WO1998050837A1 - Solid finned rotor for caliper disc brakes and the like - Google Patents

Solid finned rotor for caliper disc brakes and the like Download PDF

Info

Publication number
WO1998050837A1
WO1998050837A1 PCT/US1998/009303 US9809303W WO9850837A1 WO 1998050837 A1 WO1998050837 A1 WO 1998050837A1 US 9809303 W US9809303 W US 9809303W WO 9850837 A1 WO9850837 A1 WO 9850837A1
Authority
WO
WIPO (PCT)
Prior art keywords
fins
rotor
support plate
annular
extending
Prior art date
Application number
PCT/US1998/009303
Other languages
French (fr)
Inventor
Weston E. Dickerson
Original Assignee
Hayes Lemmerz International, Inc.
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 Hayes Lemmerz International, Inc. filed Critical Hayes Lemmerz International, Inc.
Priority to JP54848398A priority Critical patent/JP2001524197A/en
Priority to EP98923348A priority patent/EP0981785A4/en
Priority to AU75659/98A priority patent/AU7565998A/en
Priority to CA002289072A priority patent/CA2289072A1/en
Publication of WO1998050837A1 publication Critical patent/WO1998050837A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1316—Structure radially segmented
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/132—Structure layered
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels

Definitions

  • the present invention relates to rotors for caliper disc brakes and the like.
  • Rotors are generally well known in the art, and are used extensively in caliper disc brakes, power transmission devices, clutches, and other similar machinery and mechanisms.
  • Brake rotors are typically cast from a ferrous material, such as cast grey iron, and are then machined in multiple operations to shape the rotor, and form the opposite friction surfaces which interface with associated brake pads.
  • Cast aluminum rotors are available to reduce the weight and corrosion problems associated with ferrous metal rotors, although the heat resistance and brake surface toughness of cast aluminum is typically less desirable than that of other types of rotors.
  • solid cast iron or cast aluminum rotors are preferred from the standpoint of strength.
  • the ability of a brake rotor to quickly transfer and dissipate heat generated during the braking process is also a very desirable feature, as excess heat leads to premature brake wear and/or failure.
  • vented rotors are generally preferred for their increased cooling characteristics.
  • the present invention is a rotor for caliper disc brakes and the like.
  • the rotor of the invention includes an inner hub or hat section having a central, outboard mounting face for mounting the rotor on a drive member and a hat wall which extends from the periphery of the mounting face.
  • An outer friction portion adapted to interface with associated friction members is connected to the hat wall of the hat section.
  • the outer friction portion of the rotor of the invention includes an annular support plate having a friction ring section on both of the major surfaces thereof.
  • Each of the friction ring sections is formed of a plurality of circumferentially spaced apart fins.
  • Each of the fins includes a substantially flat friction surface, so that the plurality of fins combines to define an annular, non- continuous friction surface on each face of the support plate adapted to interface with an associated friction member, such as a brake pad.
  • Fig. 1 is a front elevational view of a rotor embodying the present invention.
  • Fig. 2 is a cross-sectional view, taken along the line 2- 2 in Fig. 1.
  • the rotor 10 is of the type adapted for use in conjunction with a variety of mechanical devices, such as caliper disc brakes and the like.
  • the rotor 10 includes a radially inner hub or hat section 12 having a central mounting face 14 for mounting the rotor 10 on an associated drive member (not shown) , such as a spindle or vehicle axle.
  • the hat section 12 also includes a generally cylindrical shoulder or hat wall 16 extending from the periphery of the mounting face 14.
  • the central mounting face 14 of the hat section 12 of rotor 10 is provided with a central pilot aperture 18 in which a spindle hub or the like (not shown) may be closely received, and a plurality of circumferentially spaced apart fastener apertures 20 in which fasteners (also not shown) may be received to mount the rotor 10 on an associated drive mechanism in the conventional manner.
  • the rotor 10 also includes an outer friction portion, denoted generally by the reference numeral 30 in the drawings.
  • the outer friction portion 30 of the rotor 10 of the invention includes an annular core or support plate 32 extending from the hat wall 16 of the hat section 12, proximate the inboard edge thereof (on the left as shown in Fig. 2) .
  • the support plate 32 is preferably of a solid construction for increased strength, and includes an annular inboard surface 34 and an annular outboard surface 36.
  • An inboard friction ring section 38 is provided on the inboard surface 34 of the support plate 32, and an outboard friction ring section 40 is provided on the outboard surface 36 of the support plate 32.
  • the friction ring section 38 is formed of a plurality of circumferentially spaced apart fins 42 extending from the inboard surface 34 of the support plate 32.
  • the friction ring section 40 is formed of a plurality of circumferentially spaced apart fins 44 extending from the outboard surface 36 of the support plate 32.
  • the plurality of fins 42 and 44 are mirror images of one another, so that only the fins 42 will be discussed in further detail.
  • Each of the fins 42 includes a substantially flat friction surface 42a, so that the combination of the plurality of surfaces 42a of fins 42 defines an annular, though non-continuous, friction surface adapted to interface with an associated friction member, such as a brake pad.
  • the fins 42 are generally radially extending, although they are preferably angled somewhat from a true radial direction, and are most preferably formed in the generally spiral configuration illustrated in Fig 1. In this manner, an associated friction member, such as a brake pad, will not simultaneously engage the entire leading edge of any of the fins 42.
  • the fins 42 are also preferably shaped so as to increase in width from the radially inner ends to the radially outer ends thereof, as best seen in Fig. 1.
  • the fins 42 are preferably formed so that the peripheral edge defining the friction surface 42a is rounded, thereby further facilitating the smooth engagement of the fins 42 with the associated friction member.
  • the fins 42 are preferably formed of a size and shape and with a particular spacing for a given application such that the associated friction member simultaneously engages more than one fin 42 upon activation. In many applications, it will be desired to have the associated friction member simultaneously engage three or more fins 42 upon activation .
  • the generally radially extending space between fins 42 should be as large as possible to provide for enhanced air flow about the fins 42, as long as the total surface area 42a engaged by the associated friction member is sufficient to provide the desired braking force.
  • the fins 42 are spaced radially from the radially outer surface of the hat wall 16 of the rotor 10 to further enhance the air flow about the fins 42.
  • the shape, size and location of the fins 42 and 44 can be varied to achieve the desired braking force and air flow characteristics .
  • the rotor 10 of the invention may be formed of any suitable material, such as cast grey iron, aluminum or alloys or composites thereof, as examples.
  • the rotor 10 may be formed using conventional manufacturing methods, such as casting.
  • the rotor 10 is preferably formed of cast grey iron using conventional techniques with a core modified to provide for a rotor structure embodying the invention.
  • the rotor 10 of the invention provides the strength of a solid rotor with the desirable increased cooling characteristics of a vented rotor.

