EP0879364A2 - Frein a etrier fixe et plaquettes de frein appropriees - Google Patents

Frein a etrier fixe et plaquettes de frein appropriees

Info

Publication number
EP0879364A2
EP0879364A2 EP97905056A EP97905056A EP0879364A2 EP 0879364 A2 EP0879364 A2 EP 0879364A2 EP 97905056 A EP97905056 A EP 97905056A EP 97905056 A EP97905056 A EP 97905056A EP 0879364 A2 EP0879364 A2 EP 0879364A2
Authority
EP
European Patent Office
Prior art keywords
brake
housing
pad
lining
back plate
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.)
Withdrawn
Application number
EP97905056A
Other languages
German (de)
English (en)
Inventor
Manfred Reuter
Hans-Dieter Leidecker
Rolf Weiler
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.)
Continental Teves AG and Co OHG
Original Assignee
ITT Manufacturing Enterprises LLC
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
Priority claimed from DE19607056A external-priority patent/DE19607056A1/de
Priority claimed from DE1996135838 external-priority patent/DE19635838A1/de
Application filed by ITT Manufacturing Enterprises LLC filed Critical ITT Manufacturing Enterprises LLC
Publication of EP0879364A2 publication Critical patent/EP0879364A2/fr
Withdrawn legal-status Critical Current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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/228—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a separate actuating member for each side
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/04—Attachment of linings
    • F16D2069/0425—Attachment methods or devices
    • F16D2069/0441—Mechanical interlocking, e.g. roughened lining carrier, mating profiles on friction material and lining carrier

