brake disc, disc brake with one brake disc and vehicle with one brake disc

Description

[0001] The invention relates to a brake disc, a disc brake with a brake disc, a vehicle with a brake disc and a method for manufacturing a brake disc.

[0002] Disc brakes on vehicles such as bicycles, motorcycles, and cars consist of a brake disc against which a braking element is pressed to reduce the vehicle's speed. The resulting friction heats up the brake disc. This can lead to damage to both the brake disc and the braking element, which impairs the disc brake's function. Particularly in the case of electrically powered bicycles, which are heavier than conventional bicycles and capable of higher speeds, there are increased demands on braking performance and, consequently, on heat dissipation.

[0003] From DE 10 2018 121 330 A1, a brake disc with a first and a second outer disc and an inner disc is known. There, a brake disc is proposed which, in particular for cooling, has chambers in which a coolant is arranged.

[0004] Further prior art is cited in CN 202 768 693 U, DE 20 2014 105414 U1, DE 20 2004 005284 U1, JP 2003 278810 A, KR 2016 0133715 A, US 2013 / 284549 A1 and US 2004 / 178029 A1.

[0005] A disadvantage of brake discs known from the prior art is that, particularly during prolonged braking at high speeds, such as those occurring during long downhill stretches, the heat generated in the brake disc cannot be dissipated quickly enough. Furthermore, brake discs known from the prior art are very expensive to manufacture.

[0006] The invention is therefore based on the objective of providing a brake disc that has particularly effective heat dissipation and is also easy to manufacture.

[0007] Furthermore, the invention is based on the objective of providing a disc brake and a vehicle with such a brake disc.

[0008] The problem is solved according to the invention by a brake disc having the features of claim 1, a disc brake according to claim 14 and a vehicle according to claim 15.

[0009] Advantageous embodiments and further developments of the invention are specified in the dependent claims.

[0010] A brake disc according to the invention for a disc brake, preferably for bicycles, comprises a first outer disc, a second outer disc, an inner disc with a cylindrical surface, and at least one air passage. The at least one air passage includes a ventilation channel arranged in the inner disc, with an inner channel end and an outer channel end. The ventilation channel is arranged such that the outer channel end is located in the cylindrical surface of the inner disc, and the inner channel end is located on an imaginary first partial circle of the brake disc. Here and in the following, a partial circle is preferably defined as a circle whose diameter is smaller than an outer diameter of the brake disc and which is arranged concentrically to the brake disc.Furthermore, the at least one air passage includes a ventilation bore with a ventilation bore diameter arranged in the first outer pane and / or the second outer pane. The inner pane is arranged between the first outer pane and the second outer pane such that the at least one ventilation bore is in operative communication with the inner end of the channel.

[0011] Preferably, the at least one ventilation bore is operatively connected to the inner end of the channel in such a way that air can flow from the inner end of the channel into the ventilation bore. The at least one ventilation bore is preferably designed as a through-hole. Air flowing in at the outer end of the channel can thus flow through the ventilation channel to the inner end of the channel and back out to the outside via the at least one ventilation bore. A ventilation flow can therefore be directed through the brake disc via the at least one air passage, which can dissipate the heat present in the brake disc.

[0012] Particularly preferably, the at least one ventilation bore is arranged on the first pitch circle so that, when the inner disc is appropriately aligned with the first outer disc and / or the second outer disc, it coincides with the inner channel end. The longitudinal axis of the at least one ventilation bore is preferably arranged parallel to an axis of rotation of the brake disc.

[0013] Preferably, the first and second outer panes are identical. Particularly preferably, they are mirror images of each other and arranged in a symmetrical manner. This allows the same inner end of the channel to be operatively connected to the at least one ventilation bore of both the first and second outer panes. Part of the air flowing in through the outer end of the channel can thus escape to the outside through the at least one ventilation bore of the first outer pane, and the other part through the at least one ventilation bore of the second outer pane.

[0014] The inner pane preferably has a thickness sufficient to allow the at least one ventilation channel to extend completely across it. In the direction of the axis of rotation, the at least one ventilation channel can thus be bounded by the first outer pane and the second outer pane.