Landscapes

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

Abstract

A rotor (10) for caliper disc brakes and the like has an outer friction portion including an annular support plate (32) having a friction ring section on both of the major surfaces thereof adapted to interface with an associated friction member, such as a brake pad. Each of the friction ring sections is formed of a plurality of circumferentially spaced apart fins (42, 44). Each of the fins, (42, 44) includes a substantially flat friction surface (42a), so that the plurality of such surfaces (42a) combine to define an annular, non-continuous friction surface on each face of the support plate (32). The rotor (10) of the invention combines the strength of a solid rotor with the desirable increased cooling characteristics of a vented rotor.

Description

TITLE SOLID FINNED ROTOR FOR CALIPER DISC BRAKES AND THE LIKE
BACKGROUND OF THE INVENTION The present invention relates to rotors for caliper disc brakes and the like.
Rotors are generally well known in the art, and are used extensively in caliper disc brakes, power transmission devices, clutches, and other similar machinery and mechanisms. Brake rotors are typically cast from a ferrous material, such as cast grey iron, and are then machined in multiple operations to shape the rotor, and form the opposite friction surfaces which interface with associated brake pads. Cast aluminum rotors are available to reduce the weight and corrosion problems associated with ferrous metal rotors, although the heat resistance and brake surface toughness of cast aluminum is typically less desirable than that of other types of rotors. In addition, there are some composite rotors, in which different portions of the rotor are formed of different materials.
In general, solid cast iron or cast aluminum rotors are preferred from the standpoint of strength. However, the ability of a brake rotor to quickly transfer and dissipate heat generated during the braking process is also a very desirable feature, as excess heat leads to premature brake wear and/or failure. Thus, vented rotors are generally preferred for their increased cooling characteristics.
It would therefore be desirable to provide a rotor which combines the desirable strength of a solid rotor with the improved cooling characteristics of a vented rotor.
SUMMARY OF THE INVENTION The present invention is a rotor for caliper disc brakes and the like. The rotor of the invention includes an inner hub or hat section having a central, outboard mounting face for mounting the rotor on a drive member and a hat wall which extends from the periphery of the mounting face. An outer friction portion adapted to interface with associated friction members is connected to the hat wall of the hat section.
The outer friction portion of the rotor of the invention includes an annular support plate having a friction ring section on both of the major surfaces thereof. Each of the friction ring sections is formed of a plurality of circumferentially spaced apart fins. Each of the fins includes a substantially flat friction surface, so that the plurality of fins combines to define an annular, non- continuous friction surface on each face of the support plate adapted to interface with an associated friction member, such as a brake pad. BRIEF DESCRIPTION OF THE DRAWINGS The advantages of the invention will become readily apparent to those skilled in the art from the following detailed description of a preferred embodiment when considered in the light of the accompanying drawings, in which:
Fig. 1 is a front elevational view of a rotor embodying the present invention; and
Fig. 2 is a cross-sectional view, taken along the line 2- 2 in Fig. 1.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
For purposes of description herein, the terms "upper, " "lower," "right," "left," "rear," "front," "vertical," "horizontal," and derivatives thereof shall relate to the invention oriented in Figs. 1 and 2. However, it is to be understood that the invention may assume various alternative orientations, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions and other physical characteristics relating to the embodiments disclosed herein are not to be considered as limiting, unless the claims expressly state otherwise. Referring now to the drawings, there is illustrated in Fig. 1 a rotor in accordance with the invention, denoted generally by the reference numeral 10. The rotor 10 is of the type adapted for use in conjunction with a variety of mechanical devices, such as caliper disc brakes and the like. The rotor 10 includes a radially inner hub or hat section 12 having a central mounting face 14 for mounting the rotor 10 on an associated drive member (not shown) , such as a spindle or vehicle axle. The hat section 12 also includes a generally cylindrical shoulder or hat wall 16 extending from the periphery of the mounting face 14.
