US20140102835A1 - Flanged shim for brake squeal attenuation - Google Patents
Flanged shim for brake squeal attenuation Download PDFInfo
- Publication number
- US20140102835A1 US20140102835A1 US13/965,784 US201313965784A US2014102835A1 US 20140102835 A1 US20140102835 A1 US 20140102835A1 US 201313965784 A US201313965784 A US 201313965784A US 2014102835 A1 US2014102835 A1 US 2014102835A1
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- Prior art keywords
- pad assembly
- support plate
- brake pad
- plate
- brake
- 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.)
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Classifications
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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
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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
- F16D65/0018—Dynamic vibration dampers, e.g. mass-spring systems
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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
- 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
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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
- F16D65/02—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
- F16D65/095—Pivots or supporting members therefor
- F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
- F16D65/0971—Resilient means interposed between pads and supporting members or other brake parts transmitting brake actuation force, e.g. elements interposed between brake piston and pad
Definitions
- the present inventions relates to brake pad assemblies for disc brakes in general and more particularly to a shim structure of a disc brake pad assembly for sound damping brake squeal noise in a disc brake apparatus.
- the typical disc brake pad assembly 1 illustrated in FIGS. 1A and 1B , consists of a friction pad 4 attached by bonding to a face of a steel backing plate 2 , which gives the friction pad 4 necessary support to resist a pressure load from a brake piston and/or caliper.
- the present invention provides an improved brake pad assembly for a disc brake apparatus.
- the brake pad assembly comprises a backing plate having a flat inner face and a flat outer face oriented opposite to the inner face, a friction member fixed to the inner face of the backing plate, and an anti-squeal shim attached to the outer face of the backing plate.
- the anti-squeal shim includes a flat support plate attached to the outer face of the backing plate and a straight flat flange plate.
- the support plate of the anti-squeal shim has a peripheral edge including opposite outer and inner edges and opposite side edges.
- the flange plate is in the form of a flexible cantilever formed integrally with the support plate and extends away from one of the outer, inner and opposite side edges of the support plate of the anti-squeal shim.
- the anti-squeal shim of the brake pad assembly in accordance with the present invention substantially increases stiffness and energy dissipation of the brake pad assembly, and resulting vibration damping during the braking operation of the disc brake apparatus of the vehicle. Consequently, the brake pad assembly in accordance with the present invention allows for significant overall reduction of braking noise.
- FIG. 1A is a perspective view of a conventional disc brake pad assembly
- FIG. 1B is a cross-sectional view of the conventional disc brake pad assembly
- FIG. 2 is a fragmented cross-sectional view of a disc brake apparatus including brake pad assemblies in accordance with the first exemplary embodiment of the present invention
- FIG. 3A is a perspective view of a brake pad assembly in accordance with the first exemplary embodiment of the present invention.
- FIG. 3B is a cross-sectional view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention taken along the line 3 B- 3 B of FIG. 3A ;
- FIG. 3C is an exploded cross-sectional view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention taken along the line 3 B- 3 B of FIG. 3A ;
- FIG. 3D is a side view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention.
- FIG. 4A is a perspective view of the brake pad assembly in accordance with the second exemplary embodiment of the present invention.
- FIG. 4B is a cross-sectional view of the brake pad assembly in accordance with the second exemplary embodiment of the present invention taken along the line 4 B- 4 B of FIG. 4A ;
- FIG. 5A is a perspective view of a brake pad assembly in accordance with the third exemplary embodiment of the present invention.
- FIG. 5B is a cross-sectional view of the brake pad assembly in accordance with the third exemplary embodiment of the present invention taken along the line 5 B- 5 B of FIG. 5A ;
- FIG. 6 is a table of test results for a conventional brake pad assembly
- FIG. 7 is a table of test results for the brake pad assembly in accordance with the first exemplary embodiment of the present invention.
- FIG. 2 of the drawings illustrates a disc brake apparatus, generally denoted by reference numeral 10 , for a motor vehicle.
- the disc brake apparatus 10 includes a brake rotor 12 rotatably mounted to a brake support member 14 , a movable caliper 16 also mounted to the brake support member 14 so as to straddle the brake rotor 12 , and inner and outer brake pad assemblies 20 a and 20 b, respectively, slidably supported by the brake support member 14 so as to be movable over a predetermined distance in the axial direction of the brake rotor 12 .
- the caliper 16 includes a cylinder portion 17 a receiving a brake piston 18 therein, and a reaction arm 17 b.
