JP2002227891A - Disc brake rotor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a floating type disc brake rotor reduced in weight with simple structure, improved in assembling workability by reducing the number of part items and reduced in cost. SOLUTION: This disc brake rotor comprises: an outer rotor 2 having a disc shape sliding part 2a; and an inner rotor 3 inwardly fitted to the outer rotor 2 with a predetermined annular gap interposed therebetween and having a plurality of wheel attaching holes 8. A fitting part of the outer rotor 2 is provided with a projection 2c, and a fitting part of the inner rotor 3 is provided with a recess 3d fitting with the projection 2c, thereby constituting an engaging part 10, whereby the two rotors 2 and 3 are connected by the engaging part 10 so as to capable of transmission of torque. A plurality of pin holes 7 are formed having centers positioned on a circumference of the annular gap provided to the fit part of the outer rotor 2 and the inner rotor 3, and a caulking pin 6 is loosely fitted to each of the pin hole 7. The outer rotor 2 and the inner rotor 3 are caulked with the caulking pin 6 via a disc spring 4 and a washer 5, thereby regulating a relative movement in an axial direction of the two rotors 2 and 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disk brake rotor, and more particularly to a floating type disk brake rotor used for a braking device of a motorcycle.

[0002]

2. Description of the Related Art Conventionally, in a disk brake rotor of a motorcycle, heat generated during braking causes the pad sliding portion to thermally expand, causing warpage or undulation of the sliding portion, thereby inducing an uneven contact of the brake pad. However, there have been problems such as uneven wear of the sliding portion and reduction of the braking force. Recently, a floating type disk brake rotor as shown in FIG. 5 has been generally used in order to improve this disadvantage.

FIG. 5 (a) is a plan view showing a conventional floating type disk brake rotor. In a disk brake rotor 50, an inner rotor 52 is fitted in an outer rotor 51 as a separate piece, and both are caulking pins. 55
Is crimped. FIG. 5 (b) is a view of A- of FIG. 5 (a).
The disc spring 53 and the washer 54 are provided in a state where a clearance is provided between the inner diameter of the pin hole 56 and the caulking pin 55 in a cross-sectional view taken along line A of FIG.
Is crimped into a floating state. Due to this clearance, the outer rotor 5 due to heat generated during braking is provided.
1 can be absorbed.

FIGS. 6 (a) and 6 (b) are partially enlarged sectional views of FIG. 5 (b). FIG.
(B) shows the state after caulking. A washer 54a is provided on the inner diameter side of the washer 54 so that the disc spring 53 mounted on the caulking pin 55 is centered on the caulking pin 55 and caulked. The disc spring 53 and the washer 54 are mounted after being integrally fixed before fitting to the caulking pin 55. That is, after the in-row portion 54a of the washer 54 is inserted into the inner hole 53a of the disc spring 53, the two portions of the in-row portion 54a are swaged to integrate them. Next, after the integrated disc spring 53 and the washer 54 are fitted to the caulking portion 55a of the caulking pin 55, the caulking portion 55a
To complete the work.

As described above, the disc spring 53 is provided with the washer 5 in advance.
4, the center of the disc spring 53 is not displaced when the caulking pin 55 is caulked, the assembling work can be simplified, and the working efficiency is improved.

[0006]

However, the outer rotor 51 and the inner rotor 52 must be connected to each other so that torque can be transmitted by only the caulking pin 55, and the relative movement of both rotors in the axial direction must be restricted. Instead, a large number of caulking pins 55 need to be arranged on the circumference. Naturally, if the engine has a high output, it is inevitable to increase the number of crimping pins 55 or to increase the size. Further, in such a situation, the number of parts is large, the man-hour required for the caulking work is inevitable, and the efficiency of assembling the disc brake rotor is inevitably reduced. In addition, such a structure has a limitation in weight reduction, which impairs vehicle characteristics such as fuel efficiency and steering stability, and has been desired to be improved.

The present invention has been made in view of such circumstances, and a disk brake rotor which can be reduced in weight with a simple structure, reduces the number of parts, improves workability in assembling, and reduces costs. To provide.