The central mounting face 14 of the hat section 12 of rotor 10 is provided with a central pilot aperture 18 in which a spindle hub or the like (not shown) may be closely received, and a plurality of circumferentially spaced apart fastener apertures 20 in which fasteners (also not shown) may be received to mount the rotor 10 on an associated drive mechanism in the conventional manner.
The rotor 10 also includes an outer friction portion, denoted generally by the reference numeral 30 in the drawings. The outer friction portion 30 of the rotor 10 of the invention includes an annular core or support plate 32 extending from the hat wall 16 of the hat section 12, proximate the inboard edge thereof (on the left as shown in Fig. 2) . The support plate 32 is preferably of a solid construction for increased strength, and includes an annular inboard surface 34 and an annular outboard surface 36. An inboard friction ring section 38 is provided on the inboard surface 34 of the support plate 32, and an outboard friction ring section 40 is provided on the outboard surface 36 of the support plate 32. The friction ring section 38 is formed of a plurality of circumferentially spaced apart fins 42 extending from the inboard surface 34 of the support plate 32. Likewise, the friction ring section 40 is formed of a plurality of circumferentially spaced apart fins 44 extending from the outboard surface 36 of the support plate 32. In the preferred embodiment illustrated, the plurality of fins 42 and 44 are mirror images of one another, so that only the fins 42 will be discussed in further detail. Each of the fins 42 includes a substantially flat friction surface 42a, so that the combination of the plurality of surfaces 42a of fins 42 defines an annular, though non-continuous, friction surface adapted to interface with an associated friction member, such as a brake pad.
The fins 42 are generally radially extending, although they are preferably angled somewhat from a true radial direction, and are most preferably formed in the generally spiral configuration illustrated in Fig 1. In this manner, an associated friction member, such as a brake pad, will not simultaneously engage the entire leading edge of any of the fins 42. The fins 42 are also preferably shaped so as to increase in width from the radially inner ends to the radially outer ends thereof, as best seen in Fig. 1. In addition, the fins 42 are preferably formed so that the peripheral edge defining the friction surface 42a is rounded, thereby further facilitating the smooth engagement of the fins 42 with the associated friction member. Moreover, the fins 42 are preferably formed of a size and shape and with a particular spacing for a given application such that the associated friction member simultaneously engages more than one fin 42 upon activation. In many applications, it will be desired to have the associated friction member simultaneously engage three or more fins 42 upon activation .
The generally radially extending space between fins 42 should be as large as possible to provide for enhanced air flow about the fins 42, as long as the total surface area 42a engaged by the associated friction member is sufficient to provide the desired braking force. In addition, in a preferred embodiment, the fins 42 are spaced radially from the radially outer surface of the hat wall 16 of the rotor 10 to further enhance the air flow about the fins 42. Of course, the shape, size and location of the fins 42 and 44 can be varied to achieve the desired braking force and air flow characteristics .
The rotor 10 of the invention may be formed of any suitable material, such as cast grey iron, aluminum or alloys or composites thereof, as examples. The rotor 10 may be formed using conventional manufacturing methods, such as casting. The rotor 10 is preferably formed of cast grey iron using conventional techniques with a core modified to provide for a rotor structure embodying the invention.
The rotor 10 of the invention provides the strength of a solid rotor with the desirable increased cooling characteristics of a vented rotor.

