US20150107086A1 - Method for producing a carrier body with a damper mass for modifying the vibration for a brake lining of a disk brake - Google Patents

Method for producing a carrier body with a damper mass for modifying the vibration for a brake lining of a disk brake Download PDF

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Publication number
US20150107086A1
US20150107086A1 US14/311,901 US201414311901A US2015107086A1 US 20150107086 A1 US20150107086 A1 US 20150107086A1 US 201414311901 A US201414311901 A US 201414311901A US 2015107086 A1 US2015107086 A1 US 2015107086A1
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United States
Prior art keywords
pin
shaped projection
hole
force
head
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US14/311,901
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English (en)
Inventor
Ilhami Karatas
Christian Mueller
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Honeywell International Inc
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Honeywell International Inc
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Application filed by Honeywell International Inc filed Critical Honeywell International Inc
Assigned to HONEYWELL INTERNATIONAL INC. reassignment HONEYWELL INTERNATIONAL INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Karatas, Ilhami, MUELLER, CHRISTIAN
Publication of US20150107086A1 publication Critical patent/US20150107086A1/en
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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
    • F16D65/0043—Brake maintenance and assembly, tools therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K25/00—Uniting components to form integral members, e.g. turbine wheels and shafts, caulks with inserts, with or without shaping of the components
    • 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
    • F16D65/0006—Noise or vibration control
    • 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
    • F16D65/0006—Noise or vibration control
    • F16D65/0018—Dynamic vibration dampers, e.g. mass-spring systems
    • 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
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • 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
    • F16D2065/134—Connection
    • F16D2065/1344—Connection permanent, e.g. by casting
    • 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
    • F16D2250/00—Manufacturing; Assembly
    • F16D2250/0023—Shaping by pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49826—Assembling or joining
    • Y10T29/49945—Assembling or joining by driven force fit

Definitions

  • the present description relates to a method for producing a carrier body for a brake lining of a disk brake, at least one first damper mass being arranged rigidly on a friction lining carrier plate of the carrier body for modifying the vibration.
  • EP 1 307 665 B1 has disclosed a brake block for a disk brake, which brake block has a plate for carrying a friction lining, the brake block having a device which is assigned rigidly to the plate, in order to form a single rigid body and for varying the mass of at least one part of the plate, in order to achieve an inertia of the brake block which substantially prevents vibrations of the brake block which might cause a noise of the disk brake during braking.
  • a brake lining back plate for a brake lining of a vehicle disk brake is described in DE 10 331 052 A2.
  • a damper mass for modifying the vibration is provided on the brake lining back plate, at least one elongate arm being formed integrally on a carrying section for the brake lining, which elongate arm has an end which is connected to the carrying section and a free end, runs without contact next to the carrying section as far as a free end and lies in the main plane of extent of the brake lining back plate.
  • WO 2009/001 381 A1 has disclosed a brake block for disk brakes, which brake block has a plate which serves as support for a frictional material layer, at least one weight being applied to the plate and being fastened thereto, by means of clamps.
  • the weight modifies the mass of at least one part of the plate, in order to achieve an inertia of the brake block, which inertia substantially prevents the vibrations of the brake block during braking.
  • the weight has at least one abutment face which is suitable for abutting the edge of the plate and, as a result, defines a limitation of the rotation of the weight about a rotational axis of the disk.
  • Embodiments disclosed herein improve a method for producing a carrier body for a friction lining of a disk brake in such a way that the rigid connection between the friction lining carrier plate of the carrier body and a damper mass of the carrier body is more robust than the solutions proposed in the prior art and withstands higher loadings.
  • This problem is solved by a method for producing a carrier body for a brake lining of a disk brake.
  • the carrier body has a friction lining carrier plate for receiving a friction lining and at least one first damper mass which is connected rigidly to the friction lining carrier plate for modifying the vibration.
  • the production method includes the following steps:
  • the production method provides that the force which is directed perpendicularly onto the first pin-shaped projection by way of pressing is exerted until a rigid connection exists between the friction lining carrier plate and the first damper mass.
  • the friction lining carrier plate can be composed of any suitable material and is of substantially plate-shaped configuration.
  • a friction lining, or friction lining material is attached on the first side face of the friction lining carrier plate.
