Multipart brake disc, friction disc ring part, securing element, and method for producing a brake disc

Abstract

The invention relates to a multipart brake disc (1), in particular a brake disc with a lightweight construction, comprising a brake disc ring part (2) and a receiving pot part (3), wherein the friction disc ring part (2) is rotationally fixed to the radial exterior of the receiving pot part (3), and the friction disc ring part (2) and the receiving pot part (3) are additionally operatively connected together by means of at least one elongated securing element (18), wherein the at least one elongated securing element (18) is arranged in a through-bore (14) of the receiving pot part (3) and in a borehole (10) of the friction ring part (2), the at least one elongated securing element (18) is inserted solely into the receiving pot part (3) and into the friction disc ring part (2), and the at least one elongated securing element (18) is fixed in the friction disc ring part (2) in a frictionally engaged manner.

Description

[0001] Multi-part brake disc, friction disc ring part, fastening element and method for producing a brake disc

[0002] The invention relates to a multi-part brake disc, in particular a lightweight brake disc, with a friction disc ring part and with a receiving pot part, in which the friction disc ring part is arranged radially outwardly on the receiving pot part in a rotationally fixed manner, in which the friction disc ring part and the receiving pot part are additionally operatively connected to one another by means of at least one elongate fastening element, wherein the at least one elongate fastening element is arranged in a through-bore of the receiving pot part and in a hole in the friction ring part.

[0003] The invention further relates to a friction disc ring part for a multi-part brake disc.

[0004] The invention also relates to a fastening element for a multi-part brake disc.

[0005] The invention also relates to a method for producing a brake disc from a plurality of functional parts, in which a friction disc ring part with an inner diameter is arranged on a radially outwardly arranged receiving surface with an outer diameter of a receiving pot part.

[0006] Generic multi-part brake discs are known from the prior art and can be used, for example, on vehicles, in particular motor vehicles, such as cars, trucks, or the like. The brake discs are each attached to the wheel hubs of the vehicle by means of a screw connection. Such brake discs are often designed in multiple parts, i.e., the brake discs each have a generally cup-shaped receiving part to which the actual friction disc of the brake disc is attached. The friction disc can interact with brake pads of the braking system as needed, while the cup-shaped receiving part is screwed to the wheel hub of the vehicle axle. The present invention is based on the object of providing an improvement or alternative to the prior art.

[0007] According to a first aspect of the invention, the stated object is achieved by a multi-part brake disc, in particular a lightweight brake disc, with a friction disc ring part and with a receiving cup part, in which the friction disc ring part is arranged radially on the outside on the receiving cup part in a rotationally fixed manner, in which the friction disc ring part and the receiving cup part are additionally operatively connected to one another by means of at least one elongate fastening element, wherein the at least one elongate fastening element is arranged in a through-bore of the receiving cup part and in a hole in the friction disc ring part, wherein the at least one elongate fastening element is arranged so as to be merely inserted into both the receiving cup part and the friction disc ring part, and wherein the at least one elongate fastening element is arranged in a frictionally locked manner in the friction disc ring part.

[0008] Because the fastening element is only inserted into the two functional components, an additional interaction between the functional components friction disc ring part and receiving pot part and the fastening element can be created in an extremely simple manner.

[0009] In particular, there is no need for complex threaded holes in the friction disc ring part and / or in the receiving pot part in order to hold the fastening element to the brake disc.

[0010] In this respect, multi-part brake discs can be manufactured significantly more cost-effectively using the present invention.

[0011] The following terminology is explained:

[0012] The invention relates to both solid and internally ventilated brake discs.

[0013] In this case, both multiple through-holes and multiple holes can be distributed along the circumferential direction of the brake disc and thus also along the circumferential direction of the friction disc ring part or the receiving cup part. For the purposes of the invention, the term "bore" refers to any type and shape of openings or holes that extend radially in the respective functional component.

[0014] In particular, the hole can extend as a blind hole or as a continuous hole in the friction disc ring part, for example as part of an internal ventilation of a friction disc ring part.

[0015] In this respect, the fastening element can be at least partially incorporated in a ventilation channel of the friction disc ring part, or can be arranged completely in the solid material of one friction disc half of two friction disc halves of the friction disc ring part.

[0016] In the context of the present patent application, “elongated” is to be understood as a pin which has a longitudinal extension, wherein the pin is longer along its longitudinal extension than it is in its transverse extension, in particular by more than 20%, especially more than 30% longer, wherein the transverse extension is preferably its diameter and / or wherein the longitudinal extension can preferably be understood as along a longitudinal axis, especially a rotational symmetry axis, of the fastening element.

[0017] While the friction disc ring part is preferably made of a cast material, the receiving pot part is preferably made of a sheet metal construction.

[0018] Like the hole, the through hole is preferably designed to be completely thread-free.

[0019] In particular, by means of the operative connection described here between the fastening part, the friction disc ring part, and the receiving cup part, an axial securing device on the multi-part brake disc can be realized, so that, for example, an unwanted axial displacement between the friction disc ring part and the receiving cup part along the axis of rotation of the multi-part brake disc can be excluded. The fastening element can be particularly well secured in the friction disc ring part if the at least one elongated fastening element is arranged in the friction disc ring part by means of a press-fit connection. A press-fit connection can be achieved by simply driving the fastening element through the through-bore of the receiving cup part into the hole in the friction disc ring part.

[0020] A further improved connection, in particular between the fastening element and the friction disc ring part, can be achieved if the at least one elongate fastening element is arranged in a form-fitting manner in the friction disc ring part.

[0021] In particular, by means of a positive connection, compressive forces can be reduced which act on the material of the friction disc ring part from the inside out due to the introduction of the fastening element into the friction disc ring part.

[0022] In this respect, it is advantageous if the at least one elongate fastening element is arranged in the friction disc part by means of a positive connection.

[0023] If the at least one elongate fastening element and the friction disc ring part are at least partially interlocked with each other, adverse internal pressure forces in the friction disc ring part can be avoided or at least reduced.

[0024] This can be achieved, in particular, if the fastening element interacts with the friction disc ring part primarily by means of suitable toothing. In other words, elevations provided on the outer surface of the fastening element primarily interact with the material of the friction disc ring part, whereby the forces acting on the material within the bore can be reduced, particularly compared to a fastening element that has a smooth outer surface. An advantageous embodiment can be provided if the at least one elongated fastening element has a surface structure, preferably a directional surface structure, at least partially on its outer surface.

[0025] By arranging a suitable surface structure on the outside of the fastening element, a positive connection acting in accordance with the invention between the fastening element and the friction disc ring part can be produced particularly advantageously.

[0026] A suitable surface structure can be designed in a variety of ways. The surface structure can be particularly simple if it includes grooves, ridges, or the like.

[0027] If the surface structure preferably extends in the longitudinal direction of the elongated fastening element, the fastening element can be inserted, for example, with less insertion forces, in particular into the friction disc ring part.

[0028] The surface structure can be formed completely or partially on the fastening element.

[0029] In any case, the surface structure, in particular grooves thereof, is preferably designed in such a way that when the friction disc ring part expands radially, the receiving pot part can preferably be moved along with it in the same order of magnitude.

[0030] If the at least one elongate fastening element is arranged pressed into the material of the friction disc ring part by means of at least one surface structure, a positive connection can be advantageously provided.

[0031] The fastening element can be designed differently in the sense of the invention, as already explained above.

[0032] Preferably, however, the fastening element is designed as a pin element that is fixedly arranged at least in the friction disc element, for example as a cylindrical pin, grooved pin, rivet pin, dowel pin, or the like. In this respect, it is advantageous if the at least one elongated fastening element is a pin element.

[0033] In particular, a longitudinally slotted pin element is advantageous since this allows an overload protection device to be formed on the fastening element.

[0034] In this respect, it makes sense if the fastening element is in the form of a dowel pin.

[0035] Furthermore, it is advantageous if the at least one elongated fastening element is a hollow pin element. Using a hollow pin element, additional ventilation, in particular additional internal ventilation, can be effectively achieved with respect to the friction disc ring part on the multi-part brake disc.