Definitions

  • the invention relates to a brake caliper brake according to the preamble of claim 1 and associated brake pads.
  • a generic fixed caliper brake is disclosed in the published patent application DE 41 31 130 AI.
  • the two brake linings are arranged on both sides of the brake disc in a shaft inside the brake housing so that they can be removed radially and can be pressed against the brake disc by means of hydraulic actuating devices provided on both sides of the brake disc.
  • the brake pads are guided axially by a retaining pin and are tangential to the axially extending, protruding pad supports in the housing for the transmission of the peripheral forces during the braking process.
  • the disadvantage of such brakes lies in their considerable noise development during braking. This noise development can be attributed to the vibration excitation of the entire brake due to fluctuations in the frictional force between the brake lining and the brake disc.
  • EP 0 163 030 B1 also discloses brake linings which can be used, for example, in a generic fixed caliper brake and have through holes in the backing plate which are filled by the friction lining mass. These through holes, on the other hand, are used less for noise control and more for a shear-proof connection of the friction lining and back plate.
  • the object of the invention is to reduce the noise development in fixed caliper brakes by means of targeted measures on the brake housing and on the brake lining, which influence the vibration behavior of the entire brake without causing additional component expenditure or additional weight on the brake.
  • the invention consists in specifically reducing the material rigidity at suitable points on the brake housing and also on the brake pads in order to create subsystems damped on the brake, which create the overall vibration of the Reduce the fixed caliper brake and prevent noise.
  • One embodiment of the invention provides an axially extending pin as a lining support, which can swing both radially and tangentially.
  • the axially extending lining support has a radially extending groove on the side facing the hydraulic actuation device, which reduces the housing rigidity in the axial direction.
  • the rigidity of the brake pad backplate is also reduced on the brake pads by making through holes. These through holes are located in the vicinity or directly on the tangential face of the back plate and are either filled with friction lining or with another material with good damping properties. The remaining radial webs of the lining back plate together with the filled through holes form tangentially acting, damped vibration systems, which transmit the vibration excitation during braking only to the housing in a strongly damped manner.
  • plastic parts are preferably used as filling material for the through-holes, which in one variant are introduced directly into the associated through-holes on the tangential end face of the lining backing plate, precisely at the point that comes into contact with the housing-fixed lining support. This results in the greatest damping effects.
  • At least one vibration damper is provided on the brake housing, which is integrally connected to the brake housing.
  • This vibration damper is arranged such that it can vibrate in relation to the brake housing and can thus reduce the overall vibration of the fixed caliper brake.
  • the vibration damper is connected either via a web small cross-section directly when casting the brake housing or by massive casting with subsequent machining of the cast housing.
  • Fig. 1 is a view of a housing part
  • Fig. 2 is a partial view of the pad support of the
  • FIG. 3 is a partially sectioned plan view of a housing part of a fixed caliper brake
  • FIG. 4 is a partial view of a brake pad with an elongated through hole and a lateral opening of the through hole to the edge of the back plate
  • FIG. 5 is a partial view of a brake pad with a round through hole and a lateral opening of the through hole to the edge of the back plate
  • FIG. 6 is a partial view of a brake pad with a through hole directly on the tangential face of the pad back plate
  • Fig. 8 two views of a brake pad with two slot-like through holes, a round Through hole and a frame-shaped covering back plate,
  • Fig. 10 is a view from the outside of a brake housing part with integrated vibration absorbers.
  • FIG. 1 shows a brake housing part 1 of a two-part brake caliper.
  • a brake housing part 1 which is arranged on both sides of the brake disc, not shown, contains a hydraulic actuating device 2, which is able to press a brake pad, also not shown, onto the brake disc.
  • the brake pads are accommodated in a shaft 3 open radially outwards in the brake housing.
  • the linings are supported on axially extending, peg-shaped lining systems 4. These lining systems 4 are connected essentially only at the end 5 facing away from the brake disc in the radially open shaft 3 by casting on the brake housing. This means that they can vibrate both radially and tangentially.
  • the vibrations transmitted by the brake linings via the lining systems 4 to the brake housing 1 due to fluctuations in the frictional force during the braking intervention are reduced as a result of natural material damping of the vibrating lining systems 4.
  • the peg-shaped lining systems 4 thus represent independently vibrating subsystems that reduce the vibration of the entire fixed-caliper brake and thus prevent the generation of brake noises.
  • FIG. 2 shows a partial view of a lining system 4 of the brake housing part 1 from FIG. 1 from the viewing direction A. It illustrates the reduction in the material rigidity of the Pad system 4 compared to previous pad supports, which are connected to the brake housing almost over their entire length (dashed line in FIG. 2).
  • the lowering of the material rigidity on the lining system 4 allows it to perform independent vibrations as a subsystem of the fixed caliper brake, which vibrations are only transferred to the fixed caliper housing to a small extent and are additionally damped by the material damping properties of the material system 4.
  • Fig. 3 an embodiment of the fixed caliper brake with brake pad 6 is shown in a partially sectioned plan view.
  • the brake lining 6, which consists of the friction lining 7 and the backing plate 8, is supported on the lining system 4 which tangentially delimits the radially outward shaft 3.
  • a radially extending groove 9 is formed at the end 5 of the axially extending lining system 4, which faces the hydraulic actuating device 2.
  • This groove 9 is preferably formed directly when the housing 1 is cast, but can also be produced by a machining process.
  • the groove 9 causes a reduced rigidity of the brake housing and thus allows the lining system 4 to vibrate in the axial direction. Furthermore, the groove 9 weakens the transmission of the vibration excitation during the braking process from the brake pad 6 via the pad system 4 to the brake housing 1.
  • FIGS. 4 to 8 show examples of differently designed brake pads 6 for fixed-caliper brakes. 4 to 6, only half a brake pad 6 is shown, since the entire brake pad is mirror-symmetrical. All of the covering shapes shown have at least one through hole in their covering back plate 8 in the vicinity of the tangential end faces 11.
  • the through holes 10, 12 each have an opening 13 to the edge of the lining back plate and are filled with friction lining mass 7.
  • the radial extent of the through holes 10, 11 extends at least over the region of the tangentially projecting contact surfaces 14 of the lining back plate 8, via which the brake lining 6 is supported on the brake housing.
  • the through hole is designed as an elongated hole 10 extending radially over almost the entire length of the brake pad back plate with opening 13 to the radially inner back plate edge.
  • a thin web 15 remains at the tangential end of the lining back plate, which can oscillate in the tangential direction and acts like a spring element.
  • the friction lining mass 7 filling the elongated hole 10 acts in connection with the tangentially vibrating web 15 of the lining back plate 8 like a damping element and reduces the vibration which is excited by the brake intervention.
  • the brake pad 6 in Fig. 5 has in its back plate 8 a round through hole 12 at the level of the tangential contact surface 14 of the brake pad with opening 13 to the tangential edge of the back plate.
  • the web 15 and the lining mass 7 act as a filling of the through hole like a damped vibration system, which is supposed to consume part of the vibration energy in order to cause the entire brake caliper to vibrate less.
  • Fig. 6 shows a brake pad with through hole 16 directly on the tangential edge of the back plate.
  • the filling of the through hole 16, which consists of an inserted plastic part 17, directly forms the tangentially projecting contact surface 14 of the brake lining on the lining support fixed to the housing.
  • the plastic part 17, which is of course made of a different material with good Damping properties can exist, has primarily a damping function with respect to the vibration excitation during braking.
  • other filler materials that have good damping properties for example plastic, can be used in an analogous manner.
  • FIG. 7 shows two views of a brake lining which has rectangular through holes 18 filled with friction lining mass 7, which are surrounded by the backing plate 8 in the form of a closed frame.
  • the three radially extending webs 15 of the back plate are oscillatable as resilient elements in the tangential direction. Their vibration, which is caused by the brake intervention, is damped to a high degree by the filling 7 of the large through holes 18 and thus prevents the generation of braking noises.
  • FIG. 8 shows two views of a brake lining with three through holes 19, 20, all of which are filled with friction lining mass 7.
  • Two through holes are formed in the vicinity of the tangential end face 11 of the back plate as radial elongated holes 19, while the third through hole 20 has a round contour approximately in the middle of the back plate.
  • This version with three through holes 19, 20 increases the number of radially extending webs 15 of the back plate and thus also the number of tangentially resilient elements, which has a favorable effect on the damping vibration behavior of the brake pad.
  • the brake linings explained here are additionally equipped with a damping plate (not shown), for example made of sheet metal, on the back of the back plate.
  • a damping plate for example made of sheet metal
  • FIGS. 9 and 10 show brake housings 1 of fixed caliper brakes which have integrated vibration absorbers 21.
  • the vibration absorbers 21 are each integrally attached to the brake housing 1 via a connecting section 22 with a small material cross section.
  • the vibration absorbers 21 are capable of oscillating with respect to the brake housing 1.
  • the integrated vibration damper 21 not only affects the natural frequency of the entire fixed-caliper brake but also directly consumes a part of the vibration energy of the overall system by the vibration damper 21 which oscillates in braking operation. The vibration of the entire brake can thus be reduced and the generation of braking noises is avoided.
  • the direction of vibration 23 of the vibration absorber 21 can be selected more or less freely by the design of the connecting sections 22 and the location of the connection to the brake housing.
  • the vibration absorbers 21 are molded when casting the brake housing 1.
  • the configuration of the connecting section 22 as a thin web 24 is ideally provided directly during the casting and does not require any further processing step.
  • the vibration damper 21 can also be cast onto the brake housing 1 in a massive manner and only the connecting section 22 with a small cross section can be produced in a subsequent machining process.
  • a material is removed by making an incision 25 or a groove on the connecting section 22 between the vibration damper 22 and the brake housing 1, and the material stiffness of the connecting section 22 is thus decisively reduced.
  • An elastic connecting section 22 is created, which enables oscillation damper 21 to oscillate relative to the brake housing.
  • vibration absorbers are not limited to the type of fixed caliper brake listed here.
  • vibration damping e.g. brake holders, floating calipers, frame calipers, etc.

Landscapes

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

Abstract

L'invention concerne un frein à étrier fixe dans lequel, en vue de réduire les bruits lors du freinage, la rigidité du matériau est abaissée en des points appropriés du corps de frein (1) et des plaquettes de frein (6), ce qui contribue ainsi à former sur le frein, des systèmes partiels à oscillations amorties. Ces dispositions se répercutent par un effet neutre, dans une large mesure, sur le poids, et réduisent les vibrations de l'ensemble du frein, ce qui atténue les bruits lors du freinage.
EP97905056A 1996-02-24 1997-02-19 Frein a etrier fixe et plaquettes de frein appropriees Withdrawn EP0879364A2 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19607056A DE19607056A1 (de) 1996-02-24 1996-02-24 Festsattelbremse mit zugehörigen Bremsbelägen
DE19607056 1996-02-24
DE1996135838 DE19635838A1 (de) 1996-09-04 1996-09-04 Festsattelbremse mit zugehörigen Bremsbelägen
DE19635838 1996-09-04
PCT/EP1997/000785 WO1997031195A2 (fr) 1996-02-24 1997-02-19 Frein a etrier fixe et plaquettes de frein appropriees

Publications (1)

Publication Number Publication Date
EP0879364A2 true EP0879364A2 (fr) 1998-11-25

Family

ID=26023213

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97905056A Withdrawn EP0879364A2 (fr) 1996-02-24 1997-02-19 Frein a etrier fixe et plaquettes de frein appropriees

Country Status (3)

Country Link
EP (1) EP0879364A2 (fr)
JP (1) JP2000506247A (fr)
WO (1) WO1997031195A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19903757A1 (de) * 1999-01-30 2000-08-24 Ruetgers Automotive Ag Verfahren und Vorrichtung zum Vermindern bzw. Vermeiden der Geräuschentwicklung von Reibungsbremsen und -kupplungen
DE19925004A1 (de) * 1999-05-31 2000-12-07 Porsche Ag Bremssattel für eine Scheibenbremsanlage
DE10331052B4 (de) 2003-07-09 2018-07-12 Volkswagen Ag Bremsbelagrückenplatte für einen Bremsbelag einer Fahrzeug-Scheibenbremse
JP4677757B2 (ja) * 2004-10-13 2011-04-27 トヨタ自動車株式会社 ディスクブレーキ用パッド

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE625643A (fr) * 1961-12-06
FR1340988A (fr) * 1962-09-15 1963-10-25 Ferodo Sa Patin de frottement pour frein à disque
DE1425391B1 (de) * 1963-09-03 1970-09-17 Textar Gmbh Bremsbacke fuer Teilbelagscheibenbremse
US3357523A (en) * 1966-01-24 1967-12-12 Bendix Corp Restraint system for disc brake noise reduction
GB1310843A (en) * 1969-09-03 1973-03-21 Aisin Seiki Spot disc brakes
FR2171562A5 (fr) * 1972-02-07 1973-09-21 Ferodo Sa
GB2061428B (en) * 1979-10-19 1983-06-22 Lucas Industries Ltd Friction pad assemblies for vehicle disc brakes
JPS57163736A (en) * 1981-03-31 1982-10-08 Nissin Kogyo Kk Disk brake for vehicle
DE3333670C2 (de) * 1983-09-17 1986-06-19 Daimler-Benz Ag, 7000 Stuttgart Schwimmsattelbremse für Kraftfahrzeuge
JPS60151432A (ja) * 1984-01-18 1985-08-09 Akebono Brake Ind Co Ltd デイスクブレ−キのノイズ防止方法
DE3736126A1 (de) * 1987-10-26 1989-05-11 Porsche Ag Bremsvorrichtung
DE3918369A1 (de) * 1989-01-31 1990-08-02 Teves Gmbh Alfred Scheibenbremse
DE4020668A1 (de) * 1990-06-29 1992-01-02 Teves Gmbh Alfred Geraeuscharmer schwimmsattel fuer teilbelagscheibenbremsen
DE4418955B4 (de) * 1994-05-31 2004-01-29 Bayerische Motoren Werke Ag Festsattel-Teilbelagsscheibenbremse für Kraftfahrzeuge
DE4435669A1 (de) * 1994-10-06 1996-04-11 Textar Gmbh Scheibenbremse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9731195A3 *

Also Published As

Publication number Publication date
WO1997031195A2 (fr) 1997-08-28
WO1997031195A3 (fr) 1997-12-04
JP2000506247A (ja) 2000-05-23

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