Claims

WHAT IS CLAIMED IS:
1. A rotor comprising: a hat section including a mounting face and a hat wall extending from said mounting face; an annular support plate extending radially outwardly from the hat wall of said hat section, said support plate having first and second annular surfaces; and a first plurality of circumferentially spaced apart fins extending from the first annular surface of said support plate and a second plurality of circumferentially spaced apart fins extending from the second annular surface of said support plate .
2. A rotor as defined in claim 1, wherein the annular support plate includes a solid annular member.
3. A rotor as define in claim 1, wherein the first plurality of circumferentially spaced apart fins is mirror image of the second plurality of circumferentially spaced apart fins.
4. A rotor as defined in claim 1, wherein the fins of said first and second plurality of fins are generally radially extending.
5. A rotor as defined in claim 1, wherein the fins of said first and second plurality of fins are slightly angled from a radial direction so that an associated friction member will not simultaneously engage the entire leading edge of any of the fins.
6. A rotor as defined in claim 5, wherein the fins of said first and second plurality of fins are slightly angled from a radial direction so that the radially inner end of each fin is offset from the radially outer end thereof in the intended forward direction of rotation for the rotor.
7. A rotor as defined in claim 1, wherein the fins of said first and second plurality of fins are shaped so as to increase in width from the radially inner ends to the radially outer ends thereof.
8. A rotor as defined in claim 1, the fins of said first and second plurality of fins are formed so that at least a portion of the peripheral edge defining the friction surface of each of said fins is rounded to facilitate the smooth engagement of the fins with an associated friction member.
9. A rotor comprising: a mounting section including a mounting face and a wall extending from said mounting face; an annular support plate extending radially outwardly from the wall of said mounting section, said support plate having first and second annular surfaces; and a first plurality of circumferentially spaced apart fins extending from the first annular surface of said support plate .
10. A rotor comprising: a mounting section including a mounting face and a wall extending from said mounting face; an annular support member extending radially outwardly from the wall of said mounting section, said support plate having a first annular, non-continuous friction surface adapted to interface with an associated friction member.
PCT/US1998/009303 1997-05-05 1998-05-05 Solid finned rotor for caliper disc brakes and the like WO1998050837A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP54848398A JP2001524197A (en) 1997-05-05 1998-05-05 Rotor with integrated fins for caliper disc brakes, etc.
EP98923348A EP0981785A4 (en) 1997-05-05 1998-05-05 Solid finned rotor for caliper disc brakes and the like
AU75659/98A AU7565998A (en) 1997-05-05 1998-05-05 Solid finned rotor for caliper disc brakes and the like
CA002289072A CA2289072A1 (en) 1997-05-05 1998-05-05 Solid finned rotor for caliper disc brakes and the like

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US4556897P 1997-05-05 1997-05-05
US60/045,568 1997-05-05
US5473198A 1998-04-03 1998-04-03
US09/054,731 1998-04-03

Publications (1)

Publication Number Publication Date
WO1998050837A1 true WO1998050837A1 (en) 1998-11-12

Family

ID=26722931

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1998/009303 WO1998050837A1 (en) 1997-05-05 1998-05-05 Solid finned rotor for caliper disc brakes and the like

Country Status (5)

Country Link
EP (1) EP0981785A4 (en)
JP (1) JP2001524197A (en)
AU (1) AU7565998A (en)
CA (1) CA2289072A1 (en)
WO (1) WO1998050837A1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046831A3 (en) * 1999-04-16 2002-11-20 Jordi Nadal Aloy Improved disc brake
WO2009026458A1 (en) 2007-08-22 2009-02-26 Tech M3, Inc. Brake disk and method of making same
US8084089B2 (en) 2007-02-20 2011-12-27 Tech M3, Inc. Wear resistant coating for brake disks with unique surface appearance and method for coating
US8449943B2 (en) 2007-02-20 2013-05-28 Tech M3, Inc. Composite brake disks and methods for coating
US8893863B2 (en) 2007-08-22 2014-11-25 Tech M3, Inc. Reduction of particulate emissions from vehicle braking systems
US10012279B2 (en) 2013-03-15 2018-07-03 Tech M3, Inc. Braking systems incorporating wear and corrosion resistant rotors
US10197121B2 (en) 2013-03-15 2019-02-05 Tech M3, Inc. Wear resistant braking systems

