Disc for a Disc Brake

Abstract

The present invention relates to a disc for a disc brake comprising a support bell and braking band being coaxial with each other. The support bell has a plurality of radial housings and the braking band has a plurality of connecting elements suitable to connect it to the bell. The connecting elements are integral and made as one piece with said braking band and overhang from the braking band in order to engage the corresponding radial housings. The connecting elements are at least partially surrounded by walls being integral and made as one piece with the support bell such as to be fastened in the axial direction and in the tangential direction and such as to be capable of sliding in the radial direction.

Description

The present invention relates to a disc for a disc brake, particularly though not exclusively, for applications in the car field.

It is known that the discs of the above-mentioned type consist of two parts sharing a rotation axis. A first part, the support bell, is destined to be connected to the wheel hub of a vehicle, whereas the remaining peripheral part, the braking band, is destined to cooperate with the disk brake calipers to carry out the braking action on the vehicle. The braking band can be either solid or, such as in the examples represented in the annexed figures, ventilated. The ventilated band comprises two binders being connected by a plurality of bridges, such as to define cooling air ducts.

With reference to the disc and the rotation axis thereof, any direction parallel to said axis is defined as being axial, any perpendicular direction to the axis and incident thereto is defined as being radial, and any direction tangential to a circumpherence centered on said axis and laying on a normal plane to said axis is defined as being tangential.

It is also known that, when the brake is being operated, the friction between the brake caliper pads and the braking band surface generates a considerable amount of heat that requires to be released. The generated heat causes a number of unwanted phenomena, first of all the overheating of the components and the consequent thermal expansion and distortion of the same.

In the disc brake field, the need is particularly felt to provide the braking band in a material that, besides ensuring the desired friction characteristics, is capable of maintaining its mechanical characteristics as much unchanged as possible upon increase in the operating temperature. In view of the above, it is particularly convenient to manufacture the braking band of cast iron.

Likewise, the need is particularly felt of manufacturing the support bell of a material that is as much light as possible, first of all to reduce the mass of the disc and consequently the non-suspended masses of the vehicle. In view of the above, it is particularly convenient to manufacture the support bell of a light alloy, such as aluminium alloy.

With reference to the prior art discs, it should be noted that the distortions caused by heat strain entail inconveniences in the operation of the disc brake, first of all the uneven wear of the brake caliper pads. This is mainly due to the fact that, contrary to the braking band, which tends to be radially deformed while remaining coplanar with itself, the support bell is deformed by taking the shape of a cone that also defines the twist of the braking band. The deformation of the support bell substantially defines the twist and accordingly the loss of coplanarity of the braking band.

From what has been stated above, there emerges a double need of maintaining unchanged the transmission of the braking torque from the braking band to the support bell and, at the same time, allowing the braking band to radially dilate, due to the heat stress to which it is subjected as much independently from the support bell as possible.

The patent EP1092889, in the name of the same applicant, describes a disc in which the bell of aluminium alloy and the braking band of cast iron are joint by a plurality of stainless steel pins. The pins, which are interference coupled in the braking band and slackly in the bell, make it possible for the band to radially dilate. This solution is particularly expensive and complicated from the point of view of construction. Furthermore, the small section of the steel pins induce high stress peaks in the material in the step of transmission of the braking torque from the band to the bell.

It is also known from patent U.S. Pat. No. 6,152,270, in the name of the same applicant, a disc having a braking band of cast iron and a support bell made of a light alloy. Both pieces are produced by subsequent castings in such a way as to be intimately adhered, so that they are integral to each other. This solution, though being cost-effective and easy to implement, does not allow the band to radially dilate independently from the bell.

The problem at the heart of the present invention is to conceive a disc for a disc brake that has such structural and functional characteristics to meet the above-mentioned requirement and overcoming, at the same time, the drawbacks cited with reference to the prior art.

This problem is resolved by a disc for disc brake in accordance with claim 1.