  • a damper mass which is connected rigidly to the friction lining carrier plate, the vibration can be modified and therefore noise during braking can be reduced. As a result, the resonant frequency of the apparatus is modified.
  • a damper mass is to be understood to mean a mass element which is made from any suitable material and is not fastened to a plurality of objects, or is not connected rigidly to a plurality of objects, but is rather connected rigidly merely to the friction lining carrier plate of the carrier body.
  • a rigid connection is to be understood to mean a connection between the friction lining carrier plate and the damper mass, the damper mass not being rotatable or pivotable about an axis, but rather being arranged fixedly on the friction lining carrier plate in a defined and predetermined position.
  • the rigid connection between the friction lining carrier plate and the first damper mass can therefore be separated merely by the action of violence or a very high force.
  • a pin-shaped projection which protrudes from the first side face of the first damper mass is to be understood to mean a projection of elongate configuration.
  • it can be an elongate projection which is cylindrical, conical, or else of angular configuration.
  • An elongate projection is to be understood to mean a projection which has a greater length than maximum width.
  • the head of the pin-shaped projection is to be understood to mean the end of the pin-shaped projection.
  • the head of the pin-shaped projection is therefore arranged in the region of an end side of the first pin-shaped projection, said end side facing away from the first side face of the first damper mass. Starting from the first side face of the first damper mass, the pin-shaped projection therefore extends to its end or its head.
  • the head of the pin-shaped projection is configured integrally with the pin-shaped projection.
  • the pin-shaped projection is preferably configured integrally with the damper mass.
  • the head of the pin-shaped projection is formed by the end-side region of the pin-shaped projection.
  • the end side of the pin-shaped projection represents its head.
  • said head is deformed and has the shape of a flat head and/or the shape of a mushroom head.
  • said head has a greater diameter or a greater maximum width in comparison with the remaining pin-shaped projection. Said head is therefore deformed by the exertion of the force in such a way that it is widened as viewed circumferentially.
  • the first pin-shaped projection is inserted into the first hole of the friction lining carrier plate in such a way that the head of the first pin-shaped projection protrudes out of the first hole, the first pin-shaped section is of longer configuration than the depth of the first hole. It is preferably provided that, before the exertion of force on the first pin-shaped projection and after the insertion of the first pin-shaped projection into the first hole, the first pin-shaped projection protrudes out of the first hole not only with its end side, but also beyond this. After the exertion of the force on the first pin-shaped projection, the latter still protrudes with its head out of the first hole.
  • the first pin-shaped projection is preferably inserted into the first hole of the friction lining carrier plate as a result, by the friction lining carrier plate being placed onto the first damper mass with an outwardly protruding first pin-shaped projection.
  • the method step “pressing of the first damper mass onto the friction lining carrier plate” is to be understood to mean that, by means of a suitable means, either the first damper mass is pressed onto the friction lining carrier plate and/or the friction lining carrier plate is pressed onto the first damper mass.
  • the friction lining carrier plate might be pressed by means of a hold-down onto the first damper mass, or the friction lining carrier plate which has been placed onto the first damper mass might be pressed down.
  • the expression “perpendicularly onto the first pin-shaped projection” is to be understood to mean that a force is exerted on the head of the first pin-shaped projection, that is to say on that end of the pin-shaped projection which protrudes out of the first hole of the friction lining carrier plate after insertion into the first hole.
  • the first pin-shaped projection is upset in its longitudinal direction by way of pressing. This means that the first pin-shaped projection has a shorter length after the exertion of the perpendicularly directed force than before the exertion of the perpendicularly directed force.
  • the first pin-shaped projection has a greater width or thickness at least in regions after the exertion of the perpendicularly directed force than before the exertion of the perpendicularly directed force.
  • the first pin-shaped projection is in contact with the inner wall of the first hole of the friction lining carrier plate via a positively locking connection after the exertion of the perpendicularly directed force.
  • exertion of a force is to be understood to mean that the force is exerted not only abruptly, such as in the case of riveting, but rather by pressing onto the first pin-shaped projection.
  • the material of the first pin-shaped projection can be upset in an improved manner by virtue of the fact that the force is not directed abruptly, but rather by way of pressing and perpendicularly onto the first pin-shaped projection.
