Ventilated disc brake band

Abstract

"Ventilated type disc brake disc brake band" The present invention relates to a brake band (1) for a ventilated disc brake disc (2) that can avoid vibrations that induce annoying squealing during braking. The brake band (1) extends between an inner diameter (D1) near an axis of rotation (XX) of the brake band (1) and an outer diameter (D2) distal to the axis of rotation (XX). The axis of rotation defines an axial direction (XX). The brake band (1) defines a radial direction (RR) substantially perpendicular to the axial direction (XX) and a circumferential direction (CC) perpendicular to both the axial direction (XX) and the radial direction (RR). The brake band (1) includes two plates (3, 4) facing each other. The plates (3, 4) include inner surfaces (5, 6) that directly or indirectly face and define a gap (7). The plates (3, 4) are connected to each other by heat-dissipating and connecting elements (16, 17, 18, 19), also referred to as connecting elements. The connecting elements (16, 17, 18, 19) protrude from one plate toward the opposite plate, thereby forming a bridge connecting the plates (3, 4) to each other. At least one of the connecting elements is a fin (19) extending from near the inner diameter (D1) to near the outer diameter (D2). The fin (19) has a fin outer end (20) located near the outer diameter (D1). The fin outer end (20) of the fin (19) has an extension portion along the circumferential direction, i.e., an circumferential width (Lo). The fin (19) has a fin inner end (21) located near the inner diameter (D1). The fin inner end (21) of the fin (19) has a predetermined extension line along the inner circumferential direction, i.e., an inner circumferential direction. When considering a cross section taken along a cross section consisting of the radial direction (RR) and the circumferential direction (CC) created by passing through the mean air flow point through the gap, the circumferential width (Lo) is greater than the inner circumferential width (Li).

Description

[Technical Field]

[0001] The present invention relates to a brake band, a ventilated disc for disc brakes, and in particular to vehicles having said ventilated disc, although this application is not limited to the automotive sector. [Background technology]

[0002] In a disc brake, a brake caliper is generally arranged across the outer periphery of a brake disc configured to rotate about an axis of rotation (AA) that defines an axial direction (XX). The brake disc is defined by a radial direction (RR) that is substantially perpendicular to the axial direction (XX), a circumferential direction (CC) that is perpendicular to the axial direction (XX) and the radial direction (RR), and a local tangential direction (TT). The tangential direction (TT) is perpendicular to the axial direction (XX) and the radial direction (RR) at the intersection of the axial and radial directions.

[0003] As is known, a disc for a disc brake consists of a bell designed to connect the disc to the hub of the vehicle, from which extends an annular portion, called the brake band, intended to cooperate with the brake pads of the caliper. In the case of a ventilated disc, the brake band is made up of two plates facing each other and connected to each other by connecting elements, for example in the form of pins or fins. The outer surfaces of the two plates define the opposing braking surfaces, while the inner surfaces, together with the pins or fins, form air channels for cooling the disc. These air channels are traversed by an air flow following a centrifugal direction during the rotational movement of the disc itself.

[0004] The brake band is intended to cooperate with a disc brake caliper configured to apply braking force to the vehicle by applying friction to the opposing surfaces of two plates, termed braking surfaces, by means of the pads.

[0005] During braking, friction between the pads of the brake caliper and the braking surface of the brake band is known to generate a large amount of heat that requires disposal.

[0006] The heat generated can actually cause several undesirable phenomena, such as deformation of the brake band, the formation of cracks on the braking surface or local alteration of the state of the material forming the brake band, resulting in the deterioration of the brake band itself.

[0007] In particular, in applications to high performance automobiles with improved braking efficiency, there is a lot of energy to be disposed of, and the need for disposing of heat generated during braking becomes even more apparent.

[0008] Ventilated discs of the type mentioned above have undergone a continuous evolution over time, in particular with regard to the number and shape of the so-called ventilation grooves, thus defining the gap formed by the two axially facing plates.

[0009] Among the known ventilated disks, the so-called "pin disks" have been shown to be particularly efficient in terms of heat rejection performance (i.e. cooling), in which the ventilation channels are internally limited by specific post connecting elements, which can be defined as "pins" that connect two plates laterally and have equal radial and circumferential extensions that are limited or substantially slightly different relative to their axial extension.

