US20020084155A1 - Disc brake rotor - Google Patents

Disc brake rotor Download PDF

Info

Publication number
US20020084155A1
US20020084155A1 US09/754,688 US75468801A US2002084155A1 US 20020084155 A1 US20020084155 A1 US 20020084155A1 US 75468801 A US75468801 A US 75468801A US 2002084155 A1 US2002084155 A1 US 2002084155A1
Authority
US
United States
Prior art keywords
vanes
rotor
width
inverted
proximal
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.)
Granted
Application number
US09/754,688
Other versions
US6454058B1 (en
Inventor
Robert Ballinger
Kenneth Dunlap
Michael Riehle
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.)
BWI Co Ltd SA
Delphi Technologies Inc
Original Assignee
Delphi Automotive Systems LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Delphi Automotive Systems LLC filed Critical Delphi Automotive Systems LLC
Assigned to DELPHI AUTOMOTIVE SYSTEMS reassignment DELPHI AUTOMOTIVE SYSTEMS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BALLINGER, ROBERT S., DUNLAP, KENNETH B., REIHLE, MICHAEL A.
Priority to US09/754,688 priority Critical patent/US6454058B1/en
Priority to EP01204980A priority patent/EP1221558A3/en
Assigned to DELPHI TECHNOLOGIES, INC. reassignment DELPHI TECHNOLOGIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LAYMAN, JOHN C., ZEHNDER, JAMES W.II
Assigned to DELPHI TECHNOLOGIES INC. reassignment DELPHI TECHNOLOGIES INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BALLINGER, ROBERT S., DUNLAP, KENNETH B., REIHLE, MICHAEL A.
Publication of US20020084155A1 publication Critical patent/US20020084155A1/en
Priority to US10/198,533 priority patent/US6655508B2/en
Publication of US6454058B1 publication Critical patent/US6454058B1/en
Application granted granted Critical
Assigned to BWI COMPANY LIMITED S.A. reassignment BWI COMPANY LIMITED S.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DELPHI AUTOMOTIVE SYSTEMS, LLC
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00Parts or details
    • F16D65/0006Noise or vibration control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00Parts or details
    • F16D65/02Braking members; Mounting thereof
    • F16D65/12Discs; Drums for disc brakes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00Parts or details
    • F16D65/02Braking members; Mounting thereof
    • F16D2065/13Parts or details of discs or drums
    • F16D2065/1304Structure
    • F16D2065/1328Structure internal cavities, e.g. cooling channels