  • the first pin-shaped projection therefore fills the first hole of the friction lining carrier plate in an improved manner after the exertion of the perpendicularly directed force and forms an improved and, in particular, greater positively locking component between the first pin-shaped projection and the inner wall of the first hole.
  • a more robust connection between the friction lining carrier plate and the first damper mass can be achieved by way of the improved positively locking connection, or by way of the greater positively locking component between the first pin-shaped projection and the inner wall of the first hole.
  • a carrier body which is produced in this way therefore withstands higher loadings during operation.
  • the force which is directed perpendicularly onto the first pin-shaped projection by way of pressing is exerted until the first pin-shaped projection is upset to such an extent that it forms a fully circumferential positively locking connection with the inner wall of the first hole in at least one region inside the first hole.
  • the perpendicularly directed force is exerted on the first pin-shaped projection until a fully circumferential positively locking connection is formed inside the first hole between the first pin-shaped projection and the inner wall of the first hole in the region of the outlet of the first hole, that is to say that region of the first hole which adjoins the head of the first pin-shaped projection directly.
  • the perpendicularly directed force might be exerted on the first pin-shaped projection until a completely circumferential positively locking connection is formed inside the first hole between the first pin-shaped projection and the inner wall of the first hole in the region of the middle and/or the start of the pin-shaped projection.
  • the rigid connection between the first damper mass and the friction lining carrier plate is more robust and withstands higher loadings, in particular, by virtue of the fact that the positively locking connection between the first pin-shaped projection and the inner wall of the first hole is formed in a fully circumferential manner at least in regions.
  • the force which is directed perpendicularly onto the first pin-shaped projection by way of pressing is exerted until the first pin-shaped projection is upset to such an extent that it forms a positively locking connection with the inner wall of the first hole substantially over the entire depth of the first hole inside the first hole. It is particularly preferably provided here that the perpendicularly directed force is exerted until the first pin-shaped projection forms a positively locking connection with the inner wall of the first hole both in a fully circumferential manner and over the entire depth of the first hole. It is therefore particularly preferably provided that a positively locking connection between the first pin-shaped projection and the inner wall of the first hole is formed in the entire region inside the first hole after the exertion of the perpendicularly directed force on the first pin-shaped projection.
  • the force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing, is preferably exerted over the entire pressing duration with a substantially constant strength. It is therefore preferably provided that the perpendicularly directed force is exerted on the first pin-shaped projection by means of a predefined strength and is kept constant over the entire pressing duration. Material damage, in particular in the region of the head of the first pin-shaped projection, can be avoided by the exertion of the force on the first pin-shaped projection, which exertion of force is homogeneous in this way. For example, it can therefore be avoided that the material frays or has crack formations in the region of the head of the first pin-shaped projection after the exertion of the force.
  • the rigid connection between the friction lining carrier plate and the first damper mass is also of more robust design as a result.
  • the force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing is preferably exerted over a pressing duration of from 0.5 s to 10 s, particularly preferably over a pressing duration of from 0.5 s to 5 s, and very particularly preferably over a pressing duration of from 1 s to 2.5 s. It is therefore preferably provided that the force is exerted for a considerably longer time on the first pin-shaped projection than in the case of striking, for example in the case of riveting. This can achieve a situation where the material of the first pin-shaped projection is deformed, or is upset, in a gentler and more homogeneous manner. It can therefore be avoided that the material of the first pin-shaped projection is damaged, for example frayed, or cracks are formed during the exertion of the perpendicularly directed force.
  • the force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing is exerted with a strength of from 10 kN to 80 kN, particularly preferably with a strength of between 20 kN and 60 kN, and very particularly preferably with a strength of from 25 kN to 50 kN.
  • the perpendicularly directed force might be exerted constantly with a strength of from 30 kN to 35 kN, and over a pressing duration of from 1 s to 2.5 s.
  • the rotational movements of the presser for example a pressure head, or rotational movements of the first damper mass are performed during the exertion of the perpendicularly directed force.
  • a force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing is therefore preferably exclusively provided in order to produce a rigid connection between the friction lining carrier plate and the first damper mass.
  • No tumbling of the pressure head or the damper mass is preferably provided during the exertion of the force which is directed perpendicularly onto the first pin-shaped projection.