[0010] For example, a breathable "pin disc" is known from EP 1 373 751 B1, in which the pins are geometrically arranged along three concentric circles coaxial with the disc and having different radii, forming three "ranks", the pins having different types of cross-section when cut in a plane parallel to the two plates (for example pins with a "diamond" cross-section in the middle and outer ranks, and "drop-shaped" pins in the outer ranks).

[0011] Other ventilated discs with a "pin" structure are known, for example, from WO2004 / 102028 and US Pat. No. 5,542,503.

[0012] Among ventilated discs, so-called "fin" or "wing" discs are known, in which the air passages are confined internally by specific connecting elements that are elongated along the direction of flow, for example oriented parallel to the radial direction (RR), or spiral connecting two plates laterally.

[0013] It is also known that the braking action exerted by the tapered pads against the braking surface of the disc generates heat, which in turn can raise the temperature of the disc to such an extent that the disc itself becomes incandescent, especially in demanding applications. Furthermore, the high temperature of the disc during braking can lead to deformation of the disc and poor contact between the pad and the braking surface. Furthermore, the friction material of the pad undergoes a kind of vitrification, which can lead to contamination by the disc material.

[0014] Furthermore, it has been found that higher temperatures reach the mid-annular portion of the braking surface, i.e., the mid-annular portion of the outer surface of each plate, an area that is prone to crack formation during the life of the disc.

[0015] In order to avoid the above-disclosed drawbacks, there is a particular need felt in this field, on the one hand, to increase the efficiency of dissipation of the heat generated by braking in order to limit the temperature reached by the disc during and after braking, and on the other hand, to increase the mechanical resistance of these intermediate portions of the braking band.

[0016] Solutions are disclosed in WO 2004 / 102028, as well as in WO 2002 / 064992, US 7,066,306, US 7,267,210, US 2006 0,243,546, US 2004 0,124,047, US 6,367,599, US 5,542,503 and US 4,865,167. Although satisfactory from various points of view, these known solutions fail to achieve a compromise between the desired mechanical resistance in the intermediate annular region of the brake band and the contrasting need to maximize the air flow in the same region, which would eliminate the significant local temperature rise caused by the braking action.

[0017] However, it is worth noting that the above-mentioned type of ventilated disc does not provide a solution to a further problem that may affect disc brakes, particularly disc brakes with ventilated discs, and which arises at the same time as the above-mentioned problem and which should be solved at the same time, as will be briefly explained below.

[0018] As is known, during braking, the disc and the brake band in particular may mechanically vibrate at different frequencies that correlate with different natural vibration modes of the disc itself. Such vibrations of the disc may result, for example, from resonances caused by vibrations of objects mechanically coupled to the disc to which forces are applied during braking, if the vibration frequency of such objects coincides with or is sufficiently close to the natural vibration frequency of the disc.

[0019] The aforementioned vibrations are also known to cause audible sounds, particularly in the form of harsh squeals, when the resonant frequency is in the audible range (for example between 2 and 9 kHz, followed by a more or less harsh squeal).

[0020] As a result, a need arises to devise a solution to reduce or eliminate such squeal by constructive means of "shifting" the vibration frequency of the disk to a value other than that which is excited.

[0021] Several solutions are known for disks with structures different from the "pin" structure described above.

[0022] For example, IT 1 273 754 discloses a brake band having protrusions projecting on the inside of the plates towards the gap between the two plates at specific positions and masses specifically identified to reduce the vibrations and subsequent noise that occur.

[0023] Another ventilated disc having a structure adapted to reduce annoying vibration phenomena is known, for example from US Pat. No. 4,523,666.

[0024] U.S. Patent No. 3,983,973 issued to Knorr-Bremse GmbH shows a brake disc including a pair of friction plates spaced apart to form an air passage. A braking force may be applied to the plates by the brake linings of the brake pads. The two plates are interconnected by a plurality of flow guide ribs or fins, defining an air passage between the friction plates. Radial grooves formed on the opposing surfaces of the friction plates contain strips of vibration-damping material. These inserts are made of metal elements that damp vibration and have a coefficient of expansion greater than that of the ferrous materials from which the friction plates are made, such as lead, bronze, or copper.

[0025] A similar solution is known from publication US2009035598.