- the caliper 16 is integrally formed as a single-piece such as by casting. It will be appreciated that the brake piston 18 is movable over a predetermined distance in the direction of an axis of rotation of the brake rotor 12 . During the braking operation, when the brake piston 18 presses the inner brake pad assembly 20 a inwardly into a braking contact with the brake rotor 12 of the disc brake apparatus 10 , the outer brake pad assembly 20 b is pressed and moved toward the brake rotor 12 by means of the reaction arm 17 b of the movable caliper 16 .
- the reference numeral 20 will be used when generically referring to the brake pad assemblies 20 a and 20 b rather than reciting all two reference numerals.
- disc brake apparatus 10 illustrated in FIG. 2 is shown as using both inner and outer brake pad assemblies according to the present invention, it will be appreciated that only one of the inner and outer brake pad assemblies may be used according to the present invention.
- FIGS. 3A-3D of the drawings illustrate in detail the first exemplary embodiment of the brake pad assembly 20 in accordance with the present invention, for use in the disc brake apparatus 10 of the motor vehicle.
- the brake pad assembly 20 comprises a backing plate 22 having a peripheral edge 23 (best shown in FIG. 3D ) and a friction pad (or lining) 24 fixedly attached to an inner face 22 a of the backing plate 22 (i.e. the side of the backing plate 22 facing the brake rotor 12 when mounted in the disc brake apparatus 10 as shown in FIG. 2 ) by any appropriate means known in the art, such as by adhesive bonding or with rivets, to define a brake pad.
- the backing plate is made of steel
- the friction pad 24 is made of any appropriate friction material known in the art.
- any other appropriate composite or plastic materials may be used to make the backing plate 22 .
- the brake pad assembly 20 further comprises an anti-squeal (sound damping) shim 26 to reduce and/or to eliminate undesired brake squeal noise generated by the brake pad assembly 20 during the braking operation thereof.
- the anti-squeal shim 26 of the brake pad assembly 20 comprises a substantially flat support plate (or support portion) 28 in contact with the backing plate 22 , and a straight, flat flange plate (or flange portion) 30 extending from the flat support plate 28 so as to be in the form of a flexible cantilever formed integrally with the support plate 28 of the anti-squeal shim 26 .
- the straight flange plate 30 has a distal free edge 31 (shown in FIGS.
- the straight flange plate 30 of the anti-squeal shim 26 is perpendicular to the support plate 28 thereof and has a rectangular shape.
- the straight flange plate 30 can have any other appropriate shape. Dimensions of the flange plate 30 , such as width and length) can be varied to achieve the desired frequency.
- both the support plate 28 and the flange plate 30 are formed integrally from a single blank of shim material, such as steel.
- the anti-squeal shim 26 is formed as a single-piece part by stamping.
- the anti-squeal shim 26 can be made of any appropriate material, such as multilayer composite material.
- the anti-squeal shim 26 is made of a stainless steel plate coated on one face thereof with a layer of a heat resisting adhesive and with a layer of paint on the other face thereof
- the support plate 28 is fixedly attached to an outer face 22 b of the backing plate 22 (i.e. the side of the backing plate 22 facing away from the brake rotor 12 when mounted in the disc brake apparatus 10 as shown in FIG. 2 ) by any appropriate means known in the art, such as by adhesive bonding or by riveting.
- the anti-squeal shim 26 is positioned (sandwiched) between the hydraulically actuated piston 18 of the disc brake apparatus 10 and the outer face 22 b of the backing plate 22 of the brake pad assembly 20 , or between the reaction arm 17 b of the caliper 16 and the outer face 22 b of the backing plate 22 of the associated brake pad assembly 20 .
- the straight flange plate 30 of the anti-squeal shim 26 extends from the flat support plate 28 of the anti-squeal shim 26 in the direction away from the backing plate 22 .
- the anti-squeal shim 26 is flanged at the strategic edges of the flat support plate 28 thereof where there is little or no interference with the brake piston 18 , the reaction arm 17 b or other portions of the caliper 16 .
- the flange plate 30 of the anti-squeal shim 26 is free, i.e. not in contact with any part of the disc brake apparatus 10 .
- the support plate 28 of the anti-squeal shim 26 has a peripheral edge having four vertices 27 a, 27 b, 27 c and 27 d, and including opposite outer and inner edges 32 and 33 , respectively, and opposite side edges 34 a and 34 b.
- the term “outer peripheral edge of the support plate” as used herein refers to the edge 32 of the support plate 28 disposed closer to an outer peripheral edge 15 of the brake rotor 12 when the brake pad assembly 20 is installed in the disc brake apparatus 10
- the term “inner peripheral edge of the support plate” refers to the edge 33 of the support plate 28 farthest from the outer peripheral edge 15 of the brake rotor 12 when the brake pad assembly 20 is installed in the disc brake apparatus 10 .
