps the corresponding second connection area.

More preferably, said first connection area is housed in a recess of the second connection area.

Even more preferably, said first connection area is not radially in contact with the second connection area.

Advantageously, in this way the recess of the second connection area can be made without the need for strict dimensional tolerances. In the case in which the first and second component are made of different materials (for example steel and aluminum, respectively), the different thermal dilations of the first and second component do not generate radial loads on the recess of the second connection area.

Preferably, said braking track comprises a plurality of through openings, of elongated shape and inclined with respect to a direction of extension of a side edge of said brake pads.

Advantageously, the Applicant has found that—thanks to such an inclination—the noisiness during braking is reduced, since during braking the side edge of the brake pads does not meet the entire through opening at once, but meets it gradually.

Moreover, the Applicant has found that—using the same inclination for all of the through openings—the noisiness is constant during braking.

Preferably, said through openings have an inclination, with respect to said direction of extension of said side edge of said brake pads, comprised in the range between 5° and 60° mm, including extreme values, preferably in the range between 15° and 40° mm, including extreme values, and more preferably said inclination is about 29°.

Advantageously, the Applicant has found that with the inclinations indicated above the noisiness of the brake disc during braking is particularly low.

Preferably, the number of said through openings is a multiple of the number of first connection portions.

Advantageously, the Applicant has found that in this way the noisiness of the brake disc during braking is significantly reduced.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With initial reference toFIGS. 1-7 and 9, reference numeral10wholly indicates a first embodiment of a brake disc for a bicycle according to the present invention.

The brake disc10is configured to be mounted on a hub (not illustrated) of a wheel of the bicycle.

The hub is mounted on the frame of the bicycle. In particular, the frame comprises two opposite support arms of the wheel at the respective free end portions of which there are housing seats of opposite free end portions of the hub.

A caliper12(FIG. 7) of a disc brake is fixed onto the frame of the bicycle. In particular, the caliper is fixed in a conventional manner to one of the support arms of the wheel.

Inside the caliper12there are at least two opposite brake pads14(FIG. 6).

The brake disc10rotates inside the space defined between the opposite brake pads14. By actuating the brake lever (not illustrated), the brake pads14are brought towards the brake disc10, generating friction on the brake disc10and, consequently, braking the wheel.

In particular, the hub extends along a longitudinal axis X that coincides with the rotation axis of the bicycle wheel and of the brake disc10(FIG. 1).

The hub comprises a disc seat for housing and locking in rotation the brake disc10, and a shoulder, which provides an abutment position in the axial direction for the brake disc10mounted on the disc seat.

The disc seat comprises a grooved radially outer surface, i.e. a radially outer surface that extends longitudinally and is provided with longitudinal grooves.

The brake disc10comprises a grooved radially inner surface42amatching that of the disc seat, i.e. a radially inner surface42athat extends longitudinally and is provided with longitudinal grooves matching those of the grooved radially outer surface of the disc seat.

More in general, the disc seat is shaped according to a shape coupling profile. This term is meant to indicate that the profile of the disc seat has geometric characteristics such as to allow the transmission of a torsion between the hub (on which the disc seat is formed) and the brake disc10mounted on such a disc seat with a matching profile. A shape coupling profile can for example be a polygonal profile, or a circular profile with an alteration (for example, leveled along a cord), or other. In particular, the shape coupling profile of the disc seat illustrated in the non-limiting example of the figures is a grooved profile, with ridges and throats, oriented in a direction parallel to the axis X.

The shoulder is adjacent to an axially inner side of the disc seat.

Adjacent to the opposite axially outer side of the disc seat there is a threaded portion, formed at a free end portion of the hub, for coupling with a lock nut (not illustrated), which holds the brake disc10in the disc seat, against the shoulder.

The brake disc10comprises a first component30and a second component40.

The first component30comprises a braking track32and the second component40comprises a radially inner annular portion42for coupling with the hub.

The braking track32is configured to cooperate with the brake pads14and has a substantially annular extension, so that the radially outer profile of the first component30is substantially circular. In order to make the first component30less sharp, the radially outer edge30aof the first component30is rounded, as shown inFIG. 3.

The radially inner annular portion42is provided with the grooved radially inner surface42adescribed earlier.

The first component30is preferably made of a first material that ensures good characteristics of braking and of resistance both to oxidation and to wear, like for example steel, whereas the second component40is preferably made of a second lighter material, like for example aluminum or alloys thereof or other light alloys. Aluminum (or alloys thereof) is particularly recommended due to its ability to more easily transfer and dispose of the heat developed during braking.

The first component30comprises a plurality of first connection portions34that extend from the braking track32towards the inside (i.e. towards the axis X of the brake disc10). The first connection portions34comprise respective first connection areas36at which the first component30is connected to the second component40. The first connection portions34are equally circumferentially spaced and, in the example illustrated inFIGS. 1-7 and 9, there are seven of them. InFIGS. 1-7 and 9, so as not to overcomplicate the graphical representation, the reference numerals are indicated only on some of the first connection portions34, as well as only on some of other elements described hereinafter.