[0026] It is known from US2012111692 to couple a passive damper of the scook type to a braking system in order to reduce vibrations.

[0027] Other solutions showing breathable braking bands connected by fins are known from WO2006067816, GB2076090 and US4867284.

[0028] From US6131707, WO2016020820, WO2017153902, WO2017153873, EP0318687, WO2011058594, WO2006105131, US2006219500, US6145636, US2010122880, US6325185, and US4523666. US5004078, Si23474, GB2060796, DE102013210700, EP3421833, WO2015092671, GB2286438, DE102004056645, EP2192321 publication, WO2008078352 publication, US3983973 publication, DE202006017092 publication, US20090000884 publication, From the solutions of DE202015102580, EP3084256, EP2507108, EP2276946, EP2145119, EP2100051, WO200792116, WO2004102028 and EP1433973 it is known to provide connections between the brake band plates which are unevenly distributed in the circumferential direction in order to reduce the natural vibrations excited by the braking action and to increase the ventilation of the gaps.

[0029] However, these distributions of the connecting elements of the plates create structural irregularities which, in certain braking situations, generate quite unwanted stresses concentrated in the brake band.

[0030] Therefore, a need has arisen for a new ventilated disc structure that simultaneously provides both particularly efficient cooling performance and characteristics that minimize vibration and noise during braking, while avoiding the generation of concentrated stresses in the brake band that could impair its integrity and duration.

[0031] The above-mentioned known examples of ventilated discs and respective braking bands are not able to fully meet all the highly desirable requirements mentioned.

[0032] The same applicant's patent application EP 2 715 179 B1 aims to partially solve these problems and in particular to reduce the natural frequencies of vibration modes of the braking band, including out-of-plane vibrations of the plates of the band itself. In particular, this solution comprises pins shaped to protrude into the gaps between the connecting elements.

[0033] This known solution, although satisfactory from many points of view, does not completely solve the problem, and in particular highlights the need to find a solution that makes it possible to easily create the shape of the surfaces that delimit the gaps between the brake bands.

[0034] Therefore, there remains a strong need to increase the mass near the outer edges of the brake band to reduce the out-of-plane type natural vibration modes of the brake band which, when excited, have a very adverse effect on braking performance.

[0035] In particular, a need is felt to devise a shape for the connecting elements of the brake band plates that makes it possible to reduce the amplitude of the most troublesome natural vibration modes of the brake band, in particular in terms of their specific frequencies.

[0036] The basic object of the present invention is therefore to provide a brake band and a disc for a brake band having structural and functional characteristics such that they meet the aforementioned requirements, while at the same time overcoming the drawbacks mentioned with reference to the prior art and satisfying the aforementioned felt needs. Summary of the Invention

[0037] It is an object of the present invention to provide a braking system that has a reduced tendency to produce these vibration waves and the resulting squeal.

[0038] This object and other objects and advantages are achieved by a brake band according to claim 1, a disc brake disc according to claim 10 and a vehicle according to claim 11.

[0039] Some advantageous embodiments are the subject of the dependent claims.

[0040] From the analysis of this solution, it became clear how the proposed solution makes it possible to achieve a much better braking comfort with respect to prior art solutions, and therefore a reduction in vibrations, and in particular the absence of vibrations that lead to squealing.

[0041] Furthermore, the proposed solution maintains, even in some embodiments, a very high and improved disc cooling efficiency, for example thanks to the increased airflow turbulence through the brake band gap, a turbulence determined by the particular shape of the fins associated with the forming pins present between the plates.

[0042] Furthermore, the proposed solution made it possible to increase the mass of the brake band and stiffen the radial part of the brake band, thereby breaking the circular symmetry of the distribution of the pins with fins extending over the entire radial height of the band, and increasing the mass especially near the radial outer edge of the brake band, reducing the out-of-plane type natural vibration modes of the brake band, which when excited have a very negative effect on the performance of the brake.

[0043] Furthermore, the proposed solution makes it possible to ensure a greater mass between the forming pins due to its radially outer part, especially the enlarged fins near the outer edge of the disc, thereby simplifying the manufacturing process.

[0044] Furthermore, the proposed solution makes it possible to avoid large annular areas of hollow gaps vacant from the connecting elements or shaped pins, and therefore to avoid poor temperature distribution on the brake band, which would cause disc vibrations or other unbalance phenomena.