- opposite side edges refers to the edges 34 a and 34 b of the support plate 28 disposed between the opposite outer and inner edges 32 , 33 thereof.
- the outer edge 32 extends between the vertices 27 a and 27 b
- the inner edge 33 extends between the vertices 27 c and 27 d
- the opposite side edges 34 a and 34 b extend between the vertices 27 a - 27 c and 27 b - 27 d, respectively.
- the vertices 27 a, 27 b, 27 c and 27 d of the support plate 28 of the anti-squeal shim 26 are disposed (located) on the outer face 22 b of the backing plate 22 within the peripheral edge 23 thereof.
- the vertices 27 a, 27 b, 27 c and 27 d of the support plate 28 of the anti-squeal shim 26 do not extend beyond the peripheral edge 23 of the backing plate 22 .
- the straight flange plate 30 extends from the inner edge 33 of the support plate 28 of the anti-squeal shim 26 .
- the inner edge 33 of the support plate 28 is in the form of the straight line extending between the vertices 27 c and 27 d.
- FIGS. 4A-4B illustrate a second exemplary embodiment of a brake pad assembly of the present invention, generally depicted by the reference character 120 .
- Components, which are unchanged from the previous exemplary embodiment of the present invention, are labeled with the same reference characters.
- Components, which function in the same way as in the first exemplary embodiment of the present invention depicted in FIGS. 2 and 3 A- 3 D are designated by the same reference numerals to which 100 has been added, sometimes without being described in detail since similarities between the corresponding parts in the two embodiments will be readily perceived by the reader.
- the brake pad assembly 120 of FIGS. 4A-4B corresponds substantially to the brake pad assembly 20 of FIGS.
- a straight flange plate 130 of the anti-squeal shim 126 extends from an outer edge 132 of a support plate 128 of the anti-squeal shim 126 of the brake pad assembly 120 according to the second exemplary embodiment of the present invention, as illustrated in FIGS. 4A and 4B . Consequently, the outer edge 132 of the support plate 128 is in the form of the straight line extending between the corresponding vertices of a peripheral edge of the support plate 128 .
- FIGS. 5A-5B illustrate a third exemplary embodiment of a brake pad assembly of the present invention, generally depicted by the reference character 220 .
- Components, which are unchanged from the previous exemplary embodiment of the present invention, are labeled with the same reference characters.
- Components, which function in the same way as in the first exemplary embodiment of the present invention depicted in FIGS. 2 and 3 A- 3 D are designated by the same reference numerals to which 200 has been added, sometimes without being described in detail since similarities between the corresponding parts in the two embodiments will be readily perceived by the reader.
- the brake pad assembly 220 of FIGS. 5A-5B corresponds substantially to the brake pad assembly 20 of FIGS.
- a straight flange plate 230 of the anti-squeal shim 226 extends from a side edge 234 b of a support plate 228 of the anti-squeal shim 226 of the brake pad assembly 220 according to the third exemplary embodiment of the present invention, as illustrated in FIGS. 5A and 5B .
- the straight flange plate 230 can extend from any of the side edges 234 a, 234 b of the support plate 228 of the anti-squeal shim 226 according to the third exemplary embodiment of the present invention.
- any of the side edges 234 a, 234 b of the support plate 228 from which the straight flange plate 230 extends is in the form of the straight line extending between the corresponding vertices of a peripheral edge of the support plate 228 .
- any edge of the support plate ( 28 , 128 or 228 ) of the anti-squeal shim ( 26 , 126 or 226 ), from which the straight flange plate ( 30 , 130 or 230 ) extends, is in the form of the straight line extending between the corresponding vertices of the peripheral edge of the support plate ( 28 , 128 , or 228 ).
- the anti-squeal shim ( 26 , 126 or 226 ) according to the present invention may be provided with more than one straight flange plate ( 30 , 130 or 230 ) extending from any of the outer, inner or side edges of the support plate in any possible combinations.
- the anti-squeal shim 26 may have two straight flange plates 30 including one extending from the inner edge 33 of the support plate 28 and one extending from the outer edge 32 thereof.
- any combination of two, three or four straight flange plates 30 is within the scope of the present invention.
- the anti-squeal shim 26 is flanged only when there is little or no interference with the brake piston any part of the disc brake apparatus 10 .
- the straight flange plate ( 30 , 130 or 230 ) extends outwardly from the flat support plate ( 28 , 128 , or 228 ) of the anti-squeal shim ( 26 , 126 or 226 ) in the direction away from the backing plate 22 .
- the flange plate ( 30 , 130 or 230 ) is located as close as possible to the peripheral edge 23 of the backing plate 22 so that the shim area in contact with the backing plate 22 (i.e. the area of the support plate ( 28 , 128 , or 228 )) is maximized in order to achieve maximum damping.