[0036] Of course, the fastener can also be made of solid material if this is advantageous for a specific application. However, a fastener made of solid material is significantly heavier, which would disadvantageously increase the rotating masses on a brake disc if the fastener were made of solid material.

[0037] If at least one elongated fastening element is a heavy-duty dowel pin (clamping bush), high shear forces can still be safely absorbed by the elongated fastening element.

[0038] This also makes it possible to achieve a solid pin character without having to accept the assembly disadvantages of a solid pin.

[0039] It has also been shown that the production of this multi-part brake disc can be further improved if the elongated fastening element has a toothed slot. By means of offset teeth along the toothed slot, additional axial tension can be achieved on the multi-part fastening element. Toothed slotted fastening elements are often also referred to as "Connex spring pins." Such a toothed slot can achieve a high seating strength with respect to both the receiving cup part and the friction disc ring part. Such a toothed slot is also frequently referred to as a shaft slot.

[0040] In addition, any resulting bore and center distance tolerances can be easily bridged if the elongated fastening element has a toothed slot, especially the heavy-duty spring pin.

[0041] In any case, the tooth slot also allows for better roundness, which means that the elongated fastening element with tooth slot can also be used as a precise axle element.

[0042] Ultimately, with a suitable design, this simplifies assembly and disassembly, although in this case disassembly should be seen more from the perspective of improved recycling.

[0043] In particular, this makes it possible to provide a precision dowel pin with particularly high positioning accuracy and seating strength.

[0044] It is particularly advantageous if a heavy-duty spring pin with toothed slot is used, taking into account DIN EN ISO 8752 (2009-10).

[0045] The elongate fastening element can be provided with sufficient strength if the elongate fastening element has an outer diameter of 4.5 mm or more, preferably 5.5 mm or more, and particularly preferably 6 mm or more in the unloaded state.

[0046] If the elongate fastener has an outer diameter of 9 mm or less, preferably 8 mm or less, and particularly preferably 6 mm or less, in the unloaded state, the mass or weight per fastener can be kept low.

[0047] It is advantageous if the elongate fastening element has a wall thickness of 0.8 mm or more, preferably 1 mm or more, and particularly preferably 1.2 mm or more, based on the total wall thickness of the elongate fastening element, in particular having a rolled body. This allows the elongate fastening element to be designed to be sufficiently strong.

[0048] If the elongated fastening element has a wall thickness of 2 mm or less, preferably of 1.6 mm or less and particularly preferably of 1.2 mm or less, the elongated fastening element can be installed on the multi-part brake disc in a weight-optimized manner.

[0049] Furthermore, it is advantageous if the elongated fastening element has a length of 5 mm or more, preferably 8 mm or more, and preferably 10 mm or more. Such a selected length of the fastening element can always ensure a sufficient penetration depth of the elongated fastening element into the body of the friction disc ring part, in particular, almost independent of the thickness of the receiving pot part.

[0050] If the elongate fastening element has a length of 18 mm or less, preferably 15 mm or less and preferably 12 mm or less, the elongate fastening element can be advantageously designed with regard to its mass or weight, while still being able to ensure a sufficiently large friction surface between the fastening element and in particular the friction disc ring part.

[0051] In particular, a length of 10 mm plus / minus 0.25 mm is particularly advantageous in order to always be able to ensure a good operative connection between the receiving pot part and the friction disc ring part by means of the elongated fastening element, while at the same time the elongated fastening element protrudes by at least 2 mm on the inside of the receiving pot part.

[0052] In order to be able to insert the elongate fastening element into the through-bore of the receiving pot part and subsequently also into the hole in the friction disc ring part without any problems, in particular with regard to an automated insertion process, it is advantageous if the elongate fastening element has a chamfer at each of its ends, in particular with a chamfer length of 1.30 mm plus / minus 0.1 mm and a chamfer width of 0.40 mm or less. Furthermore, it is advantageous if the at least one elongate fastening element has a mass of 2.2 g or less, preferably 1.8 g or less and particularly preferably 1.2 g or less, since this can advantageously influence the overall mass of the multi-part brake disc.

[0053] A still sufficient strength can be achieved if the at least one elongate fastening element has a mass of 0.4 g or more, preferably 0.6 g or more and particularly preferably 0.8 g or more.

[0054] It has been found that a mass of 1 g can be achieved particularly advantageously in terms of a very favorable weight (less rotating and oscillating masses) and still very good strength.

[0055] In particular, it is advantageous if the mass of a single elongated fastening element is dependent on the number of fastening elements. For example, the mass of each individual fastening element can be selected to be lower the higher the number of fastening elements installed on the multi-part brake disc.

[0056] Preferably, the number of fastening elements on the multi-part brake disc is 18 pieces or less, preferably 15 pieces or less and particularly preferably 13 pieces or less, and / or 8 pieces or more, preferably 10 pieces or more and particularly preferably 12 pieces or more.

[0057] The fewer such fastening elements there are on the multi-piece brake disc, the less mass or weight they add to the multi-piece brake disc. At the same time, the fewer elongated fastening elements also reduce the number of positive connection points between the mounting cup and the friction disc ring.

[0058] However, the more fasteners there are, the more mass or weight these elongated fasteners impose on the multi-part brake disc, resulting in a total mass to be accelerated on a vehicle, especially on the vehicle's wheel suspension. It has been found that a number of 13 elongated fasteners is particularly advantageous for an outer diameter of the friction disc ring part of approximately 323 mm, especially when the outer diameter of the receiving cup part is approximately 165 mm.

[0059] Furthermore, the fastening element can be made of different materials.

[0060] The fastening element can be provided on the multi-part brake disc in a particularly cost-effective manner if the at least one elongate fastening element has a base body made of steel, in particular of a spring steel, such as a tempered spring strip steel 55Si7 or the like, which also has particularly good strength.

[0061] The fastening element can be very easily inserted through the through-bore of the receiving pot part and into the hole of the annular disc element if the at least one elongated fastening element has a cylindrical base body.

[0062] It is understood that the fastening element may also have other basic shapes, such as oval, rectangular or the like, if this should be advantageous for a particular application.

[0063] The insertion depth of the fastening element into the annular disc element can advantageously be limited if the at least one elongated fastening element has a head region and a shaft region. The head region advantageously allows the fastening element to be supported on the inside of the receiving cup part.

[0064] In order to be able to additionally ventilate, i.e., cool, the friction disc ring part, especially in the area of ​​the fastening element, it is advantageous if the at least one elongated fastening element has a ventilation opening for ventilating the friction disc ring part. This makes it possible to additionally carry heat out of the interior of the friction disc ring part through the fastening element or to additionally carry air into the interior of the friction disc ring part.

[0065] A further advantageous embodiment provides that the at least one elongate fastening element and / or the receiving pot part have a surface coating, in particular a corrosion coating.

[0066] A suitable surface coating can provide protection against contact corrosion, for example, which generally provides improved protection for the multi-part brake disc during continuous operation.

[0067] In this case, a suitable surface coating can be applied only partially or entirely to the fastening element or the receiving pot part. A partially applied surface coating can further reduce manufacturing costs.

[0068] Another advantageous embodiment variant can be provided with regard to a loss prevention device, by means of which the friction disc ring part and the receiving pot part are secured to one another, in particular axially secured, wherein the loss prevention device has at least one friction and / or positive connection comprising at least one elongate fastening element.

[0069] As already mentioned above, this can additionally prevent unwanted axial displacement of the friction disc ring part and the receiving pot part.

[0070] It is also advantageous if the anti-loss device has a hardness gradient that slopes downwards from the at least one elongated fastening element to the friction disc ring part. This allows the harder fastening element to advantageously penetrate and be secured in the softer material of the friction disc ring part.

[0071] Joining the functional components friction disc ring part and receiving pot part can be carried out more advantageously if the receiving pot part has a cylindrical receiving area with a radially outwardly arranged cylindrical receiving surface for receiving the inside of the ring part.