[0045] Furthermore, the proposed solution allows for increased mass near the outer edge, avoiding blockage or excessive restriction of the air passages, while at the same time structurally strengthening the band to limit crack formation and propagation.

[0046] Furthermore, the proposed solution makes it possible to ensure increased resistance to thermal breakdown.

[0047] Furthermore, the proposed solution allows for the provision of shaped pins and elongated fins in the radially outer portion, further increasing the surface area available for heat exchange. [Brief explanation of the drawings]

[0048] Further features and advantages of the device, the brake disc and the vehicle will become apparent from the following description of preferred embodiments thereof, given as non-limiting examples, with reference to the accompanying drawings.

[0049] [Figure 1] FIG. 1 is a perspective, partially cut-away view of a disc brake disc having a brake band according to the present invention. [Figure 2] FIG. 2 is a cross-sectional view taken along the media plane of the fluid flow through the gap in the brake band in FIG. [Figure 3] 3 is an enlarged detail perspective view of the brake band portion of FIG. 2. FIG. [Figure 4] FIG. 4 is a partial cross-sectional perspective view of a disc brake disc having a brake band according to a further embodiment of the present invention. [Figure 5] FIG. 5 is a cross-sectional view taken along the media plane of the fluid flow through the gap in the brake band in FIG. [Figure 6] FIG. 6 is an enlarged detailed perspective view of the brake band portion of FIG. [Figure 7] FIG. 7 is a partial cross-sectional perspective view of a disc brake disc having a brake band according to a further embodiment of the present invention. [Figure 8]FIG. 8 is a cross-sectional view taken along the media plane of the fluid flow through the gap in the brake band in FIG. [Figure 9] 9 is an enlarged detailed perspective view of the brake band portion of FIG. 8. FIG. [Figure 10] FIG. 10 is a partial cross-sectional perspective view of a disc brake disc having a brake band according to a further embodiment of the present invention. [Figure 11] FIG. 11 is a cross-sectional view taken along the media plane of the fluid flow through the gap in the brake band in FIG. [Figure 12] 12 is an enlarged, detailed perspective view of the brake band portion of FIG. 11. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0050] According to a general embodiment, a disc braking band 1 for a ventilated disc brake 2 is provided.

[0051] The brake band 1 extends between an inner diameter D1 close to the axis of rotation XX of the brake band 1 and an outer diameter D2 remote from the axis of rotation XX, which axis of rotation defines an axial direction XX.

[0052] The brake band 1 defines a radial direction RR that is substantially perpendicular to the axial direction XX, and a circumferential direction CC that is perpendicular to both the axial direction XX and the radial direction RR.

[0053] The brake band 1 is composed of two plates 3 and 4 facing each other.

[0054] The plates 3, 4 face each other directly or indirectly and comprise inner surfaces 5, 6 defining a gap 7 which defines a ventilation conduit for the brake band 1.

[0055] The plates 3, 4 have outer surfaces 8, 9.

[0056] The outer surfaces 8, 9 are made up of opposing flat circumferential portions which define braking surfaces 10, 11. That is, a portion of the outer surfaces 8, 9 cooperates with a brake pad housed in a brake caliper to provide a braking action when clamped by the brake band 1, and the portion of the outer surfaces 8, 9 which is brushed by or related to the pad defines the braking surface 10, 11.

[0057] The plates 3, 4 are composed of plate bodies 12, 13 having thicknesses 14, 15 on the extension of the axial direction XX. That is, when observed in the axial direction, each plate 3, 4 exhibits a plate thickness 14, 15 given by the thickness of the plate body 12 of that plate 3, 4 in the axial direction.

[0058] The plates 3, 4 are joined together by heat dissipation or connecting elements 16, 17, 18 of the plates 3, 4.

[0059] The connecting elements 16, 17, 18 are formed as pillars and / or ribs projecting from one plate towards the opposite plate in the form of connecting bridges of the plates 3, 4.

[0060] Advantageously, at least one of said connecting elements is a fin 19 which is integral and extends from near said inner diameter D1 to near said outer diameter D2.

[0061] The fins 19 include outer fin ends 20 located near the outer diameter D1.