- the flange plate ( 30 , 130 or 230 ) extends substantially along an entire length of the corresponding edge of the support plate ( 28 , 128 , or 228 ) of the anti-squeal shim ( 26 , 126 or 226 ).
- the straight flange plate 30 on the anti-squeal (sound damping) shim 26 has a twofold effect: first, the flange shape changes the stiffness of the brake pad assembly 20 , thus altering modal alignment with respect to squeal rotor modes; and second, the straight flange plate 30 increases the energy dissipation and resulting damping at modes of interest.
- the brake pad assembly in accordance with the present invention allows for overall reduction of noise from 28% to 6%, as illustrated in FIGS. 6 and 7 .
- the novel anti-squeal shim of the brake pad assembly in accordance with the present invention substantially increases stiffness and energy dissipation of the brake pad assembly, and resulting vibration damping during the braking operation of the disc brake apparatus of the vehicle. Consequently, the brake pad assembly in accordance with the present invention allows for significant overall reduction of braking noise.
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Abstract
Description
- This Application claims the benefit under 35 U.S.C. 119(e) of U.S. Provisional Application Ser. No. 61/026,521 filed Feb. 6, 2008 by Kappagantu, R., which is hereby incorporated herein by reference in its entirety and to which priority is claimed.
- 1. Field of the Invention
- The present inventions relates to brake pad assemblies for disc brakes in general and more particularly to a shim structure of a disc brake pad assembly for sound damping brake squeal noise in a disc brake apparatus.
- 2. Description of the Prior Art
- Conventionally, in a disc brake apparatus two opposite brake pad assemblies compress a brake rotor in order to decelerate or stop the rotation of the brake rotor. The typical disc
brake pad assembly 1, illustrated inFIGS. 1A and 1B , consists of afriction pad 4 attached by bonding to a face of asteel backing plate 2, which gives thefriction pad 4 necessary support to resist a pressure load from a brake piston and/or caliper. - When the brake piston presses a back face of the
backing plate 2 of the discbrake pad assembly 1 inwardly during the braking operation, an inner surface of thefriction pad 4 is engaged in frictional, braking contact with the brake rotor of the disc brake apparatus. Such an action creates high operating temperatures of the disc brake apparatus (500 C.° or more) and high specific area pressures (about 1000 kg/cm2) as the brake piston normally has a relatively small cross section. The friction between the brake rotor and the brake pad assembly generates vibration of the elements of the brake pad assembly during braking operation. As a result, unpleasant and often loud braking noise, particularly relatively high pitched and undesired brake “squeal” noise, frequently occurs during the braking operation. - Numerous solutions to the brake noise problem have been proposed, many of which rely on the principle of damping vibrations. One of the most common solutions known in the art is placing of a noise-damping shim 6 (as illustrated in
FIGS. 1A and 1B ) in the form of a plate-like piece having a vibration-damping characteristic, between the backing plate of the brake pad assembly and the piston or caliper of the disc brake apparatus. - While known solutions to the brake noise problem, including but not limited to the noise-damping shims discussed above, have proven to be acceptable for various disc brake applications, such devices are nevertheless susceptible to improvements that may enhance their performance, cost and packaging. With this in mind, a need exists to develop improved anti-squeal shims for the disc brake apparatuses that advance the art.
- The present invention provides an improved brake pad assembly for a disc brake apparatus. The brake pad assembly comprises a backing plate having a flat inner face and a flat outer face oriented opposite to the inner face, a friction member fixed to the inner face of the backing plate, and an anti-squeal shim attached to the outer face of the backing plate. The anti-squeal shim includes a flat support plate attached to the outer face of the backing plate and a straight flat flange plate. The support plate of the anti-squeal shim has a peripheral edge including opposite outer and inner edges and opposite side edges. The flange plate is in the form of a flexible cantilever formed integrally with the support plate and extends away from one of the outer, inner and opposite side edges of the support plate of the anti-squeal shim.
- The anti-squeal shim of the brake pad assembly in accordance with the present invention substantially increases stiffness and energy dissipation of the brake pad assembly, and resulting vibration damping during the braking operation of the disc brake apparatus of the vehicle. Consequently, the brake pad assembly in accordance with the present invention allows for significant overall reduction of braking noise.