[0072] Preferably, this creates a circular receiving seat for the friction disc ring part on the receiving pot part.

[0073] A further expedient embodiment can be created if the receiving pot part has a cylindrical receiving area with an outer diameter Da and the friction disc ring part has an inner diameter Di, wherein the ratio D a / Dj is 1 .01 or greater, preferably 1 .02 or greater.

[0074] In this context, it is advantageous if the receiving pot part has a cylindrical receiving area with an outer diameter D aand the friction disc ring part have an inner diameter Di, wherein the ratio D a / Di is 1 ,06 or less, preferably 1 ,05 or less.

[0075] A diameter ratio D is preferred a / Di between 1 ,02 and 1 ,04 is targeted.

[0076] Due to the diameter ratios D given above a / Di a particularly robust operative connection between the friction disc ring part and the receiving pot part can be realized.

[0077] The ratio D a / The relevant dimensions refer to the largest inner diameter of the friction disc ring part and the largest outer diameter of the receiving cup part. Tolerances regarding roundness deviations should be disregarded.

[0078] In addition to the advantage of a particularly robust operative connection between the friction disc ring part and the receiving pot part, it has been shown that it is no less advantageous, if not even more advantageous, if the diameter ratio D a / Dj is chosen to be significantly smaller than indicated above.

[0079] In particular, this can significantly improve the assembly capability without critically neglecting the operative connection between the friction disc ring part and the receiving cup part with regard to the manufacture of the present multi-part brake disc, in particular with regard to a still good torsional security of the functional components of the multi-part brake disc when they are joined together and in particular when the through hole and the hole are made in the relevant functional components of the multi-part brake disc.

[0080] In this respect, a preferred embodiment provides that the receiving pot part has a cylindrical receiving area with an outer diameter D a and the friction disc ring part has an inner diameter Di, wherein the ratio Da / Dj is 1.00088 or greater, preferably 1.00089 or greater, and particularly preferably 1.0009 or greater.

[0081] The conditions chosen here allow for particularly good assembly of the friction disc ring part and the receiving pot part while still maintaining good resistance to rotation.

[0082] The anti-twist security during assembly can be advantageously improved if the receiving pot part has a cylindrical receiving area with an outer diameter Da and the friction disc ring part has an inner diameter Di, whereby the ratio D a / Dj is 1 .001 or smaller, preferably 1 .000999 or smaller, and particularly preferably 1 .00091 or smaller. This ensures a very tight connection between the friction disc ring part and the receiving pot part.

[0083] Furthermore, it is advantageous if the receiving pot part has a cylindrical receiving area with an outer diameter D a and the friction disc ring part have an inner diameter Di, wherein the ratio D a / Dj is 1.00027 or less, preferably 1.00025 or less, and particularly preferably 1.00022 or less. This ensures a very tight connection between the friction disc ring part and the receiving cup part.

[0084] If the receiving pot part has a cylindrical receiving area with an outer diameter Da and the friction disc ring part has an inner diameter Di, the ratio D a / Dj is 1 ,00019 or greater, preferably 1 ,0002 or greater and particularly preferably 1 ,00021 or greater, sufficient resistance to rotation during assembly can still be ensured with good assembly properties.

[0085] Good assembly can still be guaranteed, especially if the ratio D a / Dj 1 ,000909, wherein this ratio is based on a preferably largest outer diameter of 165.15 mm with regard to the receiving pot part and a preferably smallest inner diameter of 165 mm with regard to the friction disc ring part.

[0086] A still very good frictional connection and thus a good torsion resistance of the friction disc ring part and the receiving pot part during assembly can be achieved if the ratio D a / Dj is 0.999, wherein this ratio is based on a preferably smallest outer diameter of 165.05 mm with regard to the receiving pot part and a preferably largest inner diameter of 165.063 mm with regard to the friction disc ring part.

[0087] Advantageous press connections between the friction disc ring part and the receiving pot part can be provided if the friction disc ring part has an inner diameter Di of 164.9 mm or larger, preferably of 165 mm or larger and particularly preferably of 165.05 mm or larger.

[0088] Likewise, advantageous press connections can be provided between the friction disc ring part and the receiving pot part if the friction disc ring part has an inner diameter Di of 166 mm or smaller, preferably of 165.063 mm or smaller and particularly preferably of 165 mm or smaller.

[0089] A suitable counterpart for the advantageous press connections can be provided if the receiving pot part has an outer diameter Di of 164.95 mm or larger, preferably of 165 mm or larger and particularly preferably of 165.05 mm or larger.

[0090] The selection of suitable press connections can be advantageously expanded if the receiving pot part has an outer diameter Di of 165.5 mm or smaller, preferably of 165.15 mm or smaller, and particularly preferably of 165 mm or smaller. As already described above, the operative connection between the fastening element and the friction disc ring part can be achieved particularly easily if the hole in the friction disc ring part is thread-free.

[0091] Furthermore, it is expedient if the hole drilled in the friction disc ring part has two different hole diameter ranges, whereby the hole drill receives two different functional areas and can accordingly also assume two functions.

[0092] In this context, it is particularly useful if a larger hole diameter range of the bore is positioned radially further inward than a smaller hole diameter range. This allows the fastening element to be easily positioned into the radially outer hole diameter range.

[0093] In this respect, a preferred embodiment also provides that the at least one elongate fastening element is fastened to the friction disc ring part in the smaller hole diameter region arranged radially further outwards.

[0094] If, on the one hand, at least one elongate fastening element is arranged in the larger hole diameter area arranged radially further inwards and, on the other hand, material of the receiving pot part can be introduced, the hole arranged in the friction disc ring part can structurally easily assume several different functions.

[0095] Furthermore, it is advantageous if an edge region of the through-bore of the receiving pot part can be displaced into the larger hole diameter region arranged radially further inwards.

[0096] This allows, among other things, the hole in the friction disc ring part to serve an additional function in addition to securing the fastening element, namely that of a receiving space, escape space, or insertion space for material areas, material residues, or the like of the receiving cup part. Accordingly, it is advantageous if the hole has an insertion space for inserting material from the receiving cup part.

[0097] Advantageously, the insertion space has a hole diameter which is larger than the outer diameter of the at least one fastening element which is arranged in the insertion space.

[0098] This leaves enough space in the insertion space between the outer surface of the fastening element and the inner wall of the hole for material to be introduced from the receiving pot part.

[0099] It is also particularly advantageous if the friction disc ring part has crack prevention holes which are arranged radially further outwards at the respective end of the hole bores.

[0100] By means of such a crack prevention hole, any crack formation originating from a hole drilling can be stopped so that a corresponding crack cannot spread further in the material of the friction disc ring part.

[0101] Preferably, the crack prevention holes run transversely to the hole drillings.

[0102] In order to ensure that the at least one elongated fastening element fits well and reliably within the bores, it is advantageous if the through-bore of the receiving pot part and the hole of the friction disc ring part each have a hole diameter L-Dj and the at least one elongated fastening element has a pin diameter SD a where the ratio SDa / L-Dj is 1.0551 or greater, preferably 1.0593 or greater, and more preferably 1.0612 or greater.

[0103] An introduction of the at least one elongated fastening element into the respective bore can advantageously be carried out if the ratio SD a / L-Di is 1 .0751 or less, preferably 1 .0712 or less, and particularly preferably 1 .0631 or less. Here, the ratio SD a / L-Dj refer to both bores and the respective at least one elongate fastening element, or at least only one of the two bores and the respective at least one elongate fastening element.

[0104] Such a ratio SD a / L-Dj can be designed particularly well if at least one elongated fastening element has a pin diameter SD aof 6.4 mm, with one or both holes having a hole diameter L-Dj of 6 mm. Here, the ratio SD a / L-Di a value of exactly 1 .06667.