[0062] The outer fin end portions 20 of the fins 19 define a predetermined extension line along the outer circumferential direction, that is, a circumferential width Lo.

[0063] The fins 19 define inner fin ends 21 located near the inner diameter D1.

[0064] The fin inner end portion 21 of the fin 19 is formed by a predetermined extension line along the inner circumferential direction, that is, an inner circumferential width Li.

[0065] Advantageously, when considering a cross section taken along a cross section formed by a radial direction RR and a circumferential direction CC and passing through the center of gravity of the air flow passing through said gap, said outer circumferential width Lo is greater than said inner circumferential width Li.

[0066] According to an embodiment, the at least one fin 19 has a radially outer end 26. The outer radial end 26 forms a base surface 27. The base surface 27 constitutes a circumferential extension having a straight or arcuate extension parallel to the outer edge of the braking band 1, which defines the outer diameter D2.

[0067] According to an embodiment, the at least one fin 19 includes a shank portion 28 extending away from the inner diameter D1. The shank portion 28 is bounded by two opposite side surfaces 38, 39, at least one of the shank side surfaces 38, 39 being oriented substantially along the radial direction RR.

[0068] According to an embodiment, the at least one fin 19 comprises a shank portion 28 extending away from the inner diameter D1, the shank portion 28 being bounded by two opposite side surfaces 38, 39, both of which are oriented substantially along the radial direction RR.

[0069] According to an embodiment, the at least one fin 19 comprises a shank portion 28 extending away from the inner diameter D1. The shank portion 28 is defined by two opposing side surfaces 38, 39, at least one of the shank side surfaces 38, 39 including at least one shank linear stretch 40.

[0070] According to an embodiment, the at least one fin 19 comprises a shank portion 28 extending away from the inner diameter D1. The shank portion 28 is bounded by two opposite side surfaces 38, 39, both of which include opposite shank linear stretches 40, 41.

[0071] According to an embodiment, the at least one fin 19 includes a radially outer portion 29 located near the radially outer end 20 of the fin 19. The at least one fin 19 includes a shank portion 28 located near the inner radial end 21 of the fin 19.

[0072] According to the embodiment, in a cross section along a plane including the radial direction RR and the circumferential direction CC, which cross section passes through the center of gravity of the air flow passing through the gap, the cross-sectional end or outer periphery of the fin 19 is connected from the radial outer portion 29 to the shank portion 28.

[0073] According to an embodiment, the outer radial portion 29 tapers toward the inner diameter D1 passing near the outer diameter D2.

[0074] According to an embodiment, the shank portion 28 mainly projects in the radial direction RR and has a substantially constant width (i.e., circumferential length) over its entire length.

[0075] Advantageously, said radially outer portion 29 is tapered and connected to said shank portion 28 .

[0076] By providing a tapered radially outer portion connected to said shank portion, it is possible to significantly improve the permeability and therefore the cooling of the disc. In fact, the tapered radial portion directs the flow of cooling fluid through the disc, improving the cooling efficiency of the disc itself. At the same time, the connection to the shank portion allows the inclusion of fins that increase the stiffness and strengthen the entire radial extension of the permeable braking band of the disc, without discontinuities, thereby improving the structural and dynamic performance of the disc itself.

[0077] According to an embodiment, the outer radial portion 29 is defined by two opposite outer radial portion flanks 42, 43. The outer radial portion flanks 42, 43 are arcuate and connected to the shank portion 28.

[0078] According to an embodiment, said at least one fin 19 comprises a fin connector 22 connecting said fin 19 to said inner surfaces 5,6 of said plates 3,4.

[0079] According to an embodiment, the at least one fin 19 includes a radially outer portion 29 located near the radially outer end 20 of the fin 19. The at least one fin 19 includes a shank portion 28 located near the inner radial end 21 of the fin 19.

[0080] According to an embodiment, in a cross section including the radial direction RR and the circumferential direction CC and passing through the center of gravity of the air flow through the gap, the radially outer portion 29 has a substantially rectangular or elliptical shape that is elongated in the circumferential direction CC or the tangential direction TT.

[0081] According to an embodiment, the shank portion 28 defines a width in the circumferential direction CC that is substantially constant over the majority of its extension in the radial direction RR.

[0082] According to an embodiment, the shank portion 28 is connected to the outer radial portion 29 at a location substantially halfway along the circumferential or tangential length of the outer radial portion 29 .

