EP3990801A1 - Rotor ventilé de l'intérieur - Google Patents

Rotor ventilé de l'intérieur

Info

Publication number
EP3990801A1
EP3990801A1 EP20735536.3A EP20735536A EP3990801A1 EP 3990801 A1 EP3990801 A1 EP 3990801A1 EP 20735536 A EP20735536 A EP 20735536A EP 3990801 A1 EP3990801 A1 EP 3990801A1
Authority
EP
European Patent Office
Prior art keywords
cooling
disk
elements
pane
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20735536.3A
Other languages
German (de)
English (en)
Inventor
Torsten Holzapfel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brembo SGL Carbon Ceramic Brakes GmbH
Original Assignee
Brembo SGL Carbon Ceramic Brakes GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brembo SGL Carbon Ceramic Brakes GmbH filed Critical Brembo SGL Carbon Ceramic Brakes GmbH
Publication of EP3990801A1 publication Critical patent/EP3990801A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F16D65/847—Features relating to cooling for disc brakes with open cooling system, e.g. cooled by air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F16D65/128—Discs; Drums for disc brakes characterised by means for cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2200/00—Materials; Production methods therefor
    • F16D2200/0034—Materials; Production methods therefor non-metallic
    • F16D2200/0039—Ceramics
    • F16D2200/0043—Ceramic base, e.g. metal oxides or ceramic binder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2200/00—Materials; Production methods therefor
    • F16D2200/0034—Materials; Production methods therefor non-metallic
    • F16D2200/0052—Carbon