[0105] If tolerances are taken into account, for example with regard to the smallest possible pin diameter SD a in combination with a largest possible hole diameter L-Dj, it is advantageous if the through hole of the receiving pot part and the hole of the friction disc ring part each have a hole diameter L- Dj and the at least one elongated fastening element has a pin diameter SD a where the ratio SD a / L-Di is 1 .0345 or greater, preferably 1 .0391 or greater and particularly preferably 1 .0419 or greater, and / or wherein the ratio SD a / L-Di is 1.0651 or less, preferably 1.0574 or less, and particularly preferably 1.0461 or less.

[0106] It has been found that a ratio SD a / L-Di of exactly 1 .04575 is particularly advantageous. Such a ratio SD a / L-Di can be replaced, for example, by a pin diameter SD a of 6.4 mm and a hole diameter L-Dj of 6.12 mm.

[0107] If the tolerances run in exactly the other direction, namely with a largest possible pin diameter SD a of approximately 6.7 mm in combination with a smallest possible hole diameter L-Dj, approximately 6 mm, it is advantageous if the through hole of the receiving pot part and the hole of the friction disc ring part each have a hole diameter L-Dj and the at least one elongated fastening element has a pin diameter SD a where the ratio SD a / L-Dj is 1 ,0111 or greater, preferably 1 , 1011 or greater and particularly preferably 1 , 1143 or greater, and / or wherein the ratio SD a / L-Dj is 1,1199 or less, preferably 1,1187 or less, and particularly preferably 1,1177 or less.

[0108] For the relevant hole or pin dimensions, a ratio SD a / L-Dj of exactly 1 .11667 proved to be particularly suitable.

[0109] The object of the invention is achieved according to a second aspect by a friction disc ring part for a multi-part brake disc with at least one thread-free hole, which extends radially outwards from the inner side of the ring part and which has different hole diameters.

[0110] As a result, a fastening element holding bore can be created in the friction disc ring part, which, in addition to holding the fastening element, can also fulfil at least one further function, as has already been described in detail above.

[0111] In order to achieve a comprehensive operative connection or securing in the sense of the invention, it is advantageous if a plurality of holes are arranged in the circumferential direction of the inner side of the ring.

[0112] According to a third aspect of the invention, the object is achieved by a fastening element for a multi-part brake disc with an elongated base body, wherein the fastening element has at least one surface structure by means of which the base body can penetrate at least partially into the material of the friction disc ring part.

[0113] By means of this surface structure, a particularly close operative connection can be created between the fastening element and the friction disc ring part.

[0114] The insertion depth of the fastening element, which is preferably designed as a pin element, can be reliably limited if the elongated base body has a head region and a shaft region, wherein the head region and the shaft region have different outer diameters, in particular the head region has a larger outer diameter than the shaft region. According to a fourth aspect of the invention, the object is achieved by a method for producing a brake disc from several functional parts, in which a friction disc ring part with an inner diameter is fastened to a radially outer receiving surface with an outer diameter D a a receiving pot part, in which the inner diameter Di and the outer diameter D a with a ratio D a / Di of 1 ,00088 or greater or with a ratio D a / Di of 1.00027 or smaller is selected before the friction disc ring part is arranged on the receiving surface, in which after the friction disc ring part has been arranged on the receiving surface, a through-bore and a hole are each made in the friction disc ring part and in the receiving pot part with a single drilling process, and in which in each case an elongate fastening element is introduced from radially further inside through the respective through-bore into the respective corresponding hole, wherein the elongate fastening element is fastened in the hole of the friction disc ring part at least partially in a frictionally engaged and / or positively engaged manner.

[0115] By means of such a method, the friction disc ring part and the receiving pot part can advantageously be permanently connected to one another.

[0116] Furthermore, a method for producing a brake disc from a plurality of functional parts is also advantageous, in which a friction disc ring part is arranged on a radially outwardly arranged receiving surface of a receiving pot part in such a way that through holes arranged on the receiving surface and holes arranged in the friction disc ring part are brought into alignment, and in which an elongate fastening element is introduced from radially further inward through the respective through hole and into the respective corresponding hole, wherein the elongate fastening element is fastened in the hole of the friction disc ring part at least partially in a frictionally engaged and / or positively engaged manner.

[0117] Using the manufacturing method described here, a multi-part brake disc can be manufactured particularly easily. In particular, the fastening element can be secured particularly easily using a frictional connection, in particular a press-fit connection, or a form-fit connection.

[0118] The present manufacturing process can be further simplified if the elongated fastening element is driven into the hole.

[0119] By driving the fastening element in this way, in particular into the friction disc ring part, there is no longer any need to screw in a fastening screw, as was previously the case.

[0120] The term “hammering in” in the sense of the invention includes any method by which the fastening element can be introduced, in particular, into the friction disc ring part, for example by pressing it, pressing it, or the like, into the hole, in particular discontinuously or continuously.

[0121] The fastening element can, for example, also be secured in the hole of the friction disc ring part in a particularly reliable manner, bypassing a threaded connection, if the elongated fastening element is secured in the hole by means of a grooved, in particular longitudinally grooved, lateral surface section of the fastening element.

[0122] In this respect, it is advantageous with regard to a method variant if the elongated fastening element penetrates into the material of the friction disc ring part outside the hole when the elongated fastening element is introduced into the hole.

[0123] In this case, the fastening element can actually cut into the material of the friction disc ring part beyond the inner wall of the hole in order to ensure an even more secure fit of the fastening element.

[0124] If the elongated fastening element is inserted into the bore with insertion forces of 4 kN or more, preferably 6 kN or more, and particularly preferably 8 kN, a secure fit between the fastening element and, in particular, the friction disc ring part can always be ensured. The fastening element can be inserted with a reasonable amount of force if the elongated fastening element is inserted into the bore with insertion forces of 12 kN or less, preferably 10 kN or less, and particularly preferably 8 kN.

[0125] According to a fifth aspect of the invention, the stated object is achieved by using a pin element, in particular an at least partially longitudinally grooved pin element, for securing a friction disc ring part of a multi-part brake disc to a receiving pot part of the multi-part brake disc.

[0126] Using such a pin element, the production of a multi-part brake disc can be significantly simplified.

[0127] The following terminology should also be explained:

[0128] It should be expressly pointed out that, in the context of this patent application, indefinite articles and indefinite numerical expressions such as "one...", "two...", etc. are generally to be understood as "at least one...", "at least two...", etc., unless the context or the specific text of a particular passage indicates that only "exactly one...", "exactly two...", etc. are intended. Furthermore, all numerical expressions and information on process parameters and / or device parameters are to be understood in the technical sense, i.e., subject to the usual tolerances. Even the explicit specification of the restriction "at least" or "at least" or similar does not imply that the simple use of "one", i.e., without the specification of "at least" or similar, means "exactly one."

[0129] The invention will be explained in more detail below using exemplary embodiments with reference to the drawings, which show

[0130] Fig. 1 shows schematically a sectional partial view of a possible embodiment of a multi-part brake disc with a receiving pot part and with a friction disc ring part, into which an elongated fastening element is inserted in order to additionally secure an operative connection between the receiving pot part and the friction disc ring part;

[0131] Fig. 2 shows schematically a sectional partial view of the receiving pot part of the multi-part brake disc from Figure 1;

[0132] Fig. 3 shows schematically a sectional partial view of the friction disc ring part of the multi-part brake disc from Figure 1;

[0133] Fig. 4 shows a schematic sectional view of an operative connection of the elongated fastening element to the multi-part brake disc from Figure 1;

[0134] Fig. 5 shows a schematic view of the elongated fastening element on the multi-part brake disc from Figure 1;

[0135] Fig. 6 shows a schematic view of a further receiving pot part of an alternative multi-part brake disc;

[0136] Fig. 7 shows schematically a sectional view of the further receiving pot part shown in Fig. 6 along the section line AA;

[0137] Fig. 8 shows a schematic view of another friction disc ring part of the alternative multi-part brake disc;

[0138] Fig. 9 shows a schematic sectional view of the further friction disc ring part shown in Fig. 8 along the section line FF with the further receiving pot part from Figs. 6 and 7 indicated to the right with the direction of assembly;

[0139] Fig. 10 shows schematically a side view of an elongated fastening element having a tooth slot;

[0140] Fig. 1 1 schematically shows a front view of the fastening element shown in Figure 10;

[0141] Fig. 12 schematically shows a partially sectioned assembly view of the alternative multi-part brake disc; Fig. 13 schematically shows a sectional view along section line AA of the alternative multi-part brake disc shown in Figure 12;

[0142] Fig. 14 shows schematically a sectional detailed view along the section line BB of the alternative multi-part brake disc shown in Figure 12;

[0143] Fig. 15 schematically shows a further sectional detail view along the section line CC of the alternative multi-part brake disc shown in Figure 12; and

[0144] Fig. 16 schematically shows a sectional view of another friction disc ring part with a more concave receiving area for receiving, for example, the further receiving pot part from Figures 6 and 7.