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DE538507C (en) * 1930-07-10 1931-11-16 Siemens Schuckertwerke Akt Ges flywheel
FR788671A (en) * 1935-04-12 1935-10-14 Novi Improvements to magnetic flywheels for internal combustion engines
US2753808A (en) * 1950-02-15 1956-07-10 Kluge Dorothea Centrifugal impeller
US3314509A (en) * 1965-04-16 1967-04-18 Buffalo Brake Beam Co Railway brake discs
US3443454A (en) * 1966-07-19 1969-05-13 Holset Engineering Co Means for cooling torsional vibration damper
US3899054A (en) * 1974-02-08 1975-08-12 Abex Corp Disc brakes with cooling rods
US3993415A (en) * 1974-01-12 1976-11-23 Suddeutsche Kuhlerfabrik, Julius Fr. Behr Fan with fluid friction clutch
US4555239A (en) * 1982-06-01 1985-11-26 Dayco Corporation Belt pulley and method of making the same

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US2587047A (en) * 1950-04-27 1952-02-26 Westinghouse Air Brake Co Rotor for disk brakes
DE1210266B (en) * 1958-12-31 1966-02-03 Schuler L Ag Disc friction clutch for presses
US3289797A (en) * 1962-09-10 1966-12-06 Wehr Steel Company Rotary motion control device
DE1480298A1 (en) * 1964-11-17 1969-07-10 Teves Gmbh Alfred Friction brake for motor vehicles, especially tracked vehicles
US3623577A (en) * 1969-11-13 1971-11-30 Kelsey Hayes Co Corrugated rotor for disk brakes

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE538507C (en) * 1930-07-10 1931-11-16 Siemens Schuckertwerke Akt Ges flywheel
FR788671A (en) * 1935-04-12 1935-10-14 Novi Improvements to magnetic flywheels for internal combustion engines
US2753808A (en) * 1950-02-15 1956-07-10 Kluge Dorothea Centrifugal impeller
US3314509A (en) * 1965-04-16 1967-04-18 Buffalo Brake Beam Co Railway brake discs
US3443454A (en) * 1966-07-19 1969-05-13 Holset Engineering Co Means for cooling torsional vibration damper
US3993415A (en) * 1974-01-12 1976-11-23 Suddeutsche Kuhlerfabrik, Julius Fr. Behr Fan with fluid friction clutch
US3899054A (en) * 1974-02-08 1975-08-12 Abex Corp Disc brakes with cooling rods
US4555239A (en) * 1982-06-01 1985-11-26 Dayco Corporation Belt pulley and method of making the same

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* Cited by examiner, † Cited by third party
Title
See also references of EP0981785A4 *

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046831A3 (en) * 1999-04-16 2002-11-20 Jordi Nadal Aloy Improved disc brake
US10968970B2 (en) 2007-02-20 2021-04-06 Tech M3, Inc. Composite brake disks and methods for coating
US8084089B2 (en) 2007-02-20 2011-12-27 Tech M3, Inc. Wear resistant coating for brake disks with unique surface appearance and method for coating
US8449943B2 (en) 2007-02-20 2013-05-28 Tech M3, Inc. Composite brake disks and methods for coating
US11692601B2 (en) 2007-02-20 2023-07-04 Tech M3, Inc. Reduction of particulate emissions from vehicle braking systems
WO2009026458A1 (en) 2007-08-22 2009-02-26 Tech M3, Inc. Brake disk and method of making same
US8893863B2 (en) 2007-08-22 2014-11-25 Tech M3, Inc. Reduction of particulate emissions from vehicle braking systems
US12025195B2 (en) 2007-08-22 2024-07-02 Tech M3, Inc. Brake disk and method of making same
US10670095B2 (en) 2007-08-22 2020-06-02 Tech M3, Inc. Brake disk and method of making same
US11635116B2 (en) 2007-08-22 2023-04-25 Tech M3, Inc. Brake disk and method of making same
US10197121B2 (en) 2013-03-15 2019-02-05 Tech M3, Inc. Wear resistant braking systems
US11624416B2 (en) 2013-03-15 2023-04-11 Tech M3, Inc. Wear resistant braking systems
US10895295B2 (en) 2013-03-15 2021-01-19 Tech M3, Inc. Wear resistant braking systems
US20190368560A1 (en) * 2013-03-15 2019-12-05 Tech M3, Inc. Wear resistant braking systems
US10012279B2 (en) 2013-03-15 2018-07-03 Tech M3, Inc. Braking systems incorporating wear and corrosion resistant rotors

Also Published As

Publication number Publication date
JP2001524197A (en) 2001-11-27
AU7565998A (en) 1998-11-27
EP0981785A4 (en) 2000-12-06
CA2289072A1 (en) 1998-11-12
EP0981785A1 (en) 2000-03-01

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