Definitions

  • the invention relates to an internally ventilated rotor which can in particular serve as a brake disc.
  • Internally ventilated brake discs primarily have the function of decelerating a rotationally moving body. The kinetic energy is converted into heat.
  • Improving dissipation is aimed at the rapid release of heat to the environment. This takes place via forced convection in the internally ventilated area.
  • the convection is directly dependent on the shape and area of the cooling elements in the internally ventilated area and the cooling channels defined above.
  • Air can circulate between the friction rings of internally ventilated brake discs.
  • connecting ribs There are through-flow connecting elements, for example in the form of connecting ribs.
  • the connecting ribs can e.g. be designed as a truss-like structure, as described in DE 195 37 392.
  • GB 2543020 describes an internally ventilated brake disc which is conventionally cast from metal with the aid of a lost core formed from sand and resin.
  • the brake disk described there comprises two friction rings which have a common axis of rotation and are spaced apart along this axis so that there is an air-filled gap. It also includes a large number of air guide blades that extend outwardly in relation to this axis in order to guide cooling air through the gap filled with air. Along its extension all air guide blades are twisted outwards.
  • GB 2543020 proposes producing lost cores by means of 3D printing for certain air guide lamella shapes.
  • Fiber-reinforced ceramic brake disks have hitherto had the disadvantage, due to production, that intermediate elements, in particular in the form of cooling fins, are made wide in relation to the height due to the limited malleability of the starting material.
  • European Patent No. 2,334,945 proposes a method with which it is to be made possible to make the shape of the cooling channels more economical and simpler. The method comprises: (a) creating load disks, friction surfaces and air guide elements of the disc rotor by separate processes using a carbon-fiber reinforced carbon-carbon composite material, (b) connecting the load disks, friction surfaces and air guide elements produced by separate processes an assembly, and (c) performing a liquid silicon melt infiltration process on the associated assembly.
  • the material of the load discs and the air guide elements is always the same.
  • the present invention is based on the object of providing an internally ventilated rotor which enables the greatest possible braking power with at the same time the minimum total weight of the braking device.
  • an internally ventilated rotor comprising at least two disk elements connected to one another via at least one cooling element
  • the at least one cooling element has a textile structure which extends from a disk element contact area of the cooling element, with which the cooling element is in contact with a disk element, to another disk element contact area of the cooling element, with which the cooling element is in contact with another disk element.
  • the number of cooling elements via which the disk elements are connected to one another is not limited.
  • the invention can be implemented with only one cooling element, e.g. if it is a cord-shaped cooling element, similar to that shown in FIG. 5, if this cooling element does not run up and down in a circular manner, but up and down in a spiral shape between the disk elements.
  • a small number of cooling elements can e.g. also exist when the rotor anyway has support elements which connect the two disk elements in addition to the cooling elements.
  • the textile structure preferably comprises parallel fibers and at least one of the parallel fibers extends from the one disk element contact area of the cooling element to the other disk element contact area of the cooling element.
  • a plurality of the parallel fibers extend from one disk element contact area into the other disk element contact area. Any tensile load is then transmitted directly from one disk element to the other disk element via the fiber (s).
  • Fibers are seen here as running parallel when they run at an angle of at most 15 ° to one another at every point on the cooling element.
  • one of several fibers running in parallel can run in a completely different direction at one point on the cooling element another fiber of the parallel fibers at a different point of the cooling element.
  • FIG. 5A as an example, in which a large number of fibers running in parallel, only a part of which is shown, run up and down together parallel to one another at every point on the cooling element.
  • European Patent No. 2,334,945 proposed air guiding elements may have a higher rigidity than cooling elements of the present invention. According to the invention, however, the same rigidity of the rotor can be achieved by a higher number of more filigree cooling elements or by a more closely meshed network of disk element contact areas realize the disc elements. Since at the same time a particularly high cooling element surface is created, the invention achieves better dissipation of the heat generated during braking with the same rigidity of the rotor.
  • the textile structure is preferably a scrim or a woven fabric and a plurality of fibers running parallel therein extend from the one pane element contact area of the cooling element to the other pane element contact area of the cooling element. This has the effect that these parallel fibers are loaded in their main load direction and that their tensile strength is used to the best possible extent.