The first connection areas36are made at respective free end portions of the first connection portions34.

In particular, each first connection portion34comprises a radially outer end34ajoined to the braking track32and a radially inner end34bat the respective first connection area36.

In the example illustrated inFIGS. 1-7 and 9, the first connection portions34comprise a respective pair of connector elements35that extend between the respective first connection area36and the braking track32. The pair of connector elements35defines a through opening of elongated shape37between them.

The connector elements35have a slightly divergent or substantially parallel arrangement, from the respective first connection area36towards the braking track32.

In the example illustrated inFIGS. 1-7 and 9, each connector element35has the same axial thickness.

The first connection portion34extends in a direction inclined with respect to a radial direction passing through the center of the radially inner annular portion42and through the radially inner end34b. Such an inclination with respect to the radial direction is comprised in the range between 5° and 70°, including extreme values, preferably in the range between 30° and 60°, including extreme values, and more preferably in the range between 45° and 55°, including extreme values.

The braking track32comprises a plurality of through slits32a, of elongated shape and inclined with respect to a direction of extension of a side edge14aof the brake pads14(FIG. 6).

In other words, given that the side edge14aof the brake pads14extends according to a direction substantially parallel to a radial direction that passes through the center of the brake pad14and through the center of the brake disc10, the through slits32aare substantially inclined with respect to such a radial direction.

The direction of the through slits32ais defined as the direction along which an edge of such openings extends. Such an edge is preferably the edge of the through slit32awhich firstly comes into contact with the brake pad14during normal use of the bicycle.

In particular, the through slits32ahave an inclination, with respect to the direction of extension of the side edge14a, comprised in the range between 5° and 60°, including extreme values, preferably in the range between 15° and 40° including extreme values, and more preferably said inclination is about 29°.

All of the through slits32ahave substantially the same inclination, or in any case an inclination comprised in the aforementioned ranges, including extreme values.

The number of through slits32ais a multiple of the number of first connection portions34. In particular, in the example illustrated inFIGS. 1-7 and 9, there are seven first connection portions34and there are forty-nine slits32a.

The second component40comprises a plurality of second connection portions44, in equal number to that of the plurality of first connection portions34. The second connection portions44are equally circumferentially spaced. The second connection portions44extend outwards from the radially inner annular portion42towards the first component30and comprise respective second connection areas46, at which the second component40is connected to the first component30. InFIGS. 1-7 and 9, so as not the overcomplicate the graphical representation, the reference numerals are indicated only of some of the second connection portions44, as well as only some of other elements described hereinafter.

The second connection areas46are made at respective free end portions of the second connection portions44.

In particular, each second connection portion44comprises a radially outer end44aat the respective second connection area46and a radially inner end44bjoined to the radially inner annular portion42.

The second connection portions44comprise a respective pair of arms45that extend between the respective second connection area46and the radially inner annular portion42. The pair of arms45defines a through opening47between them.

The pair of arms45has divergent arrangement from the respective second connection area46towards the radially inner annular portion42. Such divergent arms45thus extend in different directions.

As illustrated in the attached figures, a first arm45of the pair of arms45has inclination, with respect to a radial direction passing through the center of the radially inner annular portion42and the second connection area46, opposite to the inclination of the other divergent arm.

Preferably, the first divergent arm45is inclined with respect to the other divergent arm by an angle comprised between 15° and 90°, more preferably comprised between 20° and 60°, even more preferably comprised between 35° and 45°.

In the example illustrated inFIGS. 1-7 and 9, each arm45has the same axial thickness.

The divergent arms45have a non-rectilinear but arched extension.

The arched extension of the divergent arms45defines a concavity thereof so that a line passing through the end of an arm45constrained to the second connection area46and through the end of the same arm constrained to the radially inner annular portion42does not intercept portions of the arm comprised between the two ends.

As more clearly illustrated inFIG. 2, the concavity of both divergent arms45faces in the same direction.

Preferably, the concavity of an arm45directly faces the through opening37and the concavity of the arm45, of the second connection portion44, circumferentially preceding (in accordance with the direction of rotation of the brake disc) faces the opposite way with respect to the through opening37.

The through opening47has rounded edges at joining areas of each arm45with the respective second connection area46and with the radially inner annular portion42. In other words, each arm45is connected with the respective second connection area46and with the radially inner annular portion42without sharp edges, but with rounded edges.

Such rounded edges have radii of curvature comprised in the range between 1 mm and 6 mm, including extreme values, preferably in the range between 2 mm and 4 mm, including extreme values, and more preferably in the range between 2.5 mm and 3 mm, including extreme values. Such radii of curvature make it possible to have a homogeneous distribution of stresses between the divergent arms45.