  • the force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing is exerted by means of a pressure head.
  • the pressure head has a pressing face which faces the head of the first pin-shaped projection during the pressing operation, or during the exertion of the force on the first pin-shaped projection.
  • the pressure head is pressed with its pressing face perpendicularly onto the head of the first pin-shaped projection.
  • the head of the first pin-shaped projection represents the end region, that is to say the end-side region which faces away from the first side face of the first damper mass.
  • the pressing face of the pressure head is preferably substantially smooth. This means that the pressing face of the pressure head does not have any relatively large unevennesses or projections or recesses. Furthermore, it is preferred that the pressing face of the pressure head represents a planar surface. This achieves a situation where the head of the pin-shaped projection has a likewise substantially planar end-side face after the exertion of the force on the first pin-shaped projection. As an alternative, the pressing face of the pressure head can have a concave shape, the result of which is that the head of the first pin-shaped projection has an upwardly curved shape, or a convex shape, after the exertion of the force on the first pin-shaped projection.
  • the pressing face of the pressure head is preferably oriented parallel to the head, that is to say parallel to the end side of the first pin-shaped projection, during the exertion of the force.
  • the pressing face of the pressure head is therefore oriented parallel to that side of the first pin-shaped projection which faces away from the first side face of the first damper mass.
  • the pressing face of the pressure head is oriented substantially parallel to the first side face of the first damper mass and/or parallel to the first side face of the friction lining carrier plate during the exertion of the force.
  • An advance between the pressure head, that is to say between the pressing face of the pressure head, and the head of the first pin-shaped projection of less than 100 cm is preferably provided. This means that the pressure head is moved from a rest position in the direction of the head of the first pin-shaped projection before exertion of the force on the pin-shaped projection, the spacing between the pressing face of the pressure head and the head of the first pin-shaped projection being less than 100 cm during this rest position.
  • the advance is particularly preferably smaller than 50 cm, or very particularly preferably smaller than 25 cm.
  • the advance can extremely preferably be smaller than 10 cm or smaller than 5 cm.
  • the pressing operation therefore differs from a striking movement not only as a result of the longer pressing duration, but also as a result of a smaller advance or smaller spacing between the pressing face of the pressure head and the head of the first pin-shaped projection before introduction of the force to the head of the first pin-shaped projection.
  • the force which is directed perpendicularly onto the first pin-shaped projection, by way of pressing, is exerted until the first pin-shaped projection bears with its head against a first chamfer partially in the region of a first edge of the first hole.
  • the first edge of the first hole is a circumferential edge which delimits the first hole, in the region of the transition between a second side face of the friction lining carrier plate and the hole inner side, or the inner wall, of the first hole.
  • a chamfer is to be understood to mean a bevel or rounding of the first edge.
  • the head of the first pin-shaped projection After insertion of the first pin-shaped projection into the first hole of the friction lining carrier plate and fastening of the first damper mass to the friction lining carrier plate, the head of the first pin-shaped projection preferably bears at least partially against the first chamfer.
  • the head of the first pin-shaped projection therefore preferably bears tightly against the first chamfer at least in regions.
  • the mushroom-shaped or flat head of the first pin-shaped projection bears with its underside and/or edge region against the first chamfer after the exertion of the force on the first pin-shaped projection.
  • An improved positively locking connection between the damper mass and the friction lining carrier plate can be achieved by way of the provision of a first chamfer in the region of the first edge of the first hole in the friction lining carrier plate.
  • the connection between the first damper mass and the friction lining carrier plate becomes more robust.
  • the material of the pin-shaped projection is not damaged, or is not damaged so quickly and easily, in the region of its head during fastening. For example, crack formations in the region of the head of the first pin-shaped projection can therefore be avoided or at least reduced.
  • the first chamfer can be configured as a bevel or else as a rounding of the first edge of the first hole of the friction lining carrier plate.
  • a bevel very particularly preferably a fully circumferential bevel, of the first edge of the first hole of the friction lining carrier plate is formed by the first chamfer.
  • the first hole has a greater opening in this region than in the interior of the first hole.
  • the first chamfer is at a first angle with respect to the inner wall of the first hole, the first angle being between 10° and 80°.