  • a desired load capacity of the rotor is made possible with even more filigree cooling elements, that is to say with an even lower overall weight of the rotor.
  • the invention is not limited to embodiments in which the textile structure is a scrim or a woven fabric.
  • the textile structure can e.g. also be a fleece. This has thermal advantages, since fibers also run in the thickness direction of the cooling element and the cooling effect is thus further improved.
  • the combination of nonwovens with nonwovens and / or woven fabrics is conceivable.
  • a cooling element in which the textile structure is a fleece can be present in a mechanically less stressed area (e.g. in the vicinity of a support element which is already present, which connects the two pane elements in addition to the cooling elements). Then in particular the
  • Improved heat dissipation can be used in a mechanically more heavily loaded area (e.g. at a greater distance from an already existing one
  • a cooling element in which the textile structure is a scrim or a woven fabric. Then the mechanical load capacity (but also the thermal load capacity) is further increased there. Twisted threads, yarns, cords, knitted fabrics, braids and felts are also suitable as textile structures or as part of textile structures.
  • Layered composite cooling elements are also conceivable, having scrims and / or
  • the textile structure and / or the parallel fibers can include carbon fibers, silicon carbide fibers, boron nitride fibers, or mixtures thereof.
  • the person skilled in the art selects the fibers depending on whether there will be particularly pronounced mechanical loads and / or thermal loads where the fiber is to be used. It uses the different mechanical and thermal properties of the different fibers in a targeted manner.
  • Carbon fibers are particularly preferred because they have high tensile strength at high temperature and at the same time have a low density. Due to their high temperature resistance, they remain in the semi-finished product during the entire production process, including siliconization.
  • the shape of the cooling element (s) is not subject to any restrictions. In principle, any shape is conceivable.
  • the at least one cooling element is a cooling plate.
  • a targeted arrangement of cooling plates allows channels to be defined in a particularly simple manner. So the air flow can be controlled. Compared to more filigree cooling elements such as cooling rods, there is another advantage that the fibers in panels support one another.
  • the cooling elements can be curved.
  • the cooling elements can be twisted along their extension, as described in GB 2543020, since the prepregs that can be used to produce the cooling elements can be shaped accordingly.
  • the cooling elements (or their precursors, eg prepregs) can be brought into the desired shape and then cured.
  • the cooling elements preferably have a rough and / or structured surface. This favors the formation of turbulent flows; consequently, the heat generated during braking is dissipated from the rotor more efficiently.
  • the invention comprises configurations of the rotor with large or small cooling elements. Smaller, more filigree cooling elements are preferred, however, since they enable even more efficient heat dissipation to be achieved.
  • the ratio of the cooling surface A of the cooling element facing the interior of the brake disc, for example the cooling plate, to the volume V of the section of the cooling element facing the interior of the brake disc, for example the cooling plate is at least 0.25 mm -1 , in particular at least 0.4 mm -1 , further preferably at least 0.5 mm -1 , particularly preferably at least 0.6 mm -1 , for example at least 0.8 mm -1 . In calculating this ratio, only those cooling element surfaces and those cooling element volume areas that face the interior are included.
  • the cooling element or the cooling elements are inclined. It then runs / you do not run orthogonally to the surfaces of the disc elements.
  • the cooling element extends at least at one point which lies between two adjacent disk elements and is equidistant from these two disk elements, at an angle of less than 89 °, in particular of less than 80 °, e.g. less than 70 °.
  • the angle is preferably more than 20, especially more than 30 °, e.g. more than 35 °.
  • the person skilled in the art selects this angle depending on the coefficient of friction, among other things. With very low coefficients of friction, the disc elements are
  • Disc elements are less pressed together by the contact pressure of the brake shoes with the same braking power.
  • the torsional moment is at
  • the rotor has at least two oppositely inclined cooling elements, e.g. Has cooling plates, or two oppositely inclined cooling element regions of a cooling element.
  • inclined in opposite directions means that one of the two cooling elements or one of the two cooling element areas would be stretched as a whole and the other cooling element or the other cooling element area would be compressed as a whole if one of the two disk elements was about the common axis of rotation relative to the other disk element both disc elements would be rotated in the sense of the torsional moment described above.
  • At least one of the cooling elements always counteracts failure of the rotor in that it (and preferably its fibers) are subjected to tensile stress. This leads to a stiffening of the rotor. If the cooling elements are not mutually inclined, they generally have less to oppose a rotation of the one disk element relative to the other disk element about the common axis of rotation of both disk elements. Because the twisting would then (because of a parallelogram effect) not necessarily lead to a tensile load in one of the cooling elements. To achieve a predefined braking performance, a rotor according to the invention with mutually inclined cooling elements can thus be designed to be even more material-saving overall and the entire braking system can thus be designed to be lighter.
  • preferred rotors according to the invention have at least one pair of adjacent cooling elements, for example cooling plates. Orthogonal projections of the four disk element contact areas in the respective inner surface of the disk element in contact with the respective disk element contact area define four
  • Projection surfaces Four points lying within the projection surface define the corners of a rapezes. If a point can be defined in each of the four projection surfaces so that the four points define a trapezoid, a rotor according to the invention is present which is preferred in this sense.
  • Cooling elements e.g. Cooling plates, define the oppositely inclined
  • Cooling elements e.g. Cooling plates, a cooling channel that tapers or widens in the radial direction.
  • the cooling plates are then preferably arranged such that the two edges of the cooling plates lying closer to the axis of rotation of the rotor run closer to one another than the two edges of the cooling plates lying further away from the axis of rotation of the rotor; or that the two edges lying closer to the axis of rotation of the rotor are further away from one another than the two edges of the cooling plates which are further away from the axis of rotation of the rotor.
  • This can e.g. can be achieved by an arrangement of cooling plates shown in FIGS. 8 to 10.
  • a pair of oppositely inclined cooling plates can define a cooling channel that tapers outward in the radial direction and another pair of oppositely inclined cooling plates can define a cooling channel that widens outward in the radial direction.
  • the invention also includes rotors according to the invention in which one or more cooling elements extend back and forth between the disk elements.
  • a cooling element has many disk element contact areas along the cooling element, with which the cooling element is in alternating contact with the one and the other disk element.
  • the at least one cooling element can have at least three pane element contact areas, at least two pane element contact areas being in contact with the one pane element and one along the cooling elements between these disk element contact areas lying disk element contact area is in contact with the other disk element.
  • the textile structure extends through the pane element contact area, which lies along the cooling element between the other pane element contact areas.
  • the textile structure then preferably extends from the first pane element contact area over a multiplicity of further pane element contact areas up to the last pane element contact area.
  • the textile structure is then preferably a fiber bundle, for example a carbon fiber bundle.
  • the fibers extending through several disk element contact areas give the rotor according to the invention a maximum of stability.
  • two of the four trapezoidal angles are preferably the same size. Angles that differ by no more than 5 ° are considered to be equal. Preferably the two smaller angles are each less than 89 °, in particular less than 80 °, e.g. less than 70 ° but at the same time 20 °, in particular more than 30 °, e.g. more than 35 °.
  • Trapezoid occupies at most 10% of the total length of all four edges of the trapezoid, preferably at most 8%, in particular at most 6%, e.g. at most 4% of the total length of all four edges of the trapezoid.
  • the cooling elements or cooling element areas are then (in a rough approximation) aligned in the form of a triangle, two cooling elements or two cooling element areas of a cooling element defining two sides of the triangle and a section of one of the two disk elements defining the third side of the triangle. It can be seen that this further increases the torsional stiffness of the rotor.
  • the greatest longitudinal extent of a cooling element between disk elements is preferably at most 70% of the radius of the disk element with the largest radius.
  • the cooling elements or cooling element regions are preferably distributed in the rotor in such a way that certain cooling elements or cooling element regions run around within an inner region of the rotor and other cooling elements or cooling element regions run around within an outer region of the rotor.
  • the interior and exterior areas do not overlap.
  • the cooling elements or cooling element areas are thus arranged such that an outermost point of an inner cooling element or cooling element area is less far from the axis of rotation of the rotor than an innermost point of an outer cooling element. This spacing in the radial direction ensures additional eddies, i.e. in large areas for turbulent flows, so that the heat generated during braking is dissipated particularly efficiently.
  • the disk element contact areas can be attached flat to the inner surfaces of the two disk elements. However, it is preferred if the disk element contact areas run in recesses in the two disk elements.