[0083] According to an embodiment, the brake band 1 comprises at least one connecting element 16, 17, 18. The connecting element 16, 17, 18 connects the plates 3, 4 and has a radial length that is less than the height of the brake band (i.e. the radial distance between the inner diameter D1 and the outer diameter D2). The connecting elements are called pins 16, 17, 18.

[0084] According to an embodiment, at least one pin 17 is arranged directly opposite at least one fin 19 .

[0085] According to an embodiment, the braking band 1 comprises at least two pins 16, 17, 18. The at least two pins 17 are arranged directly opposite the at least one fin 19 from their opposite sides 36, 37.

[0086] According to an embodiment, the brake band 1 comprises at least one connecting element 16, 17, 18. The connecting element 16, 17, 18 connects the plates 3, 4 and has a radial length RR that is less than the height of the brake band (i.e. the radial distance between the inner diameter D1 and the outer diameter D2). The connecting elements 16, 17, 18 are called pins 16, 17, 18.

[0087] According to an embodiment, said at least one pin is a plurality of pins 16, 17, 18.

[0088] According to an embodiment, the plurality of pins 16 , 17 , 18 are arranged according to three ranks: outer ranks 23 , middle ranks 24 and inner ranks 25 .

[0089] According to the embodiment, the plurality of pins 16, 17, 18 are arranged according to three ranks: outer rank 23, middle rank 24, and inner rank 25, and at least one pin 17 of the middle rank 24 faces at least one side 37, 38 of the fin 19.

[0090] According to an embodiment, at least one pin 16 has a drop shape in a cross section defined by a radial direction RR and a circumferential direction CC, the cross section passing through the center of gravity of the airflow passing through the gap.

[0091] According to an embodiment, at least one pin 16 tapers towards said inner diameter D1.

[0092] According to an embodiment, at least one pin 17, 18 has a diamond-shaped cross section in a radial direction RR and a circumferential direction CC, which crosses the center of gravity of the air flow passing through said gap.

[0093] According to an embodiment, the plurality of pins 16 , 17 , 18 are arranged according to three ranks: outer ranks 23 , middle ranks 24 and inner ranks 25 .

[0094] According to an embodiment, said outer rank 23 consists of at least one drop-shaped pin 16 or only drop-shaped pins 16 .

[0095] According to the embodiment, said intermediate rank 24 consists of at least one diamond pin 17 or only diamond pins 17 .

[0096] According to the embodiment, said inner rank 25 is composed of at least one diamond pin 18 or only diamond pins 18 .

[0097] According to an embodiment, the plurality of pins 16, 17, 18 are arranged according to three ranks: outer rank 23, middle rank 24, and inner rank 25. All pins 16, 17, 18 are To be located at the four corners of a rectangle are placed.

[0098] According to an embodiment, the brake band 1 comprises a plurality of pins 19 .

[0099] According to an embodiment, the fins 19 are uniformly distributed in the circumferential direction along the gap 7 providing one fin 19 every 60°.

[0100] According to an embodiment, said fins 19 are six fins 19 distributed uniformly in the circumferential direction along said gap 7 .

[0101] According to an embodiment, the fins 19 are arranged in pairs in the gap 7 .

[0102] According to an embodiment, the fins 19 are arranged in the gap 7 in pairs of fins that are uniformly distributed circumferentially along the gap 7 .

[0103] According to an embodiment, the fins 19 are arranged in pairs in the gap, where at least one pin 17 is provided between the pair of fins 19.

[0104] According to an embodiment, the fins 19 are arranged in pairs in the gap, where at least one pin 17 is provided between the pair of fins 19, and the pairs of pins with at least one intermediate pin are uniformly distributed circumferentially along the gap 7.

[0105] The present invention further relates to a disc brake disc 2 comprising a brake band 1 defined by any one of the above-described embodiments and a bell 33 associated with said brake band 1 and configured for connection to a wheel hub of a vehicle.

[0106] The invention further relates to a vehicle equipped with a disc brake disc 2 as defined above.

[0107] Embodiments of the present invention are illustrated by the following non-limiting examples.

[0108] According to an embodiment, the brake band 1 has an outer diameter D2 of 380 mm, an inner diameter of 228 mm and a thickness of 34 mm.