  • the first angle between the first chamfer and the inner wall of the first hole particularly preferably lies between 25° and 60°, and very particularly preferably between 40° and 50°.
  • the first angle might be 45°.
  • the first angle is preferably of substantially constant configuration in a fully circumferential manner around the first hole, or in a fully circumferential manner along the first edge of the first hole.
  • the first chamfer preferably protrudes over a first depth into the first hole, the first depth corresponding to less than 50% of the entire depth of the first hole.
  • the first depth, over which the first chamfer protrudes into the first hole particularly preferably corresponds to less than 40%, very particularly preferably to less than 30%, of the entire depth of the first hole.
  • the first chamfer might protrude into the first hole over a first depth of less than 20% of the entire depth of the first hole.
  • the depth of the first hole corresponds substantially to the thickness of the friction lining carrier plate in the region of the first hole.
  • the first hole is therefore provided continuously in the friction lining carrier plate.
  • the depth of the first hole is to be understood to mean the entire depth or the length of the first hole through the friction lining carrier plate.
  • the first depth, over which the first chamfer protrudes into the hole is to be understood to mean the spacing between a plane which lies on the second side face of the friction lining carrier plate and the end of the first chamfer inside the first hole along a center axis of the first pin-shaped projection.
  • the first depth is therefore to be understood to mean the spacing which protrudes perpendicularly into the first hole as far as the end of the first chamfer.
  • the first pin-shaped projection can have any suitable shape.
  • the first pin-shaped projection is preferably of conical configuration.
  • the cross section of the first pin-shaped projection decreases toward the head of the first pin-shaped projection as viewed from the first side face of the first damper mass.
  • the cross section particularly preferably decreases in a constant and linear manner toward the head of the first pin-shaped projection as viewed from the first side face of the first damper mass. It is therefore preferably provided that the first pin-shaped projection is of conical configuration at least in regions or has the shape of a conical segment.
  • the cross section of the first pin-shaped projection can be of round, oval or angular configuration.
  • At least one notch is preferably arranged in the first chamfer. It is particularly preferably provided here that the at least one notch is arranged in a fully circumferential manner around the first hole. Furthermore, it is preferably provided that the notch is arranged in an annular manner in the first chamfer around the first hole. Furthermore, a plurality of notches which are spaced apart from one another can be arranged in an annular manner in the first chamfer around the first hole.
  • the inner wall of the first hole is at a second angle with respect to the first side face of the first damper mass, the second angle lying between 75° and 105°, particularly preferably between 80° and 100°, and very particularly preferably between 85° and 95°.
  • the second angle can be of substantially right-angled configuration in the region of a second edge of the first hole.
  • the inlet region of the first hole in the region, in which the first side face of the first damper mass bears against the first side face of the friction lining carrier plate can therefore preferably be of substantially right-angled configuration, the outlet region of the first hole, that is to say in the region of the first edge of the first hole, being beveled by way of the first chamfer.
  • the first pin-shaped projection preferably protrudes with its head over a first length out of the first hole, the first length corresponding to less than 25%, particularly preferably to less than 15%, very particularly preferably to less than 10%, of the entire depth, or length, of the first hole.
  • a friction lining carrier plate for a brake lining of a disk brake for motor vehicles usually has a thickness of between 5 mm and 15 mm.
  • the first hole might have an overall depth of 10 mm, the first pin-shaped projection protruding with its head merely over a first length of from 1 mm to 2 mm out of the first hole.
  • the first length, over which the first pin-shaped projection protrudes with its head out of the first hole is defined after the exertion of the force on the first pin-shaped projection, or after production of the rigid connection between the friction lining carrier plate and the first damper mass.
  • the first pin-shaped projection can have any suitable cross section.
  • the first pin-shaped projection can have an angular cross section, for example a triangular, rectangular, pentagonal or hexagonal cross section.
  • the first pin-shaped projection can have a round or oval cross section. It is preferably provided here that the shape of the first hole, or the cross section of the first hole has a corresponding cross section to the cross section of the first pin-shaped projection.
  • the maximum width of the pin-shaped projection is preferably of slightly smaller configuration than the minimum opening width of the first hole. The first pin-shaped projection can therefore be inserted into the first hole without deformation or the relatively great action of force.
  • the first damper mass is pressed onto the friction lining carrier plate during the entire pressing duration.