- Other objects and advantages of the invention will become apparent from a study of the following specification when viewed in light of the accompanying drawings, wherein:
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FIG. 1A is a perspective view of a conventional disc brake pad assembly; -
FIG. 1B is a cross-sectional view of the conventional disc brake pad assembly; -
FIG. 2 is a fragmented cross-sectional view of a disc brake apparatus including brake pad assemblies in accordance with the first exemplary embodiment of the present invention; -
FIG. 3A is a perspective view of a brake pad assembly in accordance with the first exemplary embodiment of the present invention; -
FIG. 3B is a cross-sectional view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention taken along theline 3B-3B ofFIG. 3A ; -
FIG. 3C is an exploded cross-sectional view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention taken along theline 3B-3B ofFIG. 3A ; -
FIG. 3D is a side view of the brake pad assembly in accordance with the first exemplary embodiment of the present invention; -
FIG. 4A is a perspective view of the brake pad assembly in accordance with the second exemplary embodiment of the present invention; -
FIG. 4B is a cross-sectional view of the brake pad assembly in accordance with the second exemplary embodiment of the present invention taken along theline 4B-4B ofFIG. 4A ; -
FIG. 5A is a perspective view of a brake pad assembly in accordance with the third exemplary embodiment of the present invention; -
FIG. 5B is a cross-sectional view of the brake pad assembly in accordance with the third exemplary embodiment of the present invention taken along theline 5B-5B ofFIG. 5A ; -
FIG. 6 is a table of test results for a conventional brake pad assembly; -
FIG. 7 is a table of test results for the brake pad assembly in accordance with the first exemplary embodiment of the present invention. - The preferred embodiment of the present invention will now be described with the reference to accompanying drawings.
- For purposes of the following description, certain terminology is used in the following description for convenience only and is not limiting. The words “top”, “bottom”, “right”, “left”, “lower”, “upper”, “inner” and “outer” designate directions in the drawings to which reference is made. The words “uppermost” and “lowermost” refer to position in a vertical direction relative to a geometric center of the apparatus of the present invention and designated parts thereof. The terminology includes the words above specifically mentioned, derivatives thereof and words of similar import. Additionally, the word “a” as used in the claims means “at least one”.
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FIG. 2 of the drawings illustrates a disc brake apparatus, generally denoted byreference numeral 10, for a motor vehicle. Thedisc brake apparatus 10 includes abrake rotor 12 rotatably mounted to abrake support member 14, amovable caliper 16 also mounted to thebrake support member 14 so as to straddle thebrake rotor 12, and inner and outerbrake pad assemblies brake support member 14 so as to be movable over a predetermined distance in the axial direction of thebrake rotor 12. Thecaliper 16 includes acylinder portion 17 a receiving abrake piston 18 therein, and areaction arm 17 b. Preferably, thecaliper 16 is integrally formed as a single-piece such as by casting. It will be appreciated that thebrake piston 18 is movable over a predetermined distance in the direction of an axis of rotation of thebrake rotor 12. During the braking operation, when thebrake piston 18 presses the innerbrake pad assembly 20 a inwardly into a braking contact with thebrake rotor 12 of thedisc brake apparatus 10, the outerbrake pad assembly 20 b is pressed and moved toward thebrake rotor 12 by means of thereaction arm 17 b of themovable caliper 16. - In view of the structural similarities of the inner and outer
brake pad assemblies reference numeral 20 will be used when generically referring to thebrake pad assemblies - Although, the
disc brake apparatus 10 illustrated inFIG. 2 is shown as using both inner and outer brake pad assemblies according to the present invention, it will be appreciated that only one of the inner and outer brake pad assemblies may be used according to the present invention. -
FIGS. 3A-3D of the drawings illustrate in detail the first exemplary embodiment of thebrake pad assembly 20 in accordance with the present invention, for use in thedisc brake apparatus 10 of the motor vehicle. Thebrake pad assembly 20 comprises abacking plate 22 having a peripheral edge 23 (best shown inFIG. 3D ) and a friction pad (or lining) 24 fixedly attached to aninner face 22 a of the backing plate 22 (i.e. the side of thebacking plate 22 facing thebrake rotor 12 when mounted in thedisc brake apparatus 10 as shown inFIG. 2 ) by any appropriate means known in the art, such as by adhesive bonding or with rivets, to define a brake pad. Preferably, the backing plate is made of steel, while thefriction pad 24 is made of any appropriate friction material known in the art. Alternatively, any other appropriate composite or plastic materials may be used to make thebacking plate 22. - The