Definitions

  • the present invention relates generally to disc brake rotors as used in a vehicle braking system. More particularly, the invention relates to a vehicle brake rotor that incorporates a plurality of vanes designed to reduce noise generated in the brake system.
  • Another technique involves a disc brake pad assembly having clench tabs extending through rubber-like grommets in openings in a caliper housing leg so that the grommets are retained in the openings and the brake pad assembly is retained on the housing leg.
  • the grommets provide a noise dampening action during braking to reduce noise.
  • Every natural frequency of a vibrating system has associated with it a mode shape that describes the pattern of deformation associated with that natural frequency.
  • the mode shape is generally accepted or described by defining the pattern of nodes (loci of points of zero deformation) on the surface of the structure.
  • nodes loci of points of zero deformation
  • the mode shape of an annular circular plate includes nodal circles and diameters.
  • a typical structure of a brake rotor includes a central disc portion that is adapted to be mounted to an axle of a vehicle as in known in the art, by fasteners.
  • An extending portion typically connects one of a pair of rotor friction plates or cheeks to the central disc portion.
  • An outboard plate is the portion of the rotor that includes a friction surface attached to the central disc portion adjacent to the wheel and faces outward from the vehicle body.
  • An inboard plate faces inward toward the vehicle body.
  • a plurality of vanes extend from an inner surface of the first or outboard plate to connect a second inboard plate thereto.
  • the vanes are typically arranged in a radial fashion about the rotor.
  • the vanes hold the first and second plates in a parallel, side-by-side relationship.
  • vanes have an overall regular elongate, rod, coffin or rectangular shape with a generally constant width and cross-sectional area. In other words, many current vanes start out a rectangular cross-section at one end and remain rectangular throughout the longitudinal distance of the vane at an opposite end.
  • a prior-art plate typically has a thickness or cross-section remaining substantially constant along the radial direction.
  • a rotor may possess a number of inherent resonance modes.
  • the rotor may generate vibrations including a mode characterized by radial (and potentially transverse and some tangential) displacement of the plates of the rotor.
  • the rotor may generate vibrations in a mode referred to as an X-mode, characterized by mainly transverse (with some radial and tangential) displacement of the plates of the rotor.
  • a transverse modal vector is defined by one nodal diameters at the friction radius of the rotor and X order nodal diameters defined by the number of transverse antinodes. Coupling of a radial and an X-mode in a rotor results in a hybrid mode vibration. In a hybrid mode, one plate exhibits radial mode behavior and the other plate exhibits X-mode behavior.
  • An aspect present invention provides a rotor for a disc brake including a pair of friction plates arranged coaxially in a parallel, spaced-apart relationship and a plurality of vanes extending between the pair of friction plates.
  • the vanes have a proximal end, a distal end and a mid-portion extending between the proximal end and the distal end.
  • the proximal end of a plurality of the plurality of vanes include a first width, the mid-portion including a second width, the first width being substantially greater than the second width.
  • first width of half the vanes is substantially greater than the second width.
  • the first width of the other half of the vanes can be substantially the same as the second width.
  • the first width of at least half the vanes can be from about 50 percent greater than the second width to about twice that of the second width.
  • a plurality of the plurality of vanes can include an inverted T-shaped portion adjacent the proximal end of the vanes.
  • Half of the vanes can include an inverted T-shaped portion adjacent the proximal end of the vanes.
  • the inverted T-shaped portion is at least 50% wider than a width of the mid-portion.
  • the rotor may further include an angled portion located between each inverted T-shaped portion and the mid-portion.
  • An aspect of the present invention provide a method of reducing noise in a disc brake rotor including stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes and reducing hybrid vibration modes in an audible frequency range.
  • the proximal portion of the plurality of vanes can include an inverted T-shaped portion.
  • Half of the plurality of vanes can include an inverted T-shaped portion at a proximal portion.
  • the other half of the plurality of vanes can include a substantially constant width from a proximal portion to a distal portion of the vanes.
  • a rotor for a disc brake including means for stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes and means for reducing hybrid vibration modes in an audible frequency range.
  • the proximal portion of the plurality of vanes can include an inverted T-shaped portion.
  • Half of the plurality of vanes can include an inverted T-shaped portion at a proximal portion.
  • the other half of the plurality of vanes can include a substantially constant width from a proximal portion to a distal portion of the vanes.