  • the first damper mass is therefore also pressed onto the friction lining carrier plate during the exertion of the perpendicularly directed force on the first pin-shaped projection.
  • a second damper mass for modifying the vibration is connected rigidly to the friction lining carrier plate.
  • the second damper mass is preferably configured in the same way as the first damper mass.
  • the friction lining carrier plate has a second hole, through which the second pin-shaped projection, namely the pin-shaped projection of the second damper mass, is inserted. All the abovementioned features with regard to the first damper mass, and the first hole in the friction lining carrier plate, are also provided for the second damper mass and the second hole of the friction lining carrier plate.
  • the friction lining carrier plate can have a second chamfer in the region of the first edge of the second hole, which second chamfer is connected at least in regions to the head of the second pin-shaped projection after insertion of the second pin-shaped projection.
  • a carrier body for a brake lining of a disk brake is provided, which carrier body has been produced according to the abovementioned production method.
  • FIG. 1 a shows a diagrammatic illustration of a brake lining having a friction lining carrier plate and holes arranged therein for receiving damper masses
  • FIG. 1 b shows a cross section of a brake lining having a friction lining carrier plate and a friction lining which is arranged on the friction lining carrier plate
  • FIG. 2 a shows a perspective view of a carrier body having a friction lining carrier plate and two damper masses which are arranged thereon,
  • FIG. 2 b shows a perspective view of a detail of a friction lining carrier plate and the damper mass which is connected thereto,
  • FIGS. 3 a - 3 d show different shapes of damper masses
  • FIG. 4 shows a cross-sectional illustration of a detail of the connection of a damper mass to the friction lining carrier plate
  • FIG. 5 shows a cross-sectional illustration of a detail of the connection of a damper mass to the friction lining carrier plate
  • FIG. 6 shows a further cross-sectional illustration of a detail of the connection of a damper mass to the friction lining carrier plate.
  • FIGS. 1 a and 1 b show a brake lining 200 in a front view and in cross section.
  • the brake lining 200 has a carrier body 100 , merely the friction lining carrier plate 10 of the carrier body 100 being shown without damper masses 14 , 15 attached thereto. Furthermore, the brake lining 200 has a friction lining 11 which is arranged on the first side face 12 of the friction lining carrier plate 10 .
  • the friction lining carrier plate 10 has in each case one hole, namely a first hole 20 and a second hole 21 for receiving the pin-shaped projections 18 , 19 of the two damper masses 14 , 15 .
  • the outlet opening of the first hole is delimited by a first circumferential edge 22 on the second side face 13 of the friction lining carrier plate 10 .
  • a first chamfer 26 is arranged in the region of said first edge 22 of the first hole 20 .
  • the first edge 22 of the first hole 20 is beveled circumferentially.
  • the friction lining carrier plate 10 has a thickness 32 which, in the region of the first hole 20 and the second hole 21 , corresponds to the respective depth 33 , 34 of the corresponding hole 20 , 21 .
  • the first chamfer 26 and the second chamfer 27 protrude over a first depth 37 , and a second depth 38 , into the first hole 20 , and into the second hole 21 , respectively.
  • the first chamfer 26 is at a first angle 35 with respect to the inner wall 40 of the first hole 20 .
  • the second chamfer 27 is at a second angle 36 with respect to the inner wall 41 of the second hole 21 .
  • FIGS. 2 a and 2 b show a perspective view of a carrier body 100 having a friction lining carrier plate 10 and two damper masses 14 , 15 which are fastened rigidly thereto.
  • the first damper mass 14 is arranged with its first pin-shaped projection 18 in the first hole 20 of the friction lining carrier plate 10 .
  • the end or the head 28 of the first pin-shaped projection 18 protrudes out of the first hole 20 .
  • both the first pin-shaped projection 18 and the second pin-shaped projection 19 are upset and, in particular in the region of the head of the first pin-shaped projection 18 and in the region of the head 29 of the second pin-shaped projection 19 , are deformed in such a way that the respective head 28 , 29 of the two pin-shaped projections 18 , 19 bears at least partially against the respective chamfer 26 , 27 in the region of the first edge 22 of the first hole 20 , and in the region of the first edge 24 of the second hole 21 .