Further characteristics and the advantages of the disc for a disc brake according to the invention will become apparent from the description of a preferred embodiment thereof, which is merely illustrative and non-limiting, with reference to the annexed figures, in:

FIG. 1 shows a disc for a disc brake according to the invention in a perspective view;

FIG. 2 shows the disc from FIG. 1 in a partially sectional perspective view;

FIG. 3 shows the disc from FIG. 1 in a partially sectional perspective view;

FIG. 4 shows the disc from FIG. 1 in a partially sectional front view;

FIG. 5 shows a section taken along the line V-V of FIG. 4;

FIG. 6 shows a braking band according to the invention taken along the line VI-VI of FIG. 7;

FIG. 6 a shows a detail from FIG. 6;

FIG. 7 shows a braking band according to the invention taken along the line VII-VII of FIG. 6;

FIGS. 8.a and 8.b show a detail of a braking band according to the invention in two steps of the manufacturing process;

FIGS. 9.a, 9.b and 9.c show three different embodiments of a detail of a braking band according to the invention;

FIG. 10 shows a section taken along the line X-X of FIGS. 4 and 5;

FIGS. 11.a to 11.e are subsequent steps of the method for manufacturing the disc according to the invention.

With reference to the above mentioned figures, with 1 there is generally indicated a disc according to the invention that is destined to be used in a disc brake (not shown) of a vehicle, for example a car.

The disc 1 has a substantially circular shape that develops around a symmetry axis being indicated with x-x and can be defined a middle plane, the outline thereof being indicated with a dotted line in FIG. 6.

The disc 1 comprises a support bell 2 and a braking band 3, that is coaxial with the support bell 2, being provided with a plurality of connecting elements 4 suitable to connect the braking band 3 to the support bell 2.

The support bell 2 comprises a central portion 5 destined to be connected, in a conventional manner, to the wheel hub of a vehicle and a peripheral annular portion 6 which is cantilevered from the central portion 5, for example in a direction substantially parallel to x-x axis.

The braking band 3 is embodied by an annular disc of a preset thickness S and height H, which is coaxially supported by the peripheral annular portion 6 of the support bell 2. The braking band 3 is destined to cooperate with the disc brake caliper to exert the braking action on the vehicle.

With particular reference to FIGS. 8.b and 9.a, each of the connecting means 4 is embodied for example by a prismatic projection having a quadrangular section, which is suitable to radially connect the braking band 3 to the support bell 2. In FIG. 9.a there is shown how both side faces 40 of the prismatic projection are parallel to the r-r radial axis passing through the center of the projection 4.

Alternatively, projections having different shapes can be also used.

With particular reference to FIG. 9.b, for example, the side faces 40 of the projection 4 are not parallel to each other. Each of them defines an angle α with the direction r‘-r’ parallel to the radial axis r-r passing through the center of the projection. The angle α can vary, according to the particular design requirements, from 0° to 3°. Consequently, the angle 2α defined between two opposite faces 40 can vary from 0° and 6.

With particular reference to FIG. 9.c, again, the projection 4 has side faces 40 being parallel for the first length thereof being contiguous to the root and convergent in the second end length where a chamfer 42 is formed. In other words, the projection of FIG. 9.c is similar to that of FIG. 9.a, to which the sharp edges at the ends radially near to axis x-x have been chamfered.

The configuration of FIG. 9.c with the chamfered sharp edges, besides from a geometry like that of FIG. 9.a with parallel side faces 40, can also be adopted from a geometry like that in FIG. 9.b with slightly inclined faces.

Independently of the geometry selected, the side faces 40 of the single projection 4 are arranged such as to limit their surface roughness within preset values. Preferably, the side faces 40 of the projections have an average surface roughness R_a less than 6.4×10⁻⁶ meters.

The connecting elements 4, i.e. the projections, are made as one piece with the braking band 3 such as to be integral therewith.

As can be seen in the annexed drawings, the projections 4 are joined to the body of the braking band 3 by means of fillets 44. More particularly, the detail of the band section from FIG. 6.a and the detail of the section in the middle plane of FIGS. 8.a and 8.b should be seen. Upon defining the particular union radius during the design step, one should take into account the type of material employed for manufacturing the braking band 3 in a known manner.

The projections 4 are housed in corresponding radial housings 8 being obtained in the peripheral annular portion 6 of the support bell 2. These radial housings are 8 defined by walls 80 being made as one piece with the bell body 2, such as being integral therewith.

