JPS6350504Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a disc rotor for disc brakes, and more specifically, the annular sliding part to which the brake pads are pressed is provided with a number of radial ventilation holes that extend in the radial direction and open at both the inner and outer peripheral edges. The present invention relates to a disc rotor for a disc brake which has a large number of vanes arranged at approximately equal intervals and between each ventilation hole.

Generally, when a disc rotor is assembled on the axle with even a slight inclination, a localized high surface pressure area is generated at a portion of the sliding portion where the inner and outer sliding surfaces for both brake pads are different from each other by approximately 180 degrees. During braking, this high surface pressure portion generates a large amount of frictional heat compared to other sliding surface portions, and tends to store frictional heat. By the way, the disc rotor mentioned at the beginning is generally called a ventilated disc rotor, and by circulating cooling air through each ventilation hole when the disc rotor rotates, the frictional heat stored in the disc rotor during braking is quickly removed. Although this type of disc rotor is designed to dissipate heat, if the brake pad is suddenly pressed against both the inner and outer sliding surfaces of the annular sliding part during high deceleration braking, etc. A large amount of frictional heat is generated and stored in the high surface pressure area of the sliding surface. For this reason, an uneven temperature distribution occurs in the annular sliding part of the disc rotor, which is formed uniformly in the circumferential direction by making the shape and arrangement of each vane part uniform, and the high surface pressure that is the highest temperature occurs. The disk rotor tends to be bent in a curved manner on both sides with the radial center line passing through the section as a node, so-called two-fold thermal deformation easily occurs, and this thermal deformation also tends to gradually increase elastically. Further, in this type of disc rotor, since the deformation is uniform in the circumferential direction as described above, the disc rotor is likely to cause vibration in addition to the above-mentioned thermal deformation, resulting in brake squeal. As a measure to prevent this vibration, it is possible to consider means to make the disc rotor locally non-uniform in the circumferential direction.

The present invention was developed in light of these circumstances, and its main purpose is to prevent thermal deformation of this type of disc rotor without impairing its heat dissipation effect.
The purpose is also to prevent vibration.

Hereinafter, the present invention will be explained based on the drawings. FIGS. 1 and 2 show a first embodiment of a disc rotor according to the present invention. This disc rotor 10 includes an annular attachment part 11 that is attached to an axle (not shown), a cylindrical flange part 12 that protrudes inward from the outer periphery of the annular flange part 11, and a cylindrical flange part 12 that extends from the inner end periphery of the cylindrical flange part 12 to the outer periphery side. A protruding annular sliding portion 13 is provided. The annular sliding part 13 is formed thicker than the annular mounting part 11 and the cylindrical flange part 12, and has both inner and outer sliding surfaces 13a, 1 that are pressed against each brake pad (not shown) on both its inner and outer surfaces.
It has become 3b. In addition, the annular sliding portion 13 includes
A large number of ventilation holes 14a, 14 extending in the radial direction
b, 14c are formed radially. Each of the ventilation holes 14a, 14b, 14c has a fan shape in the circumferential direction of the annular sliding part 13, opens at both the inner and outer peripheral edges 13c, 13d of the annular sliding part 13, and each of the ventilation holes 14a, 14b , 14c form a large number of vane portions 15a, 15b, 15c, and 15d.

Each of the ventilation holes 14a to 14c is divided into three groups, and each ventilation hole 14a constitutes the first group, each ventilation hole 14b constitutes the second group, and each ventilation hole constitutes the third group. 14c are provided at equal intervals, between the ventilation holes between adjacent groups, that is, between the ventilation holes 14a and 14b, and between the ventilation holes 1
4b and the ventilation hole 14c, and between the ventilation hole 14c and the ventilation hole 14a, the distance is slightly larger.
From this, between each ventilation hole 14a in each group, 14b
Vane portions 15a, 15b, 15c of the same shape and located at equal intervals are formed between the ventilation holes 14a and 14c, and between the ventilation holes 14a and 14b, and between the ventilation holes 14b.
and between the ventilation hole 14c and the ventilation hole 14c and the ventilation hole 1
4a, three vane portions 15d are formed which are wider in the circumferential direction of the annular sliding portion 13 than the many vane portions 15a to 15c and are approximately the same width in the circumferential direction as each of the ventilation holes 14a to 14c. ing. Each of these vane portions 15d has a fan shape, and the cylindrical flange portion 12
Each vane portion 15d extends around the inner end of the
They are located at equal intervals of 120°.

In the disk rotor 10 configured in this way, the annular sliding portion 13 has both inner and outer peripheral edges 13.
A large number of ventilation holes 14a to 14 open to c and 13d.
c and a large number of vane portions 15a to 15d are formed, so that when the disk rotor 10 rotates, cooling air flows through each of the ventilation holes 14a to 14c, thereby reducing frictional heat generated in the disk rotor 10, particularly in the annular sliding portion 13. Dissipates heat efficiently.

By the way, the disk rotor 10 according to this embodiment
In this case, three vane portions 15d, which are wider than the large number of vane portions 15a to 15c, are equally spaced at an interval of 120°. Each of these vane parts 15d
Since these are extremely rigid parts, the center line in the radial direction passing through each vane part 15d cannot become a node of bifolding during thermal deformation. In this embodiment, since the highly rigid vane portions 15d are located at three locations in the circumferential direction, there are three locations equally spaced in the circumferential direction that cannot become two-fold joints. Therefore, in such a disk rotor 10, the phenomenon of two-fold bending due to thermal deformation is unlikely to occur, and if a two-fold node occurs at a location away from the three locations mentioned above, the vanes at three highly rigid locations are unlikely to occur. The portion 15d functions to prevent thermal deformation by acting as a tension against thermal deformation caused by bending into a curved shape. As a result, thermal deformation of the entire annular sliding portion 13 is suppressed, and the phenomenon of the disk rotor 10 being bent in two is prevented. In addition, the presence of each vane portion 15d makes the disc rotor 10 locally non-uniform in the circumferential direction, and the occurrence of brake squeal due to vibration caused by the circumferential uniformity is prevented. In addition, since the inner peripheral side end of each vane portion 15d extends to the cylindrical flange portion 12, the frictional heat generated on the inner sliding surface 13a is more effectively transmitted to the cylindrical flange portion 12, and the cylindrical flange Part 1
Heat is also radiated from the inner and outer sliding surfaces 13a and 13b.
Non-uniform thermal stress is suppressed.

3 and 4 show a second embodiment of the disc rotor according to the present invention. The disc rotor 20 of the second embodiment includes an annular mounting part 21, a cylindrical flange part 22, and an annular sliding part 23, like the disc rotor 10 of the first embodiment.
The annular sliding portion 23 is formed thick, and its inner and outer surfaces are formed into both inner and outer sliding surfaces 23a and 23b to which each brake pad is pressed.

Therefore, the large number of ventilation holes provided in the annular sliding portion 23 are divided into three groups: each ventilation hole 24a, each ventilation hole 24b, and each ventilation hole 24c.
The ventilation holes 24a to 24c in each group are formed in a fan shape at equal intervals, and each vane portion 25 of the same shape in each group
a, each vane portion 25b and each vane portion 25c are formed. In addition, no ventilation holes are formed between each group located at equal intervals of 120 degrees, and between the ventilation holes 24a and 24b, between the ventilation holes 24b and 24c, and between the ventilation holes 24c and the ventilation holes. Between 24a and 24a, an annular sliding portion 2 is inserted from each vane portion 25a to 25c.
3, each vent hole 24a to 24c is wide in the circumferential direction.
Three fan-shaped vane portions 25d are formed which are slightly wider than the width in the circumferential direction. Therefore, in the disc rotor 20, as in the disc rotor 10 of the first embodiment, thermal deformation is suppressed without impairing the heat dissipation effect, the phenomenon of the disc rotor 20 being bent in two is prevented, and the brake squeal phenomenon is also prevented. Prevented.

In each of the above embodiments, three fan-shaped vanes 15d and 25d are formed at equal intervals of 120 degrees, but thermal deformation can be more effectively suppressed without impairing the heat dissipation effect of the disc rotor. For suppression, three or five locations are preferable. Further, the above-mentioned vane portion can be changed into an appropriate shape that is wider in the circumferential direction of the annular sliding portion than each of the other vane portions.

In addition, in the generally used ventilated disc rotor of the type shown in each of the above embodiments, the permissible limit is that each vent hole is blocked at about six locations evenly in the circumferential direction due to cooling effect, etc. In order for the ventilated portions 15d, 25d having high rigidity to function effectively within the permissible limits, the number of ventilated portions 15d, 25d is three or five. When there are four highly rigid vanes evenly spaced in the circumferential direction, the two vanes located 180 degrees apart are on the same straight line, and therefore cannot become two-fold nodes. There are only two parts equally spaced in the circumferential direction. In addition, if there are five highly rigid vane parts evenly distributed in the circumferential direction, there are five parts that cannot become two-fold nodes, but if there are six vane parts, There are only three locations in the same area. Therefore, if there are 4 or 6 highly rigid vanes evenly distributed in the circumferential direction, the vanes do not function effectively as a means to prevent the vane from breaking in two; If they are disposed unevenly in the circumferential direction in order to function properly, the balance during rotation of the disc rotor will be greatly impaired.

As explained above, the present invention provides a large number of ventilation holes radially and at approximately equal intervals in the annular sliding part to which the brake pads are pressed, extending in the radial direction and opening at both the inner and outer peripheral edges. In a disc rotor for a disc brake in which a large number of vanes are formed between the pores, three or five vanes located at approximately equal intervals among the respective vanes are moved in the annular sliding direction from each other vane part. Its structural feature lies in that it is wide in the circumferential direction of the vent hole and is formed to be approximately the same as or wider than the circumferential width of the ventilation hole.
Therefore, according to the present invention, without impairing the heat dissipation effect of this type of disc rotor, it is possible to suppress the thermal deformation that tends to occur during high deceleration braking and prevent the phenomenon of double bending. Squeal can be prevented.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional side view showing a first embodiment of a disc rotor according to the present invention, and FIG. 2 is a side view of FIG.
3 is a longitudinal sectional front view taken along the line, FIG. 3 is a longitudinal sectional side view showing the second embodiment of the disc rotor according to the present invention, and FIG.
The figure is a longitudinal sectional front view taken along the - line in FIG. 3. Explanation of symbols, 10, 20...disc rotor,
11, 21...Annular attachment part, 13, 23...Annular sliding part, 14a-14c, 24a-24c...Vent hole, 15a-15c, 25a-25c...Vane part, 15d, 25d...Fan shape Vane part.

Claims (1)

[Scope of utility model registration request] A large number of ventilation holes extending in the radial direction and opening at both the inner and outer circumferential edges are provided radially and at approximately equal intervals in the annular sliding portion to which the brake pads are pressed, and a large number of vanes are provided between each ventilation hole. In the disk rotor for a disk brake, three or five of the vane portions located at approximately equal intervals are wider in the circumferential direction of the annular sliding portion than the other vane portions, and A disc rotor for a disc brake, characterized in that the width is approximately the same as or wider than the circumferential width of a ventilation hole.