[0145] The multi-part brake disc 1 shown in Figure 1 essentially consists of a friction disc ring part 2 and a receiving cup part 3, wherein the friction disc ring part 2 is arranged on a cylindrical receiving surface 5 of the receiving cup part 3. The cylindrical receiving surface 5 is located on a cylindrical receiving area 6 of the receiving cup part 3.

[0146] The multi-part brake disc has a rotation axis 8.

[0147] While the friction disc ring part 2 has a plurality of holes 10 which are evenly distributed in the circumferential direction 12 of the multi-part brake disc 1, the receiving pot part 3 has corresponding through holes 14 which overlap with each other when the friction disc ring part 2 and the receiving pot part 3 are properly assembled.

[0148] The holes 10 extend in the friction disc ring part 2 from an inner side 13 of the ring part in radial directions 16 (shown only as an example) from radially further inside to radially further outside.

[0149] In other words, both the holes 10 and the through holes 14 run transversely to the axis of rotation 8 of the multi-part brake disc 1. An elongate fastening element 18 is arranged in each hole 10 and in each through hole 14, wherein each elongate fastening element 18 is driven from radially further inward to radially further outward, in particular into the respective hole 10, namely through the associated through hole 14.

[0150] The elongated fastening element 18 is frictionally fixed at least to the friction disc ring part 2.

[0151] In this respect, a good frictional connection (not explicitly numbered), preferably as a press-fit connection (also not further numbered), is produced between the elongate fastening element 18 and the friction disc ring part 2 by simply driving the elongate fastening element 18 into the hole 10.

[0152] In particular, the multi-part brake disc 1 has, due to the existing frictional connection, a favorable loss prevention device 20, by means of which the friction disc ring part 2 and the receiving pot part 3 are held secured to one another, in particular axially secured to one another.

[0153] Preferably, the elongate fastening element 18 is optionally also operatively connected to the friction disc ring part 2 by means of a positive connection (not further numbered) in that the elongate fastening element 18 is at least partially toothed with the friction disc ring part 2 within the hole 10.

[0154] Further details, particularly with regard to the friction disc ring part 2, the receiving pot part 3 and the elongated fastening element 18, are additionally shown in Figures 2 to 5.

[0155] According to the illustration in Figure 2, the through-bore 14 in the receiving pot part 3 is shown in more detail, wherein the through-bore 14 has an edge region 22 facing the friction disc ring part 2.

[0156] In this embodiment, the receiving pot part 3 has an outer diameter 22 with a value D on its cylindrical receiving area 6 a . According to the illustration in Figure 3, the area of ​​the hole 10 in the friction disc ring part 2 is shown in more detail, wherein it is clearly visible that the hole 10 has different hole diameters 26 and 27, so that the hole 10 also has two different hole diameter areas 28 and 29.

[0157] As can be clearly seen in particular from the illustration in Figure 4, the elongated fastening element 18 is fastened to the friction disc ring part 2 in the smaller hole diameter region 29 arranged radially further outwards.

[0158] The larger hole diameter area 28 also provides an insertion space 30 at the hole 10, into which material areas of the receiving pot part 3 can escape if necessary, if this should be necessary for assembly reasons, in particular when driving the elongated fastening element 18 through the through hole 14.

[0159] In this embodiment, the friction disc ring part 2 has an inner diameter 32 with a value Di on its ring part inner side 13.

[0160] In this embodiment, the mounting diameter ratio Da / Dj is preferably 1.03.

[0161] As shown by way of example in the illustration according to Figure 4, a crack prevention hole 36 is arranged on the friction disc ring part 2 at the end 34 of each hole 10.

[0162] The crack prevention holes 36 are not shown separately in the illustration in Figure 1, but only as an example in Figure 4.

[0163] According to the illustration in Figure 5, the elongated fastening element 18 is shown in more detail.

[0164] In this exemplary embodiment, the elongated fastening element 18 is constructed as a pin element 38, wherein the pin element 38 is designed as a hollow pin element (not separately numbered again), whereby advantageous ventilation ratios of > 80% can be achieved at the center of the friction disc ring part 2. Therefore, the elongated fastening element 18 has a ventilation opening 40 (not shown here) for ventilating the friction disc ring part 2, which is arranged through the entire elongated fastening element 18.

[0165] The elongated fastening element 18 has a cylindrical base body 42 so that it can be easily inserted into the likewise cylindrical bores 10 and 14.

[0166] Furthermore, the elongated fastening element 18 has a head region 44 and a shaft region 45.

[0167] The elongated fastening element 18 has an outer diameter 46 in the region of the shaft region 45, which is smaller than the larger hole diameter 26 of the hole 10 and smaller than the outer diameter 48 at the head region 44.

[0168] In any case, the elongate fastening element 18 has a longitudinal extension 50, and the elongate fastening element 18 has on its lateral surface 52 a lateral surface section 54 with a surface structure 56.

[0169] In this embodiment, the shaft region 45 has a directional surface structure 56.

[0170] The surface structure 56 thus has, in the longitudinal extension 50 of the elongated fastening element 18, a plurality of grooves 58 which are arranged over the entire circumference of the lateral surface 52, at least in the shaft region 45.

[0171] The grooves 58 create a toothing on the lateral surface 52.

[0172] According to the illustrations in Figures 6 and 7, a further embodiment of a further receiving pot part 103 of an alternative multi-part brake disc 100 (see Figures 12 to 15) is shown before assembly with the associated further friction disc ring part 102 (see also Figures 8 and 9).

[0173] The additional receiving cup part 103 therefore does not yet have any through holes 114 (see Figure 12, numbered only as an example). The additional receiving cup part 103 consists of a sheet metal construction and thus has a sheet metal body 103A with a central axis 103B, wherein the central axis 103B coincides with the rotational axis 108 of the alternative multi-part brake disc 100. The sheet metal body 103A has a standard sheet metal wall thickness 103C of 2.5 mm.

[0174] Furthermore, the further receiving pot part 103 is characterized by a bottom region 103D and a collar region 103E, wherein the collar region 103E forms the cylindrical receiving surface 105 on which a friction disc ring part 102 of the alternative multi-part brake disc 100 is arranged.

[0175] The cylindrical receiving surface 105 is located on a cylindrical receiving area 106 of the receiving pot part 103.

[0176] The further receiving pot part 103 has five mounting holes 160, which serve for mounting the entire alternative multi-part brake disc 100 on a wheel hub of a motor vehicle (not shown here).

[0177] The mounting holes 160 each have a diameter 160A of 15 mm.

[0178] The mounting holes 160 are located on a bolt circle 161 with a bolt circle diameter 161 A of 112 mm and with a pitch 161 B of 72°.

[0179] The further receiving pot part 103 also has a positioning mark 162 for easier assembly to the wheel hub.

[0180] Furthermore, in this further embodiment, the further receiving pot part 103 has an outer diameter 124 of exactly 165.1485 mm with regard to its cylindrical receiving area 106 or its cylindrical receiving surface 105.

[0181] At the cylindrical receiving area 106, the sheet metal body 103A has a maximum sheet metal wall thickness 103C of 3 mm.