[0008]

In order to achieve the above object, according to the first aspect of the present invention, an outer rotor having a disk-shaped sliding portion and a predetermined annular clearance are provided on the outer rotor. An inner rotor having a plurality of wheel mounting holes, a concave portion or a convex portion formed at one of the fitting portions of the outer rotor and the inner rotor, and the other engaged with the concave portion or the convex portion. Forming a convex portion or a concave portion, connecting these two rotors so that torque can be transmitted by an engaging portion composed of the concave and convex portions, and separately providing a means for regulating the axial relative movement of the outer rotor and the inner rotor. The structure provided in the fitting part was adopted. Thereby, at the time of braking, even if the outer rotor itself thermally expands due to heat generated by the sliding portion of the outer rotor, it is allowed by the engaging portion formed of the irregularities, and no distortion occurs in the sliding portion, Further, a large torque can be transmitted with a simple structure, so that the weight can be reduced and the assembling workability can be improved.

According to a second aspect of the present invention, a caulking pin is loosely fitted in a plurality of holes having a center on the circumference of the annular clearance, and the caulking pin is inserted through the disc spring and a washer. By caulking the outer rotor and the inner rotor, the relative movement of the two rotors in the axial direction is restricted. In this way, not only the caulking operation is reduced by half, but also the size of the caulking pin itself can be reduced, and the weight of the disc brake rotor can be reduced.

[0010] The invention according to claim 3 further comprises:
The caulking pin and the engaging portion composed of the concave and convex portions are alternately arranged on the circumference, so that the dynamic balance is good and the dimensional change due to the temperature difference between the outer rotor and the inner rotor can be efficiently absorbed.

Further, since the circumferential clearance of the engaging portion composed of the concave and convex portions is set smaller than the loose fitting clearance of the caulking pin, the caulking pin can be used during braking. Therefore, it is only necessary to restrict the relative movement of the outer rotor and the inner rotor in the axial direction, and the size can be reduced.

Further, in the invention according to the fifth aspect, a shielding plate is fixed to the engaging portion formed of the concave-convex portion, and the relative movement of the outer rotor and the inner rotor in the axial direction is regulated. According to such a configuration, complicated crimping work of the crimping pin can be eliminated, the man-hour for the assembling work can be further improved, and the cost can be reduced.

[0013]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 shows an embodiment of a disk brake rotor according to the present invention, FIG. 1 (a) is a plan view thereof, FIG. 1 (b) is a sectional view taken along line AA of FIG. 1 (a), FIG. 1C is a cross-sectional view taken along line BB of FIG.
FIG. 1D is a partial sectional view taken along line CC of FIG. 1A.

In FIG. 1, a disc brake rotor 1
The inner rotor 3 is a separate piece and is fitted inside the outer rotor 2 via a predetermined annular clearance δ, and both are caulked by a hollow caulking pin 6 via a disc spring 4 and a washer 5. . As shown in FIGS. 2B and 2C, semicircular recesses 2e and 3e are formed in the inner diameter portion of the outer rotor 2 and the outer diameter portion of the inner rotor 3, and the two rotors 2 and 3 are fitted. Each of the caulking pins 6 is loosely fitted into a plurality of holes 7 having a center on the circumference of the annular clearance δ provided at the joint portion, and the caulking pins 6 are fitted through the disc spring 4 and the washer 5 to the outer rotor 2. And the inner rotor 3 is swaged. Here, a clearance e is provided between the inner diameter of the pin hole 7 and the caulking pin 6, and the clearance e can absorb distortion of the outer rotor 2 due to heat generated during braking.

A washer 5a is provided on the inner diameter side of the washer 5 so that the disc spring 4 mounted on the caulking pin 6 is accurately centered on the caulking pin 6 and caulked without shifting the position. Before the disc spring 4 and the washer 5 are fitted to the caulking pin 6, the disc spring 4 and the washer 5 are mounted after being integrally fixed. That is, as shown in FIG.
After inserting the spigot portion 5a into the inner hole 4a of the disc spring 4,
As shown in FIGS. 3A and 3B, 2 to 4 of the inlay portion 5a
The portion is crimped to form a crimped portion 5b, and the two are integrated. In addition, as shown in FIG.
The staking may be formed by caulking the in-row portion 5a 'at two to four places, and then the disc spring 4 may be fitted and integrated by elastic deformation. Next, as shown in FIGS. 2A and 2B, after the integrated disc spring 4 and the washer 5 are fitted to the caulking portion 6a of the caulking pin 6, the caulking portion 6a is removed. Caulking.

In FIG. 1A, a plurality of drainage holes 2d are formed in the sliding portion 2a of the outer rotor 2 in the circumferential direction to prevent wear powder and moisture from staying in the sliding portion 2a. In particular, it is possible to effectively prevent clogging of muddy water during braking on off-road. With this drain hole 2d,
Further, the air cooling effect of the sliding portion 2a is enhanced, and the outer rotor 2
The outer rotor 2 is reduced in weight together with the plurality of recesses 2b formed in the inner diameter of the outer rotor 2. The shape of the drain hole 2d is not limited to a circular hole, but may be a slit shape.

A plurality of mounting holes 8 for mounting to wheels (not shown) are formed in the bracket portion 3f of the inner peripheral portion of the inner rotor 3 at equal intervals around the circumference.
A long window 9 for weight reduction is also formed between 8. Further, a concave portion 3a and a through hole 3b are formed in the outer diameter portion of the inner rotor 3 so as to face the concave portion 2b of the outer rotor 2, thereby reducing the weight of the inner rotor 3. The through hole 3b has a substantially triangular shape, and a reinforcing rib 3c is provided between the through holes 3b and 3b.

A radially extending convex portion 2c is formed on the inner diameter portion of the outer rotor 2, and a concave portion 3d engaging with the convex portion 2c is formed on the outer diameter portion of the inner rotor 3, respectively. By the joint portion 10, the outer rotor 2 and the inner rotor 3 are integrated so that torque can be transmitted in the circumferential direction. Here, if the engaging portion 10 is configured by engaging the concave and convex portions 2c and 3d with a predetermined clearance in the radial direction, the sliding portion 2a of the outer rotor 2 generates heat during braking,
Even if the volume expands, it can be absorbed by the engagement portion 10 without distortion. Further, as shown in FIG. 1D, a predetermined clearance f is formed in the circumferential direction between the convex portion 2c and the concave portion 3d of the engaging portion 10.
Is formed, the volume expansion of the convex portion 2c is allowed. If this circumferential clearance f is set smaller than the clearance e formed between the inner diameter of the pin hole 7 of the rotor and the caulking pin 6, substantially no rotational torque is generated at the caulking pin 6, and mainly Torque can be transmitted only by the engagement portion 10.

FIG. 4 is a partial plan view showing another embodiment.
With a configuration reverse to the above-described engaging portion 10, a concave portion 2c 'is formed in the inner diameter portion of the outer rotor 2', and a convex portion 3d 'is formed in the outer diameter portion of the inner rotor 3'. Both rotors 2 ', 3' are integrated so as to be able to transmit torque in the circumferential direction.

Although the structure in which the engaging portions 10, 10 'are formed between the caulking pins 6, 6 at four equally spaced positions in the circumferential direction is exemplified, the number and arrangement are not limited thereto, and can be changed as appropriate. At the time of braking, the sliding portion 2 of the outer rotor 2, (2 ')
a generates heat and the outer rotors 2 and (2 ') expand in volume, the annular clearance δ between the outer rotors 2 and (2') and the inner rotors 3 and (3 '), and the clearance between the caulking pins 6 and the pin holes 7. e, it can be absorbed by the radial clearance and the circumferential clearance f of the concavo-convex portion of the engaging portion 10 (10 ').

The means for restricting the relative movement of the two rotors in the axial direction is not limited to the above-described caulking pin. For example, a shield plate can be removed with bolts on the front and back of the recess 3d of the inner rotor 3 shown in FIG. And the axial movement of the convex portion 2c formed on the inner diameter portion of the outer rotor 2 can be restricted. Further, the shielding plate may be fastened to the front and back of the convex portion of the outer rotor.

As described above, by integrating the outer rotor and the inner rotor so as to be able to transmit torque by the floating type by the engaging portion formed of the uneven portion,
During braking, even if the outer rotor itself thermally expands due to heat generated by the sliding portion of the outer rotor, the engagement portion formed of the uneven portion allows the expansion, and no distortion occurs in the sliding portion. In addition, since a means for regulating the relative movement of the outer rotor and the inner rotor in the axial direction is separately provided, not only the assembling work such as crimping of the crimping pin as this regulating means is reduced by half, but also the regulating means is reduced. The size can be reduced, and the cost and weight can be reduced.

Furthermore, by alternately arranging the regulating means and the engaging portions formed of the concave and convex portions on the circumference, the dynamic balance of the disc brake rotor is improved, and the dimensional change due to the temperature difference between the outer rotor and the inner rotor is efficiently reduced. Can be well absorbed.

The applicant of the present invention has proposed a floating-type floating type having an optimal configuration that retains the contradictory functions of strength and weight reduction and minimizes thermal deformation based on data obtained by computer simulation analysis and the like by the finite element method. A disk brake rotor was obtained.

Next, the material of the disk brake rotor according to the present invention will be described. The disc brake rotor is
The outer rotor is formed of stainless steel, and the inner rotor is formed of an aluminum alloy, because the outer rotor is required to have contradictory performances such as being thin, hard to break, and having high friction and not being worn. This allows
Compared to the conventional disk brake rotor made of stainless steel, the weight was reduced by almost half, and the maneuverability was greatly improved. The caulking pin, washer, and disc spring are each formed of stainless steel.

Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments at all, but is merely an example, and is within the scope of the present invention. Needless to say, the present invention can be embodied in various forms, and the scope of the present invention is indicated by the description of the claims, and furthermore, the equivalent meanings described in the claims, and all within the scope Including changes.

[0027]

As described above in detail, the floating type disk brake rotor according to the present invention has conflicting performances such as being thin, hard to be broken, large in friction and not being worn, and has strength and weight reduction. It is possible to obtain an optimal configuration that retains conflicting functions and suppresses thermal deformation as much as possible. Furthermore, the number of parts can be minimized, the number of work steps can be reduced with a simple configuration, and cost reduction and weight reduction can be achieved.

[Brief description of the drawings]

1A is a plan view showing an embodiment of a floating type disk brake rotor according to the present invention. FIG. 1B is a cross-sectional view taken along the line AA in FIG. 1A. FIG. (D) Partial sectional view taken along line CC of FIG. 1 (a).

FIG. 2 (a) is a partially enlarged cross-sectional view showing a state before crimping of a crimping pin according to the present invention; (b) is a partially enlarged cross-sectional view showing a state after crimping of a crimping pin according to the present invention; b) II-II line cross-sectional view

3 (a) is a perspective view showing a state in which a disc spring and a washer according to the present invention are integrated, (b) a sectional view of the same, (c) an exploded perspective view of the same, and (d) another embodiment of the same. Exploded perspective view showing

FIG. 4 is a partial plan view showing another embodiment of the disc brake rotor according to the present invention.

5A is a plan view showing a conventional floating type disk brake rotor, and FIG. 5B is a cross-sectional view taken along line AA in FIG. 5A.

6A is a partially enlarged cross-sectional view showing a conventional caulking pin before crimping, and FIG. 6B is a partially enlarged cross-sectional view showing a conventional caulking pin after caulking.

[Explanation of symbols]

 1 ·········· Disc brake rotor 2, 2 ′ ······· Outer rotor 2a ······ Sliding portion 2b ····· Recess 2c, 2c '··· Part 2d Drainage hole 2e Recess 3 Inner rotor 3a Recess 3b Through hole 3c ... Rib 3d, 3d '... Recess 3e ... Recess 3f ... Bracket 4 ... Bellet spring 5,5' ... Washer 5a, 5a ': Inlay section 5b, 5b': Caulking section 6: Caulking pin 6a: Caulking section 7: Pin hole 8 mounting holes 9 long windows 10 ′ engaging portions δ annular clearance e pins Clearance f ... Directional clearance 50 Disc brake rotor 51 Outer rotor 52 Inner rotor 53 Disc spring 53a Inner hole 54 ····· Washer 54a ····· Inlay part 55 ······ Caulking pin 55a ······ Caulking part

Claims (5)

[Claims] 1. An outer rotor having a disk-shaped sliding portion, an inner rotor fitted inside the outer rotor via a predetermined annular clearance and having a plurality of wheel mounting holes, and the outer rotor and the inner rotor. A concave portion or a convex portion is formed on one of the fitting portions of the rotor, and a convex portion or a concave portion engaging with the concave portion or the convex portion is formed on the other. And a means for restricting the relative movement of the outer rotor and the inner rotor in the axial direction is separately provided in the fitting portion. 2. A caulking pin is loosely fitted in a plurality of holes having a center on the circumference of the annular clearance, and the caulking pin is caulked to the outer rotor and the inner rotor via a disc spring and a washer. 2. The disk brake rotor according to claim 1, wherein the relative movement of the two rotors in the axial direction is restricted. 3. The disk brake rotor according to claim 2, wherein said caulking pins and said engaging portions comprising said concave and convex portions are alternately arranged in a circle. 4. The disk brake rotor according to claim 2, wherein a clearance in the circumferential direction of the engaging portion formed of the concave and convex portions is set smaller than a loose fit of the caulking pin. 5. The disk brake rotor according to claim 1, wherein a shielding plate is fixed to the engaging portion formed of the concave and convex portions, and a relative movement of the outer rotor and the inner rotor in the axial direction is regulated.