US20030127292A1 - Brake component, disc brake, drum brake, and method for manufacturing a brake component - Google Patents

Brake component, disc brake, drum brake, and method for manufacturing a brake component Download PDF

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Publication number
US20030127292A1
US20030127292A1 US10/248,290 US24829003A US2003127292A1 US 20030127292 A1 US20030127292 A1 US 20030127292A1 US 24829003 A US24829003 A US 24829003A US 2003127292 A1 US2003127292 A1 US 2003127292A1
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US
United States
Prior art keywords
brake
brake member
contact surface
side surfaces
recited
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.)
Abandoned
Application number
US10/248,290
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English (en)
Inventor
Johan Hulten
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.)
Volvo Truck Corp
Original Assignee
Volvo Lastvagnar AB
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 Volvo Lastvagnar AB filed Critical Volvo Lastvagnar AB
Assigned to VOLVO LASTVAGNAR AB reassignment VOLVO LASTVAGNAR AB ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HULTEN, JOHAN
Publication of US20030127292A1 publication Critical patent/US20030127292A1/en
Priority to US11/306,376 priority Critical patent/US7322448B2/en
Abandoned legal-status Critical Current

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    • 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • 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
    • 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
    • F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/007—Auxiliary mechanisms for non-linear operation

Definitions

  • the present invention relates to a brake member or arrangement that includes a backing plate carrying a brake lining which exhibits at least one contact surface and side surfaces surrounding that contact surface and in which the side surfaces are connected to the contact surface and to the backing plate. More particularly, the invention relates to a brake member where the occurrence of brake squeal can be reduced by means of the design of a brake lining, particularly by design of the side surfaces of the brake lining.
  • TECHNICAL BACKGROUND When engaging the brakes of a vehicle, sometimes so called brake squeal is created. This effect is something that occurs both where disc and drum brakes are concerned. Typical frequencies of this noise are around a few kHz and within the sensitivity range of human hearing. The squeal noise that is produced decreases as the distance increases from the sound source, but can still be approximately 140 dB when close to the braking device. Most people will appreciate that city buses which stop at frequent intervals within densely populated areas, can be particularly disturbing. One frequent reason for complaint on new private cars, lorries and buses is brake squeal, including in association with ABS-braking systems. Even if brake squeal does not influence the braking power, and in turn safety, the problem is still of great importance because it is annoying to the customer, and therefore merits solution.
  • US 5145037 discloses a disc brake where the occurrence of brake squeal is intended to be reduced by means of beveling end regions of the brake disc within a region, the extension of which is dependent on the width between claws included in a brake yoke carrying a backing plate where the brake lining is arranged.
  • An object of the present invention is to provide a brake member where the occurrence of brake squeal when a fluctuating load being applied onto the brake member is reduced.
  • This object is achieved by means of a brake member or arrangement that includes a backing plate carrying a brake lining which exhibits at least one contact surface and side surfaces surrounding that contact surface and in which the side surfaces are connected to the contact surface and to the backing plate.
  • the contact surface is adapted so that it exhibits an edge area surrounding the contact surface and in which at least a portion of the edge area exhibits a local deformation stiffness in a direction vertical to a plane through the contact surface which differs, at most, fifteen percent from the deformation stiffness in a central area in the interior of the contact surface.
  • Further objects of the invention are to provide this effect in different types of brake members including disc- and drum-style brakes that can suffer from the occurrence of brake squeal when applying a fluctuating load onto the brake member.
  • Still another object of the invention is to provide a method for manufacturing brake members where the occurrence of brake squeal when applying a fluctuating load onto the brake member is reduced.
  • Fig. 1 demonstrates exemplary deformation of a known brake lining when subjected to an equilibrium load, a larger and a smaller load;
  • FIG. 2 illustrates the pressure distribution of a known brake lining when subjected to an equilibrium load, a larger and a smaller load
  • FIG.3 is a perspective view of a brake lining configured according to the present invention.
  • Fig.4 is a graphical representation of deformation ratio as a function of the inclination of a side surface
  • FIG.5 is a cross-sectional view of a brake member configured according to the present invention.
  • FIG.6 is a cross-sectional view of an alternative embodiment of a brake member configured according to the invention.