The radial housings 8, being provided by means of a method that will be described herein below, are perfectly complementary to the side faces 40 of the respective projections 4 or at least some lengths thereof.

In other words, the radial housings 8 at least partially surround the projections 4 such as to restrain the movements thereof in the axial and tangential directions.

The coupling between the projection 4 and the housing 8 is not an interference coupling, on the contrary it provides a backlash, even though very small.

The surfaces of the side faces 40 and the walls 80 are intimately coupled to each other without any adhesion to each other. In other words, the surfaces of the side faces 40 and the walls 80 are intimately coupled and disjointed.

In view of the above, it will appreciated by those skilled in the art that both the walls 80 and the side faces 40 are made such as to allow that, while movements in the axial and tangential directions are prevented because the side faces 40 rest on walls 80, the radial movement of the single projection 4 within the single housing 8 is not prevented by anything.

Particularly, the radial movement is not prevented either by macroscopic fittings or micro-telescoping of both materials composing the projection 4 and the walls 80 of housing 8. These micro-telescoping may occur with greater surface roughness of the surfaces.

With particular reference to FIG. 11, the above method for manufacturing the disc according to the invention, provides first of all that the braking band 3 be manufactured of a suitable material, for example cast iron.

Advantageously, in a manner known per se, the braking band 3 is provided by casting, for example in a sand mould 70. In this manufacturing step of the band, the connecting elements 4 are also manufactured, for example the protrusions 4 described above.

It is particularly advantageous, in this casting step, to provide a stock 35, 45 both on the braking band 3 itself and the side faces 40 of the projections 4. In FIG. 6 there is outlined how the surface 30 of the braking band 3 will be after the stock 35 has been removed; in FIG. 6, in the detail of FIG. 6.a and in FIG. 8.a there is outlined how the side face 40 of the projection 4 will be after the stock 45 has been removed.

The stock being provided upon the casting step has to be removed in order to bring the braking band to the desired thickness S, and at the same time, to bring the projections 4 to the desired size.

This step of removing the stock can be brought to completion in a manner known per se by means of tool machining. FIGS. 8.a and 8.b show two projections 4 at the end of the casting step and at the end of the step of removing the stock 45, respectively.

In accordance with an embodiment, in this step there is also defined the geometry of protrusions 4. In particular, as described above, one may provide that the faces 40 are parallel, or one may provide that they are biased relative to each other according to a small angle, preferably comprised 0° and 6°.

Simultaneously and independently from the selection on the parallelism of the faces 40, one may also decide whether to provide a chamfer 42 or let the faces 40 end with a sharp edge.

In accordance with an embodiment of the method, during this working step, the desired surface roughness is conferred to the faces of the projections. Particularly, the surface roughness R_a will be preferably less than 6.4×10⁻⁶ meters.

In accordance with another embodiment of the method, during the manufacturing step of the braking band, any stock 45 cannot be provided on the projections 4 of the braking band 3, such that the desired geometry is already conferred thereto. For example, the braking band can be obtained by means of chill casting instead of sand. It is thus possible to obtain an improved control on the shape of the piece being manufactured by casting. In accordance with this method, due to a manufacturing step of the braking band 3 allowing to control the geometry, the surface finishing step may even be superfluous. In fact, the projections 4 being manufactured for example by chill casting may already have a suitable surface roughness, without requiring further working to avoid micro-telescoping.

Once that the braking band 3 and the projections 4 have reached the desired size and surface roughness, the method for manufacturing the disc according to the invention provides that the braking band is placed in a mould 72 for casting the support bell 2. The mould 72, which is schematically represented in FIG. 11.c, houses the braking band 3 such as to cause the projections 4 to overhang towards the inside of cavity 2′, which is complementary to the shape of the bell 2.

Thereafter, the molten metal destined to form the bell 2, preferably a light alloy, for example an aluminium alloy is cast in the cavity 2′.

In this way, in the support bell 2, a housing 8 is manufactured for each projection 4. The surfaces of the side faces 40 and the walls 80 thus made are intimately coupled to each other without any adhesion occurring to each other.