Each second connection portion44comprises a reinforcing arm49that extends from the second connection area46and reaches another second connection portion44that is located circumferentially adjacent to the aforementioned second connection portion44.

In particular, each reinforcing arm49extends from the second connection area46and reaches an arm45of the other second connection portion44that is located circumferentially adjacent. In the example illustrated inFIGS. 1-7 and 9, the reinforcing arm49reaches the divergent arm45at or close to its radially outer end44a.

Each reinforcing arm49of a second connection portion44has arrangement substantially parallel to that of the first connection portion34of the first component30.

In the example illustrated inFIGS. 1-7 and 9, the reinforcing arms49have lower axial thickness than that of the arms45.

As shown inFIG. 7, the maximum outer diameter of the second component40is within a circumference C that does not interfere with the caliper12.

In other words, the maximum outer diameter of the second component40is smaller than the inner diameter of the braking track32.

The connection between the second connection portions44of the second component40and the corresponding first connection portions34of the first component30, and in particular the connection between the second connection areas46and the corresponding first connection areas36, takes place through connecting members50.

Such a connecting member50is preferably a rivet52. The rivet52is perforated and is received in respective through holes36c,46cformed in the first and second connection area36,46. Moreover, the rivet52is mounted with axis substantially parallel to the axis X and is caulked. The caulking52aof the rivet52is carried out on the first connection area36, whereas the shoulder52bof the rivet52rests on the second connection area46.

The transfer of the braking force takes place through the rivets52that work cutting through the contact surface between the first and second connection area36,46. The lateral stresses on the brake disc10are discharged onto the contact surface between the first and second connection area36,46.

As illustrated inFIGS. 4 and 5, the first connection area36axially overlaps the corresponding second connection area46and is housed in a recess46aof the second connection area46.

As illustrated inFIGS. 4 and 5, the first connection area36is not radially in contact with the second connection area46. In other words, a space is provided in the radial direction between side wall46bof the recess46aof the second connection area46and side wall36aof the first connection area36. The side wall46band the side wall36aare arranged substantially parallel to the axis X.

The connecting members50are equally spaced apart by a distance L (FIG. 9) comprised in the range between 10 mm and 80 mm, including extreme values, preferably in the range between 20 mm and 50 mm, including extreme values, and more preferably in the range between 35 mm and 40 mm, including extreme values.

FIG. 8shows a second preferred embodiment of a brake disc for a bicycle in accordance with the present invention, wholly indicated with10.

In such aFIG. 8, elements that are analogous or functionally corresponding to those described above with reference to the first embodiment illustrated inFIGS. 1-7 and 9are indicated with the same reference numeral and for their detailed description reference should be made to what has been outlined above.

The second embodiment of the brake disc10illustrated inFIG. 8differs from the one illustrated inFIGS. 1-7 and 9substantially in that the brake disc10has a smaller outer diameter than that of the brake disc10illustrated inFIGS. 1-7 and 9, as can be clearly seen from the visual comparison ofFIGS. 8 and 9.

For example, the brake disc10ofFIG. 8has an outer diameter equal to 140 mm, whereas the brake disc10ofFIG. 9has an outer diameter equal to 160 mm.

The distance L between the connecting members50of the brake disc10ofFIG. 8is substantially unchanged with respect to that of the brake disc10ofFIG. 9.

In order to obtain this, the number of connecting members50of the brake disc10ofFIG. 8, i.e. the number of first and second connection portions34and44, is less than that of the brake disc10ofFIG. 9. In particular, there are six connecting members50of the brake disc10ofFIG. 8, instead of the seven connecting members50of the brake disc10ofFIG. 9.

There are six first and second connection portions34and44of the brake disc10ofFIG. 8and there are forty-two through slits32a.

FIGS. 10-12show a third preferred embodiment of a brake disc for a bicycle in accordance with the present invention, wholly indicated with10.

In suchFIGS. 10-12, elements that are analogous or functionally corresponding to those described above with reference to the first embodiment illustrated inFIGS. 1-7 and 9are indicated with the same reference numeral and for their detailed description reference should be made to what is outlined above.

The third embodiment of the brake disc10illustrated inFIGS. 10-12differs from that illustrated inFIGS. 1-7 and 9substantially in that the second connection areas46of the brake disc10are not provided with the recesses46aforeseen in the second connection areas46of the brake disc10ofFIGS. 1-7 and 9. The first connection areas36axially overlap the corresponding second connection areas46, as illustrated inFIGS. 10-12.

In this case, the second component40can be made of punched sheet steel, composite material or plastic material.

In particular, the second component40can be made of steel and the forming takes place with successive molding operations.

The second component40of the brake disc10ofFIGS. 1-9is generally made of forged aluminum (or alloys thereof) and then machined.

Of course, those skilled in the art can bring numerous modifications and variants to the brake disc for a bicycle of the present invention, in order to satisfy specific and contingent requirements, all of which are in any case covered by the scope of protection defined by the following claims.