[0015] In a preferred embodiment of the invention, the at least one ventilation channel is inclined, at least partially, relative to the radial direction of the inner disc. The radial direction of the inner disc preferably relates to the axis of rotation of the brake disc. Particularly preferred is the section of the at least one ventilation channel adjacent to the outer channel end being inclined relative to the radial direction. The inclination is preferably in the direction of a predetermined main rotation of the brake disc. Thus, when the brake disc rotates in the predetermined main rotation direction, the inflow of air into the at least one ventilation channel can be actively supported by the rotational movement. The at least one ventilation channel is preferably linear. However, it may be curved in certain sections.

[0016] The inner channel end can be formed by a channel end bore with a specific diameter. The inner disc can be positioned between the first outer disc and the second outer disc such that the at least one ventilation bore and the channel end bore are arranged concentrically. This simplifies the manufacturing of the at least one ventilation channel and the assembly of the brake disc, and reduces the flow resistance in the air passage. The diameter of the at least one ventilation bore is particularly preferably larger than or equal to the diameter of the channel end bore.

[0017] The diameter of the channel end bore can be larger than the width of a channel section immediately adjacent to the channel end bore. This allows the inner channel end to be wider than the rest of the ventilation channel. In particular, this reduces flow resistance at the inner channel end and simplifies its manufacture. Preferably, the at least one ventilation channel has a constant channel width. In an alternative embodiment, the at least one ventilation channel can have a variable channel width, in particular one that tapers towards the inner channel end.

[0018] In a preferred embodiment of the invention, the brake disc has several, preferably 36, uniformly offset air passages arranged rotationally. "Rotationally" here and in the following preferably refers to the axis of rotation of the brake disc. This allows for uniform and effective cooling of the brake disc. Furthermore, a brake disc with 36 air passages can be sufficiently stable and easy to manufacture.

[0019] The brake disc according to the invention has at least one fan blade which forms a blade angle of less than or equal to 90° with an end face of the brake disc. Preferably, the at least one fan blade is thus axially projected from the brake disc with respect to the axis of rotation of the brake disc. During rotation of the brake disc, the at least one fan blade can thereby be moved relative to the surrounding air mass. Preferably, the at least one fan blade is in thermally conductive contact with the brake disc, thus facilitating heat dissipation from the brake disc to the environment. The at least one fan blade can be integrally connected to the inner disc or one of the outer discs. In particular, it can be formed by an element bent out of the inner disc or one of the outer discs.

[0020] According to the invention, the at least one fan blade is arranged on the inner disc. This allows the at least one fan blade to be made of a different material than the outer discs and still be produced by simply bending it outwards. Preferably, the at least one fan blade is arranged within the first pitch circle, particularly preferably on the inner circumference of the brake disc. The first outer disc and / or the second outer disc can have a recess in which the at least one fan blade is arranged. This allows the at least one fan blade to project away from the brake disc.

[0021] In a further development of the invention, the brake disc has a first fan blade and a second fan blade, wherein the first fan blade encloses a first blade angle with the front surface of the brake disc and the second fan blade encloses a second blade angle with the front surface of the brake disc, and wherein the second blade angle is less than or equal to the first blade angle in magnitude.

[0022] Preferably, the first and second fan blades are arranged opposite each other such that air flowing towards the second fan blade is directed onto the first fan blade. The second fan blade is preferably positioned in front of the first fan blade in the main direction of rotation of the brake disc. The first and second fan blades can be angled in the same axial direction as the brake disc. Particularly when the brake disc rotates in its main direction of rotation, air flowing towards the upper surface of the second fan blade can be directed onto the underside of the first fan blade. This further improves the cooling of the brake disc. The upper surface is preferably the side of each fan blade towards which it is angled.

[0023] In one embodiment of the invention, the first and second fan blades form a pair of blades, and the inner disc has several, preferably six, uniformly offset pairs of blades. This allows for uniform and effective cooling of the brake disc.

[0024] Preferably, the inner disc is made of a copper alloy, in particular copper. Due to the high thermal conductivity of copper, such a brake disc can dissipate the generated heat particularly quickly. In combination with the at least one ventilation channel and / or the at least one fan blade arranged on the inner disc, the heat dissipation effect can be further increased.

[0025] The first outer disc and / or the second outer disc can be made of stainless steel with a ferrite component. The ferrite component, in particular, can significantly increase the coefficient of friction of the brake disc, thus achieving particularly good braking performance.