  • FIGS. 2 a and 2 b show the stage before the exertion of the force, or before the production of the rigid connection.
  • the two damper masses 14 , 15 are inserted with their pin-shaped projections 18 , 19 into the holes 20 , 21 .
  • FIGS. 3 a to 3 d show different shapes of damper masses 14 , 15 .
  • each damper mass 14 , 15 has a first, and second, pin-shaped projection 18 , 19 which protrudes from the first side face 16 of the first damper mass 14 , and from the first side face 17 of the second damper mass 15 .
  • the pin-shaped projections 18 , 19 can be configured so as to be substantially round (cf. FIG. 3 b ) and, however, also angular (cf. FIGS. 3 a , 3 c and 3 d ).
  • FIG. 4 shows a sectional illustration of the fastening region between the friction lining carrier plate 10 and a first damper mass 14 .
  • the first pin-shaped projection 18 of the first damper mass 14 is inserted into the first hole 20 of the friction lining carrier plate 10 .
  • the first damper mass 14 bears with the first side face 16 of the first damper mass 14 against the first side face 12 of the friction lining carrier plate 10 .
  • a rigid connection between the friction lining carrier plate 10 and the first damper mass 14 has been achieved by way of pressing of the first pin-shaped projection 18 .
  • the first pin-shaped projection 18 has been upset over the entire depth 33 of the first hole 20 in such a way that a positively locking connection which is formed over the full circumference and over the entire depth 33 of the first hole 20 can be seen between the first pin-shaped projection 18 and the inner wall 40 of the first hole within the first hole 20 .
  • the first pin-shaped projection 18 protrudes with its head 28 over a first length 42 out of the first hole 20 .
  • the head 28 of the first pin-shaped projection 18 bears directly in regions against the first chamfer 26 in the region of the first edge 22 of the first hole 20 .
  • the friction lining carrier plate 10 has a thickness 32 which corresponds to the depth 33 of the first hole 20 .
  • the first chamfer 26 protrudes over a first depth 37 into the first hole 20 . Furthermore, the first chamfer forms a first angle 35 with respect to the inner wall 40 of the first hole 20 .
  • FIGS. 5 and 6 show the fastening region between the friction lining carrier plate 10 and a first damper mass 14 , as a sectional illustration as has already been shown in FIG. 4 .
  • no chamfer 26 , 27 is provided in the region of the first hole 20 of the friction lining carrier plate 10 , or in the region of the first edge 22 of the first hole 20 .
  • the angle between the second side face 13 of the brake lining carrier plate 10 and the inner wall 40 of the first hole 20 is therefore right-angled.
  • the method for producing the carrier body 100 and the method steps for the rigid fastening of a damper mass 14 , 15 to a friction lining carrier plate 10 , are provided both for a refinement with chamfers 26 , 27 and without chamfers 26 , 27 .
  • the method step of pressing or the exertion of a force 44 which is directed perpendicularly onto the first pin-shaped projection 18 will be described by way of example using FIGS. 5 and 6 without chamfer 26 , 27 .
  • FIGS. 5 and 6 already show a rigid connection between the friction lining carrier plate 10 and the first damper mass 14 , in the same way as in FIG. 4 . That is to say, the head 28 of the first pin-shaped projection 18 is already deformed by way of the force 44 which is exerted on the first pin-shaped projection 18 . Furthermore, the positively locking connection between the inner wall 40 of the first hole 20 and the first pin-shaped projection 18 can be seen inside the first hole 20 , as a result of the upset first pin-shaped projection 18 .
  • the first pin-shaped projection 18 of the first damper mass 14 has been inserted for this purpose into the first hole 20 of the friction lining carrier plate 10 .
  • the first damper mass 14 has been pressed onto the friction lining carrier plate 10 by means of a hold-down 48 , in order that the first side face 16 of the first damper mass 14 bears against the first side face 12 of the friction lining carrier plate 10 .
  • the force 44 which is directed perpendicularly onto the first pin-shaped projection 18 has been exerted by means of a pressure head 45 .
  • a constant force has been exerted over a predetermined pressing duration by way of the pressing face 46 of the pressure head 45 on the end side or the head 28 of the first pin-shaped projection 18 .