brake pad assembly 20 further comprises an anti-squeal (sound damping) shim 26 to reduce and/or to eliminate undesired brake squeal noise generated by thebrake pad assembly 20 during the braking operation thereof. As illustrated inFIGS. 3A-3D , theanti-squeal shim 26 of thebrake pad assembly 20 comprises a substantially flat support plate (or support portion) 28 in contact with thebacking plate 22, and a straight, flat flange plate (or flange portion) 30 extending from theflat support plate 28 so as to be in the form of a flexible cantilever formed integrally with thesupport plate 28 of theanti-squeal shim 26. In other words, thestraight flange plate 30 has a distal free edge 31 (shown inFIGS. 3A and 3B ) axially spaced from thesupport plate 28. Preferably, thestraight flange plate 30 of theanti-squeal shim 26 is perpendicular to thesupport plate 28 thereof and has a rectangular shape. Alternatively, thestraight flange plate 30 can have any other appropriate shape. Dimensions of theflange plate 30, such as width and length) can be varied to achieve the desired frequency. As further illustrated inFIGS. 3A-3D , preferably, both thesupport plate 28 and theflange plate 30 are formed integrally from a single blank of shim material, such as steel. In other words, preferably, theanti-squeal shim 26 is formed as a single-piece part by stamping. It will be appreciated that theanti-squeal shim 26 can be made of any appropriate material, such as multilayer composite material. In the exemplary embodiment of the present invention, theanti-squeal shim 26 is made of a stainless steel plate coated on one face thereof with a layer of a heat resisting adhesive and with a layer of paint on the other face thereof - The
support plate 28 is fixedly attached to anouter face 22 b of the backing plate 22 (i.e. the side of thebacking plate 22 facing away from thebrake rotor 12 when mounted in thedisc brake apparatus 10 as shown inFIG. 2 ) by any appropriate means known in the art, such as by adhesive bonding or by riveting. In other words, theanti-squeal shim 26 is positioned (sandwiched) between the hydraulically actuatedpiston 18 of thedisc brake apparatus 10 and theouter face 22 b of thebacking plate 22 of thebrake pad assembly 20, or between thereaction arm 17 b of thecaliper 16 and theouter face 22 b of thebacking plate 22 of the associatedbrake pad assembly 20. Preferably, thestraight flange plate 30 of theanti-squeal shim 26 extends from theflat support plate 28 of theanti-squeal shim 26 in the direction away from thebacking plate 22. Theanti-squeal shim 26 is flanged at the strategic edges of theflat support plate 28 thereof where there is little or no interference with thebrake piston 18, thereaction arm 17 b or other portions of thecaliper 16. In other words, theflange plate 30 of theanti-squeal shim 26 is free, i.e. not in contact with any part of thedisc brake apparatus 10. - The
support plate 28 of theanti-squeal shim 26 has a peripheral edge having fourvertices inner edges edge 32 of thesupport plate 28 disposed closer to an outerperipheral edge 15 of thebrake rotor 12 when thebrake pad assembly 20 is installed in thedisc brake apparatus 10, while the term “inner peripheral edge of the support plate” refers to theedge 33 of thesupport plate 28 farthest from the outerperipheral edge 15 of thebrake rotor 12 when thebrake pad assembly 20 is installed in thedisc brake apparatus 10. It is to be understood that the term “opposite side edges” refers to theedges support plate 28 disposed between the opposite outer andinner edges outer edge 32 extends between thevertices inner edge 33 extends between thevertices - As further illustrated in
FIGS. 3A-3D , thevertices support plate 28 of theanti-squeal shim 26 are disposed (located) on theouter face 22 b of thebacking plate 22 within theperipheral edge 23 thereof. In other words, preferably, thevertices support plate 28 of theanti-squeal shim 26 do not extend beyond theperipheral edge 23 of thebacking plate 22. Preferably, as illustrated in FIGS. 2 and 3A-3D, thestraight flange plate 30 extends from theinner edge 33 of thesupport plate 28 of theanti-squeal shim 26. Thus, theinner edge 33 of thesupport plate 28 is in the form of the straight line extending between thevertices -
FIGS. 4A-4B illustrate a second exemplary embodiment of a brake pad assembly of the present invention, generally depicted by thereference character 120. Components, which are unchanged from the previous exemplary embodiment of the present invention, are labeled with the same reference characters. Components, which function in the same way as in the first exemplary embodiment of the present invention depicted in FIGS. 2 and 3A-3D are designated by the same reference numerals to which 100 has been added, sometimes without being described in detail since similarities between the corresponding parts in the two embodiments will be readily perceived by the reader. Thebrake pad assembly 120 ofFIGS. 4A-4B corresponds substantially to thebrake pad assembly 20 of FIGS. 2 and 3A-3D, and only ananti-squeal shim 126 of thebrake pad assembly 120 differs. Specifically, astraight flange plate 130 of theanti-squeal shim 126 extends from anouter edge 132 of asupport plate 128 of theanti-squeal shim 126 of thebrake pad assembly 120 according to the second exemplary embodiment of the present invention, as illustrated inFIGS. 4A and 4B . Consequently, theouter edge 132 of thesupport plate 128 is in the form of the straight line extending between the corresponding vertices of a peripheral edge of thesupport plate 128. -