[0026] In a preferred embodiment of the invention, the inner disk has an inner disk thickness of 0.8 mm to 1 mm and the first outer disk and the second outer disk each have an outer disk thickness of 0.5 mm to 0.7 mm.

[0027] The brake disc can have at least one mounting hole located on an imaginary second pitch circle of the brake disc, preferably with a diameter larger than the diameter of the first pitch circle. Preferably, the at least one mounting hole is designed as a through-hole through the outer and inner discs. This allows the outer and inner discs to be connected to each other via the mounting hole. Preferably, the brake disc has several mounting holes. Each mounting hole can be located between two ventilation channels. A brake disc with 36 ventilation channels therefore preferably has 36 mounting holes. This prevents noise from the outer and inner discs rubbing against each other.

[0028] The inner and outer discs can be annular in shape and floating relative to a bearing element. This prevents the brake disc from warping due to temperature fluctuations. Preferably, the brake disc has six bearing points, which are preferably arranged on the inner circumference of the brake disc, particularly alternating with the pairs of vanes. The bearing points are especially preferably located on the outer and inner discs. The bearing element is preferably star-shaped.

[0029] A disc brake according to the invention has the brake disc described above.

[0030] A vehicle according to the invention, in particular a bicycle, has the brake disc described above. The brake disc is preferably arranged such that the ventilation channels are inclined towards the main direction of rotation. The main direction of rotation is generally determined by the forward direction of travel of the vehicle.

[0031] An embodiment of the invention is explained with reference to the following figures. It shows: Figure 1 shows a two-dimensional view of an end face of an embodiment of a brake disc with the section plane AA indicated; Figure 2 shows the section view AA of the Fig. 1 The exemplary embodiment shown, Figure 3, is a three-dimensional view of the [description of the embodiment]. Fig. 1 In the exemplary embodiment shown, Figure 4 is a two-dimensional view of an end face of the inner disk of the Fig.1 The exemplary embodiment shown, Figure 5, is a side view of the [description of the embodiment]. Fig. 4 shown inner disc, Figure 6 a three-dimensional view of the in Fig. 4 shown inner disk, Figure 7, a two-dimensional view of an end face of an outer disk of the in Fig.1 The exemplary embodiment shown, Figure 8, is a three-dimensional view of the [unclear text]. Fig. 7 shown outer pane.

[0032] The Figuren 1 bis 8 The figures show different views of an exemplary embodiment. For the sake of clarity, not all reference symbols are used in every figure.

[0033] Fig. 1 shows an embodiment of a brake disc 10 for a disc brake, preferably of bicycles, with a first outer disc 12 (see in particular Fig. 7 u. 8), a preferably identical second outer disk 14 and an inner disk 16 (see in particular Fig. 4 bis 6 ) with a cylindrical surface 18. Preferably, the brake disc 10 also has several, particularly preferably 36, air passages 20. The air passages 20 are preferably arranged with uniform rotational offset with respect to a rotational axis 36 of the brake disc 10. In the figures, only individual air passages 20 are provided with reference numerals as examples. Each of the air passages 20 comprises a ventilation channel 22 arranged in the inner disc 16, with an inner channel end 24 and an outer channel end 26, wherein the ventilation channel 22 is arranged such that the outer channel end 26 is located in the cylindrical surface 18 of the inner disc 16. The inner channel end 24 is arranged on an imaginary first pitch circle 28 of the brake disc 10. The first pitch circle 28 is preferably arranged concentrically to the brake disc 10 and preferably has a first pitch circle diameter 29 that is smaller than an outer diameter 30 of the brake disc 10.Furthermore, each of the air passages 20 preferably comprises a ventilation bore 32 arranged in the first outer pane 12 and the second outer pane 14, with a ventilation bore diameter 34. As shown in particular in . Fig. 2 As shown, the inner disk 16 is arranged between the first outer disk 12 and the second outer disk 14. The inner disk 16 is positioned between the first outer disk 12 and the second outer disk 14 such that the ventilation bore 32 of each air passage 20 is in operative communication with the inner channel end 24 of the same air passage 20 (see Fig. 1 ).