[0182] The cylindrical receiving region 106, which runs concentrically around the central axis 103A in the circumferential direction 112 of the alternative multi-part brake disc 100, narrows further in the direction of the base region 103D with a constriction region 163 and then merges into this base region 103D with a 90° angled corner region 164.

[0183] The constriction area 163 has a constriction length 163A of 21.11 mm, measured from the inside of the receiving pot part 103.

[0184] The base area 103D has a maximum base diameter 166 of 148 mm before the base area 103D transitions into the corner area 164.

[0185] Radially further inside on the bottom area 103D of the further receiving pot part 103 there is a central opening 168 with an opening diameter 168A of 69 mm.

[0186] The collar area 103E of the further receiving pot part 103 has a collar height 165 between 45.5 mm and 59.5 mm, also measured from the inside of the receiving pot part 103.

[0187] According to the illustrations in Figures 8 and 9, a further embodiment of the further friction disc ring part 102 of the alternative multi-part brake disc 100 (cf. Figures 12 to 15) is shown; specifically before assembly.

[0188] The further friction disc ring part 102 does not yet have any holes 110 corresponding to through holes 114 of the further receiving pot part 103 (see Figure 12, numbered only as an example).

[0189] The further friction disc ring part 102 is designed as an internally ventilated friction disc ring part 102 and accordingly has a plurality of cooling openings 170 (numbered only as an example), some of which can also be designed differently.

[0190] The further friction disc ring part 102 has a first friction disc side 102A and a second friction disc side 102B, wherein the two friction disc sides 102A and 102B are spaced from each other by a circumferential groove 102D at least on the outer side 102C of the friction disc ring part 102. The circumferential groove 102D has a groove width 102E of 13.5 mm, and the two friction disc sides 102A and 102B each have a side width 102F of 8.75 mm (numbered only as an example).

[0191] The further friction disc ring part 102 has a total thickness of 172 of 31 mm and a total outer diameter of 174 of 319 mm.

[0192] Furthermore, the further friction disc ring part 102 has a central axis 102G and, with respect to its inner ring part side 113, an inner diameter 132 of exactly 165 mm.

[0193] This results in a ratio D with the previously described additional receiving pot part 103 and its outer diameter 124 of exactly 165.1485 mm a / Dj 1 ,0009, at least in a state in which the further friction disc ring part 102 and the further receiving pot part 103 are not yet joined together.

[0194] For example, the further receiving pot part 103 and the further friction disc ring part 102 are joined together according to the joining direction 176 to form the alternative multi-part brake disc 100, wherein an advantageous press-fit connection is established between the further receiving pot part 103 and the further friction disc ring part 102 by means of the ratio Da / Dj of 1.0009.

[0195] For the proper assembly of the further friction disc ring part 102 and the further receiving pot part 103 to form the alternative multi-part brake disc 100, a pinning 178 (see Figure 12) of the two functional components is provided; specifically, with a plurality of alternative elongated fastening elements 118, wherein such an alternative elongated fastening element 118 is shown in the illustrations according to Figures 10 and 11.

[0196] The alternative elongated fastening element 118 is designed as a chamfered spring pin 118A with a toothed slot 118B, as shown in Figures 10 and 11. In this embodiment, the spring pin 118A has a pin length 118C of 10 mm and a pin diameter 118D of 6.4 mm.

[0197] As can be seen from Figure 11, the heavy-duty spring pin 118A in this embodiment still has a total wall thickness 118E of 1.2 mm.

[0198] According to the illustrations of Figures 12 to 15, the alternative multi-part brake disc 100 is shown in an assembled state.

[0199] In this case, the further friction disc ring part 102 is arranged on a cylindrical receiving surface 105 of the further receiving pot part 103, wherein the further receiving pot part 103 and the further friction disc ring part 102 can be arranged in a rotationally fixed manner to one another by means of the press-fit connection explained above, such that a plurality of bores through the collar region 103E (through bores 114) of the further receiving pot part 103 and into the further friction disc ring part 102 (hole bores 110) can be easily machined on the alternative multi-part brake disc 100 from radially further inward to radially further outward.

[0200] In total, thirteen such bores (through bores 114 and hole bores 110) are provided on the alternative multi-part brake disc 100; specifically, at a pitch 180 of exactly 27° 41 ' 32" measured in the circumferential direction 112.

[0201] The further friction disc ring part 102 has thirteen holes 110, whereby the further receiving pot part 103 has correspondingly thirteen through holes 114 which overlap therewith.

[0202] The holes 110 extend in the further friction disc ring part 102 from an inner side 113 of the ring part in radial directions 116 (shown only as an example) from radially further inside to radially further outside.

[0203] A heavy-duty spring pin 118A is arranged in each hole 110 and in each through-hole 114, wherein each heavy-duty spring pin 118A is inserted from radially further inward to radially further outward both into the respective through-hole 114 and into the respective hole 110.

[0204] The alternative multi-part brake disc has a rotational axis 108. According to the illustration in Figure 14, a further detail of the alternative multi-part brake disc 100 is shown along the section line BB (see Figure 12), wherein the through holes 114 in the collar region 103E of the receiving pot part 103 are again explicitly shown with regard to their hole diameter 114A of 6 mm.

[0205] According to the illustration in Figure 15, another detail of the alternative multi-part brake disc 100 is shown along section line CC (see Figure 12). It can be clearly seen that the heavy-duty clamping pin 118A is inserted into the functional components of the receiving cup part 103 and the friction disc ring part 102 with a total insertion depth 182 of at least 7.8 mm, with the heavy-duty clamping pin 118A projecting further radially inward by 2 mm on the inside of the collar area 103E with a projection 184.

[0206] According to the illustration in Figure 16, another friction disc ring part 202 with a concave ring part inner side 213 is shown, wherein the other friction disc ring part 202 can be easily arranged on the further receiving pot part 103 (see in particular Figures 6 and 7).

[0207] The other friction disc ring part 202 has an inner diameter Di 232 of exactly 160 mm at the apex 288 of the concave ring part inner side 213, wherein the apex 288 is arranged at the center plane 289 of the other friction disc ring part 202.

[0208] With the inner diameter Di 232 of exactly 160 mm on the other friction disc ring part 202 and the outer diameter D a 124 of exactly 165.1485 mm of the further receiving pot part 103 results in a ratio Da / Di of 1.0321 in this constellation, at least in a state in which the further friction disc ring part 102 and the further receiving pot part 103 are not yet joined together.

[0209] Even if the inner diameter Di 232 were to be 160.5 mm due to tolerances, the outer diameter D would be a124 of exactly 165, 1485 mm of the further receiving pot part 103 still an advantageous ratio Da / Dj of 0.9978, whereby with a downwardly scattering inner diameter Di 232 of 159 mm a ratio D a / Dj of 1 .0386.

[0210] The embodiments shown here represent only initial examples of the present invention and should therefore not be considered limiting. Alternative embodiments contemplated by those skilled in the art are equally encompassed within the scope of the present invention.