FIGS. 5A-5B illustrate a third exemplary embodiment of a brake pad assembly of the present invention, generally depicted by thereference character 220. Components, which are unchanged from the previous exemplary embodiment of the present invention, are labeled with the same reference characters. Components, which function in the same way as in the first exemplary embodiment of the present invention depicted in FIGS. 2 and 3A-3D are designated by the same reference numerals to which 200 has been added, sometimes without being described in detail since similarities between the corresponding parts in the two embodiments will be readily perceived by the reader. Thebrake pad assembly 220 ofFIGS. 5A-5B corresponds substantially to thebrake pad assembly 20 of FIGS. 2 and 3A-3D, and only ananti-squeal shim 226 of thebrake pad assembly 220 differs. Specifically, astraight flange plate 230 of theanti-squeal shim 226 extends from aside edge 234 b of asupport plate 228 of theanti-squeal shim 226 of thebrake pad assembly 220 according to the third exemplary embodiment of the present invention, as illustrated inFIGS. 5A and 5B . In fact, thestraight flange plate 230 can extend from any of the side edges 234 a, 234 b of thesupport plate 228 of theanti-squeal shim 226 according to the third exemplary embodiment of the present invention. Consequently, any of the side edges 234 a, 234 b of thesupport plate 228 from which thestraight flange plate 230 extends, is in the form of the straight line extending between the corresponding vertices of a peripheral edge of thesupport plate 228. - Thus, any edge of the support plate (28, 128 or 228) of the anti-squeal shim (26, 126 or 226), from which the straight flange plate (30, 130 or 230) extends, is in the form of the straight line extending between the corresponding vertices of the peripheral edge of the support plate (28, 128, or 228). Moreover, the anti-squeal shim (26, 126 or 226) according to the present invention may be provided with more than one straight flange plate (30, 130 or 230) extending from any of the outer, inner or side edges of the support plate in any possible combinations. For example, the
anti-squeal shim 26 may have twostraight flange plates 30 including one extending from theinner edge 33 of thesupport plate 28 and one extending from theouter edge 32 thereof. In other words, any combination of two, three or fourstraight flange plates 30 is within the scope of the present invention. However, in any such case, theanti-squeal shim 26 is flanged only when there is little or no interference with the brake piston any part of thedisc brake apparatus 10. - Preferably, as illustrated in
FIGS. 3A-5B , the straight flange plate (30, 130 or 230) extends outwardly from the flat support plate (28, 128, or 228) of the anti-squeal shim (26, 126 or 226) in the direction away from thebacking plate 22. Further preferably, the flange plate (30, 130 or 230) is located as close as possible to theperipheral edge 23 of thebacking plate 22 so that the shim area in contact with the backing plate 22 (i.e. the area of the support plate (28, 128, or 228)) is maximized in order to achieve maximum damping. Further preferably, the flange plate (30, 130 or 230) extends substantially along an entire length of the corresponding edge of the support plate (28, 128, or 228) of the anti-squeal shim (26, 126 or 226). - As the brake squeal noise is produced by vibration of the
brake pad assembly 20 during braking actuation, forming thestraight flange plate 30 on the anti-squeal (sound damping)shim 26 has a twofold effect: first, the flange shape changes the stiffness of thebrake pad assembly 20, thus altering modal alignment with respect to squeal rotor modes; and second, thestraight flange plate 30 increases the energy dissipation and resulting damping at modes of interest. As a result, the brake pad assembly in accordance with the present invention allows for overall reduction of noise from 28% to 6%, as illustrated inFIGS. 6 and 7 . - Therefore, the novel anti-squeal shim of the brake pad assembly in accordance with the present invention substantially increases stiffness and energy dissipation of the brake pad assembly, and resulting vibration damping during the braking operation of the disc brake apparatus of the vehicle. Consequently, the brake pad assembly in accordance with the present invention allows for significant overall reduction of braking noise.
- The foregoing description of the preferred embodiments of the present invention has been presented for the purpose of illustration in accordance with the provisions of the Patent Statutes. It is not intended to be exhaustive or to limit the invention to the precise forms disclosed. Obvious modifications or variations are possible in light of the above teachings. The embodiments disclosed hereinabove were chosen in order to best illustrate the principles of the present invention and its practical application to thereby enable those of ordinary skill in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated, as long as the principles described herein are followed. Thus, changes can be made in the above-described invention without departing from the intent and scope thereof. It is also intended that the scope of the present invention be defined by the claims appended thereto.