  • a brake lining When a brake lining connects brake disc, alternatively brake drum, and brake lining, the connected modes are divided into separate natural frequencies of the system. Non-conservative forces, such as for example frictional forces, tend to connect these separate modes and join them into a common natural frequency in which brake squeal may arise. Accordingly, in order to prevent the creation of brake squeal, the system has to be designed such that a separation of a set of modes that primarily exhibit natural frequencies between 1 and 15 kHz can be maintained. The connection, and thereby the occurrence of brake squeal, can occur for a number of different natural frequencies and is dependent on the interaction between brake lining and brake member, including either disc or drum configurations.
  • Fig. 1 shows a symbolic representation of a known brake member 1 which interacts with a brake disc 2.
  • the brake member includes a brake lining 3 and a backing plate 4.
  • the brake lining 3 exhibits a first and a second contact surface 5a, 5b, which are intended to press against the brake disc 2 or, whenever applicable, against a brake drum.
  • the brake lining 3 exhibits a groove 6 that delimits the contact surface 5a from the contact surface 5b.
  • Fig. 1 An equilibrium condition
  • Fig. 2 schematically illustrates the pressure distribution across the contact surfaces during the run-in condition where the contact surface or surfaces of the brake lining are flat as is shown by the continuous line.
  • FIG. 1 shows deformation of the brake lining 3, with dashed lines, when it is pressed against a brake disc 2 or, whenever applicable, a brake drum with a force which is smaller than the particular force resulting in the above-mentioned flat equilibrium condition.
  • the contact surface of the brake disc is displaced from the initial position 7 into a second position 7'.
  • local deformation stiffness means the spring constant in a locally delimited area in the direction of the normal to the contact surface. Studies have shown that the spring constant of a homogenous material is lower at an edge region having vertical side surfaces than in regions having inclined side surfaces or in an inner region at a distance from the edge of the homogenous material. This means that the spring constant at the groove 6 located in the brake lining 3 exhibits a lower deformation stiffness than in an inner region of the brake lining.
  • the brake lining 3 exhibits a higher deformation stiffness at the beveled flanks 8 than in the inner region of the brake lining. This results in the brake lining bulging outwards at the region (I) located closest to said groove 6, and bulging inwards at the region (III) located closest to the beveled edge 8, when subjected to the smaller load.
  • FIG. 2 shows the pressure distribution across the brake lining 3, with dashed lines, when the brake lining is loaded with a smaller load than the abovementioned certain equilibrium force. From the explanation above, it is evident that the pressure within the region (I) is higher than within the region III when a smaller load than the equilibrium load is applied onto the brake lining. The pressure distribution at the abovementioned certain force is shown with continuous lines.
  • FIG. 1 shows deformation of the brake lining 3, with dashed lines, when the brake lining is pressed against the brake disc 2 or, whenever applicable, a brake drum, with a force exceeding the above-mentioned certain force resulting in the flat equilibrium condition.
  • the contact surface of the brake disc is displaced from the initial position 7 into a third position.
  • the local deformation stiffness of the brake lining varies across the surface, different contact forces are created across the surface of the brake lining as a result of a force that differs from the above-mentioned certain force resulting in said equilibrium condition.
  • the spring constant at the groove 6 located in the brake lining 3 exhibits a lower deformation stiffness that in an inner region of the brake lining, and the brake lining 3 exhibits a higher deformation stiffness at the beveled flanks 8, 9 than in the inner region of the brake lining. This results in the brake lining bulging inwards at the region (I) located closest to the groove 6, and bulging outwards at the region (III) located closest to the beveled edge 8, when subjected to the larger load.
  • FIG. 2 shows the pressure distribution across the brake lining 3, with dashed lines, when the brake lining is loaded with a larger load than the abovementioned certain force. From the explanation above, it is evident that the pressure within the region (I) is lower than within the region (III) when a larger load than the equilibrium load is applied onto the brake lining. The pressure distribution with the above-mentioned certain force is shown with continuous lines.
  • an object of the present invention is achieved by means of providing a brake system where a brake lining exhibits a contact surface having an edge area surrounding the contact surface wherein at least a portion of the edge area exhibits a local deformation stiffness in a direction vertical to a plane through the contact surface which differs fifteen percent (15%) at most from the deformation stiffness in a central area in the interior of the contact surface.
  • FIG. 3 shows a perspective view of a brake member 1 according to the invention.