[0211] List of reference symbols used

[0212] 1 multi-piece brake disc

[0213] 2 friction disc ring part

[0214] 3 receiving pot part

[0215] 5 cylindrical receiving surface

[0216] 6 cylindrical receiving area

[0217] 8 axis of rotation

[0218] 10 holes

[0219] 12 Circumferential direction

[0220] 13 Ring part inside

[0221] 14 through holes

[0222] 16 radial directions or radially outwards

[0223] 18 elongated fasteners

[0224] 20 Loss protection

[0225] 22 Marginal area

[0226] 24 outer diameter

[0227] 26 first hole diameter

[0228] 27 second hole diameter

[0229] 28 first hole diameter range

[0230] 29 second hole diameter range

[0231] 30 insertion space

[0232] 32 inner diameter

[0233] 34 End

[0234] 36 crack prevention holes

[0235] 38 pin element

[0236] 40 Ventilation opening

[0237] 42 base body or cylindrical base body

[0238] 44 Head area

[0239] 45 shaft area

[0240] 46 shaft outer diameter

[0241] 48 head outer diameter

[0242] 50 Longitudinal extension or longitudinal direction Shell surface Shell surface section Surface structure Grooves or ribbing Alternative multi-part brake disc Additional friction disc ring part A First friction disc side B Second friction disc side C Outside D Circumferential groove E Groove width F Side width G Central axis Additional receiving pot part A Sheet metal body B Central axis C Sheet metal wall thickness D Base area E Collar area Cylindrical receiving surface Cylindrical receiving area Rotation axis Holes Circumferential direction Ring part inside Through holes A Hole diameter Radial directions or radially outward elongated fastening elements A Heavy-duty spring pin B Toothed slot C Pin length D Pin diameter E Total wall thickness

[0243] Outer diameter

[0244] inner diameter

[0245] Mounting holes A diameter

[0246] Bolt circle A Bolt circle diameter B Pitch dimension

[0247] Positioning mark

[0248] Constriction area A Constriction length

[0249] Corner area

[0250] Collar height

[0251] Base diameter

[0252] Central opening A Opening diameter

[0253] Cooling openings

[0254] Total thickness

[0255] Total outer diameter

[0256] Joining direction

[0257] Foundation

[0258] division

[0259] Installation depth

[0260] Overhang

Claims

Patent claims 1. Multi-part brake disc (1; 100), in particular a lightweight brake disc (1; 100), with a friction disc ring part (2; 102; 202) and with a receiving pot part (3; 103), in which the friction disc ring part (2; 102; 202) is arranged radially outwardly on the receiving pot part (3; 103) in a rotationally fixed manner, in which the friction disc ring part (2; 102; 202) and the receiving pot part (3; 103) are additionally operatively connected to one another by means of at least one elongate fastening element (18; 118A), wherein the at least one elongate fastening element (18; 118A) is arranged in a through-bore (14; 114) of the receiving pot part (3; 103) and in a hole (10; 110) of the friction disc ring part (2; 102; 202), characterized in that the at least one elongate fastening element (18; 118A) is arranged so as to be merely inserted into both the receiving pot part (3; 103) and the friction disc ring part (2; 102; 202), wherein the at least one elongate fastening element (18;118A) is arranged in the friction disc ring part (2; 102; 202) in a frictionally locked manner.; 2. Multi-part brake disc (1; 100) according to claim 1, characterized in that the at least one elongate fastening element (18; 118A) is arranged in the friction disc ring part (2; 102; 202) by means of a press fit connection.

3. Multi-part brake disc (1; 100) according to claim 1 or 2, characterized in that the at least one elongate fastening element (18; 118A) is fixed in the friction disc ring part (2; 102; 202) in a form-fitting manner. is arranged, wherein in particular the at least one elongate fastening element (18; 118A) is arranged in the friction disc ring part (2; 102; 202) by means of a positive connection.

4. Multi-part brake disc (1; 100) according to one of claims 1 to 3, characterized in that the at least one elongate fastening element (18; 118A) has at least partially a surface structure (56) on its outer surface (52), preferably a directed surface structure (56), wherein in particular the surface structure (56) comprises grooves (58), score lines or the like, and wherein in particular the surface structure (56) extends in a directed manner in the longitudinal direction (50) of the elongate fastening element (18; 118A).

5. Multi-part brake disc (1; 100) according to one of claims 1 to 4, characterized in that the at least one elongate fastening element (18; 118A) is a pin element (36), in particular a longitudinally slotted pin element (36).

6. Multi-part brake disc (1; 100) according to one of claims 1 to 5, characterized in that the at least one elongate fastening element (18; 118A) is a hollow pin element (36), in particular a heavy-duty dowel pin (118A), wherein the elongate fastening element (18; 118A) has a toothed slot (118B).

7. Multi-part brake disc (1; 100) according to one of claims 1 to 6, characterized in that the at least one elongate fastening element (18; 118A) in the unloaded state has an outer diameter of 4.5 mm or more, preferably of 5.5 mm or more and particularly preferably of 6 mm or more, and / or an outer diameter of 9 mm or less, preferably of 8 mm or less and particularly preferably of 6 mm or less.

8. Multi-part brake disc (1; 100) according to one of claims 1 to 7, characterized in that the elongated fastening element (18; 118A) has a length of 5 mm or more, preferably of 8 mm or more and preferably 10 mm or more, and / or a length of 18 mm or less, preferably 15 mm or less and preferably 12 mm or less.

9. Multi-part brake disc (1; 100) according to one of claims 1 to 8, characterized in that the at least one elongate fastening element (18; 118A) has a mass of 2.2 g or less, preferably of 1.8 g or less and particularly preferably of 1.2 g or less, and / or has a mass of 0.4 g or more, preferably of 0.6 g or more and particularly preferably of 0.8 g or more.

10. Multi-part brake disc (1; 100) according to one of claims 1 to 9, characterized in that the at least one elongate fastening element (18; 118A) has a base body made of steel.

11. Multi-part brake disc (1; 100) according to one of claims 1 to 10, characterized in that the at least one elongate fastening element (18; 118A) has a cylindrical base body (42).

12. Multi-part brake disc (1; 100) according to one of claims 1 to 11, characterized in that the at least one elongate fastening element (18; 118A) has a head region (44) and a shaft region (45).

13. Multi-part brake disc (1; 100) according to one of claims 1 to 12, characterized in that the at least one elongate fastening element (18; 118A) has a ventilation opening (40) for ventilating the friction disc ring part (2; 102; 202).

14. Multi-part brake disc (1; 100) according to one of claims 1 to 13, characterized in that the at least one elongate fastening element (18; 118A) and / or the receiving pot part (3; 103) have a surface coating, in particular a corrosion coating.

15. Multi-part brake disc (1; 100) according to one of claims 1 to 14, characterized by a loss prevention device (20) by means of which the friction disc ring part (2; 102; 202) and the receiving pot part (3; 103) are secured to one another, in particular axially secured, wherein the loss prevention device (20) has at least one friction and / or form-fitting connection comprising at least one elongate fastening element (18; 118A).

16. Multi-part brake disc (1; 100) according to claim 15, characterized in that the loss prevention device (20) has an arrangement with a hardness gradient which, starting from the at least one elongate fastening element (18; 118A), drops towards the friction disc ring part (2; 102; 202).

17. Multi-part brake disc (1; 100) according to one of claims 1 to 16, characterized in that the receiving pot part (3; 103) has a cylindrical receiving area (6; 106) with a cylindrical receiving surface (5; 105) arranged radially outwards (16) for receiving the ring part inner side (13; 113).

18. Multi-part brake disc (1; 100) according to one of claims 1 to 17, characterized in that the receiving pot part (3; 103) has a cylindrical receiving area (6; 106) with an outer diameter D a (24; 124) and the friction disc ring part (2; 102; 202) have an inner diameter Di (32; 132), wherein the ratio D a / Dj is 1 .01 or greater, preferably 1 .02 or greater.

19. Multi-part brake disc (1; 100) according to one of claims 1 to 18, characterized in that the receiving pot part (3; 103) has a cylindrical receiving area (6; 106) with an outer diameter D a (24; 124) and the friction disc ring part (2; 102; 202) have an inner diameter Di (32; 132), wherein the ratio D a / Di is 1 ,06 or less, preferably 1 ,05 or less.

20. Multi-part brake disc (1; 100) according to one of claims 1 to 19, characterized in that the receiving pot part (3; 103) has a cylindrical receiving area (6; 106) with an outer diameter D a (24; 124) and the friction disc ring part (2; 102; 202) has an inner diameter Di (32; 132), wherein the ratio D a / Dj is 1.00088 or greater, preferably 1.00089 or greater, and more preferably 1.0009 or greater.

21. Multi-part brake disc (1; 100) according to one of claims 1 to 20, characterized in that the receiving pot part (3; 103) has a cylindrical receiving area (6) with an outer diameter D a (24; 124) and the friction disc ring part (2; 102; 202) have an inner diameter Di (32; 132), wherein the ratio D a / Di is 1.00027 or less, preferably 1.00025 or less, and more preferably 1.00022 or less.