  • FIG. 1 illustrates a perspective view of an embodiment of a brake rotor of the present invention including inverted T-shaped vanes
  • FIG. 2 illustrates an alternating arrangement of the vanes in the brake rotor of FIG. 1;
  • FIG. 3 illustrates a prior art rotor exhibiting deformation generated by a hybrid mode coupling of radial and X-modes of vibration
  • FIG. 4 illustrates an embodiment of the present invention exhibiting less deformation than the rotor of FIG. 3.
  • FIG. 1 one embodiment of a brake rotor is generally shown at numeral 110 .
  • the brake rotor 110 includes a central attachment portion 112 .
  • An extending portion 114 is attached adjacent to the periphery 116 of the central attachment portion 114 .
  • a first friction plate 118 (one of a pair of parallel friction plates) is depicted attached to the central attachment portion 112 by the extending portion 114 .
  • a second friction plate (not shown), which would be oriented in a parallel, spaced apart relationship to the first plate 118 is omitted to show the structure (vanes) therebetween.
  • a plurality of vanes 120 , 122 is provided that extend between the plates and are arranged in a radial fashion.
  • the vanes 120 , 122 are radial members, each having a proximal end 124 , 126 adjacent the extending portion 114 and a middle span or mid-portion 128 , 130 that extends longitudinally in a radial direction to a distal end 132 , 134 .
  • the distal end 132 , 134 is located adjacent the outer periphery 136 of the friction plates.
  • a first and a second set of vanes 120 , 122 are provided between the plates in an alternating arrangement.
  • a first vane 120 is followed by an adjacent second vane 122 , which is followed by a first vane 120 and so on, around the rotor 110 .
  • Each of the first set of vanes 120 has a generally constant width rectangular shape from proximal end 124 to distal end 132 .
  • Each of the second vanes 122 has an inverted T-shape configuration.
  • the inverted T-shaped portion 138 is located in the proximal end 126 of the vane 122 .
  • the middle span 130 of the vane 122 is essentially a longitudinally extending rectangular portion.
  • the vane 122 can include an angled portion 140 between the middle span 130 and the inverted T-shaped portion 138 .
  • the inverted T-shaped portion 138 of the vane 122 can have a width about 50% greater than that of the middle span 130 of the vane 122 .
  • the inverted T-shaped portion 138 of each vane 122 can have a width about twice that of the middle span 130 of the vane 122 .
  • the width of portion 138 can be made from about 50% greater to about twice that of the middle span 130 of the vane 1220 .
  • first vanes 120 and the second vanes 122 in an alternating configuration about the rotor 110 are the first vanes 120 and the second vanes 122 .
  • the first vanes 120 can lack the inverted T-shaped configuration of the proximal portion 126 of the second vanes 122 .
  • the widened portion or inverted T-shaped portion 138 of vanes 122 can add stiffness to the inner diameter or inner periphery 137 of the rotor 110 . This configuration may provide a beneficially modified pattern of nodal resonance modes.
  • FIG. 3 a depiction of a prior art rotor is generally shown at 210 .
  • the rotor 210 includes a central hat or disc portion 212 .
  • An outer plate 218 is connected to the central hat portion 212 .
  • Inner plate 219 is connected to the outer plate 218 by a plurality of conventional vanes, one of which is shown at 220 .
  • the rotor 210 is shown (exaggerated) exhibiting a hybrid mode deformation including 2 nd radial mode and 2 nd X-mode deformation.
  • an embodiment of the present invention includes a rotor depicted in a similar view as that shown in FIG. 3.
  • the rotor 310 includes a central hat or disc portion 312 .
  • An outer plate 318 is connected to the central hat portion 312 .
  • Inner plate 319 is connected to the outer plate 318 by first plurality of vanes, one of which is indicated at 320 and a second plurality of vanes 322 .
  • the vanes 322 may include the inverted T-shaped configuration shown in FIGS. 1 and 2.
  • the rotor of the present invention (depicted in FIG. 4) exhibits less deformation, and thus a lower amplitude or amount of overall vibration.
  • a rotor possesses a number of nodal diameter and circle modes. Each of the nodal modes generates a different pattern of resonant rotor vibration.
  • the n th nodal diameter mode (radial) converges or couples near the same frequency with the one nodal circle mode X-mode)
  • noise is often produced.
  • the convergence of the radial and X-modes produces a hybrid mode shape than contains a contribution from each mode shape.
  • the character of the hybrid mode shape includes one rotor cheek or plate being a radial mode shape and the other rotor cheek being a nodal diameter/nodal circle mode shape.
  • the radial mode content of the hybrid mode receives energy from the tangential forces of the brake linings.
  • the radial mode couples with the nodal circle/nodal diameter mode content to produce out-of-plane motion. This is the mechanism by which the hybrid mode can cause brake noise or squeal.
  • the inverted T-shape vane design increases the stiffness of the nodal circle/nodal diameter modes, thereby moving their frequencies higher in the spectrum than the radial modes.
  • the inverted T-shape vanes reduces or eliminates the hybrid coupling of these modes.