[0034] The inner disc 16 is in Fig. 1 This is particularly evident from the partial section through the first outer pane 12. The ventilation channels 22 arranged in the partial section provide a view of the second outer pane 14.

[0035] Preferably, each of the ventilation bores 32 is operatively connected to the associated inner channel end 24 in such a way that air can flow from the inner channel end 24 into the ventilation bore 32. The ventilation bores 32 are preferably designed as through-holes. Air flowing in at the outer channel end 26 can thus flow through the ventilation channel 20 to the inner channel end 24 and back to the open air via the at least one ventilation bore 32. A ventilation flow can therefore be directed through the air passages 20 through the brake disc 10, which can dissipate the heat present in the brake disc 10.

[0036] The ventilation bores 32 are particularly preferably arranged on the first pitch circle 28 so that, with appropriate alignment of the inner disk 16 with the first outer disk 12 and the second outer disk 14, they coincide with the inner channel end 24. The longitudinal axes of the ventilation bores are preferably parallel to the one in Fig. 2 arranged on the rotation axis 36 of the brake disc 10 shown.

[0037] Preferably, the first outer disk 12 and the second outer disk 14 are identically designed. Fig. 7 und 8 This can represent either the first outer disc 12 or the second outer disc 14. Particularly preferably, the first outer disc 12 and the second outer disc 14 are arranged symmetrically to each other on the brake disc 10. This allows each of the inner channel ends 24 to be operatively connected to one of the ventilation bores 32 of the first outer disc 12 and one of the ventilation bores 32 of the second outer disc 14. Part of the air flowing in through the outer channel end 26 can thus flow to the outside through the corresponding ventilation bore 32 of the first outer disc 12, and the other part through the corresponding ventilation bore 32 of the second outer disc 14.

[0038] As in the Fig. 4 bis 6 As shown, the inner disk 16 preferably has an inner disk thickness 38 over which the ventilation channels 22 can extend completely. In the direction of the axis of rotation 36, the ventilation channels 22 can thus be limited by the first outer disk 12 and the second outer disk 14.

[0039] The ventilation channels 22 can be inclined, at least partially, relative to a radial direction 40 of the inner disc 16. The radial direction of the inner disc preferably relates to the axis of rotation 36 of the brake disc 10. The inclination is preferably in the direction of a intended main rotation 42 of the brake disc 10. Thus, when the brake disc 10 rotates in the main rotation direction 42, the flow of air into the ventilation channels 22 can be actively supported by the rotational movement. Preferably, the ventilation channels 22 are linear.

[0040] As in Fig. 4 As shown, the inner channel end 24 can be formed by a channel end bore 44 with a channel end bore diameter 46. As shown in particular from Fig. 1 As can be seen, the inner disk 16 can be arranged between the first outer disk 12 and the second outer disk 14 such that the ventilation bores 32 and the channel end bores 44 are arranged concentrically. It is particularly preferred that the diameter of the ventilation bores 32 is the same as the diameter of the channel end bore 46.

[0041] The channel end bore diameter 46 can be larger than a channel section width 48 of a channel section immediately adjacent to the channel end bore 44 (see in particular Fig. 4 This allows the inner end of the duct 24 to be wider than the rest of the ventilation duct. Preferably, the ventilation ducts 22 otherwise have a constant duct width.

[0042] As especially from Fig. 2 As can be seen, the brake disc 10 can have a first fan blade 50 and a second fan blade 52. The first fan blade 52 can enclose a first blade angle 56 with an end face 54 of the brake disc 10. The second fan blade 52 can enclose a second blade angle 58 with the end face 54 of the brake disc 10. Preferably, the first blade angle 56 and the second blade angle 58 are each less than 90°. This allows the fan blades 50, 52 to project axially from the brake disc 10 with respect to the axis of rotation 36 of the brake disc 10. The first fan blade 50 and the second fan blade 52 are preferably projected in the same axial direction of the brake disc 10. Particularly preferably, the second blade angle 58 is smaller in magnitude than the first blade angle 56.

[0043] The first fan blade 50 and the second fan blade 52 can be integrally connected to the inner disc 16 (see Fig. 2 ). In particular, the fan blades 50, 52 can be formed by an element bent out of the inner disk 16.