Particularly, both the walls 80 and the side faces 40 are manufactured such as to allow the radial movement of the single projection 4 within the single housing 8, whereas the movement in the axial and tangential directions are prevented because the side faces 40 rest on the walls 80.

Particularly, the radial movement is not prevented either by macroscopic fittings or micro-telescoping of both materials composing the projection 4 and walls 80 of the housing 8. These micro-telescoping may occur with greater surface roughness of the surfaces.

In accordance with an embodiment of the method, before carrying out the cast of the support bell 2, when the projections 4 are coated with a protective layer. It is thus possible to ensure a minimum value of the coupling backlash and avoid, with even greater reliability, any possible micro-telescoping of the material of the support bell 2 and the material of the braking band 3.

This protective layer can be made for example of powdered graphite or a resin loaded with powdered graphite. In this case, upon manufacture of the bell 2, due to the temperature of the alloy to which the protective layer is put in contact, the protective layer is carbonized and transformed, in turn, to powdered graphite that is easily removed by shaking or by localized jets of compressed gas. It is thus possible to ensure a backlash slightly greater in the coupling of each projection 4 to the corresponding housing 8.

After the cast of the bell has solidified, the opening step of the moulds provides the disc according to the invention.

Those skilled in the art will appreciate that a disc according to the invention being manufactured in accordance with the described method according to the invention, overcomes the problems complained in the prior art.

Particularly, when the disc 1 according to the invention is being used, despite the high temperature being reached by the braking band 3, is not subjected to any deformation besides the thermal expansion in its plane. In fact, due to the fact that each projection 4 is enabled to radially slide within its housing 8, the braking band 3 is free to be dilated in its plane independently from the support bell 2.

The slight backlash allowing the projections 4 to radially slide within the housings 8 can be defined for example during the first operating cycles. The poor surface roughness of the side faces 40 and walls 80 allows the projections 4 to slide along the housings 8 since the very beginning. The first sliding cycles determine the removal of any micro-relief and hence define the coupling backlash.

The embodiment of the disc 1 providing a substantial parallelism of the opposite side faces 40 of the projections 4 allows to obtain considerable advantages when the thermal expansion of the braking band 3 is the greatest. In fact, due to the parallelism of the faces 40, to any radial displacement of any projection 4, which is due to the thermal expansion of the braking band 3, there will not follow any increase in the coupling backlash of the projection 4 to the housing 8.

The embodiment of disc 1 providing a small angle 2α between the opposite side faces 40 allows to obtain further advantages whenever the thermal expansion of the projections 4 is non-negligible. In fact, because of the small angle 2α, the radial displacement of each projection 4 due to the thermal expansion of the braking band 3 enables each projection 4 to dilate, in turn, without any risk of seizing within the housing 8.

The embodiment of the disc 1 providing the chamfer 42 of the sharp edges of faces 40 to those ends radially proximate to the axis x-x allows to improve the comfort during the cooling step of the disc 1 at the end of each use session. In fact, due to the chamfer 42, during the slight radial displacement of each projection 4 towards the axis x-x, one obtains a clear noise reduction due to the fact that each projection 4 slides within its housing 8.

A similar effect is also obtained by biasing the faces 40 by a small angle α relative to the radial axis r-r passing through the center of the projection 4.

Particularly, it should be noted that the projections 4, being manufactured as one piece with the braking band 3, are capable of withstanding high tangential loads and thus transmitting a considerable braking torque. Particularly, the presence of the fillets 44 allows an optimum distribution of the stress from the projection to the braking band, and vice versa.

Analogously, the walls 80 of the housings 8, being manufactured as one piece with the support bell 2, are also capable of withstanding high tangential loads and thus transmitting a considerable braking torque.

In accordance with the preferred embodiments of the disc 1, the total braking torque is distributed over a congruous number of projections 4. The particular embodiment illustrated in the annexed drawings distributes for example the total torque over 12 projections. The number of projections is preferably greater than 6 and still more preferably greater than 10.

The particular geometry of the projections 4 and housings 8 being illustrated in the annexed drawings also allows to distribute the single braking torque quota proper of each projection over a wide contact surface of the side face 40 of projection 4 to the wall 80 of the housing 8. In this way, it is possible to dramatically reduce the stress peaks on the coupling of the side face 40 with the wall 80.