  • the pressure head 45 has been moved out of its rest position with an advance 47 perpendicularly onto the end-side region or onto the head 28 of the first pin-shaped projection 18 and then subsequently the force 44 which is directed perpendicularly onto the first pin-shaped projection 18 , by way of pressing, has been exerted.
  • the advance 47 corresponds to the spacing between the pressing face 46 of the pressure head 45 and the head 28 of the first pin-shaped projection 18 in the rest position, that is to say before the initiation of the force exertion.
  • FIG. 5 shows a pressure head 45 having a pressing face 46 , the pressing face 46 being a smooth and planar surface.
  • the head 28 of the first pin-shaped projection is therefore configured in its surface as a substantially smooth planar surface after the exertion of the force 44 on the head 28 of the first pin-shaped projection 18 .
  • FIG. 6 shows a pressure head 45 having a pressing face 46 , the pressing face 46 having a concave shape.
  • the pressure head 45 therefore has an inwardly curved pressing face 46 .
  • the outer face of the head 28 of the first pin-shaped projection 18 therefore has a shape which is convex, that is to say curved outward.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Vibration Prevention Devices (AREA)
US14/311,901 2013-10-21 2014-06-23 Method for producing a carrier body with a damper mass for modifying the vibration for a brake lining of a disk brake Abandoned US20150107086A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310111594 DE102013111594B4 (de) 2013-10-21 2013-10-21 Verfahren zur Herstellung eines Trägerkörpers mit Tilgermasse zur Veränderung der Schwingung für einen Bremsbelag einer Scheibenbremse
DE102013111594.2 2013-10-21

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US20150107086A1 true US20150107086A1 (en) 2015-04-23

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US14/311,901 Abandoned US20150107086A1 (en) 2013-10-21 2014-06-23 Method for producing a carrier body with a damper mass for modifying the vibration for a brake lining of a disk brake
US15/030,921 Active US10400836B2 (en) 2013-10-21 2014-10-20 Method for producing a carrier body having a damper mass for changing the vibration for a brake lining of a disk brake

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US15/030,921 Active US10400836B2 (en) 2013-10-21 2014-10-20 Method for producing a carrier body having a damper mass for changing the vibration for a brake lining of a disk brake

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US (2) US20150107086A1 (fr)
EP (1) EP3060823B2 (fr)
JP (1) JP2016538496A (fr)
CN (1) CN105658984B (fr)
DE (1) DE102013111594B4 (fr)
WO (1) WO2015059098A2 (fr)

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US20160281805A1 (en) * 2013-11-21 2016-09-29 Continental Teves Ag & Co. Ohg Friction lining arrangement for a disk brake
ES2692352A1 (es) * 2017-06-02 2018-12-03 Trw Automotive España, S.L. Pastilla de freno para disco de freno y procedimiento de fabricación de dicha pastilla de freno para disco de freno
EP4174338A3 (fr) * 2021-10-27 2023-07-05 Nio Technology (Anhui) Co., Ltd Frein pour véhicule et véhicule

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JP6152128B2 (ja) * 2015-02-16 2017-06-21 日東電工株式会社 偏光子の製造方法
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KR101957712B1 (ko) * 2017-12-29 2019-03-14 상신브레이크 주식회사 타원형 핀을 구비한 차량용 브레이크 디스크 마찰패드 어셈블리
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US20150107946A1 (en) * 2013-10-21 2015-04-23 Honeywell International Inc. Carrier body for a brake lining of a disk brake with a damper mass for modifying the vibration
US9341221B2 (en) * 2013-10-21 2016-05-17 Honeywell International Inc. Carrier body for a brake lining of a disk brake with a damper mass for modifying the vibration
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Also Published As

Publication number Publication date
CN105658984B (zh) 2019-09-10
CN105658984A (zh) 2016-06-08
DE102013111594A1 (de) 2015-04-23
EP3060823B2 (fr) 2022-09-28
US10400836B2 (en) 2019-09-03
DE102013111594B4 (de) 2015-04-30
EP3060823A2 (fr) 2016-08-31
WO2015059098A3 (fr) 2015-11-12
JP2016538496A (ja) 2016-12-08
US20160252148A1 (en) 2016-09-01
WO2015059098A2 (fr) 2015-04-30
EP3060823B1 (fr) 2017-11-22

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