  • the textile structure then extends into the pane element. This enables a particularly firm anchoring. The risk of a brittle fracture between the cooling elements and the pane elements is reduced to a minimum. The transition between the disk element and the cooling element can then be achieved with little
  • the invention is not limited to particular disk element materials.
  • the disk elements can for example be made of steel or other metals / metal alloys that are familiar to those skilled in the art for producing brake disks.
  • at least one pane element comprises a ceramic fiber composite, such as a silicon carbide fiber composite, in particular a silicon carbide carbon fiber composite.
  • the word includes here is intended to express in particular that other materials present in the layer composite, for example where the brake lining is pressed, can be applied. These can also be included in the disk element.
  • all the disk elements comprise a ceramic fiber composite, for example a silicon carbide fiber composite, in particular a silicon carbide carbon fiber composite.
  • a material and / or form-fitting connection between the textile structure and disc elements can be achieved by a ceramic matrix, e.g. be formed by a matrix containing silicon carbide, in which the textile structure is embedded and which extends into the two disc elements.
  • the pane element contact areas are then the surfaces of the textile structure where they are in contact with the pane elements.
  • the number of disc elements is not limited. Since the invention relates to an internally ventilated rotor, the number of disc elements is at least two.
  • the ventilated area arranged between the disc elements arranged on the very outside can in turn be interrupted by disc elements.
  • Such washer elements may be advantageous for certain applications, e.g. the surface of the internally ventilated area can thus be further increased and overheating of the brake disc can be counteracted even more effectively. So the number of
  • Disk elements amount to at least three, for example. Typically two of the disk elements are then friction disk elements and at least one disk element is an intermediate disk element.
  • An intermediate disk element can also function as a support disk element, via which other disk elements, such as the friction disk elements, can be connected to a rotatable axis.
  • a rotor according to the invention can be connected to the axle via a brake disc chamber which is firmly connected to the axle and to which the rotor is attached. The rotor can be attached to the brake disc chamber with the help of conventional fastening means, such as
  • the fastening means extend only into one of the at least two disk elements.
  • the inside diameter of this disk element is then usually smaller than the inside diameter of the other disk element or the other disk elements, e.g. indicated in Figure 5, in which only one disc element bores for receiving
  • the inner diameter is understood to be the smallest distance that a disk element occupies from the axis of rotation of the rotor.
  • a friction disk element is understood to mean a disk element on the surface of which a brake lining is intended to engage.
  • Certain (ring-shaped) friction disc elements are often referred to as friction rings.
  • Internally ventilated rotors according to the invention are e.g. obtainable by a process wherein
  • Cooling elements or cooling element precursors e.g. cut into small plates
  • Prepregs are positioned in a support material relative to one another in such a way that they protrude on both sides of the support material
  • a polymer foam can be used as the support material.
  • Targeted slots can be made in it, into which platelets (prepreg platelets) reinforced with carbon fiber fabric or carbon fiber scrim are inserted so that they protrude from the support material on both sides.
  • a disk element mass a with Carbon fiber bundle sections mixed polymer resin are used.
  • the applied disk element mass is hardened (solidified) by heating.
  • the support material can then be removed, for example by pyrolysis.
  • the green compact obtained in this way is carbonized in a manner known to the person skilled in the art and then infiltrated with silicon, the silicon reacting with carbonized resin to form the matrix containing silicon carbide. The infiltration is carried out in such a way that the silicon spreads from one disk element over the cooling element platelets to the other disk element.
  • Figure 1 shows a rotor according to the invention
  • FIG. 2 shows an enlarged section of the rotor shown in FIG.
  • FIG 3 shows a cooling element of the rotor from Figures 1 and 2, in which the textile
  • FIGS. 4A and 4B show the same section through the rotor of FIGS. 1 and 2, each with different information
  • FIG. 5 shows another rotor according to the invention
  • FIG. 5A shows a section of a cooling element of the rotor from FIG.
  • Figures 6A and 6B show the same section through the rotor of Figure 5 with each
  • FIGS. 7A and 7B illustrate the production of a further rotor according to the invention on the basis of sections.
  • FIG. 8 shows yet another rotor according to the invention
  • FIG. 9 shows sections of cooling elements of the rotor from FIG.
  • FIG. 10 shows a section of FIG. 8 from above
  • the internally ventilated rotors 1 shown in the figures comprise two disk elements 2 connected to one another via at least one cooling element 3 (FIG. 1 and FIG. 5).