[0109] The two plates 3, 4 are connected to each other by connecting elements 16, 17, 18 in the form of rows arranged in three rows or ranks 23, 24, 25, which are concentric, said connecting elements 16, 17, 18 being To be located at the four corners of a rectangle are placed.

[0110] Fins 19 extending the full height of the gap 7 are present every 60 DEG.

[0111] In the outer rank 24, the connecting elements have a predetermined shape on the center of gravity of the air flow through the drop-shaped gap 7, are oriented in the radial direction RR and extend tapered towards the axis of rotation XX.

[0112] In the intermediate rank 25 and the inner rank 23 the connecting elements 17, 18 have a predetermined shape in the plane of the mean flow through the diamond gap 7.

[0113] Each rank has 47 connecting elements, 16, 17 or 18.

[0114] The fin dimensions are L0 = 14.35 mm, L i = 4 mm, and the radial length is 69 mm.

[0115] Young's modulus 123,700 MPa, Poisson's ratio 0.250, density 7.205 kg / dm 3 A modal analysis was carried out in the frequency range 20-10,000 Hz for a material with a density of 1. The results are presented below, comparing the values ​​of interest with those given in the applicant's EP Patent No. 2 715 179.

[0116] TIFF0007778068000001.tif47157 [Explanation of symbols]

[0117] 1 Brake band area 2 disc brake disc 3 plates 4 plates 5 Inner surface 6 Inner surface 7. Gap 8 Outer surface 9 Outer surface 10 Braking surface 11 Braking surface 12 Plate-shaped body 13 Plate body 14 Plate Thickness 15 Plate Thickness 16 external pin connection elements or external ranks 17 Intermediate pin connecting element or intermediate rank 18 Inner pin connecting element or inner rank 19 Fin-type connecting element 20 outer end of fin 21 Inner end of fin 23 Outer Pin Rank 24 Intermediate Pin Rank 25 inner pin rank 26 outer radial end of fin 27 Bottom surface of outer diameter side end of fin 28 Fin shank 29 outer radial part of fin 33 Bell 35 Band outer periphery 36 Finside 37 Opposite fin side 38 Shank side 39 Opposite shank 40 Shank Stretch 41 Shank perpendicular stretch 42 Radial outer partial side 43 Radially outward opposite side AA brake band or brake disc rotating shaft XX Rotational or axial direction RR Radial direction CC tangent direction D1 Inner ring diameter D2 band outer diameter Lo fin outer periphery width Li fin inner circumference width

Claims

1. A disc brake band for a disc brake, the brake band extends between an inner diameter proximate the axis of rotation defining an axial direction of the brake band and an outer diameter distal to the axis of rotation; the brake band defines a radial direction perpendicular to the axial direction, a circumferential direction perpendicular to the axial direction and the radial direction, and a tangential direction locally perpendicular to the axial direction and the radial direction; The brake band includes two opposing plates; the plates have directly or indirectly opposed inner surfaces defining a gap; the plates are joined together by connecting elements; the connecting element protrudes from one of the plates toward the other of the plates and forms a bridge connecting the plates to one another; At least one of the connecting elements is at least one fin; the at least one fin is a single section extending from near the inner diameter to near the outer diameter; the at least one fin has a fin outer edge located near the outer diameter; the fin outer end portion of the at least one fin has an outer circumferential width of a predetermined length along an outer circumferential direction, the at least one fin has an inner fin end located near the inner diameter; the inner fin end portion of the at least one fin has an inner circumferential width of a predetermined length along an inner circumferential direction, In a cross section that includes the radial direction and the circumferential direction and crosses the gap, the outer circumferential width is larger than the inner circumferential width, the at least one fin has a shank portion extending away from the inner diameter; The shank portion is defined by two opposing shank side surfaces, At least one of the two shank sides is oriented along the radial direction; the at least one fin has an outer radial portion disposed near the outer fin end of the fin; the outer radial portion tapers radially inward and is connected to the shank portion; the connecting elements face both sides of the at least one fin; the opposing connecting elements have a diamond shape in the cross section that includes the radial direction and the circumferential direction and crosses the gap; The diamond-shaped connecting element has a radial length that is less than a radial length of the at least one fin.