Obviously, those skilled in the art, aiming at satisfying contingent and specific requirements, will be able to carry out a number of modifications and variants to the disc for a disc brake according to the invention, all being however contemplated within the scope of protection of the invention such as defined in the following claims.

Accordingly, for example the step of surface finishing of the side faces 40 of the projections 4 can be brought to completion by other known methods, such as for example by dipping the workpiece in a vibrating tank containing abrasive elements.

Alternatively, the section of the protrusions 4 can vary from the rectangular one described above, being sufficient to vary also the section of the radial housings in a corresponding manner.

Claims

1. A disc for disc brake comprising a support bell defining a rotation axis x-x and having a plurality of radial housings, a braking band substantially coaxial with said rotation axis x-x, and a plurality of connecting elements suitable to connect the braking band to the support bell, wherein: said connecting elements overhang from said braking band in order to engage said corresponding radial housings; said connecting elements are integral and made as one piece with said braking band; and said connecting elements are housed in said radial housings and are at least partially surrounded by walls being integral and made as one piece with the support bell such as to be fastened in the axial direction and in the tangential direction, and such as to be free in the radial direction.

2. The disc according to claim 1 wherein said connecting elements comprise projections.

3. The disc according to a claim 1, wherein said connecting elements have a quadrangular section.

4. The disc according to claim 1, wherein said connecting elements comprise side faces.

5. The disc according to claim 4, wherein said side faces are parallel to each other.

6. The disc according to claim 4 wherein said side faces are biased to each other by an angle 2α.

7. The disc according to claim 6 wherein said angle 2α is comprised from 0° to 6°.

8. The disc according to claim 4 wherein said side faces comprise a chamfer.

9. The disc according to claim 4 wherein said side faces have an average surface roughness Raa less than 6.4×10−6 meters.

10. The disc according to claim 1 wherein between said braking band and said connecting elements there are arranged fillets.

11. The disc according to claim 1 wherein said connecting elements and said walls of said housings are intimately coupled and disjointed.

12. The disc according to claim 1 wherein the coupling of said connecting elements to said housings is a coupling with backlash.

13. A method for manufacturing a disc for disc brake comprising the steps of: manufacturing a braking band defining a rotation axis x-x; arranging on said braking band a plurality of connecting elements overhanging from said braking band, said connecting elements being integral and made as one piece with said braking band; manufacturing a support bell being substantially coaxial with said rotation axis x-x; arranging on said support bell a plurality of radial housings that are defined by walls being integral and made as one piece with said support bell, said housings being suitable to at least partially house said connecting elements such as to fasten them in the axial direction and in the tangential direction and such that they can slide in the radial direction.

14. The method according to claim 13, wherein said manufacturing step of said braking band comprises a casting step.

15. The method according to claim 14 wherein said casting step comprises a sand casting step.

16. The method according to claim 14 wherein said casting step comprises a chill casting step.

17. The method according to claim 13 wherein to said manufacturing step of said braking band there is followed a step of removing a stock.

18. The method according to claim 13 wherein said manufacturing step of said braking band comprises a step of arranging chamfers on said connecting elements.

19. The method according to claim 13 wherein said manufacturing step of said braking band comprises a step of surface finishing said connecting elements.

20. The method according to claim 19 wherein said step of surface finishing said connecting elements allows to obtain an average surface roughness Ra less than 6.4×10−6 meters.

21. The method according to claim 13 wherein to said manufacturing step of said braking band there follows a step of arranging a surface protective layer on said connecting elements.

22. The method according to claim 21 wherein said step of arranging a surface protective layer on said connecting elements comprises a step of arranging a protective layer containing graphite.

23. The method according to claim 13 wherein said manufacturing step of said support bell is subsequent to said manufacturing step of said braking band.

24. The method according to claim 19 wherein said manufacturing step of said support bell is subsequent to said step of surface finishing said connecting elements.

25. The method according to claim 13 wherein said manufacturing step of said support bell comprises a casting step.

26. The method according to claim 21 wherein to said manufacturing step of said support bell there follows a step of removing said surface protective layer.