  • the at least one cooling element 3 has a textile structure 4, as illustrated in FIG. 3 for the rotor of FIG. 1 and in FIG. 5A for the rotor of FIG.
  • the textile structure 4 extends from a disk element contact area 31 of the cooling element 3, with which the cooling element 3 is in contact with a disk element 2 is up to another pane element contact area 32, with which the cooling element 3 is in contact with another pane element 2.
  • FIGS. 2 and 3 for the rotor of FIG. 1 and from FIGS. 5A and 6A for the rotor of FIG.
  • the textile structure 4 is only indicated in FIGS. 3 and 5A. For reasons of clarity, the illustration of the textile structure 4 has been omitted in the other figures.
  • all textile structures 4 comprise fibers 5 running in parallel.
  • carbon fibers are involved.
  • other fibers e.g. Silicon carbide fibers, boron nitride fibers. This can be seen from Figures 3 and 5A.
  • not only at least one of the parallel running fibers 5 extends from one pane element contact area 31 of the cooling element 3 to the other pane element contact area 32 of the cooling element, but all the parallel running fibers 5.
  • the textile structure 4 is a scrim 41 and a multiplicity of fibers 5 running parallel therein extend from the one pane element contact area 31 of the cooling element 3 to the other pane element contact area 32 of the cooling element 3.
  • the cooling elements 3 are cooling plates (30-1 and 30-2 in the section of FIG. 4A).
  • cord-shaped cooling elements 3 run up and down in a circular manner and are thereby in contact with both disk elements 2 in alternation. This can be achieved, for example, with the help of a towpreg, which is passed through two spaced material layers, for example fleece layers, alternating from top to bottom and then again from bottom to top, in order to connect the material layers to one another at the desired distance.
  • the material layers sewn with Towpreg in this way can be transferred into a rotor according to the invention, for example, by applying solidifiable disk element mass (e.g.
  • a towpreg is understood to mean a cord-shaped, impregnated fiber bundle. It can be impregnated with a resin, for example.
  • the fiber bundle can for example be a carbon fiber bundle.
  • a non-impregnated, cord-shaped fiber bundle for example cord-shaped carbon fiber bundle, could also be used.
  • the application of the solidifiable disk element mass can be dispensed with and only the towpreg and possibly resin components contained in the material layers connected to it are hardened, then carbonated and then infiltrated with silicon.
  • protruding towpreg sections can be milled off.
  • FIGS. 7A and 7B show that cooling elements 3 can initially be brought into contact with the disk elements or disk element precursors in such a way that they protrude beyond the outer surfaces of the disk elements or the disk element precursors present before silicon infiltration (FIG. 7A).
  • the towpreg can be passed through two spaced material layers, for example fleece layers, alternating from top to bottom and then again from bottom to top, as described above.
  • the arrow leading from FIG. 7A to the upper illustration of FIG. 7B indicates that the sections of the cooling elements 3 that protrude beyond the outer surfaces of the disk elements can be milled off.
  • the milling can e.g. take place before an infiltration with silicon, since the then present SiC-free cooling element precursor can be processed more easily than after the infiltration with silicon (associated with the formation of very hard SiC).
  • the ratio of the cooling surface A of the cooling element 3 facing the interior of the brake disk to the volume V of the section of the cooling element facing the interior of the brake disk is far more than 0.4 mm 1 .
  • cooling elements 3, 3-1, 3-2 in all shown diarysfor men at the point that lies between two adjacent disk elements 2 and is the same distance from these two disk elements 2, at an angle of less than 89 ° to these two disc elements.
  • Sections 4A, 6A, 7B each show this most clearly, even without the point equally distant from the two adjacent pane elements being drawn in one of the figures. From these sections it is also immediately apparent that they each have at least two oppositely inclined cooling elements (3-1 and 3-2 in FIG. 7B), such as oppositely inclined cooling plates (30-1, 30-2 in FIG. 4A) or two oppositely inclined cooling element regions of a cooling element (310, 320 in FIG. 6A). Dotted trapezoids are shown in FIGS.
  • the four corners of the trapezoids each lie in projection surfaces which are defined by orthogonal projections, that is to say projections orthogonal to the inner surfaces of the pane elements.
  • the outlines of the projection surfaces are indicated in the sections of FIGS. 4A, 4B, 6A, 6B and 7B in each case with dashed lines running in the projection direction.
  • the rotor according to the invention from FIGS. 1 to 4B has pairs of adjacent cooling plates (30-1, 30-2 in FIG. 4A).
  • Orthogonal projections (see dashed lines in FIGS. 4A and 4B) of the four pane element contact areas 31-1, 32-1, 31-2, 32-2 into the respective inner surface 21, 22 of the pane element in contact with the respective pane element contact area define four Projection areas A31-1, A32-1, A31-2, A32-2.
  • Four points P31-1, P32-1, P31-2, P32-2 located within the projection surfaces again define the corners of the aforementioned trapezoid.
  • FIG. 7B An arrangement of separated or separated cooling elements similar to the cooling plates from FIGS. 1 to 4B exists in the rotor according to the invention, which is indicated in section in FIG. 7B.