22. Multi-part brake disc (1; 100) according to one of claims 1 to 21, characterized in that the friction disc ring part (2; 102; 202) has an inner diameter Di (32; 132) of 164.9 mm or greater, preferably of 165 mm or greater and particularly preferably of 165.05 mm or greater.

23. Multi-part brake disc (1; 100) according to one of claims 1 to 22, characterized in that the friction disc ring part (2; 102; 202) has an inner diameter Di (32; 132) of 166 mm or less, preferably of 165.063 mm or less and particularly preferably of 165 mm or less.

24. Multi-part brake disc (1; 100) according to one of claims 1 to 23, characterized in that the receiving pot part (3; 103) has an outer diameter Di (24; 124) of 164.95 mm or greater, preferably of 165 mm or greater and particularly preferably of 165.05 mm or greater.

25. Multi-part brake disc (1; 100) according to one of claims 1 to 24, characterized in that the receiving pot part (3; 103) has an outer diameter Di (24; 124) of 165.5 mm or smaller, preferably of 165.15 mm or smaller and particularly preferably of 165 mm or smaller.

26. Multi-part brake disc (1; 100) according to one of claims 1 to 25, characterized in that the hole (10; 110) made in the friction disc ring part (2; 102; 202) is designed to be thread-free.

27. Multi-part brake disc (1; 100) according to one of claims 1 to 26, characterized in that the hole (10; 110) introduced into the friction disc ring part (2; 102; 202) has two hole diameter ranges (28, 29) different from one another, wherein in particular a larger hole diameter range (28) of the hole (10; 110) is arranged radially further inward than a smaller hole diameter range (29) of the hole (10; 110).

28. Multi-part brake disc (1; 100) according to claim 27, characterized in that in the smaller hole diameter region (29) arranged radially further outwards, the at least one elongate fastening element (18; 118A) is fastened to the friction disc ring part (2; 102; 202).

29. Multi-part brake disc (1; 100) according to claim 27 or 28, characterized in that in the larger hole diameter region (29) arranged radially further inward, on the one hand the at least one elongate fastening element (18; 118A) is arranged and on the other hand material of the receiving pot part (3; 103) can be introduced.

30. Multi-part brake disc (1; 100) according to one of claims 27 to 29, characterized in that an edge region (22) of the through-bore (14; 114) of the receiving pot part (3; 103) can be displaced into the larger hole diameter region (28) arranged radially further inward.

31. Multi-part brake disc (1; 100) according to one of claims 1 to 30, characterized in that the hole (10; 110) has an introduction space (30) for introducing material of the receiving pot part (3; 103), wherein in particular the introduction space (30) has a hole diameter (26) which is larger than the outer diameter (46; 118D) of the at least one fastening element (18; 118A) which is arranged in the introduction space (30).

32. Multi-part brake disc (1; 100) according to one of claims 1 to 31, characterized in that the friction disc ring part (2; 102; 202) has crack prevention holes (36) which are arranged radially further outwards at the respective end (34) of the hole bores (10; 110).

33. Multi-part brake disc (1; 100) according to one of claims 1 to 32, characterized in that the through-bore (14; 114) of the receiving pot part (3; 103) and the hole (10; 110) of the friction disc ring part (2; 102; 202) each have a hole diameter L-Dj (114A) and the at least one elongate fastening element (18; 118A) has a pin diameter SD a (118D), where the ratio SD a / L-Dj is 1 ,0551 or greater, preferably 1 ,0593 or greater and particularly preferably 1 ,0612 or greater, and / or wherein the ratio SD a / L-Dj is 1.0751 or less, preferably 1.0712 or less, and particularly preferably 1.0631 or less.

34. Multi-part brake disc (1; 100) according to one of claims 1 to 32, characterized in that the through-bore (14; 114) of the receiving pot part (3; 103) and the hole (10; 110) of the friction disc ring part (2; 102; 202) each have a hole diameter L-Dj (114A) and the at least one elongate fastening element (18; 118A) has a pin diameter SD a (118D), where the ratio SD a / L-Di is 1 .0345 or greater, preferably 1 .0391 or greater and particularly preferably 1 .0419 or greater, and / or wherein the ratio SD a / L-Di is 1.0651 or less, preferably 1.0574 or less, and particularly preferably 1.0461 or less.

35. Multi-part brake disc (1; 100) according to one of claims 1 to 32, characterized in that the through-bore (14; 114) of the receiving pot part (3; 103) and the hole (10; 110) of the friction disc ring part (2; 102; 202) each have a hole diameter L-Dj (114A) and the at least one elongate fastening element (18; 118A) has a pin diameter SD a (118D), where the ratio SD a / L-Dj is 1 ,0111 or greater, preferably 1 ,1011 or greater and particularly preferably 1 ,1143 or greater, and / or wherein the ratio SD a / L-Dj is 1 ,1199 or less, preferably 1,1187 or less and more preferably 1,1177 or less.

36. Friction disc ring part (2; 102; 202) for a multi-part brake disc (1; 100), in particular for a multi-part brake disc (1; 100) according to one of the preceding claims, with at least one thread-free hole (10; 110) which extends from the ring part inner side (13; 113) radially further outwards (16) and which has different hole diameters (26, 27).

37. Friction disc ring part (2; 102; 202) according to claim 36, characterized in that a plurality of holes (10; 110) are arranged in the circumferential direction (12; 112) of the ring inner side (13; 113).

38. Fastening element (18) for a multi-part brake disc (1; 100), in particular for a multi-part brake disc (1; 100) according to one of claims 1 to 26, with an elongated base body (42), wherein the fastening element (18; 118A) has at least one surface structure (56) by means of which the base body (42) can penetrate at least partially into the material of the friction disc ring part (2; 102; 202).

39. Method for producing a brake disc (1; 100) from several functional parts, in which a friction disc ring part (2; 102; 202) with an inner diameter Di (32; 132) is fixed to a radially outwardly arranged receiving surface (5; 105) with an outer diameter D a (24; 124) of a receiving pot part (3; 103) is arranged, in which the inner diameter Di (32; 132) and the outer diameter D a (24; 124) with a ratio D a / Di of 1 ,00088 or greater or with a ratio D a / Di of 1.00027 or smaller is selected before the friction disc ring part (2; 102; 202) is arranged on the receiving surface (5; 105), in which after the friction disc ring part (2; 102; 202) has been arranged on the receiving surface (5; 105), a through-bore (14; 114) and a hole (10, 110) are each made in the friction disc ring part (2; 102; 202) and in the receiving pot part (3; 103) with a single drilling process, and in which an elongated fastening element (18; 118A) is inserted from radially further inside is introduced through the respective through-bore (14; 114) into the respective corresponding hole (10; 110), wherein the elongate fastening element (18; 118A) is fastened in the hole (10; 110) of the friction disc ring part (2; 102; 202) at least partially in a frictionally engaged and / or positively engaged manner.

40. Method according to claim 39, characterized in that the elongate fastening element (18; 118A) is driven into the hole (10; 110).

41. Method according to claim 39 or 40, characterized in that the elongate fastening element (18; 118A) is fixed in the hole (10; 110) by means of a grooved, in particular longitudinally grooved, lateral surface section (54) of the elongate fastening element (18; 118A).

42. Method according to one of claims 39 to 41, characterized in that the elongate fastening element (18; 118A) penetrates into the material of the friction disc ring part (2; 102; 202) outside the hole (10; 110) when the elongate fastening element (18; 118A) is introduced into the hole (10; 110).

43. Method according to one of claims 39 to 42, characterized in that the elongate fastening element (18; 118A) is introduced into the hole (10; 110) with an insertion force of 4 kN or more, preferably of 6 kN or more, and particularly preferably of 8 kN.

44. Method according to one of claims 39 to 43, characterized in that the elongate fastening element (18; 118A) is introduced into the bore (10; 110) with insertion forces of 12 kN or less, preferably of 10 kN or less, and particularly preferably of 8 kN.

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