[0044] Preferably, the first fan blade 50 and the second fan blade 52 are arranged opposite each other such that air flowing towards the second fan blade 52 is directed onto the first fan blade 50. The second fan blade 52 is preferably positioned in front of the first fan blade 50 in the main direction of rotation 42 of the brake disc 10. Particularly when the brake disc 10 rotates in the main direction of rotation 42, air flowing towards a top surface 60 of the second fan blade 52 can be directed onto a bottom surface 62 of the first fan blade 50. The top surface 60 is preferably the side of the first fan blade 50 towards which it is projected.

[0045] As especially in the Fig. 2 As shown in Figures 4 to 6, the first fan blade 50 and the second fan blade 52 are preferably arranged on the inner disk 16. The first fan blade 50 and the second fan blade 52 can form a pair of blades 64. The inner disk 16 preferably has six pairs of blades 64 that are uniformly offset in rotation. Preferably, the pairs of blades 64 are arranged within the first pitch circle 28, particularly preferably on the inner circumference of the brake disk 10. The first outer disk 12 and the second outer disk 14 can have a recess 66 in which the at least one fan blade is arranged (see Figure 4). Fig. 7 u. 8).

[0046] Preferably, the inner disc 16 is made of a copper alloy, in particular copper. Due to the high thermal conductivity of copper, the brake disc 10 can dissipate the heat generated particularly quickly. In combination with the ventilation channels 22 and the fan blades 50, 52 arranged on the inner disc 16, the heat dissipation effect can be further increased. The first outer disc 12 and the second outer disc 14 can be made of stainless steel with a ferrite content. In particular, the ferrite content can significantly increase the coefficient of friction of the brake disc 10, thus achieving particularly good braking performance.

[0047] The inner thickness 38 of the inner disc 16 is preferably 0.8 mm to 1 mm. The first outer disc 12 and the second outer disc 14 each have an outer thickness 68 of 0.5 mm to 0.7 mm (see Fig. 2 ).

[0048] As among others in Fig. 1 As shown, the brake disc 10 preferably has mounting holes 70. Each of the mounting holes 70 can be arranged between two ventilation channels 22. A brake disc 10 with 36 ventilation channels thus preferably has 36 mounting holes 70. The mounting holes 70 are preferably arranged on an imaginary second pitch circle 72 of the brake disc 10 with a second pitch circle diameter 74, wherein the second pitch circle diameter 74 is particularly preferably larger than the first pitch circle diameter 29. Preferably, the mounting holes 70 are designed as through holes through the outer discs 12, 14 and the inner disc 16. In this way, the outer discs 12, 14 and the inner disc 16 can be connected to each other by means of the mounting holes 70.

[0049] As particularly in Fig. 1As shown in Figure 3, the inner disc 16 and the outer discs 12, 14 can be annular in shape and floating relative to a bearing element 76. Preferably, the brake disc 10 has six bearing points 78, which are preferably arranged on the inner circumference of the brake disc 10, particularly alternating with the pairs of wings 64. The bearing points 78 are especially preferably arranged on the outer discs 12, 14 and on the inner disc 16. The bearing element 76 is preferably star-shaped.

[0050] A non-inventive method for manufacturing the brake disc 10 can be characterized in that the inner disc 16 and the outer discs 12, 14 are at least partially manufactured by laser cutting. This allows the outer discs 12, 14 and the inner disc 16 to be easily cut from a metal plate. In particular, the pairs of blades 64 can be cut out of the inner disc 16 by a simple T-cut, wherein the longitudinal line of the T preferably defines the opposing edges of the first fan blade 50 and the second fan blade 52. Reference symbol list

[0051] 10 Brake disc 12 First outer disc 14 Second outer disc 16 Inner disc 18 Casing surface 20 Air passage 22 Ventilation channel 24 Inner channel end 26 Outer channel end 28 First pitch circle 29 First pitch circle diameter 30 Outer diameter of brake disc 32 Ventilation hole 34 Ventilation hole diameter 36 Axis of rotation 38 Inner disc thickness 40 Radial direction 42 Main direction of rotation 44 Channel end hole 46 Channel end hole diameter 48 Channel section width 50 First fan blade 52 Second fan blade 54 End face of brake disc 56 First blade angle 58 Second blade angle 60 Top of second fan blade 62 Bottom of first fan blade 64 Blade pair 66 Recess 68 Outer disc thickness 70 Mounting hole 72 Second pitch circle 74 Second Pitch circle diameter 76 Bearing element 78 Bearing position

Claims

1. Brake disc (10) for a disc brake, preferably for bicycles, comprising the following features: • a first outer disc (12), • a second outer disc (14), • an inner disc (16) with a surface (18), and • at least one air passage (20), comprising ∘ a ventilation channel (22) arranged in the inner disc (16) with an inner channel end (24) and an outer channel end (26), wherein the ventilation channel (22) is arranged such that the outer channel end (26) is arranged in the outer surface (18) of the inner disc (16) and the inner channel end (24) is arranged on an imaginary first pitch circle (28) of the brake disc (10) having a first pitch circle diameter (29), ∘ a ventilation bore (32) arranged in the first outer disc (12) and / or the second outer disc (14) with a ventilation bore diameter (34), • wherein the inner disc (16) is arranged between the first outer disc (12) and the second outer disc (14) in such a way that the at least one ventilation bore (32) is in operative connection with the inner channel end (24), characterized in that the brake disc (10) comprises at least one fan blade (50, 52) which, with an end face (54) of the brake disc (10), encloses a blade angle (56, 58) of less than or equal to 90°, wherein the at least one fan blade (50, 52) is arranged on the inner disc (16).

2. Brake disc according to claim 1, characterized in that the at least one ventilation channel (32) is inclined at least in sections relative to the radial direction (40) of the inner disc (16).

3. Brake disc according to any one of the preceding claims, characterized in that the inner channel end (24) is formed by a channel end bore (44) with a channel end bore diameter (46), and the inner disc (16) is arranged between the first outer disc (12) and the second outer disc (14) in such a way that the at least one ventilation bore (32) and the channel end bore (44) are arranged concentrically.

4. Brake disc according to claim 3, characterized in that the channel end bore diameter (46) is larger than a channel section width (48) of a channel section immediately adjacent to the channel end bore (44).

5. Brake disc according to any one of the preceding claims, characterized in that the brake disc (10) comprises a plurality, preferably 36, of air passages (20) that are rotatably evenly spaced.

6. Brake disc according to any one of the preceding claims, characterized in that the brake disc (10) comprises a first fan blade (50) and a second fan blade (52), wherein the first fan blade (50) forms a first blade angle (54) with the end face (54) of the brake disc (10) (56) with the end face (54) of the brake disc (10), and the second fan blade (52) forms a second blade angle (58) with the end face (54) of the brake disc (10), and wherein the second blade angle (58) is smaller than or equal to the first blade angle (56).

7. Brake disc according to claim 6, characterized in that the first fan blade (50) and the second fan blade (52) are arranged opposite each other in such a way that air flowing onto the second fan blade (52) is directed onto the first fan blade (50).

8. Brake disc according to any one of claims 6 to 7, characterized in that the first fan blade (50) and the second fan blade (52) form a pair of blades (64) and the inner disc (16) has several, preferably six, pairs of blades (64) that are evenly spaced in a rotational direction.

9. Brake disc according to any one of the preceding claims, characterized in that the inner disc (16) is made of a copper material, in particular copper.

10. Brake disc according to any one of the preceding claims, characterized in that the first outer disc (12) and / or the second outer disc (14) is made of stainless steel with a ferrite content.

11. Brake disc according to any one of the preceding claims, characterized in that the inner disc (16) has an inner disc thickness (38) of 0.8 mm to 1 mm, and the first outer disc (12) and the second outer disc (14) each have an outer disc thickness (68) of 0.5 mm to 0.7 mm.

12. Brake disc according to any one of the preceding claims, characterized in that the brake disc (10) comprises at least one mounting hole (70) which is arranged on an imaginary second pitch circle (72) of the brake disc (10) having a second pitch circle diameter (74), wherein the second pitch circle diameter (74) is larger than the first pitch circle diameter (29).

13. Brake disc according to any one of the preceding claims, characterized in that the inner disc (16) and the outer discs (12, 14) are circular in shape and are mounted in a floating manner relative to a bearing element (76).

14. Disc brake with a brake disc (10) according to any one of the preceding claims.

15. Vehicle, in particular a bicycle, with a brake disc (10) according to any one of claims 1 to 13.