Abstract

A disc brake including a pair of friction plates arranged coaxially in a parallel, spaced-apart relationship and a plurality of vanes extending between the pair of friction plates, each of said vanes having a proximal end, a distal end and a mid-portion extending between the proximal end and the distal end, the proximal ends of a plurality of the vanes having a first width, the mid-portion having a second width, the first width being substantially greater than the second width. The vanes can include a T-shaped portion adjacent the proximal end.

Description

    TECHNICAL FIELD
  • The present invention relates generally to disc brake rotors as used in a vehicle braking system. More particularly, the invention relates to a vehicle brake rotor that incorporates a plurality of vanes designed to reduce noise generated in the brake system. [0001]
  • BACKGROUND OF THE INVENTION
  • Noise generated during a brake application has been increasing as the size of vehicles has been decreasing. Attempts have been made to reduce the noise generated using various systems and methods. One such technique involves the use of sound adsorption coatings on the pad assembly. While such coatings have some effectiveness, the addition of the coating adds cost to the manufacture and at times, undesirable noise occurs when the thickness of the coating has not been uniform. [0002]
  • Another technique involves a disc brake pad assembly having clench tabs extending through rubber-like grommets in openings in a caliper housing leg so that the grommets are retained in the openings and the brake pad assembly is retained on the housing leg. The grommets provide a noise dampening action during braking to reduce noise. [0003]
  • Individual noise problems have been reduced through the modification of the ingredients in the composition of materials that make up a brake pad. In many of these cases, while noise may have been abated somewhat, the braking effectiveness of the system has been changed by the modification of the brake pad material. Still another technique of reducing brake noise involves affixing a ring damper about a periphery of a brake rotor in a disc brake system. The ring damper is held in place by a groove formed in the periphery of the disc and is pre-loaded against the rotor both radially and transversely. [0004]
  • The above techniques involve the reduction of noise by absorbing or masking the noise after it has been created or by adding costly complexity to the braking system. It would be advantageous to design the system to reduce the potential for the creation of noise. It has been suggested that much of brake squeal or noise is influenced by the excitation of the natural frequencies of a rotor caused by the rubbing of friction pads on a rotor surface. There is evidence that a disc brake rotor may have a dozen or more naturally occurring frequencies. While most of these are in the axial direction, others are in the torsional direction. In simulated braking applications only certain of these natural frequencies create brake noise or squeal. Every natural frequency of a vibrating system has associated with it a mode shape that describes the pattern of deformation associated with that natural frequency. In a continuous structure, the mode shape is generally accepted or described by defining the pattern of nodes (loci of points of zero deformation) on the surface of the structure. Experiments have shown that the mode shape of an annular circular plate, a shape like that of a brake rotor, includes nodal circles and diameters. Thus, a beneficial effect on brake noise should be attainable if the nodal diameter modes of an installed disc rotor are maintained at a maximum separation, thereby reducing or eliminating coupling of the nodal diameter modes in the audible frequency range. [0005]
  • A typical structure of a brake rotor includes a central disc portion that is adapted to be mounted to an axle of a vehicle as in known in the art, by fasteners. An extending portion typically connects one of a pair of rotor friction plates or cheeks to the central disc portion. An outboard plate is the portion of the rotor that includes a friction surface attached to the central disc portion adjacent to the wheel and faces outward from the vehicle body. An inboard plate faces inward toward the vehicle body. [0006]
  • A plurality of vanes extend from an inner surface of the first or outboard plate to connect a second inboard plate thereto. The vanes are typically arranged in a radial fashion about the rotor. The vanes hold the first and second plates in a parallel, side-by-side relationship. Typically, vanes have an overall regular elongate, rod, coffin or rectangular shape with a generally constant width and cross-sectional area. In other words, many current vanes start out a rectangular cross-section at one end and remain rectangular throughout the longitudinal distance of the vane at an opposite end. Similarly, a prior-art plate typically has a thickness or cross-section remaining substantially constant along the radial direction. [0007]
  • A rotor may possess a number of inherent resonance modes. In use, the rotor may generate vibrations including a mode characterized by radial (and potentially transverse and some tangential) displacement of the plates of the rotor. Further, the rotor may generate vibrations in a mode referred to as an X-mode, characterized by mainly transverse (with some radial and tangential) displacement of the plates of the rotor. A transverse modal vector is defined by one nodal diameters at the friction radius of the rotor and X order nodal diameters defined by the number of transverse antinodes. Coupling of a radial and an X-mode in a rotor results in a hybrid mode vibration. In a hybrid mode, one plate exhibits radial mode behavior and the other plate exhibits X-mode behavior. [0008]
  • It would be advantageous to provide an apparatus and method to prevent the occurrence of hybrid mode behavior in a disc brake rotor. [0009]
  • SUMMARY OF THE INVENTION
  • An aspect present invention provides a rotor for a disc brake including a pair of friction plates arranged coaxially in a parallel, spaced-apart relationship and a plurality of vanes extending between the pair of friction plates. The vanes have a proximal end, a distal end and a mid-portion extending between the proximal end and the distal end. The proximal end of a plurality of the plurality of vanes include a first width, the mid-portion including a second width, the first width being substantially greater than the second width. [0010]
  • Other aspects of the present invention provide a rotor wherein the first width of half the vanes is substantially greater than the second width. The first width of the other half of the vanes can be substantially the same as the second width. The first width of at least half the vanes can be from about 50 percent greater than the second width to about twice that of the second width. [0011]
  • In another aspect of the invention, a plurality of the plurality of vanes can include an inverted T-shaped portion adjacent the proximal end of the vanes. Half of the vanes can include an inverted T-shaped portion adjacent the proximal end of the vanes. The inverted T-shaped portion is at least 50% wider than a width of the mid-portion. The rotor may further include an angled portion located between each inverted T-shaped portion and the mid-portion. [0012]
  • An aspect of the present invention provide a method of reducing noise in a disc brake rotor including stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes and reducing hybrid vibration modes in an audible frequency range. The proximal portion of the plurality of vanes can include an inverted T-shaped portion. Half of the plurality of vanes can include an inverted T-shaped portion at a proximal portion. The other half of the plurality of vanes can include a substantially constant width from a proximal portion to a distal portion of the vanes. [0013]
  • Another aspect of the present invention provides a rotor for a disc brake including means for stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes and means for reducing hybrid vibration modes in an audible frequency range. The proximal portion of the plurality of vanes can include an inverted T-shaped portion. Half of the plurality of vanes can include an inverted T-shaped portion at a proximal portion. The other half of the plurality of vanes can include a substantially constant width from a proximal portion to a distal portion of the vanes. [0014]
  • The foregoing and other features and advantages of the invention will become further apparent from the following detailed description of the presently preferred embodiments, read in conjunction with the accompanying drawings. The detailed description and drawings are merely illustrative of the invention rather than limiting, the scope of the invention being defined by the appended claims and equivalents thereof.[0015]
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 illustrates a perspective view of an embodiment of a brake rotor of the present invention including inverted T-shaped vanes; [0016]
  • FIG. 2 illustrates an alternating arrangement of the vanes in the brake rotor of FIG. 1; [0017]
  • FIG. 3 illustrates a prior art rotor exhibiting deformation generated by a hybrid mode coupling of radial and X-modes of vibration; and [0018]
  • FIG. 4 illustrates an embodiment of the present invention exhibiting less deformation than the rotor of FIG. 3. [0019]
  • DESCRIPTION OF THE PREFERRED EMBODIMENT
  • Referring to FIG. 1 one embodiment of a brake rotor is generally shown at [0020] numeral 110. The brake rotor 110 includes a central attachment portion 112. An extending portion 114 is attached adjacent to the periphery 116 of the central attachment portion 114. A first friction plate 118 (one of a pair of parallel friction plates) is depicted attached to the central attachment portion 112 by the extending portion 114. A second friction plate (not shown), which would be oriented in a parallel, spaced apart relationship to the first plate 118 is omitted to show the structure (vanes) therebetween. A plurality of vanes 120, 122 is provided that extend between the plates and are arranged in a radial fashion. The vanes 120, 122 are radial members, each having a proximal end 124, 126 adjacent the extending portion 114 and a middle span or mid-portion 128, 130 that extends longitudinally in a radial direction to a distal end 132, 134. The distal end 132, 134 is located adjacent the outer periphery 136 of the friction plates.
  • In one embodiment, a first and a second set of [0021] vanes 120, 122 are provided between the plates in an alternating arrangement. In other words, a first vane 120 is followed by an adjacent second vane 122, which is followed by a first vane 120 and so on, around the rotor 110. Each of the first set of vanes 120 has a generally constant width rectangular shape from proximal end 124 to distal end 132. Each of the second vanes 122 has an inverted T-shape configuration. The inverted T-shaped portion 138 is located in the proximal end 126 of the vane 122. The middle span 130 of the vane 122 is essentially a longitudinally extending rectangular portion. The vane 122 can include an angled portion 140 between the middle span 130 and the inverted T-shaped portion 138. The inverted T-shaped portion 138 of the vane 122 can have a width about 50% greater than that of the middle span 130 of the vane 122. The inverted T-shaped portion 138 of each vane 122 can have a width about twice that of the middle span 130 of the vane 122. Also, the width of portion 138 can be made from about 50% greater to about twice that of the middle span 130 of the vane 1220.
  • Referring to FIGS. 1 and 2, in an alternating configuration about the [0022] rotor 110 are the first vanes 120 and the second vanes 122. The first vanes 120 can lack the inverted T-shaped configuration of the proximal portion 126 of the second vanes 122. The widened portion or inverted T-shaped portion 138 of vanes 122 can add stiffness to the inner diameter or inner periphery 137 of the rotor 110. This configuration may provide a beneficially modified pattern of nodal resonance modes.
  • Referring to FIG. 3, a depiction of a prior art rotor is generally shown at [0023] 210. The rotor 210 includes a central hat or disc portion 212. An outer plate 218 is connected to the central hat portion 212. Inner plate 219 is connected to the outer plate 218 by a plurality of conventional vanes, one of which is shown at 220. In this illustration, the rotor 210 is shown (exaggerated) exhibiting a hybrid mode deformation including 2nd radial mode and 2nd X-mode deformation.
  • Referring to FIG. 4, an embodiment of the present invention includes a rotor depicted in a similar view as that shown in FIG. 3. The rotor [0024] 310 includes a central hat or disc portion 312. An outer plate 318 is connected to the central hat portion 312. Inner plate 319 is connected to the outer plate 318 by first plurality of vanes, one of which is indicated at 320 and a second plurality of vanes 322. The vanes 322 may include the inverted T-shaped configuration shown in FIGS. 1 and 2. Compared to the prior art rotor of FIG. 3, the rotor of the present invention (depicted in FIG. 4) exhibits less deformation, and thus a lower amplitude or amount of overall vibration.
  • As discussed above, a rotor possesses a number of nodal diameter and circle modes. Each of the nodal modes generates a different pattern of resonant rotor vibration. When the n[0025] th nodal diameter mode (radial) converges or couples near the same frequency with the one nodal circle mode X-mode), noise is often produced. The convergence of the radial and X-modes produces a hybrid mode shape than contains a contribution from each mode shape. The character of the hybrid mode shape includes one rotor cheek or plate being a radial mode shape and the other rotor cheek being a nodal diameter/nodal circle mode shape. The radial mode content of the hybrid mode receives energy from the tangential forces of the brake linings. The radial mode couples with the nodal circle/nodal diameter mode content to produce out-of-plane motion. This is the mechanism by which the hybrid mode can cause brake noise or squeal. In operation, the inverted T-shape vane design increases the stiffness of the nodal circle/nodal diameter modes, thereby moving their frequencies higher in the spectrum than the radial modes. The inverted T-shape vanes reduces or eliminates the hybrid coupling of these modes.
  • While the embodiments of the invention disclosed herein are presently considered to be preferred, various changes and modifications can be made without departing from the spirit and scope of the invention. The scope of the invention is indicated in the appended claims, and all changes that come within the meaning and range of equivalents are intended to be embraced therein. [0026]

Claims (17)

1. A rotor for a disc brake comprising:
a pair of friction plates arranged coaxially in a parallel, spaced-apart relationship; and
a plurality of vanes extending between the pair of friction plates, each of the vanes having a proximal end, a distal end and a mid-portion extending between the proximal end and the distal end, the proximal end of a plurality of the plurality of vanes including a first width, the mid-portion including a second width, the first width being greater than the second width.
2. The rotor of claim 1 wherein the first width is substantially greater than the second width.
3. The rotor of claim 2 wherein the vanes other than the vanes having the first width have a third width, the third width being substantially the same as the second width.
4. The rotor of claim 2 wherein the first width is about 50 percent greater than the second width.
5. The rotor of claim 1 wherein the first width is about twice that of the second width.
6. The rotor of claim 1 wherein a plurality of the plurality of vanes includes an inverted T-shaped portion adjacent the proximal end of the vanes.
7. The rotor of claim 6 wherein at least half of the vanes include an inverted T-shaped portion adjacent the proximal end of the vanes.
8. The rotor of claim 6 wherein the inverted T-shaped portion is at least 50% wider than the second width.
9. The rotor of claim 6 further comprising an angled portion located between each inverted T-shaped portion and a respective mid-portion.
10. A method of reducing noise in a disc brake rotor comprising:
stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes; and
reducing hybrid vibration modes in an audible frequency range.
11. The method of claim 10 wherein the proximal portion of the plurality of vanes includes an inverted T-shaped portion.
12. The method of claim 11 wherein at least one half of the plurality of vanes include an inverted T-shaped portion at the proximal portion.
13. The method of claim 12 wherein each vane other than the lat least one half of the plurality of vanes includes a substantially constant width from a proximal portion to a distal portion.
14. A rotor for a disc brake comprising:
means for stiffening a radially inner portion of the brake rotor with a proximal portion of a plurality of vanes; and
means for reducing hybrid vibration modes in an audible frequency range.
15. The rotor of claim 14 wherein the proximal portion of the plurality of vanes includes an inverted T-shaped portion.
16. The rotor of claim 15 wherein at least one half of the plurality of vanes include an inverted T-shaped portion at a proximal portion.
17. The rotor of claim 16 wherein each vane other than the at least one half of the plurality of vanes include a substantially constant width from a proximal portion to a distal portion.
US09/754,688 2001-01-03 2001-01-03 Disc brake rotor Expired - Lifetime US6454058B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US09/754,688 US6454058B1 (en) 2001-01-03 2001-01-03 Disc brake rotor
EP01204980A EP1221558A3 (en) 2001-01-03 2001-12-18 Disc brake rotor
US10/198,533 US6655508B2 (en) 2001-01-03 2002-07-18 Disc brake rotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US09/754,688 US6454058B1 (en) 2001-01-03 2001-01-03 Disc brake rotor

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10/198,533 Division US6655508B2 (en) 2001-01-03 2002-07-18 Disc brake rotor

Publications (2)

Publication Number Publication Date
US20020084155A1 true US20020084155A1 (en) 2002-07-04
US6454058B1 US6454058B1 (en) 2002-09-24

Family

ID=25035876

Family Applications (2)

Application Number Title Priority Date Filing Date
US09/754,688 Expired - Lifetime US6454058B1 (en) 2001-01-03 2001-01-03 Disc brake rotor
US10/198,533 Expired - Lifetime US6655508B2 (en) 2001-01-03 2002-07-18 Disc brake rotor

Family Applications After (1)

Application Number Title Priority Date Filing Date
US10/198,533 Expired - Lifetime US6655508B2 (en) 2001-01-03 2002-07-18 Disc brake rotor

Country Status (2)

Country Link
US (2) US6454058B1 (en)
EP (1) EP1221558A3 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100282552A1 (en) * 2008-03-12 2010-11-11 Bayerische Motoren Werke Aktiengesellschaft Brake Disc Having Ribs Arranged Between Two Friction Rings
US8668058B2 (en) 2005-03-30 2014-03-11 Federal-Mogul Worldwide, Inc. Vented disc brake rotor

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6454058B1 (en) * 2001-01-03 2002-09-24 Delphi Technologies, Inc. Disc brake rotor
US20090000884A1 (en) 2007-06-26 2009-01-01 Akebono Corporation (North America) Brake rotor
US20090050422A1 (en) * 2007-08-23 2009-02-26 Akebono Corporation (North America) Grooved disc brake rotor
US20090166137A1 (en) * 2007-08-23 2009-07-02 Akebono Corporation (North America) Retracted vane rotor
US8336682B2 (en) * 2007-08-31 2012-12-25 Honda Motor Co., Ltd. Ventilated brake disk and method
US7922839B2 (en) * 2007-10-04 2011-04-12 Miks Engineering Method for brake rotor assembly and manufacture
US20100206674A1 (en) 2009-02-16 2010-08-19 Gm Global Technology Operations, Inc. Disc Brake Rotors with Tilted Vane Geometry
DE102019129447A1 (en) * 2019-10-31 2021-05-06 Bayerische Motoren Werke Aktiengesellschaft Web arrangement for an internally ventilated brake disc

Family Cites Families (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2603316A (en) * 1952-07-15 Brake rotor
US2412432A (en) * 1945-04-26 1946-12-10 American Steel Foundries Brake rotor
US2627325A (en) * 1949-08-06 1953-02-03 American Steel Foundries Brake rotor
DE1210266B (en) * 1958-12-31 1966-02-03 Schuler L Ag Disc friction clutch for presses
GB1156316A (en) * 1965-07-21 1969-06-25 Dunlop Co Ltd Disc Brakes
US3298476A (en) * 1965-08-13 1967-01-17 Budd Co Disc brake rotor
JPS56120833A (en) * 1980-02-27 1981-09-22 Nissan Motor Co Ltd Disc brake rotor
JPS56164237A (en) * 1980-05-21 1981-12-17 Nissan Motor Co Ltd Disc brake rotor
GB2144186A (en) * 1983-07-07 1985-02-27 Powell Duffryn Castings Limite Disc for disc brake
US4523666A (en) * 1983-08-03 1985-06-18 Motor Wheel Corporation Brake rotor with vibration harmonic suppression, and method of manufacture
US4705146A (en) * 1984-04-02 1987-11-10 Allied Corporation Disc brake
DE3432374A1 (en) * 1984-09-03 1986-04-30 Knorr-Bremse AG, 8000 München SHAFT BRAKE DISC, IN PARTICULAR FOR DISC BRAKES OF RAIL VEHICLES
GB8502954D0 (en) * 1985-02-06 1985-03-06 Lucas Industries Ltd Discs
US6260699B1 (en) * 1987-08-26 2001-07-17 United States Surgical Corporation Packaged synthetic absorbable surgical elements
US5161652A (en) * 1988-10-18 1992-11-10 Honda Giken Kogyo Kabushiki Kaisha Ventilated disk brake rotor
US5139117A (en) * 1990-08-27 1992-08-18 General Motors Corporation Damped disc brake rotor
EP0512853B1 (en) * 1991-05-10 1996-08-21 KIRIU MACHINE MFG. Co., Ltd. Ventilated-type disc rotor
JPH05240276A (en) * 1992-02-28 1993-09-17 Aisin Takaoka Ltd Ventilated disk
JP3252157B2 (en) * 1992-07-15 2002-01-28 株式会社豊田中央研究所 Brake disc rotor
US5492205A (en) * 1994-08-29 1996-02-20 General Motors Corporation High cooling air flow rate brake rotor
US5544726A (en) * 1994-09-06 1996-08-13 Ford Motor Company Brake rotor with flow through ventilation
US5542503A (en) * 1995-06-06 1996-08-06 Kelsey-Hayes Company Rotor for disc brake assembly
GB2307959B (en) * 1995-12-05 1999-11-10 T & N Technology Ltd Disc brake rotors
JP3450158B2 (en) * 1996-07-24 2003-09-22 トヨタ自動車株式会社 Disc rotor for disc brake
JP3480264B2 (en) * 1997-09-18 2003-12-15 日産自動車株式会社 Ventilated rotor
US6193023B1 (en) * 1997-12-23 2001-02-27 Hayes Lemmerz International, Inc. Rotor with alternate rib designs
JPH11257386A (en) * 1998-03-10 1999-09-21 Nissan Motor Co Ltd Brake disk
US6053290A (en) * 1998-06-19 2000-04-25 Dana Corporation Dual web brake rotor
JP3777811B2 (en) * 1998-07-29 2006-05-24 日産自動車株式会社 Brake disc rotor
US6241055B1 (en) * 1998-09-11 2001-06-05 Hayes Lemmerz International, Inc. Rotor with viscoelastic vibration reducing element and method of making the same
US6454058B1 (en) * 2001-01-03 2002-09-24 Delphi Technologies, Inc. Disc brake rotor
US6405839B1 (en) * 2001-01-03 2002-06-18 Delphi Technologies, Inc. Disc brake rotor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8668058B2 (en) 2005-03-30 2014-03-11 Federal-Mogul Worldwide, Inc. Vented disc brake rotor
US20100282552A1 (en) * 2008-03-12 2010-11-11 Bayerische Motoren Werke Aktiengesellschaft Brake Disc Having Ribs Arranged Between Two Friction Rings
US8869953B2 (en) * 2008-03-12 2014-10-28 Bayerische Motoren Werke Aktiengesellschaft Brake disc having ribs arranged between two friction rings

Also Published As

Publication number Publication date
US6454058B1 (en) 2002-09-24
US6655508B2 (en) 2003-12-02
EP1221558A2 (en) 2002-07-10
US20020179383A1 (en) 2002-12-05
EP1221558A3 (en) 2003-12-17

Similar Documents

Publication Publication Date Title
US6405839B1 (en) Disc brake rotor
EP0205713B1 (en) Brake rotor with vibration harmonic suppression
US6454058B1 (en) Disc brake rotor
EP1551646B1 (en) Reduction of torsional vibration in rail vehicle wheel sets
US8668058B2 (en) Vented disc brake rotor
US20030037999A1 (en) Vibration inhibiting structure for rotor
JPH04503239A (en) dual disc brake
CA1211386A (en) Disc brake assembly
US3983973A (en) Vibration damper for a brake disk
US6467590B2 (en) Arrangement for preventing the squealing of a disk brake
JP7209703B2 (en) brake device
WO2003021126A1 (en) Multi-disc brake structural assymmetry
US5971112A (en) Drum brake assembly and brake shoes for same
JP2002295549A (en) Disk brake
US20020056597A1 (en) Assembly for vehicle brake disk
JPH11287266A (en) Disc brake
JPS6288823A (en) Clutch plate assembly containing no asbestos
WO2020128705A1 (en) Braking band of a disc for disc brake of ventilated type
JPS59194139A (en) Ventilated brake disk
JPH07167176A (en) Disk brake
JP2001227571A (en) Disk rotor for disk brake
JP4998327B2 (en) Disc rotor mounting structure
US20200166093A1 (en) Brake disc for a vehicle disc brake
JPH0254452B2 (en)
JPH07208517A (en) Brake drum having vibration damping structure

Legal Events

Date Code Title Description
AS Assignment

Owner name: DELPHI AUTOMOTIVE SYSTEMS, MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BALLINGER, ROBERT S.;DUNLAP, KENNETH B.;REIHLE, MICHAEL A.;REEL/FRAME:011451/0295;SIGNING DATES FROM 20001221 TO 20001222

AS Assignment

Owner name: DELPHI TECHNOLOGIES, INC., MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ZEHNDER, JAMES W.II;LAYMAN, JOHN C.;REEL/FRAME:012752/0621

Effective date: 20001221

AS Assignment

Owner name: DELPHI TECHNOLOGIES INC., MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BALLINGER, ROBERT S.;DUNLAP, KENNETH B.;REIHLE, MICHAEL A.;REEL/FRAME:012779/0152;SIGNING DATES FROM 20001221 TO 20001222

STCF Information on status: patent grant

Free format text: PATENTED CASE

FPAY Fee payment

Year of fee payment: 4

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 8

AS Assignment

Owner name: BWI COMPANY LIMITED S.A., LUXEMBOURG

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DELPHI AUTOMOTIVE SYSTEMS, LLC;REEL/FRAME:024892/0813

Effective date: 20091101

FPAY Fee payment

Year of fee payment: 12