  • the brake member is arranged in a general way for interacting with a brake disc or a brake drum. Examples of such interaction and included elements necessary in order to provide a functioning braking device are well known. Exemplary arrangements are found in US 5,145,037 and GB 2 143 916, each of which are expressly incorporated by reference for purposes of disclosure of such arrangements, and which constitute an example of a disc brake where brake members according to the invention can be utilized.
  • SE 504 272 provides an example of a drum brake where brake members according to the invention can be utilized.
  • the brake member 1 includes a brake lining 3 and a backing plate 4.
  • the brake lining 3 and backing plate 4 are designed in one piece.
  • the brake lining 3 can be attached to the backing plate 4 in any way known to the skilled person.
  • the brake lining 3 constitutes a wear surface when the brake member is used for braking, and the backing plate distributes the pressure force from braking cylinders (not shown) to the brake lining when the brake member is utilized in a brake device.
  • braking cylinders not shown
  • One example of the design of a brake device having braking cylinders can be found in US 5,145,037.
  • the brake lining exhibits a first and a second contact surface 5a, 5b which are intended to be pressed against a brake disc or, whenever applicable, against a brake drum. It should be appreciated that such a disc or drum is not shown in Fig. 3, but would be positioned above the lining 3 for pressed engagement therewith. Furthermore, the brake lining 3 in this embodiment exhibits a groove 6 that delimits the contact surface 5a from the contact surface 5b.
  • the invention also can be utilized with brake linings having a single wear surface, but is particularly advantageous with brake linings having several wear surfaces separated by grooves, since the edge/area-ratio of the contact surfaces of such brake members is usually larger.
  • the contact surfaces 5a and 5b exhibit an edge area 9 including a first edge area 9a surrounding the first contact surface 5a and a second edge area 9b surrounding the second contact surface 9b.
  • the contact surfaces 5a, 5b are worn down during the life of the brake member, so that they are flat and exhibit a surface normal e z .
  • the edge area is defined as the area where the contact surfaces 5a, 5b are connected to side surfaces 10-15.
  • the side surfaces exhibit surface normals e s extending in different directions from the surface normal e z of the contact surfaces (see Figs. 5 and 6).
  • the side surfaces include a front and a rear flank 11, 12 that are beveled.
  • the flanks are introduced in order to compensate for the edge effects that arise during the force transfer from the braking cylinders to the backing plate.
  • the invention can be utilized both with brake linings designed without flanks, as well as with brake linings designed with flanks.
  • the front and rear flanks usually are designed with a surface normal which is inclined approximately fifteen degrees in relation to the surface normal e z of the contact surface.
  • said side surfaces include a first set of side surfaces 10, 13 extending between said front and rear flanks 11, 12. Whenever applicable, said side surfaces further include a second set of side surfaces 14, 15 between which the groove 6 extends.
  • Figure 4 shows a diagram of deformation ratio as a function of the inclination of a side surface. It is assumed that areas having the same local deformation stiffness will have the same contact pressure when the brake lining is subjected to different loads. Thus, the brake member should be designed such that the local stiffness is the same across the entire contact surface of a brake lining. Accordingly, the diagram shows how the deformation ratio varies with the inclination of a side surface in relation to the contact surface. The calculation has been performed for flat side surfaces having a surface normal e s which forms an angle between 74 o and 90 o with the surface normal e z of the contact surface. This means that the side surface forms a flat surface that is slightly beveled in the portion of the side surface facing the contact surface.
  • the diagram further shows preferred embodiments of the invention where the brake lining exhibits side surfaces that exhibit an angle between 78 and 86 degrees in relation to the contact surface when the deformation ratio differs by less than approximately fifteen percent (15%).
  • a further preferred embodiment of the invention is represented in which the brake lining exhibits side surfaces having an angle between 80 and 84 degrees in relation to the contact surface when the deformation ratio differs by less than approximately ten percent (10%).
  • Still another preferred embodiment of the invention is demonstrated where the brake lining exhibits side surfaces which exhibit an angle between 81 and 83 degrees in relation to the contact surface when the deformation ratio differs by less than approximately five percent (5%).
  • Figure 5 shows a cross-section of a brake member 1 according to the invention.
  • the brake member 1 exhibits a brake lining 3 and a backing plate 4.
  • the brake lining 3 exhibits a contact surface 5a having a surface normal e z .
  • the brake lining exhibits a side surface 16, which preferably is chosen optionally from said first and second set of side surfaces 10, 13-15.
  • the side surface 16 exhibits a surface normal e s .