  • the original, coherent cooling element precursor was completely severed in the protruding areas, so that it has pairs of adjacent cooling elements (3-1, 3-2 in FIG. 7B above).
  • orthogonal projections (see dashed lines in FIG. 7B top and bottom) of the four pane element contact areas 31-1, 32-1, 31-2, 32-2 in the respective inner surface 21, 22 of the pane element in contact with the respective pane element contact area four projection surfaces A31-1, A32-1, A31-2, A32-2, exactly as in the sections of Figures 4A, 4B.
  • four points P31-1, P32-1, P31-2, P32-2 lying within the projection surfaces define the corners of the aforementioned trapezoid.
  • the cord-shaped cooling element 3 in FIGS. 5 to 6B comprises not just two, but a large number
  • the trapezoid can nevertheless be defined in the same way as for the rotors in FIGS. 1 to 5A and 7B.
  • two of the four corners of the trapezoid P32 a , P32 b then lie in one single projection surface A32 as shown in Fig. 6B.
  • the cooling element 3 has a plurality of disk element contact areas 31, 32, 33. At least two disk element contact areas 31, 33 are in contact with one disk element.
  • a disk element contact area 32 lying along the cooling element between these disk element contact areas 31, 33 is in contact with the other disk element.
  • the textile structure 4 extends through the pane element contact area 32, which lies along the cooling element between the other pane element contact areas 31, 33.
  • I generally extend the textile structure from one end of the cord-shaped cooling element to the other end of the cord-shaped cooling element and through all the disc element contact areas located between the ends.
  • Orthogonal projections of the three pane element contact areas 31, 32, 33 into the respective inner surface 21, 22 of the pane element in contact with the respective pane element contact area thus define three projection areas A31, A32, A33.
  • One point P31, P33 located within the projection areas A31, A33 defines the corners of the trapezoid with two points P32a, P32b located within the projection area A32.
  • the textile structure extends into the disk element in all of the embodiments of the invention shown in the figures. This is always particularly preferred according to the invention, apart from the specific embodiments shown here.
  • the disk element contact areas 31, 32, 33, 31-1, 31-2, 32-1, 32-2 thus run in recesses in the two disk elements 2.
  • All of the figures show rotors in which both disk elements are silicon carbide carbon fiber composite friction disks and in which a material and form-fitting connection between disk element contact areas 31, 32, 33, 31-1, 32-1, 31-2, 32-2, and disk elements 2 is formed by a matrix containing silicon carbide, in which the textile structure 4 or the carbon fibers that run parallel to it, are embedded. The matrix extends into the two disc elements.
  • the rotor according to the invention from FIGS. 8 to 10 also has cooling elements 3 as pairs of adjacent cooling plates (30-1, 30-2).
  • the cooling plates are not only inclined in opposite directions to one another, but are also arranged in such a way that the two edges lying closer to the axis of rotation of the rotor run closer to one another than the two edges of the cooling plates which are further away from the axis of rotation of the rotor; or that the two are closer to the
  • edges of the axis of rotation of the rotor are further away from each other than the two edges of the cooling plates that are further away from the axis of rotation of the rotor.
  • cooling channels can be defined which taper or widen in the radial direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un rotor (1) ventilé de l'intérieur comprenant au moins deux éléments disque (2) reliés l'un à l'autre par l'intermédiaire d'au moins un élément de refroidissement (3), l'élément ou les éléments de refroidissement (3) présentant une structure textile (4) qui s'étend à partir d'une zone de contact (31) avec l'élément disque de l'élément de refroidissement, avec laquelle l'élément de refroidissement (3) est en contact avec un élément disque (2), jusque dans une autre zone de contact (32) avec l'élément disque de l'élément de refroidissement (3), avec laquelle l'élément de refroidissement (3) est en contact avec un autre élément disque (2).
EP20735536.3A 2019-06-28 2020-06-26 Rotor ventilé de l'intérieur Pending EP3990801A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019209499.6A DE102019209499A1 (de) 2019-06-28 2019-06-28 Innenbelüfteter Rotor
PCT/EP2020/068049 WO2020260601A1 (fr) 2019-06-28 2020-06-26 Rotor ventilé de l'intérieur

Publications (1)

Publication Number Publication Date
EP3990801A1 true EP3990801A1 (fr) 2022-05-04

Family

ID=71409395

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Application Number Title Priority Date Filing Date
EP20735536.3A Pending EP3990801A1 (fr) 2019-06-28 2020-06-26 Rotor ventilé de l'intérieur

Country Status (6)

Country Link
US (1) US20220364619A1 (fr)
EP (1) EP3990801A1 (fr)
JP (1) JP2022538219A (fr)
CN (1) CN114051563A (fr)
DE (1) DE102019209499A1 (fr)
WO (1) WO2020260601A1 (fr)

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Also Published As

Publication number Publication date
CN114051563A (zh) 2022-02-15
WO2020260601A1 (fr) 2020-12-30
JP2022538219A (ja) 2022-09-01
US20220364619A1 (en) 2022-11-17
DE102019209499A1 (de) 2020-12-31
KR20220028039A (ko) 2022-03-08

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