GB2239685A

GB2239685A - Brake disc

Info

Publication number: GB2239685A
Application number: GB9027538A
Authority: GB
Inventors: Mikio Matsuzaki; Toru Yoshino; Toshitaka Izumihara
Original assignee: Akebono Brake Industry Co Ltd; Akebono Research and Development Centre Ltd
Current assignee: Akebono Brake Industry Co Ltd; Akebono Research and Development Centre Ltd
Priority date: 1989-12-20
Filing date: 1990-12-19
Publication date: 1991-07-10
Anticipated expiration: 2010-12-19
Also published as: GB9027538D0; JPH03189431A; GB2239685B; DE4041010A1

Abstract

A brake disc 1 for preventing the squeak in a disc brake produced when friction pads comprised of a semi-metallic or a non-asbestos material are pushed onto the disc 1 to perform braking is characterised in that the disc 1 is made so that the frequency of resonance for circumferential vibration of the disc is higher than 15 kHz. This may be achieved by the use of slits 2 across an integral disc or by coupling together disc segments (figs 6 & 7). <IMAGE>

Description

SQUEAK PREVENTION DEVICE FOR DISC BRAIKE The present invention relates to

a device for effectively preventing squeak in a disc brake during the braking operation.

It has been known that in a disc brake whose disc rotor rotates together with an axle and is pinched by friction pads operated by a hydraulic actuator or the like to brake a vehicle, a very-unpleasant high-frequency noise referred to as a squeak is generated due to the hardness of the disc rotor, the relationship between the properties of the rotor and the pads and so forth when the rotor is pinched by the pads during the braking operation. It has been confirmed that if the friction pads are comprised of an organic material whose main constituent is asbestos, the direction of the vibration of the disc rotor and that of the procession of the wave of the vibration are coincident with each other as well as the flexural or torsional vibration of a plate, as shown in Fig. 8, namely, the main component of the vibration of the disc rotor is transverse vibration. Fig. 11 shows the characteristic of the transverse vibration of the disc rotor to indicate the points of resonance with regard to the transverse wave in the rotor. Fig. 12 shows the frequency and magnitude of the squeaks in the disc brake during the actual braking operation in the case that the friction pads are comprised of the organic material. It is apparent from the examination of Figs. 11 and 12 that some of the squeaks correspond to the points of fourth-order, fifthorder and seventh-order resonance in the transverse vibration. To conventionally prevent such squeaks, an annular metal member is fitted on the peripheral surface of a disc rotor to shift the points of resonance as disclosed in the US patent No. 3,286, 788 and the GB patent No. 934,096, or a plurarity of holes or grooves are provided in braking surfaces of a disc rotor to shift the points of resonance as shown in the Japanese Utility Model Application (OPI) No. 108,880/79 (the term "OPI" as used herein means an 1'unexamined published application").

However, since friction pads have been recently comprised of a semimetallic or a non-asbestos material, squeaks in a disc brake cannot be prevented enough by the conventional transverse-vibration-suppressing countermeasures mentioned above. Fig. 10 shows the frequency and magnitude of the squeaks in the disc brake with the friction pads comprised of a semi-metallic or non-asbestos material. It has turned out that the relationship between the frequency and magnitude of the squeaks is very approximate to that (shown in Fig. 9) between the frequency and magnitude of the longitudinal vibration of the disc rotor of the brake, in which the rotor performs the vibration of expansion and contraction in the direction of the thickness thereof and the wave of the vibration proceeds in the circumferential 1 i a 1 -1 direction of the rotor perpendicularly to the direction of the thickness thereof. It is understood through the comparison of Figs. 9 and 10 that there are points of resonance at 8.4 kHz (second order), 12.6 kHz (fourth order) and 17.6 kHz (sixth order) in frequency as to both the squeaks and the longitudinal vibration. As a result, it is concluded that the squeaks of the disc brake with the friction pads comprised of a semi-metallic or non-asbestos material are based on the longitudinal vibration of the disc rotor.

Accordingly, it is an object of the present invention to prevent squeaks from occurring due to the longitudinal vibration of the disc rotor of a disc brake employing friction pads which are comprised of a semi-metallic or a non-asbestos material and are pushed onto the disc rotor to perform braking. To attain the object, the disc rotor is divided so that the frequency of the second- order resonance of the rotor in the longitudinal vibration thereof is more than 15 khz which is the upper limit to the range of frequency audible to humans. To be concrete, the disc rotor is divided by an integer obtained by raising to a unit the decimal part of a value n expressed below or is divided by an integer larger than the former integer.

n=4712.4(0.512X+25.148)/ Tf7-p 3 1 (X: the outside diameter (mm) of said rotor) (E: the Young's modulus (dyn/ CM2) of said rotor) (p: the weight density (g/cm3) of the said rotor) The smaller the developed length of the disc rotor of the disc brake according to the present invention is, the higher the frequency of the longitudinal vibration of the disc rotor is. Besides, the squeaks would occur at the point of second-order, fourth-order and sixth-order resonance in the longitudinal vibration. For these reasons, the disc rotor is divided by the above-mentioned prescribed number so that the frequency of second-order resonance in the longitudinal vibration is shifted to be higher than 15 kHz which is the upper limit to the range of frequency audible to humans. As a result, the squeaks are made inaudible to humans.

In the drawings:

Fig. 1 is an experimentally obtained graph indicating the relationship between the sizes of disc rotors and the diameters for the propagation of longitudinal waves therein; Figs. 2, 3 and 4 show disc rotors divided by slits; Fig. 5 shows a ventilated disc rotor divided by slits; Fig. 6 shows a disc rotor completely divided and then coupled by steel pieces; is Fig. 7 shows a disc rotor completely divided and then coupled by fitting the divided part of the rotor in the other divided part thereof; Fig. 8 shows the principle of transverse vibration; Fig. 9 is a characteristic graph indicating the relationship between the frequency and magnitude of longitudinal vibration of a disc rotor; Fig. 10 is a characteristic graph indicating the relationship between the frequency and magnitude of squeaks which occur in actual braking operation by using friction pads of a semimetallic or non-asbestos material; Fig. 11 is a characteristic graph indicating the relationship between the frequency and magnitude of transverse vibration of a disc rotor; and Fig. 12 is a characteristic graph indicating the relationship between the frequency and magnitude of squeaks which occor in actual braking operation by using friction pads of an organic material.

It is known that the'frequency f (Hz) of a longitudinal wave which propagates in a solid bar of 9 (cm) is length, E (dyn /CM2) in Young f s modulus and p (g/CM3) in weight density is generally expressed as follows:

f=Vll=pVJE-7-p /2Q (1) - 5 In the equation (1), V, i and p denote the sound velocity (cm/s), the length (cm) of the longitudinal wave, and an integer which is the ordinal number (1, 2, 3,... or n) of the longitudinal wave. However, it turied out from experiments that since the disc rotor of the disc brake according to the present invention is circularly shaped and has no open end in the circumferential direction of the rotor, the frequency of a longitudinal wave which propagates in the rotor is not expressed by the equation (1) but as f ollows:

f=p(-E7-p /2Q=p,fE7-p /2nD (2) In the equation (2), p denotes the ordinal number of the longitudinal wave but is an even number such as 2, 4 and 6, and D denotes the diameter (cm) at which the wave propagates is in the disc rotor. It also turned out from the experiments that the diameter D and the outside diameter X of the disc rotor have a relationship between themselves as shown in Fig. 1.

According to the equation (2), the frequency of resonance of a disc rotor which is for an ordinary passenger car and is 240 mm in outside diameter is calculated to be 8,000 Hz, 12,000 Hz and 17, 000 Hz for the second-order, the fourth-order and the sixth-order longitudinal waves in the disc rotor, respectively, and the frequency of resonance of a disc rotor which is for an ordinary passenger car and is 260 mm in outside diameter is calculated to be 9,500 Hz, 1 14,500 Hz and 19,000 Hz for the second-order, the fourthorder and the sixth-order longitudinal waves in the disc rotor, respectively. These frequencies are nearly equal to those of squeaks which actually occurred.

It is understood through the examination of the equation (2) that the frequency f increases if the longitudinal wave propagation length L equal to nD is decreased. Therefore, the propagation length L at which the frequency of resonance for the second-order longitudinal wave exceeds 15 kHz which is the upper limit to the range of frequency audible to humans can be determined as follows:

L=pvE7-p 12f=v-E7-p lf=V-E1-p / 15,000 This equation means that the frequency f becomes higher than 15 kHz if the propagation length L is set to be less than NrTE7 p/ 15,000. For that reason, such a minimum division number n as to divide the circumferential length nD for the longitudinal wave propagation diameter D of the disc rotor of X in outside diameter to make the developed length of each divided part of the rotor less than L can be identified with an integer obtained by raising the decimal part of the value of nD/L to a unit. If the number n is equal to the value of nD/L, the number is expressed as follows:

n=nD/ L=15,000 / V'E-7-p- (0-52X+25.148)n/ 10 =4712.4(0.52X+25.148)/ V-E7-p The minimum division number n for preventing the generation of squeaks audible to humans can thus be determined for the 1 disc rotors of 240 mm and 260 mm in outside diameter X for the passenger cars as follows:

n=1.65 (for X=240 mm) n=1.77 (for X=260 mm) In that case, the Young's modulus E and weight density p of the disc rotors are supposed to be 12.8 x 10'1 dyn/cml and 7. 2 g/cm3, respectively. The decimal part of the minimum division number n is raised to a unit. As a result, the number becomes 2.

Dividing such disc rotors is concretely described with reference to Figs. 2, 3, 4, 5, 6 and 7 from now on.

Fig. 2 shows a disc rotor 1 provided with two slits 2 extending from the braking surface la of the rotor to the hub 1b thereof and positioned at an angular interval of 180 is degrees. The slits 2 have the same form.

Fig. 3 shows a disc rotor 1 provided with inner and outer slits 3 and 31 extending in the radial direction of the rotor and positioned at an angular interval of 180 degrees. The outer slits extend from the peripheral edge of the disc rotor to the vicinities of the inner slits which extend from the braking surface la of the rotor to the hub 1b thereof.

Fig. 4 shows a disc rotor 1 provided with two slits 4 and 41 extending from the braking surface la of the rotor to the hub 1b thereof and positioned at an angular interval of 180 degrees. The rotor 1 is also provided with a slit - 8 T is extending from the peripheral edge of the rotor to the vicinity of the slit C.

Fig. 5 shows a ventilated disc rotor 5 provided with slits positioned in the inside 5a and 5b of the rotor and similar to those shown in Figs. 2, 3 and 4. The angular interval between each of the slits positioned in the inside Sa and each of those positioned in the outside 5b may be either zero degree or 90 degrees.

The width of each of the slits shown in Figs. 2, 3, 4 and 5 depends on the size and form of the disc rotor.

However, it is preferable that the width is 4 mm or less.

Fig. 6 shows a disc rotor completely divided and then coupled by steel pieces 6 inserted into the divided parts of the rotor and secured thereto by calking or the like.

Fig. 7 shows a disc rotor completely divided and then coupled by fitting portions 7 of the divided part of the rotor in the other divided part thereof.

Although each of the disc rotors shown in Figs. 2, 3, 4, 5, 6 and 7 is divided so that the divided parts of the rotor are equal to each other, the rotors may be divided in any manner as far as the developed length of each divided part of the rotor is such as to make the frequency of resonance for the second-order longitudinal wave in the rotor higher than 15 kHz.

According to the present invention, a disc rotor is divided so that the frequency of the longitudinal wave second-order resonance, which would first occur as a squeak which is a brake noise, is made higher than the upper limit to the range of human- audible frequency by utilizing the fact that the frequency of resonance for the longitudinal wave which propagates in a body increases if the length of the body is decreased. The squeak is thus made inaudible to humans.

-1 i

Claims

1 2 3 4 5 6 1 2 3 4 5 6 7 8 9 10 11 12 13 1 2 1 2 3 1. A device for preventing the squeak in a disc brake in which friction pads comprised of a semi-metallic or a non-asbestos material are pushed onto a disc rotor to perform braking, wherein said rotor is divided so that the frequency of second-order resonance in the longitudinal vibration of said rotor is higher than 15 kHz.

2. A device for preventing the squeaking of a disc brake in which friction pads comprised of a semi-metallic or a non-asbestos material are pushed onto a disc rotor to perform breaking, wherein said rotor is divided into plural parts, the number of divided parts being determined, by an integer obtained by raising to a unit the decimal part of a value n or by an integer larger than the former integer, said value n satisfying the following relationship:

n = 4712.4(0-5l2X+25-l48)/V-E7TP where X = the outside diameter (mm) of said rotor; rotor; and rotor.

3. A device according to claim 1, wherein the disc rotor is provided with slits for dividing said rotor.

4. A device according to claim 1, wherein the disc rotor is a ventilated disc rotor provided with slits in the inside and outside of said rotor.

E = the Young's modulus (dyn /CM2) of said p: the weight density (g/CM3) of the said

5. A device according to claim 1. wherein the disc rotor is completely divided and coupled by steel pieces.

1

6. A device according to claim 1, wherein the disc 2 rotor is completely divided and coupled by fitting the 3 divided part of said rotor in the other divided part thereof.

7. A rotor for a disc brake, substantially as described with reference to any one of figures 2 to 7.

z h 12 - Published 1991 atThe Patent Office. State House. 66/71 High Holborn. London WCIR4TP. Further copies may be obtained from Sales Branch. Unit 6. Nine Mile Point. Cwmielinfach. Cross Keys. Newport, NPI 7HZ. Printed by Multiplex techniques lid, St MaTY Cray. Rent-