  • the surface normal of the side surface and the surface normal of the contact surface form an angle of (90 - alpha ) degrees with each other when the brake member is in an unloaded condition.
  • the side surface 16 and the contact surface 5a are connected in an edge area 9.
  • Figure 5 shows the brake member in a condition when subjected to a heavy load, indicated with dashed lines, wherein it can be noticed that the entire contact surface 5a has been subjected to a parallel displacement into a new position 5a'.
  • a parallel displacement under constant pressure across the surface is achieved by means of giving the edge area the same local deformation stiffness as a central area 17 in the interior of the contact surface.
  • the central area 17 in the interior of the contact surface can be defined as all points on the contact surface which are at a distance from an edge 9 which exceeds the thickness H, preferably three times the thickness of the brake lining 3, as measured in the direction of the surface normal e z of the contact surface.
  • a brake member according to the present invention is achieved when configured to have side surfaces designed in an inclined manner and with a limited variation of local deformation stiffness between edge and interior of the contact surface 5a of the brake lining 3.
  • the side surface 16 is designed to be flat, which means that the edge will be stiffened to the same degree independent of how much the lining is worn down.
  • Figure 6 shows the invention according to another embodiment, where the surface normal e s of the side surface 16 varies with the distance from the backing plate 4.
  • This embodiment can be utilized when the influence of the backing plate 4 on the local deformation stiffness of the brake member 1 makes a separate compensation by means of the edge design necessary in order to obtain an edge area having a small deviation in deformation stiffness depending on the thickness and thereby the wear of the brake lining.
  • the side surface 16 is designed with an arbitrary surface normal e s within the main portion 18 of a wear area 19 within the side surface 16, which surface normal e s makes an angle between 78 and 86 degrees with an arbitrary surface normal e z within the main portion of the contact surface when the brake member is in an unloaded condition.
  • "main portion” should be understood to mean a predominant portion of at least fifty percent or more of the total article, area or portion so described.
  • the wear area is defined as the portion of the side surface that is intended to be worn down during the working life of the brake member 1.
  • the main portion 18 of the wear area can be constituted by the entire thickness of the brake lining or a local part of this, however, preferably at least 50% of the thickness of the brake lining when the brake lining is in an original condition.
  • the side surface is designed with a surface normal e s which makes a larger angle with the surface normal e z of the contact surface at portions of the side surface which are located close to the backing plate 4 than at portions which are located close to the contact surface 5a.
  • the brake lining and the backing plate are made of materials that are well known to the skilled person.
  • the invention also relates to a method for manufacturing a brake member including a backing plate carrying a brake lining which exhibits at least one contact surface and also side surfaces surrounding the at least one contact surface.
  • the side surfaces are connected partly to the contact surface and partly to the backing plate, wherein the contact surface is designed with an edge area surrounding the contact surface, wherein at least a portion of the edge area exhibits a local deformation stiffness in a direction vertical to a plane through the contact surface which differs fifteen percent (15%) at most from the deformation stiffness in a central area in the interior of the contact surface.
  • the surfaces are designed for allowing the edge area to exhibit the deformation stiffness.
  • the side surfaces are designed with an arbitrary surface normal within the main portion of a wear area within the second set of side surfaces which makes an angle to an arbitrary surface normal within the main portion of the contact surface which is between 78 - 86 degrees, preferably between 80- 84 degrees, and even more preferably 81 - 83 degrees when the brake member is in an unloaded condition.
  • a method where the brake member is formed from a material having a varying deformation stiffness, and the variation is arranged to allow a portion of the edge area to exhibit a local deformation stiffness in a direction vertical to a plane through the contact surface which differs fifteen percent (15 %) at most from the deformation stiffness in a central area in the interior of the contact surface can also be utilized.
  • the deformation stiffness differs ten percent (10%) at most, and preferably five percent (5%).
  • the invention can be utilized for different types of disc and drum brakes which are well known to the skilled person.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
US10/248,290 2000-07-06 2003-01-06 Brake component, disc brake, drum brake, and method for manufacturing a brake component Abandoned US20030127292A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/306,376 US7322448B2 (en) 2000-07-06 2005-12-26 Brake component, disc brake, drum brake, and method for manufacturing a brake component