2. the fin outer end defines a base surface; 2. The braking band of claim 1, wherein the base surface has a circumferential extension having a linear or arcuate extension parallel to an outer edge of the braking band that defines the outer diameter.

3. (a) the at least one fin includes a shank portion extending away from the inner diameter; The shank portion is defined by two opposing shank side surfaces, At least one of the two shank sides has at least one shank linear extension; or (b) the at least one fin includes a shank portion extending away from the inner diameter; The shank portion is defined by two opposing shank side surfaces, The braking band of claim 1 , wherein each of said two shank sides has a shank linear extension.

4. the at least one fin having the shank portion disposed near an inner radial end of the fin; On a cross section that includes the radial direction and the circumferential direction and through which the air flow passing through the gap passes, (a) a cross-sectional edge or cross-sectional perimeter of the at least one fin is connected to the shank portion; or (b) the outer radial portion tapers from the outer diameter toward the inner diameter; or (c) the shank portion has a predetermined width in the circumferential direction along the entire radial length; or (d) the outer radial portion is bounded by two opposing outer radial portion side surfaces, the outer radial portion side surfaces being arcuately connected to the shank portion; 2. The brake band of claim 1.

5. The braking band of claim 1 , wherein the at least one fin has a fin connector connecting the at least one fin to the inner surface of the plate.

6. the at least one fin including the shank portion located near an inner radial end of the at least one fin; On a cross section that includes the radial direction and the circumferential direction and through which the air flow passing through the gap passes, (a) the outer radial portion has a rectangular or elliptical shape that is elongated in the circumferential or tangential direction; and / or (b) the shank portion has a constant circumferential width along the entire radial length; and / or (c) A brake band (1) according to claim 1, wherein the shank portion is connected to the outer radial portion at a position halfway along the circumferential or tangential length of the outer radial portion.

7. the connecting element has a radial length that is less than the radial length between the inner diameter and the outer diameter; the connecting element is a pin; At least one pin is provided, or The braking band of claim 1 , wherein the braking band has at least two pins.

8. the connecting element has a radial length that is less than the radial length between the inner diameter and the outer diameter; The connecting element is at least one pin, the at least one pin is a plurality of pins, (a) the plurality of pins are arranged in three ranks consisting of an outer rank, a middle rank, and an inner rank; or (b) the plurality of pins are arranged in three ranks consisting of an outer rank, a middle rank, and an inner rank, and at least one pin in the middle rank faces at least one side surface of the fin; or (c) at least one pin among the plurality of pins has a drop shape on a cross section that includes the radial direction and the circumferential direction and through which the air flow passing through the gap passes; or (d) at least one pin among the plurality of pins is tapered radially inward; (e) the plurality of pins are arranged into three ranks consisting of an outer rank, a middle rank, and an inner rank; the outer rank includes at least one drop-shaped pin or only drop-shaped pins; the intermediate rank includes at least one diamond-shaped pin or diamond-shaped pins only; the inner rank includes at least one diamond-shaped pin or diamond-shaped pins only; or (f) the plurality of pins are arranged in three ranks consisting of an outer rank, a middle rank, and an inner rank, and all of the pins are arranged so as to be located at the four corners of a rectangle; 2. A brake band according to claim 1, characterized in that it is

9. the at least one fin comprises a plurality of fins; (a) the plurality of fins are uniformly arranged at 60-degree intervals in the circumferential direction along the gap; or (b) the plurality of fins are six fins uniformly distributed circumferentially along the gap; or (c) the plurality of fins are arranged in pairs within the gap; or (d) the plurality of fins are uniformly distributed in pairs circumferentially along the gap; or (e) the plurality of fins are arranged in pairs within the gap, and at least one pin is provided between the pair of fins; or (f) the plurality of fins are arranged in pairs within the gap; At least one pin is provided between the pair of fins; 2. The braking band of claim 1, wherein said pairs of fins interposed by at least one pin are uniformly distributed circumferentially along said gap.

10. A disc brake disc comprising a brake band according to claim 1 and a bell associated with said brake band and adapted to be connected to a wheel hub of a vehicle.

11. A vehicle comprising a disc brake disc according to claim 10.

12. 2. The braking band according to claim 1, wherein the connecting element directly faces both sides of the at least one fin without any structure between the connecting element and the at least one fin.

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