Claims (20)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/965,784 US20140102835A1 (en) | 2008-02-06 | 2013-08-13 | Flanged shim for brake squeal attenuation |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US2652108P | 2008-02-06 | 2008-02-06 | |
US12/367,110 US8505699B2 (en) | 2008-02-06 | 2009-02-06 | Flanged shim for disc brake squeal attenuation |
US13/965,784 US20140102835A1 (en) | 2008-02-06 | 2013-08-13 | Flanged shim for brake squeal attenuation |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/367,110 Continuation US8505699B2 (en) | 2008-02-06 | 2009-02-06 | Flanged shim for disc brake squeal attenuation |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140102835A1 true US20140102835A1 (en) | 2014-04-17 |
Family
ID=41052451
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/367,110 Active 2030-04-25 US8505699B2 (en) | 2008-02-06 | 2009-02-06 | Flanged shim for disc brake squeal attenuation |
US13/965,784 Abandoned US20140102835A1 (en) | 2008-02-06 | 2013-08-13 | Flanged shim for brake squeal attenuation |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/367,110 Active 2030-04-25 US8505699B2 (en) | 2008-02-06 | 2009-02-06 | Flanged shim for disc brake squeal attenuation |
Country Status (1)
Country | Link |
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US (2) | US8505699B2 (en) |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5454352B2 (en) * | 2010-05-20 | 2014-03-26 | 株式会社アドヴィックス | Disc brake device |
CA3034595C (en) | 2012-05-29 | 2021-01-19 | Gripmetal Limited | Bulk textured material sheeting |
CA3040130C (en) | 2012-06-18 | 2021-09-14 | Gripmetal Limited | Process for making a laminated sheet |
CA2798303C (en) | 2012-12-07 | 2019-01-08 | Nghi Pham | Composite disc brake backing plate |
CA2821897C (en) | 2013-07-26 | 2016-08-16 | Ray Arbesman | Metal and graphite laminate |
US9950495B2 (en) | 2014-07-24 | 2018-04-24 | Nugripmetal S.A.R.L. | System and method for additive manufacturing of a three-dimensional object |
US9856938B2 (en) | 2014-09-26 | 2018-01-02 | R.A. Investment Management S.A.R.L. | Material with variable height barbs |
CA2865384A1 (en) | 2014-09-26 | 2016-03-26 | Ray Arbesman | Composite disc brake backing plate |
US9689450B2 (en) | 2014-09-26 | 2017-06-27 | R.A. Investment Management S.A.R.L. | Composite disc brake backing plate |
US9360067B1 (en) | 2015-02-05 | 2016-06-07 | R. A. Investment Management S.A.R.L. | Hybrid laminate |
US9388872B1 (en) | 2015-03-26 | 2016-07-12 | Nucap Industries Inc. | Friction fusion fastening system |
US9976610B2 (en) | 2015-09-03 | 2018-05-22 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
US9605721B1 (en) * | 2015-09-03 | 2017-03-28 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
US10315382B2 (en) | 2016-12-22 | 2019-06-11 | Gripmetal Limited | Process for manufacturing textured laminate sheet |
CA3052991A1 (en) * | 2017-02-08 | 2018-08-16 | Bendix Spicer Foundation Brake Llc | Wear optimized pad design |
US10010923B1 (en) | 2017-09-13 | 2018-07-03 | Nugripmetal S.A.R.L. | Textured sheet metal |
DE112019007224T5 (en) * | 2019-04-17 | 2021-12-30 | Hitachi Astemo, Ltd. | Disc brake and laminated spacer |
DE102022200646A1 (en) | 2022-01-20 | 2023-07-20 | Hl Mando Corporation | Brake arrangement for a vehicle disc brake with a noise-dampening pad spring or pad clip |
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GB0414108D0 (en) * | 2004-06-24 | 2004-07-28 | Meritor Heavy Vehicle Braking | A brake assembly |
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JPS57174649A (en) * | 1981-04-17 | 1982-10-27 | Matsushita Electric Ind Co Ltd | Selective absorption surface for solar heat |
US4995482A (en) * | 1988-06-14 | 1991-02-26 | Tokico Ltd. | Disc brake |
US6488131B2 (en) * | 2001-01-23 | 2002-12-03 | Meritor Heavy Vehicle Technology, Llc | Disc brake friction lining assembly |
JP2004148700A (en) * | 2002-10-31 | 2004-05-27 | Kawasaki Heavy Ind Ltd | Laminate shim made of composite material, and its manufacturing method |
Also Published As
Publication number | Publication date |
---|---|
US20090223753A1 (en) | 2009-09-10 |
US8505699B2 (en) | 2013-08-13 |
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