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE0002565-0 2000-07-06
SE0002565A SE522238C2 (sv) 2000-07-06 2000-07-06 Bromsorgan, skivbroms och trumbroms avsedda att reducera bromsskrik
PCT/SE2001/001395 WO2002002961A1 (fr) 2000-07-06 2001-06-20 Element de frein, frein a disque, frein a tambour et procede de fabrication d'un element de frein

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2001/001395 Continuation WO2002002961A1 (fr) 2000-07-06 2001-06-20 Element de frein, frein a disque, frein a tambour et procede de fabrication d'un element de frein

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US11/306,376 Continuation US7322448B2 (en) 2000-07-06 2005-12-26 Brake component, disc brake, drum brake, and method for manufacturing a brake component

Publications (1)

Publication Number Publication Date
US20030127292A1 true US20030127292A1 (en) 2003-07-10

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ID=20280405

Family Applications (2)

Application Number Title Priority Date Filing Date
US10/248,290 Abandoned US20030127292A1 (en) 2000-07-06 2003-01-06 Brake component, disc brake, drum brake, and method for manufacturing a brake component
US11/306,376 Expired - Fee Related US7322448B2 (en) 2000-07-06 2005-12-26 Brake component, disc brake, drum brake, and method for manufacturing a brake component

Family Applications After (1)

Application Number Title Priority Date Filing Date
US11/306,376 Expired - Fee Related US7322448B2 (en) 2000-07-06 2005-12-26 Brake component, disc brake, drum brake, and method for manufacturing a brake component

Country Status (8)

Country Link
US (2) US20030127292A1 (fr)
EP (1) EP1299655B1 (fr)
JP (1) JP2004502111A (fr)
AT (1) ATE338224T1 (fr)
BR (1) BR0111942A (fr)
DE (1) DE60122726T2 (fr)
SE (1) SE522238C2 (fr)
WO (1) WO2002002961A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070056256A1 (en) * 2005-09-12 2007-03-15 Frederick Tepper Electrostatic air filter
CN105041928A (zh) * 2015-07-09 2015-11-11 辽宁九通摩擦材料有限公司 一种汽车盘式刹车片及其制造方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005034861B4 (de) * 2005-07-26 2011-02-03 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Schienenfahrzeugbremsvorrichtung mit selbst stabilisierenden Bremsbelägen
US8739947B2 (en) * 2011-11-30 2014-06-03 Federal-Mogul Products, Inc. Brake lining for a drum brake assembly
CN104632959B (zh) * 2014-12-09 2017-12-19 厦门市双晋材料科技有限公司 一种制备刹车片的新型模具和工艺
US10428884B2 (en) 2015-09-02 2019-10-01 Ford Global Technologies, Llc Noise reducing brake pads

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ZA794640B (en) * 1978-09-14 1980-08-27 Lucas Industries Ltd Disc brake pad assemblies
AT385824B (de) * 1979-09-06 1988-05-25 Stahl Kurt Traegerplatte fuer den belag eines reibblockes fuer scheibenbremsen
JPS60126735U (ja) * 1984-02-02 1985-08-26 曙ブレーキ工業株式会社 デイスクブレ−キ
JPS6218439A (ja) * 1985-07-17 1987-01-27 Japan Styrene Paper Co Ltd 架橋ポリエチレン系樹脂型内発泡成型体の製造方法
FR2678334B1 (fr) * 1991-06-28 1997-04-30 Carbone Ind Dispositif de plaquette de frein a disque en particulier a garniture en carbone-carbone.
FR2681925B1 (fr) * 1991-10-01 1997-09-05 Flertex Sa Plaquette de frein a disque pour chemin de fer.
JPH0893813A (ja) * 1994-09-28 1996-04-12 Mitsubishi Motors Corp ブレーキ装置
US5842546A (en) * 1996-07-03 1998-12-01 Prattville Manufacturing, Inc. Split backplate for noise suppression in brake pad assemblies
US5836428A (en) * 1997-04-28 1998-11-17 Rome Tool & Die Co. Brake shoe assembly having brake lining retainer members
US6022502A (en) * 1997-09-30 2000-02-08 Lockhart; Wayne Composite friction assembly
US6105735A (en) * 1999-01-28 2000-08-22 Lin; Ah-Ping Brake device for a bicycle
DE10041294B4 (de) * 2000-08-23 2008-06-19 Tmd Friction Gmbh Bremsbacke

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070056256A1 (en) * 2005-09-12 2007-03-15 Frederick Tepper Electrostatic air filter
CN105041928A (zh) * 2015-07-09 2015-11-11 辽宁九通摩擦材料有限公司 一种汽车盘式刹车片及其制造方法

Also Published As

Publication number Publication date
DE60122726T2 (de) 2007-08-16
EP1299655A1 (fr) 2003-04-09
JP2004502111A (ja) 2004-01-22
WO2002002961A1 (fr) 2002-01-10
SE522238C2 (sv) 2004-01-27
SE0002565D0 (sv) 2000-07-06
BR0111942A (pt) 2003-05-13
EP1299655B1 (fr) 2006-08-30
US7322448B2 (en) 2008-01-29
DE60122726D1 (de) 2006-10-12
ATE338224T1 (de) 2006-09-15
SE0002565L (sv) 2002-01-07
US20060196738A1 (en) 2006-09-07

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AS Assignment

Owner name: VOLVO LASTVAGNAR AB, SWEDEN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HULTEN, JOHAN;REEL/FRAME:013863/0675

Effective date: 20030121

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION