WO2013145427A1 - Rotor à disque - Google Patents

Rotor à disque Download PDF

Info

Publication number
WO2013145427A1
WO2013145427A1 PCT/JP2012/079561 JP2012079561W WO2013145427A1 WO 2013145427 A1 WO2013145427 A1 WO 2013145427A1 JP 2012079561 W JP2012079561 W JP 2012079561W WO 2013145427 A1 WO2013145427 A1 WO 2013145427A1
Authority
WO
WIPO (PCT)
Prior art keywords
fin
fins
disk rotor
fin group
circumferential direction
Prior art date
Application number
PCT/JP2012/079561
Other languages
English (en)
Japanese (ja)
Inventor
智宏 横山
松島　徹
範嘉 松井
Original Assignee
トヨタ自動車株式会社
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
Priority claimed from JP2012082463A external-priority patent/JP2013210090A/ja
Priority claimed from JP2012082462A external-priority patent/JP5742773B2/ja
Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Publication of WO2013145427A1 publication Critical patent/WO2013145427A1/fr

Links

Images

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
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—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
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels

Definitions

  • the present invention relates to a disk rotor.
  • the disc brake generates braking torque by bringing the pad into contact with the rotating disc rotor by the hydraulic pressure of the hydraulic cylinder, for example.
  • vibration occurs when the pad comes into contact with the rotating disc rotor, and so-called brake noise occurs when the rotating disc rotor and the pad resonate.
  • the brake squeal includes out-of-plane squeal and in-plane squeal.
  • Out-of-plane squeal is caused by out-of-plane vibration in which the friction surface with which the pad of the disk rotor comes in contact swings in the same direction as the rotation axis.
  • In-plane squeal is caused by in-plane vibration in which the friction surface of the disk rotor vibrates in the circumferential direction of the disk rotor.
  • Measures against out-of-plane noise include those shown in Patent Document 1.
  • Patent Document 1 out-of-plane squealing caused by high-order out-of-plane vibration with a rotor order of 5 to 7 is suppressed, and four sets of fins having different shapes are configured as a set, and the set is arranged around the rotor circumference. It is periodically arranged in the direction.
  • the present invention has been made in view of the above, and an object of the present invention is to provide a disc rotor that can suppress the occurrence of in-plane noise.
  • the present invention provides a braking force in which a plurality of fins are formed in the circumferential direction between opposed sliding plates, and a pad contacts the sliding plates.
  • the fin includes a first fin group including a plurality of first fins, and a plurality of second fins including at least one of a shape and a material different from the first fin.
  • the predetermined angle is preferably 45 degrees or 90 degrees.
  • the second fin located at the end adjacent to the first fin group of the second fin group has a smaller amount of change in shape than the second fin located at the center. Is preferred.
  • the plurality of first fins and the plurality of second fins have different lengths in the radial direction of the fins.
  • the plurality of first fins and the plurality of second fins have different widths.
  • the plurality of first fins and the plurality of second fins have different fin widths, and the change amount is a change amount of the fin width.
  • the plurality of first fins have the same shape and material
  • the plurality of second fins have the same shape and material
  • the plurality of first fins have the same shape and material, and the plurality of second fins have the same material.
  • the present invention generates a braking force by forming a plurality of fins in the circumferential direction between the opposing sliding plates and contacting the pads.
  • the fins include a first fin group including a plurality of first fins, and a second fin group including a plurality of second fins having at least one of shape and material different from the first fin.
  • the first fin group and the second fin group are alternately arranged for each region divided into a predetermined number at equal intervals or substantially equal intervals in the circumferential direction.
  • the predetermined number is preferably 8 or 4.
  • the second fin located at the end adjacent to the first fin group of the second fin group has a smaller amount of change in shape than the second fin located at the center. Is preferred.
  • the disc rotor according to the present invention has an effect of suppressing the occurrence of in-plane noise.
  • FIG. 1 is a diagram illustrating a configuration example of a disc brake device including a disc rotor according to the embodiment.
  • FIG. 2 is a diagram illustrating the disk rotor according to the first embodiment.
  • FIG. 3A is a diagram illustrating a frequency analysis result of the disk rotor according to the first embodiment.
  • FIG. 3B is a diagram illustrating a frequency analysis result of the disk rotor according to the first embodiment.
  • FIG. 4A is a diagram illustrating a frequency analysis result of the disk rotor according to the first embodiment.
  • FIG. 4B is a diagram of a frequency analysis result of the disk rotor according to the first embodiment.
  • FIG. 5A is a diagram illustrating a frequency analysis result of a conventional disk rotor.
  • FIG. 5B is a diagram illustrating a frequency analysis result of the conventional disk rotor.
  • FIG. 6A is a diagram illustrating a result of brake squeal of the disc rotor according to the first embodiment.
  • FIG. 6B is a diagram illustrating a result of brake squeal of the disc rotor according to the first embodiment.
  • FIG. 6-3 is a diagram illustrating a result of brake squeal of a conventional disk rotor.
  • FIG. 7-1 is a diagram illustrating a distribution of occurrence of brake squeal in the disk rotor according to the first embodiment.
  • FIG. 7-2 is a diagram illustrating a distribution of occurrence of brake squeal in the disk rotor according to the first embodiment.
  • FIG. 7-3 is a diagram showing a distribution of occurrence of brake squeal in the conventional disk rotor.
  • FIG. 8 is a diagram illustrating the relationship between mode A and mode B.
  • FIG. 9 is a diagram illustrating a disk rotor according to the second embodiment.
  • FIG. 10 is a diagram illustrating a disk rotor according to the third embodiment.
  • FIG. 11 is a diagram illustrating a disk rotor according to the fourth embodiment.
  • FIG. 1 is a diagram illustrating a configuration example of a disc brake device including a disc rotor according to the embodiment.
  • FIG. 2 is a diagram illustrating the disk rotor according to the first embodiment.
  • FIG. 2 is a cross-sectional view in a plane orthogonal to the rotation axis of the disk rotor.
  • the disc rotor 1-1 As shown in FIG. 1, the disc rotor 1-1 according to the first embodiment is used in a disc brake device 100.
  • pads 102 and 103 provided on the caliper 101 are disposed so as to face the sliding plates 2 and 3 of the disc rotor 1-1 in the direction of the rotation axis of the disc rotor 1-1.
  • a hydraulic cylinder (not shown) is provided in the caliper 101. The distance between the pads 102 and 103 is reduced by the pressing force generated by the hydraulic cylinder, and the sliding of the disk rotor 1-1 that rotates integrally with a wheel (not shown). A frictional force is generated when the pads 102 and 103 come into contact with the moving plates 2 and 3, respectively.
  • the generated frictional force acts on the caliper 101 in a direction opposite to the rotation direction of the disc rotor 1-1, and becomes a braking force that decelerates a vehicle (not shown). That is, the disc rotor 1-1 generates a braking force.
  • the disk rotor 1-1 is a ventilated disk rotor.
  • the in-plane secondary mode is called a node (with respect to the node) every 90 degrees in the circumferential direction of the disk rotor 1-1.
  • the brake squeal that has 45 degrees becomes a stomach).
  • the disk rotor 1-1 is formed by casting a metal material such as cast iron, and includes two sliding plates 2 and 3 and a plurality of fins 4.
  • the sliding plate 2 is formed with a fixing portion 5 to which a wheel is fixed projecting in the rotation axis direction, and a fitting hole 6 to which a drive shaft (not shown) is fixed is formed.
  • the two sliding plates 2 and 3 are opposed to each other in the rotation axis direction, and a plurality of fins 4 are formed between the sliding plates 2 and 3.
  • the plurality of fins 4 are continuously formed in the circumferential direction, and both end portions in the rotation axis direction are respectively connected to the sliding plates 2 and 3.
  • a plurality of 40 fins 4 are arranged at equal intervals, and the fins 4 are divided into a first fin group 41 and a second fin group 42, and each group is alternately arranged in the circumferential direction.
  • Each first fin group 41 includes the same number of first fins 4a in the present embodiment.
  • each second fin group 42 is composed of the same number, in the present embodiment, five second fins 4b.
  • the first fin group 41 and the second fin group 42 are alternately arranged at predetermined angles in the circumferential direction with respect to the sliding plates 2 and 3, and in this embodiment, every 45 degrees. That is, the first fin group 41 and the second fin group 42 have a predetermined number of circumferentially equal intervals with respect to the sliding plates 2 and 3, and A1 continuous in the circumferential direction, which is an eight-divided region in this embodiment. Alternatingly arranged for each A8.
  • the first fin group 41 is arranged at A1, A3, A5, A7, and the second fin group 42 is arranged at A2, A4, A6, A8.
  • Each first fin 4a is made of the same material and has the same shape.
  • each 2nd fin 4b is formed with the same material and the same shape.
  • the first fin 4a and the second fin 4b are made of the same material but have different shapes.
  • the first fin 4a and the second fin 4b have the same fin width (the length in the direction orthogonal to the radial direction of the fin 4) without change, but the fin length (the radial length of the fin 4). ),
  • the second fin 4b is shorter than the first fin 4a.
  • Both the first fin 4a and the second fin 4b have a substantially rectangular cross section (both ends in the radial direction are arcs, and the fin width on the radially inner outside is 5 mm).
  • the second fin 4b has a smaller fin length than the first fin 4a, and therefore has a small mass and a low rigidity. That is, the second fin group 42 has a smaller mass and lower rigidity than the first fin group 41. Therefore, the mass and rigidity of the disk rotor 1-1 periodically change at intervals of 45 degrees in the circumferential direction.
  • in-plane squeal is considered to be the cause of brake squeal in the combined wave of SIN wave and COS wave (moving wave) with the center of the pads 102 and 103 as the reference, and these two waves being at the same frequency.
  • the in-plane noise can be suppressed by decomposing and controlling the two synthesized waves, that is, by operating the eigenvalue of the disk rotor 1-1. Since the frequency is a relationship between rigidity and mass, in this embodiment, the eigenvalue of the disk rotor 1-1 in the in-plane secondary mode is changed mainly by changing the mass.
  • the first fin group 41 and the second fin group 42 are alternately arranged at 45 degrees in the circumferential direction, and the mass is changed by 45 degrees in the circumferential direction, thereby changing the frequency in the in-plane direction by 45 degrees.
  • the eigenvalues of the disk rotor 1-1 in the in-plane secondary mode are separated.
  • FIGS. 3-1, FIG. 3-2, FIG. 4-1, and FIG. 4-2 are diagrams showing the frequency analysis results of the disk rotor according to the first embodiment.
  • FIGS. 5A and 5B are diagrams showing the frequency analysis results of the conventional disk rotor.
  • the vertical axis represents sound pressure (dB) and the horizontal axis represents frequency (kHz).
  • the disk rotor 1-1 according to the first embodiment in FIGS. 3A and 3B is different from the disk rotor 1-1 according to the first embodiment in FIGS. 4A and 4B.
  • the length of the 2nd fin 4b of the fin group 42 is short, ie, mass is small.
  • FIGS. 5A and 5B are regions in which the first fin group 41 of the disc rotor 1-1 is disposed (any one of A1, A3, A5, and A7). It is a frequency result at the time of hammering the radial direction outer side edge part in the center part of tangential.
  • the conventional disk rotor in FIGS. 5A and 5B is a disk rotor in which a plurality of fins 4 are all the second fins 4b and 40 are arranged at equal intervals.
  • FIG. 5A is a frequency result when an arbitrary radially outer end of a conventional disk rotor is hammered in a tangential direction.
  • FIG. 5B is a frequency result when the radially outer end portion of the conventional disc rotor that is shifted by 45 degrees in the circumferential direction from the position hammered in FIG. 5A is hammered in the tangential direction.
  • F 12 about 11800 Hz).
  • the shorter the second fin 4b that is, the smaller the mass, the greater the peak frequency separation in the in-plane secondary mode. That is, when the mass of the second fin group 42 is smaller than the mass of the first fin group 41, the peak frequency in the in-plane secondary mode corresponding to the second fin group 42 is in the plane corresponding to the first fin group 41. Since the frequency is higher than the peak frequency in the secondary mode, the change in mass between the first fin group 41 and the second fin group 42, that is, the change in mass by 45 degrees, the disc rotor 1-in the in-plane secondary mode. One eigenvalue can be separated.
  • FIGS. 6A and 6B are diagrams illustrating the result of brake squeal of the disk rotor according to the first embodiment.
  • FIG. 6-3 is a diagram illustrating a result of brake squeal of a conventional disk rotor.
  • FIGS. 7A and 7B are diagrams illustrating the distribution of occurrence of brake squeal in the disk rotor according to the first embodiment.
  • FIG. 7-3 is a diagram showing a distribution of occurrence of brake squeal in the conventional disk rotor.
  • FIG. 8 is a diagram illustrating the relationship between mode A and mode B. “A1, B1” in FIGS.
  • FIGS. 6-1, 7-1, and 8 correspond to the disk rotor 1-1 according to the first embodiment in FIGS. 3-1 and 3-2.
  • “A2, B2” in FIGS. 6-2, 7-2, and 8 correspond to the disk rotor 1-1 according to the first embodiment in FIGS. 4-1 and 4-2.
  • “A3, B3” in FIGS. 6-3, 7-3, and 8 correspond to the conventional disk rotors in FIGS. 5-1 and 5-2.
  • the vertical axis represents sound pressure (dB)
  • the horizontal axis represents frequency (kHz)
  • Batsu is a point where a brake squeal occurred.
  • the vertical axis represents the frequency (kHz) and the horizontal axis represents the hydraulic pressure (MPa) in the hydraulic cylinder. ”, Small level“ black square ”, and medium level“ black circle ”.
  • the vertical axis represents frequency (kHz) and the horizontal axis represents hydraulic pressure (MPa) in the hydraulic cylinder.
  • In-plane secondary squeal (about 11.65 kHz) generated by the disk rotor 1-1 indicated by “Y” in FIG. 6B and the surface generated by the disk rotor 1-1 indicated by “X” in FIG.
  • the secondary squeal (about 11.75 kHz) is the in-plane secondary squeal (about 11.55 kHz) which is the squeal in the in-plane secondary mode generated by the conventional disk rotor shown in “Z” of FIG. 6-3.
  • the frequency of the in-plane secondary squeal increases while its occurrence is suppressed. Further, as shown in FIGS.
  • in-plane secondary squeal refers to vibration of about 11 kHz to 12 kHz in the present embodiment, but varies depending on the configuration of the vibrating disk rotor and the pad, and therefore refers to vibration of 8 kHz or more in the present invention.
  • in-plane secondary squeal occurs in a wide range of hydraulic pressure, and the in-plane secondary squeal is particularly noticeable at a high hydraulic pressure.
  • in-plane secondary squeal occurs only at a high hydraulic pressure, and in-plane secondary squeal occurs in a wide range. Is suppressed.
  • the second fin 4b becomes shorter, that is, as the mass becomes smaller, the occurrence of in-plane secondary squeal is suppressed even at a higher hydraulic pressure.
  • Resonance in brake squealing can be considered to occur by the combination of mode A and mode B.
  • mode A the peak frequency in the in-plane secondary mode is constant regardless of the fluid pressure (A1 to A3 in FIG. 8).
  • mode B the peak frequency in the in-plane secondary mode increases as the hydraulic pressure increases, and then becomes constant (B1 to B3 in the figure). Since mode A is governed by frequency, as shown by A1 to A3 in the figure, it increases as the second fin 4b becomes shorter, that is, as the mass becomes smaller.
  • mode B since mode B is not governed by frequency, it does not change regardless of mass, as shown in B1 to B3 of FIG.
  • the disk rotor 1-1 mainly suppresses the generation of vibrations of 8 kHz or more in the in-plane secondary sound by changing the mass periodically by 45 degrees. can do.
  • the length of the second fin 4b is made shorter than that of the first fin 4a, so that the weight can be reduced.
  • FIG. 9 is a diagram illustrating a disk rotor according to the second embodiment.
  • FIG. 9 is a cross-sectional view in a plane orthogonal to the rotational axis of the disk rotor.
  • the disc rotor 1-2 according to the second embodiment shown in FIG. 9 is different from the second fin 4b in the disc rotor 1-1 according to the first embodiment in the shape of the second fin 4c constituting the second fin group. Since the basic configuration of the disk rotor 1-2 is the same as that of the disk rotor 1-1, the description thereof is omitted or simplified.
  • the first fin 4a and the second fin 4c are made of the same material but have different shapes.
  • the first fin 4a and the second fin 4c have the same fin length, but the fin width of the second fin 4c is wider than that of the first fin 4a.
  • the first fin 4a has a substantially rectangular cross section (both ends in the radial direction are arcs, and the fin width on the radially inner side is 5 mm).
  • the second fin 4c has a shape in which the fin width (the length in the direction orthogonal to the radial direction) becomes wider from the inner side to the outer side, that is, the cross-sectional shape is substantially a fan shape (for example, both ends in the radial direction are circular arcs).
  • the fin width on the radially inner side is 6 mm, and the fin width on the radially outer side is 8 mm. That is, since the fin width of the second fin 4c increases at least radially outward than the first fin 4a, the second fin 4c has high rigidity and a large mass. That is, the second fin group 42 has higher rigidity and a larger mass than the first fin group 41. Therefore, the rigidity and mass of the disk rotor 1-2 periodically change at intervals of 45 degrees in the circumferential direction.
  • the eigenvalue of the disk rotor 1-2 in the in-plane secondary mode is changed mainly by changing the rigidity.
  • the first fin group 41 and the second fin group 42 are alternately arranged at 45 degrees in the circumferential direction, and the rigidity is changed by 45 degrees in the circumferential direction, whereby the frequency in the in-plane direction of 45 degrees is obtained.
  • the eigenvalue of the disk rotor 1-2 in the in-plane secondary mode is changed mainly by changing the rigidity.
  • the peak frequency separation in the in-plane secondary mode increases as the width of the second fin 4b increases, that is, as the rigidity increases, as compared with the conventional disk rotor. That is, if the rigidity of the second fin group 42 is higher than the rigidity of the first fin group 41, the peak frequency in the in-plane secondary mode corresponding to the second fin group 42 is determined from the relationship between the frequency, rigidity, and weight.
  • the disk rotor 1-2 Since it becomes higher than the peak frequency in the in-plane secondary mode corresponding to the first fin group 41, the change in rigidity between the first fin group 41 and the second fin group 42, that is, the change in rigidity by 45 degrees, The eigenvalues of the disk rotor 1-2 in the in-plane secondary mode can be separated. Therefore, the occurrence of in-plane secondary squeal can be suppressed as the width of the second fin 4c is increased, that is, as the rigidity is increased. As described above, the disk rotor 1-2 according to the present embodiment can suppress the occurrence of in-plane secondary squeal mainly by periodically changing the rigidity by 45 degrees. In the disk rotor 1-2, since the width of the second fin 4c is wider than that of the first fin 4a, a decrease in strength can be suppressed.
  • FIG. 10 is a diagram illustrating a disk rotor according to the third embodiment.
  • FIG. 10 is a cross-sectional view in a plane orthogonal to the rotation axis of the disk rotor.
  • the disc rotor 1-3 according to the third embodiment shown in FIG. 10 is different from the first embodiment in that the shapes of the second fins 4d to 4f constituting the second fin group 42 are different depending on the position of the second fin group 42. 2 differs from the disc rotor 1-2 according to FIG. Since the basic configuration of the disk rotor 1-3 is the same as that of the disk rotor 1-2, the description thereof is omitted or simplified.
  • the first fin 4a and the second fins 4d to 4f are made of the same material but have different shapes.
  • the first fin 4a and the second fins 4d to 4f have the same fin length, but the fin width of the second fins 4d to 4f is wider than that of the first fin 4a.
  • the first fin 4a has a substantially rectangular cross section (both ends in the radial direction are arcs, and the fin width on the radially inner side is 5 mm).
  • the second fins 4d to 4f have a shape in which the fin width (the length in the direction orthogonal to the radial direction) becomes wider from the inner side toward the outer side, that is, the cross-sectional shape is formed in a substantially fan shape.
  • the second fin 4d is a fin 4 (two fins 4 positioned at both ends in the circumferential direction of the second fin group 42) located at an end adjacent to the first fin group 41, and the second fins 4e, 4f.
  • the shape change amount with respect to the first fin 4a which is the fin 4 located at the end adjacent to the first fin group 41, that is, the change amount of the fin width is reduced (for example, Both ends in the radial direction are arcs, the fin width on the radially inner side is 5 mm, and the fin width on the radially outer side is 6 mm).
  • the second fin 4e is a fin 4 that is located closer to the center than the fins 4 that are located at both ends of the second fin group 42, and changes in shape relative to the first fin 4a as compared to the second fin 4f.
  • the amount of change that is, the amount of change in the fin width is small, and the amount of change in the fin width with respect to the second fin 4d is large (for example, both ends in the radial direction are arcs, and the fin width on the radially inner side is 6mm, radially outward fin width 7mm).
  • the second fin 4f is a fin 4 positioned at the center of the second fin group 42, and is a fin 4 positioned at an end adjacent to the first fin group 41 as compared with the second fins 4d and 4e.
  • the amount of change in the fin width with respect to the first fin 4a is the largest (for example, both ends in the radial direction are arcs, the fin width on the radially inner side is 6 mm, and the fin width on the radially outer side is 8 mm). That is, in the second fin group 42, the second fin 4d located at the end adjacent to the first fin group 41 is shaped more than the second fins 4e and 4f located closer to the center than the second fin 4d. The amount of change is small, and in this embodiment, the amount of change in the shape of the second fins 4d to 4f gradually decreases from the center of the second fin group 42 toward both ends.
  • the fins of the second fins 4d to 4f have a higher rigidity and a larger mass because the fin width increases at least radially outward than the first fins 4a.
  • the rigidity is sequentially increased and the mass is sequentially increased. That is, the disk rotor 1-3 periodically changes in rigidity and mass at intervals of 45 degrees in the circumferential direction, and in the second fin group 42, the shape of the fin 4 gradually changes from the end toward the center. Therefore, the rigidity is higher sequentially from the end portion toward the center portion than the first fin group 41, and the mass gradually increases.
  • the eigenvalue of the disk rotor 1-3 in the in-plane secondary mode is changed mainly by changing the rigidity.
  • the first fin group 41 and the second fin group 42 are alternately arranged at 45 degrees in the circumferential direction, and the rigidity is changed by 45 degrees in the circumferential direction, whereby the frequency in the in-plane direction of 45 degrees is obtained.
  • the eigenvalues of the disc rotor 1-3 in the in-plane secondary mode are separated.
  • the rigidity of the second fin group 42 is made higher than the rigidity of the first fin group 41, the disc rotor 1-3 has an in-plane secondary mode corresponding to the second fin group 42 due to the relationship between frequency, rigidity, and weight.
  • the eigenvalues of the disk rotor 1-3 in the in-plane secondary mode can be separated. Therefore, the disc rotor 1-3 according to the present embodiment can suppress the occurrence of in-plane secondary squeal mainly by periodically changing the rigidity by 45 degrees. Further, in the disc rotor 1-3, the width of the second fins 4d to 4f is made wider than that of the first fin 4a, so that a decrease in strength can be suppressed.
  • the heat capacity of each fin 4 will change.
  • the heat capacity of the second fin 4c is higher than that of the first fin 4a. Therefore, as a result of the frictional force generated by the pads 102 and 103 coming into contact, the temperature distribution on the surface of the sliding plates 2 and 3 to be contacted by the pads 102 and 103 changes in the circumferential direction by 45 degrees.
  • the temperature rapidly changes at the boundary between the first fin group 41 and the second fin group 42, there is a possibility that the temperature changes rapidly by 45 degrees in the circumferential direction with reference to the boundary.
  • the amount of change in the shape of the second fins 4d to 4f is small from the central portion of the second fin group 42 toward both end portions adjacent to the first fin group 41. That is, since the shape of the fins 4 is small, the shape of the first fins 4a located at both ends of the first fin group 41 and the shape of the second fins 4d located at both ends of the second fin group 42 is obtained. Can be reduced. Therefore, since the temperature change in the boundary part of the 1st fin group 41 and the 2nd fin group 42 can be suppressed, the fine wave
  • FIG. 11 is a diagram illustrating a disk rotor according to the fourth embodiment.
  • FIG. 11 is a cross-sectional view in a plane orthogonal to the rotation axis of the disk rotor.
  • the disc rotor 1-4 according to the fourth embodiment shown in FIG. 11 differs from the disc rotor 1-3 according to the third embodiment in the number of fins 4. Since the basic configuration of the disk rotor 1-4 is the same as that of the disk rotor 1-3, the description thereof is omitted or simplified.
  • each first fin group 41 includes the same number of first fins 4a in the present embodiment.
  • each of the second fin groups 42 includes the same number of six second fins 4d to 4f in the present embodiment. Therefore, the first fin group 41 and the second fin group 42 are alternately arranged in the circumferential direction with respect to the sliding plates 2 and 3 every predetermined angle, and in this embodiment, every 45 degrees (approximately 45 degrees). Has been.
  • the first fin group 41 is smaller than 45 degrees, and the second fin group 42 is larger than 45 degrees. That is, the first fin group 41 and the second fin group 42 are alternately arranged in a predetermined number at substantially equal intervals in the circumferential direction. In this embodiment, the first fin group 41 and the second fin group 42 are alternately arranged for each of A1 to A8 continuous in the circumferential direction, which is an 8-divided region.
  • the first fin group 41 is arranged at A1, A3, A5, A7
  • the second fin group 42 is arranged at A2, A4, A6, A8, and A2, A4, A6, A8 rather than A1, A3, A5, A7. Is a wider area.
  • the second fin group 42 includes two second fins 4d at both ends in the circumferential direction, two second fins 4f at the center, and second fins 4e between the second fins 4d and the second fins 4f. Is arranged. Therefore, the disc rotor 1-4 according to the present embodiment can suppress the occurrence of in-plane secondary squeal mainly by changing the rigidity periodically by approximately 45 degrees as in the third embodiment. . Further, in the disk rotor 1-4, the width of the second fins 4d to 4f is made wider than that of the first fin 4a, so that a decrease in strength can be suppressed. Furthermore, it is possible to suppress the occurrence of vibration and noise due to heat during braking.
  • the number of the second fins 4d to 42f of the second fin group 42 is larger than the number of the first fins 4a of the first fin group 41, but the present invention is not limited to this.
  • the number of the first fins 4a of the one fin group 41 may be increased.
  • the first fin group 41 is larger than 45 degrees
  • the second fin group 42 is smaller than 45 degrees. That is, the first fin group 41 is arranged in A1, A3, A5, A7, the second fin group 42 is arranged in A2, A4, A6, A8, and A1, A3, A5 is more than A2, A4, A6, A8. , A7 becomes wider as a region.
  • the second fins 4d to 4f are shaped so that the fin width increases from the radially inner side toward the outer side. This is in consideration of the sand detachability caused by the disk rotors 1-1 to 1-4 being manufactured by casting, but the sliding plates 2 and 3 and the plurality of fins 4 are made of different members.
  • the second fins 4d to 4f may be shaped so that the fin width increases from the radially outer side toward the inner side.
  • the number of fins 4 is divisible by 4. However, the number is not divisible.
  • the number of fins 4 in any one of the first fin group 41 or the second fin group is increased. At this time, it is preferable that the increase number of one group is one.
  • the increase number of one group is one.
  • the first fin group 41 and the second fin group 42 are alternately arranged at intervals of approximately 45 degrees in the circumferential direction, and alternately for each of the regions divided into eight at substantially equal intervals in the circumferential direction. Will be placed.
  • the first fin 4a and the second fins 4b to 4f have different shapes and different masses and rigidity.
  • the mass and rigidity may be made different by making the material different between 4a and the second fins 4b to 4f.
  • the mass and the rigidity can be varied by using different materials.
  • the first fin 4a and the second fins 4b to 4f may have different shapes and materials.
  • In-plane primary squeal is a brake squeal having in-plane primary mode nodes every 180 degrees in the circumferential direction of the disk rotor 1-1 to 1-4 (90 degrees relative to the nodes become belly) It is.
  • the number of fins 4 is 40, 44, 48, etc.
  • the first fin group 41 and the second fin group 42 are alternately arranged in two groups each in the circumferential direction (four groups in total). It is arranged.
  • the first fin group 41 and the second fin group 42 are alternately arranged at predetermined angles in the circumferential direction with respect to the sliding plates 2 and 3, here, every 90 degrees.
  • the first fin group 41 and the second fin group 42 are arranged at equal intervals in the circumferential direction with respect to the sliding plates 2 and 3, and are continuously arranged in the circumferential direction which is a predetermined number, here, four divided areas. Alternatingly arranged for each A4.
  • the first fin group 41 is disposed at A1 and A3, and the second fin group 42 is disposed at A2 and A4.
  • the first fin group 41 and the second fin group 42 are approximately 90 degrees in the circumferential direction with respect to the sliding plates 2 and 3. Are alternately arranged. That is, the first fin group 41 and the second fin group 42 are alternately arranged for each of A1 to A4 that are continuous in the circumferential direction, which is an area divided into four parts at substantially equal intervals in the circumferential direction with respect to the sliding plates 2 and 3. (A1, A3 or A2, A4 is wider than the other).
  • the predetermined angle is 45 degrees or 90 degrees, but the present invention is not limited to this.
  • the predetermined angle only needs to correspond to the order of the in-plane squeal to be suppressed, and is (360/2 n ) / 2 when the order is n.
  • the predetermined number is 4 or 8.
  • the predetermined number only needs to correspond to the order of the in-plane squeal to be suppressed, and is 2 n ⁇ 2 when the order is n.

Landscapes

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

Abstract

L'invention porte sur un rotor à disque (1-1) conçu de telle sorte que des ailettes (4) sont formées entre des plaques coulissantes opposées de façon à être agencées dans la direction circonférentielle et que des tampons entrent en contact avec les plaques coulissantes pour générer une force de freinage. Les ailettes (4) sont combinées en : premiers groupes d'ailettes (41) qui comprennent des premières ailettes (4a) ; et seconds groupes d'ailettes (42) qui comprennent des secondes ailettes (4b) ayant une forme différente de celle des premières ailettes (4a). Les premiers groupes d'ailettes (41) et les seconds groupes d'ailettes (42) sont disposés en alternance à intervalles de 45 degrés dans la direction circonférentielle. Le résultat de cette configuration est de permettre d'éviter la formation de grincements dans le plan.
PCT/JP2012/079561 2012-03-30 2012-11-14 Rotor à disque WO2013145427A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2012-082462 2012-03-30
JP2012082463A JP2013210090A (ja) 2012-03-30 2012-03-30 ディスクロータ
JP2012082462A JP5742773B2 (ja) 2012-03-30 2012-03-30 ディスクロータ
JP2012-082463 2012-03-30

Publications (1)

Publication Number Publication Date
WO2013145427A1 true WO2013145427A1 (fr) 2013-10-03

Family

ID=49258762

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/079561 WO2013145427A1 (fr) 2012-03-30 2012-11-14 Rotor à disque

Country Status (1)

Country Link
WO (1) WO2013145427A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56164237A (en) * 1980-05-21 1981-12-17 Nissan Motor Co Ltd Disc brake rotor
JPS59107344U (ja) * 1983-01-10 1984-07-19 トヨタ自動車株式会社 デイスクブレ−キ用デイスクロ−タ
JPH0221343U (fr) * 1988-07-27 1990-02-13
JPH0418731U (fr) * 1990-06-05 1992-02-17
JP2000310263A (ja) * 1999-04-27 2000-11-07 Tokico Ltd ディスクロータ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56164237A (en) * 1980-05-21 1981-12-17 Nissan Motor Co Ltd Disc brake rotor
JPS59107344U (ja) * 1983-01-10 1984-07-19 トヨタ自動車株式会社 デイスクブレ−キ用デイスクロ−タ
JPH0221343U (fr) * 1988-07-27 1990-02-13
JPH0418731U (fr) * 1990-06-05 1992-02-17
JP2000310263A (ja) * 1999-04-27 2000-11-07 Tokico Ltd ディスクロータ

Similar Documents

Publication Publication Date Title
JP6567084B2 (ja) 鉄道車両用ブレーキライニングおよびそれを備えたディスクブレーキ
US11519473B2 (en) Braking band of a disc for a disc brake of the ventilated type
US20220290729A1 (en) Braking band of a disc for disc brake of ventilated type
US20220275843A1 (en) Braking band of a disc for disc brake of ventilated type
US20220364616A1 (en) Braking band of a disc for disc brake of ventilated type
JP5742773B2 (ja) ディスクロータ
WO2013145427A1 (fr) Rotor à disque
EP1384011B1 (fr) Bande de freinage pour frein a disque
JP6220270B2 (ja) ブレーキロータ及びブレーキロータ製造方法
JP2013210090A (ja) ディスクロータ
JP2002048166A (ja) 車両用ディスクブレーキ装置のディスクロータ
IT201800020128A1 (it) Fascia di frenatura di un disco per freno a disco di tipo ventilato
JP2017150511A (ja) ディスクブレーキ用ロータ
JP7364211B2 (ja) ブレーキロータ
JP2014202333A (ja) ディスクロータ固定構造
KR20240006454A (ko) 브레이크 디스크
JP2009138911A (ja) ディスクロータ
JP3582392B2 (ja) ベンチレーテッドロータ
WO2006067816A1 (fr) Bande de freinage d'un frein a disque
JP3839140B2 (ja) ブレーキロータ
JP2013044342A (ja) ブレーキディスクローター
JP2005133733A (ja) ディスクブレーキ用ディスクロータ
JP2008032041A (ja) ベンチレーテッドディスクロータ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12872750

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 12872750

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE