WO2015075095A1 - Reibbelaganordnung für eine scheibenbremse - Google Patents
Reibbelaganordnung für eine scheibenbremse Download PDFInfo
- Publication number
- WO2015075095A1 WO2015075095A1 PCT/EP2014/075062 EP2014075062W WO2015075095A1 WO 2015075095 A1 WO2015075095 A1 WO 2015075095A1 EP 2014075062 W EP2014075062 W EP 2014075062W WO 2015075095 A1 WO2015075095 A1 WO 2015075095A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- friction lining
- back plate
- absorber system
- absorber
- friction
- Prior art date
Links
- 239000002783 friction material Substances 0.000 claims abstract description 5
- 239000006096 absorbing agent Substances 0.000 claims description 40
- 230000005284 excitation Effects 0.000 claims description 5
- 230000007704 transition Effects 0.000 claims description 2
- 230000000284 resting effect Effects 0.000 claims 1
- 238000010521 absorption reaction Methods 0.000 abstract 2
- 210000002414 leg Anatomy 0.000 description 11
- 230000010355 oscillation Effects 0.000 description 7
- 229910000831 Steel Inorganic materials 0.000 description 4
- 238000013016 damping Methods 0.000 description 4
- 239000010959 steel Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004080 punching Methods 0.000 description 2
- 210000000689 upper leg Anatomy 0.000 description 2
- 208000001431 Psychomotor Agitation Diseases 0.000 description 1
- 206010038743 Restlessness Diseases 0.000 description 1
- 241000251131 Sphyrna Species 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 238000004026 adhesive bonding Methods 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F16D65/02—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
- F16D65/0006—Noise or vibration control
- F16D65/0018—Dynamic vibration dampers, e.g. mass-spring systems
Definitions
- Friction lining arrangement for a disc brake The invention relates to a structure such as, in particular, a
- Friction lining arrangement for a disc brake according to the preamble of claim 1.
- vibrations When braking, vibrations always occur to a certain extent.
- the vibrations are intermittent
- noise may occur that is undesirable as a comfort-reducing phenomenon.
- me ⁇ chanical effects such as restlessness or steering vibration on body components
- the acoustic effects are felt particularly uncomfortable.
- a vibration control "detuning" of the system can be achieved.
- the additional mass vibrates together with the remaining structure in amplitude and frequency.
- a disadvantage is that the additional mass has to be relatively large be ⁇ measure, thus causing weight disadvantages.
- the invention is therefore based on the object to enable a more favorable and more efficient noise reduction, which does not unnecessarily increase the vehicle mass and also opens up advantageous manufacturing processes, without compromising the performance characteristics and space requirements of a vehicle disc brake.
- a disc brake with at least one vibration-changing element is proposed to Prevent brake noise.
- a measure is proposed which relates to a brake shoe with hammerhead-shaped sequels.
- at least one additional mass is rigidly placed on the hammerhead-shaped continuation of the back plate.
- a round steel which is mounted in a bore through a center of the hammer head so that Eigenfre ⁇ frequencies detuned respectively. can be shifted against each other and ideally be set so that they do not reinforce each other.
- the fastening of the round steel takes place for example by gluing, riveting, pressing, welding or screwing into the bore of the back plate.
- the invention therefore proposes a novel, separately oscillating to the structure, absorber system.
- the proposed measure serves the purpose of at least reducing or eliminating as completely as possible noise-relevant oscillations in the circumferential direction and / or axial or other oscillation plane in a given frequency range by depriving the oscillating structure of energy, because at the same time a damping system is separately excited.
- This is the structure (friction lining) of a total mass a novel
- Tilgersystem T provided which comprises a spring having a predetermined spring stiffness and the suspended thereon, predetermined partial mass, which are coordinated with each other, and is arranged by a slender leg separately from the structure S elastically oscillating on the structure.
- This novel absorber system includes a spring function (eg in leg SL integrated) and a mass. It serves to extinguish a specific disturbing frequency / frequency band of the structure S.
- the absorber system can be integrated with a component of the structure S, that is to say be provided integrally therewith, or alternatively the absorber system T is attached to the structure as a separate assembly as shown in FIG. 2-6 shown.
- this absorber system is based on the basic principle that the mass of the absorber system by the excitation on the basis of the to be combated, defined frequency / frequency bands performs a separate, forced oscillation with a separate amplitude, while the vibration of the structure by the excitation of the absorber system withdrawn vibrational energy becomes .
- vibration cancellation occurs at rest or at a vibration amplitude AS of subordinate intensity.
- a damping component or function may additionally be provided integrated without departing from the invention.
- the additional mass on the slender leg is placed between a central portion of a back plate and a hammerhead-shaped protrusion or on the hammerhead-shaped protrusion and is arranged to vibrate separately therefrom.
- Fig. 1 shows a symmetrical friction lining 1 comprising a back plate 2.
- the back plate 2 is largely planar and has a central portion 3 with a friction material 4 adhered substantially centrally thereon.
- Slender legs extend in a plane with the central portion 3 and tangentially projecting laterally therefrom (connecting portions) 5,6 which carry the thickened, hammer-head-shaped projections 7, 8.
- the hammerhead-shaped projections 7, 8 are formed so that their body has radially outward, and wherein the slender legs 5, 6 carry the thickened body of the hammer heads 7, 8.
- These elements are thus arranged to a certain extent as legs arranged at right angles to one another, and in principle describe the shape of a L pointing radially outwards.
- the hammerhead-shaped projections 7, 8 are connected to the central section 3 via the legs 5, 6.
- a damper system 9 comprising a spring-mass arrangement is attached to the back plate 2, which is effectively effective as Tilgersystem 9 by targeted constructive predetermined design of a spring stiffness kF and a correspondingly tuned mass MT that of the structure of the friction lining 1 disturbing vibrational energy.
- An integrally inte grated ⁇ configuration can be manufactured in one operation in a particularly simple manner during the stamping process of a back plate. 2 Apart from the cost of materials, this is cost-neutral, and if necessary. Stamping waste can be avoided.
- the exact design of the absorber system and its function is as follows: In order to effectively combat interfering vibrations on the friction lining 1, the vibration modes, in particular their amplitude and frequency, must be known. The determination of these quantities can be done experimentally or mathematically.
- the absorber system is dimensioned and used to determine the structure of the vibration energy of a given fre- frequency / frequency bands.
- the absorber system 9 consisting of damper mass MT and spring kf, is set in a targeted manner to the frequency f to be eliminated, amplitude A and oscillation plane / direction.
- TilgerSystems 9 on the structure takes place in the area of a spring base point Ff.
- the absorber system 9 is in turn excited to vibrate relative to effect separate countervailing oscillations to the structure.
- the result of this energization of the damping system 9 is that the structure of the oscillations störgehoffschspeisende ⁇ supply energy is removed so that the (usually inaudible) can not be performed disturbing the relative vibration damping system. 9 Accordingly, according to the amount of energy removal, a disturbing sound radiation of the structure decreases or is completely extinguished.
- Tilgersystem 9 a one-piece component of the back plate 2, which is integrally formed during the manufacturing process (punching) of the back plate 2 without additional effort.
- Absorber mass and Tilgerfeder be shown in FIG. 1 defined by suitable design / design of your geometry so that the desired natural frequency results in the desired particular tangentially directed direction of vibration.
- the connection between the mass and the structure is designed and defined as a largely flexible Tilgerfeder.
- Your Stiff ⁇ accuracy is determined by a Elasti zticiansmodul ckenplattentechnikstoff from RUE and by the physical Randbe ⁇ conditions and the geometry of the defining parameters.
- the masses and their (spring) stiffness are in a defined Relationship to each other to ensure the required excitation / natural frequency.
- the absorber system 9 can be simply portrayed in this punching as an integral part of the back plate 2.
- a damper D and or a damper component can be inserted integrated parallel to the Tilgerfeder integrated.
- the spatial axes t, ax, r in the figures define tangential direction, axial direction and radial direction in each case with respect to a wheel rotation axis which is normalized as the axial direction.
- the expanded diameter portion 12 is located with the attachment of the mounting pin 11 on the Reibelagseite the back plate 2.
- the absorber system 9 is characterized separately vibratory placed on a reibbelagabgewandten side of the back plate 2. Due to the proximity of the
- the energy transfer is optimized.
- the absorber system 9 is particularly efficient, lightweight and space-saving.
- vibration U vibrations from the absorber system 9
- r vertical axis
- the Fig. 6 based on such, additional elasticity without preferential orientation and allows a particularly effective and at the same time lightweight so economical variant using a special interface between Tilgersystem 9 and back plate 2.
- This particularly flexible connection of the absorber mass MT can in comparison with the solutions according to Figures 1- 5 be formed with reduced weight.
- the Tilger stresses 14 has a thickened foot 15 with a paragraph 17 for attachment to the back plate 2, and wherein Tilger stresses 14 and foot 15 are connected to each other via a particularly elastic, designed as a round connecting portion 16.
- This symmetrical and very thin round pin allows while oscillations, without predetermining a preferred orientation.
- the absorber system 9 is manufactured as a shaft-symmetrical, cylindrical rotary part from a round steel, wherein the connecting section 16 is formed by a groove 18 cut in the radial direction, comprising groove flanks 19, 20 and a groove base 21. In a transition region between groove flanks 19, 20 and groove base 21, in each case a rounding with a radius 22 is provided.
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016533157A JP6303010B2 (ja) | 2013-11-21 | 2014-11-19 | ディスクブレーキの為の摩擦ライニング装置 |
KR1020167016279A KR102361419B1 (ko) | 2013-11-21 | 2014-11-19 | 디스크 브레이크용 마찰 라이닝 배열체 |
US15/036,258 US9890823B2 (en) | 2013-11-21 | 2014-11-19 | Friction lining arrangement for a disk brake |
EP14799498.2A EP3071860B1 (de) | 2013-11-21 | 2014-11-19 | Reibbelaganordnung für eine scheibenbremse |
MX2016006345A MX2016006345A (es) | 2013-11-21 | 2014-11-19 | Disposicion de forro de friccion para freno de disco. |
CN201490001180.9U CN205991116U (zh) | 2013-11-21 | 2014-11-19 | 具有质量块的摩擦块 |
CA2930903A CA2930903C (en) | 2013-11-21 | 2014-11-19 | Friction lining arrangement for a disk brake |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013223862.2 | 2013-11-21 | ||
DE102013223862 | 2013-11-21 | ||
DE102014205232.7 | 2014-03-20 | ||
DE102014205232.7A DE102014205232B4 (de) | 2013-11-21 | 2014-03-20 | Reibbelaganordnung für eine Scheibenbremse |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015075095A1 true WO2015075095A1 (de) | 2015-05-28 |
Family
ID=51903937
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/075062 WO2015075095A1 (de) | 2013-11-21 | 2014-11-19 | Reibbelaganordnung für eine scheibenbremse |
Country Status (9)
Country | Link |
---|---|
US (1) | US9890823B2 (de) |
EP (1) | EP3071860B1 (de) |
JP (1) | JP6303010B2 (de) |
KR (1) | KR102361419B1 (de) |
CN (1) | CN205991116U (de) |
CA (1) | CA2930903C (de) |
DE (1) | DE102014205232B4 (de) |
MX (1) | MX2016006345A (de) |
WO (1) | WO2015075095A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202013012442U1 (de) * | 2013-10-21 | 2016-11-23 | Federal-Mogul Bremsbelag Gmbh | Trägerkörper für einen Bremsbelag einer Scheibenbremse mit Tilgermasse zur Veränderung der Schwingung |
ITUA20163645A1 (it) | 2016-05-20 | 2017-11-20 | Freni Brembo Spa | Assieme di pastiglia, corpo pinza e pinza freno per freno a disco |
US11060503B2 (en) * | 2018-03-13 | 2021-07-13 | Wind Solutions, Llc | Yaw pad engagement features |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3918369A1 (de) * | 1989-01-31 | 1990-08-02 | Teves Gmbh Alfred | Scheibenbremse |
EP2174034A1 (de) * | 2007-06-27 | 2010-04-14 | Freni Brembo S.p.A. | Belag für scheibenbremsen |
DE102010037034A1 (de) * | 2010-08-18 | 2012-02-23 | Tmd Friction Services Gmbh | Belaghaltevorrichtung mit Schwingungstilger |
US20120111693A1 (en) * | 2009-04-02 | 2012-05-10 | Ford Global Technologies Llc | Method of Manufacturing a Transmission Clutch Assembly with Reduced Squawk |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1927135A1 (de) * | 1968-09-06 | 1970-03-19 | Sumitomo Electric Industries | Bremsbacke fuer Scheibenbremsen |
JPS5818138U (ja) * | 1981-07-29 | 1983-02-04 | 日本ブレ−キ工業株式会社 | ブレ−キ |
JPS594832U (ja) * | 1982-06-30 | 1984-01-12 | 三菱自動車工業株式会社 | デイスクパツドの構造 |
US4528739A (en) * | 1983-04-01 | 1985-07-16 | Atwood Vacuum Machine Company | Rivet and method of using the same |
WO1989011046A1 (en) | 1988-05-07 | 1989-11-16 | Alfred Teves Gmbh | Disk brake with partial lining |
DE4127113A1 (de) | 1991-08-16 | 1993-02-18 | Teves Gmbh Alfred | Bremsbacke fuer eine teilbelagscheibenbremse |
CA2174088A1 (en) | 1994-09-02 | 1996-03-14 | Shinichi Tanaka | Drum brake |
DE19524736A1 (de) | 1995-07-07 | 1997-01-09 | Bayerische Motoren Werke Ag | Bremsbacke für eine Scheibenbremse eines Kraftfahrzeugs |
ATE409816T1 (de) | 2000-08-07 | 2008-10-15 | Freni Brembo Spa | Bremsbelag für scheibenbremse |
DE10218907A1 (de) | 2002-04-26 | 2003-12-04 | Tmd Friction Europe Gmbh | Fahrwerk-Baugruppe für Kraftfahrzeuge |
DE10305308A1 (de) * | 2002-10-10 | 2004-04-22 | Feldmann, Michael | Ausgleichsgewicht für einen Bremsbelagträger |
US7032723B2 (en) * | 2002-10-22 | 2006-04-25 | Ford Global Technologies, Llc | Brake assembly with tuned mass damper |
DE60317116T2 (de) * | 2003-12-30 | 2008-08-07 | Freni Brembo S.P.A., Curno | Bremsbelag und -sattel für scheibenbremse |
US20060266599A1 (en) * | 2005-05-26 | 2006-11-30 | Eric Denys | Control of brake noise by tuned mass dampers |
JP4714642B2 (ja) * | 2005-08-31 | 2011-06-29 | 曙ブレーキ工業株式会社 | ディスクブレーキパッド |
GB0714056D0 (en) * | 2007-07-19 | 2007-08-29 | Automotive Prod Italia Sv Srl | Drum brakes |
DE102008013268A1 (de) * | 2007-10-09 | 2009-04-16 | Continental Engineering Services Gmbh | Bremsbelag für eine Teilbelag-Scheibenbremse |
JP2011017371A (ja) | 2009-07-08 | 2011-01-27 | Nissin Kogyo Co Ltd | 車両用ディスクブレーキ |
JP2011247422A (ja) * | 2011-07-01 | 2011-12-08 | Freni Brembo Spa | ディスクブレーキのためのブレーキパッド |
DE102012209335A1 (de) | 2012-06-01 | 2013-12-05 | Continental Teves Ag & Co. Ohg | Verbundkörper für eine Kraftfahrzeugbremse |
DE102013111594B4 (de) * | 2013-10-21 | 2015-04-30 | Federal-Mogul Bremsbelag Gmbh | Verfahren zur Herstellung eines Trägerkörpers mit Tilgermasse zur Veränderung der Schwingung für einen Bremsbelag einer Scheibenbremse |
DE202013012442U1 (de) * | 2013-10-21 | 2016-11-23 | Federal-Mogul Bremsbelag Gmbh | Trägerkörper für einen Bremsbelag einer Scheibenbremse mit Tilgermasse zur Veränderung der Schwingung |
-
2014
- 2014-03-20 DE DE102014205232.7A patent/DE102014205232B4/de active Active
- 2014-11-19 US US15/036,258 patent/US9890823B2/en active Active
- 2014-11-19 KR KR1020167016279A patent/KR102361419B1/ko active IP Right Grant
- 2014-11-19 WO PCT/EP2014/075062 patent/WO2015075095A1/de active Application Filing
- 2014-11-19 JP JP2016533157A patent/JP6303010B2/ja active Active
- 2014-11-19 EP EP14799498.2A patent/EP3071860B1/de active Active
- 2014-11-19 CA CA2930903A patent/CA2930903C/en active Active
- 2014-11-19 CN CN201490001180.9U patent/CN205991116U/zh active Active
- 2014-11-19 MX MX2016006345A patent/MX2016006345A/es active IP Right Grant
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3918369A1 (de) * | 1989-01-31 | 1990-08-02 | Teves Gmbh Alfred | Scheibenbremse |
EP2174034A1 (de) * | 2007-06-27 | 2010-04-14 | Freni Brembo S.p.A. | Belag für scheibenbremsen |
US20120111693A1 (en) * | 2009-04-02 | 2012-05-10 | Ford Global Technologies Llc | Method of Manufacturing a Transmission Clutch Assembly with Reduced Squawk |
DE102010037034A1 (de) * | 2010-08-18 | 2012-02-23 | Tmd Friction Services Gmbh | Belaghaltevorrichtung mit Schwingungstilger |
Also Published As
Publication number | Publication date |
---|---|
KR102361419B1 (ko) | 2022-02-09 |
MX2016006345A (es) | 2016-08-03 |
US20160281805A1 (en) | 2016-09-29 |
DE102014205232B4 (de) | 2015-07-16 |
JP2016537588A (ja) | 2016-12-01 |
US9890823B2 (en) | 2018-02-13 |
EP3071860B1 (de) | 2020-01-15 |
CN205991116U (zh) | 2017-03-01 |
KR20160088390A (ko) | 2016-07-25 |
DE102014205232A1 (de) | 2015-05-21 |
EP3071860A1 (de) | 2016-09-28 |
JP6303010B2 (ja) | 2018-03-28 |
CA2930903C (en) | 2018-06-19 |
CA2930903A1 (en) | 2015-05-28 |
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