JPH1019070A - Ventilated rotor - Google Patents

Abstract

(57) [Problem] To provide a good cooling effect by reducing ventilation resistance of cooling air in a ventilation hole, and to be able to be shared by left and right wheels of a vehicle. Kind Code: A1 A plurality of two types of ribs having different lengths are interposed between sliding plates at radial and radial intervals along a radial direction. The long ribs 5 and the short ribs 6 are arranged alternately and radially so that the radially outer ends are aligned concentrically, so that the radially inner ends of the ribs 5 and 6 are irregular. The inner peripheral surface of the sliding plate 3 on the inner side is formed as an uneven surface 3A along the line connecting the radially inner ends of the ribs 5 and 6. That is, the projection 3a is located at a position slightly inward in the radial direction from the radially inner end of the long rib 5, and the concave portion is located at a position slightly inwardly inward from the radially inner end of the short rib 6. Uneven surface 3A so that 3b is located
To form A space between the ribs 5 and 6 is defined as a ventilation hole 7.

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 which rotates together with a wheel and forms a friction surface with a brake pad, in which a ventilation hole is formed from the inner peripheral surface to the outer peripheral surface. With respect to the ventilated rotor designed to improve the cooling effect, in particular, the ventilation resistance of the cooling air in the ventilation holes is reduced to increase the flow rate and the flow velocity of the cooling air, thereby achieving better cooling. The effect can be obtained, and further cost reduction can be expected.

[0002]

2. Description of the Related Art A ventilated rotor includes an outer sliding plate located on the outer side in the vehicle width direction, an inner sliding plate located on the inner side in the vehicle width direction, and two sliding plates. And a plurality of ribs radially interposed therebetween to form a ventilation hole. The central part of the two sliding plates is cut out in a circular shape somewhat larger than the outer diameter of the axle to which this ventilated rotor is fixed,
A cylindrical member is coaxially fixed to the inner peripheral portion of the outer sliding plate. The ventilated rotor is fixed to the axle via bolt holes and the like formed on the bottom surface of the cylindrical member.

[0003] When the ventilated rotor rotates integrally with the axle, an airflow is generated in the inner peripheral portion in a direction opposite to the rotational direction, and the air in the inner peripheral portion flows into the ventilation hole due to the centrifugal force. It flows in and is exhausted from the outer peripheral surface through the ventilation holes. That is, the air passing through the ventilation holes takes heat from the inner surface of the sliding plate and the side surfaces of the ribs, so that the cooling effect of the ventilated rotor is expected. Therefore, increasing the flow rate and flow rate of the cooling air passing through the ventilation holes is a key point for obtaining a large cooling effect.

A conventional ventilated rotor for increasing the cooling effect is disclosed in, for example, Japanese Patent Application Laid-Open No.
Japanese Patent Application Laid-Open No. 129452/12952. The conventional ventilated rotor described in this publication divides each rib into a relatively short inner peripheral side rib disposed on the inner peripheral side and a relatively long outer peripheral side rib disposed on the outer peripheral side. In addition, each inner peripheral rib is positioned between two adjacent outer peripheral ribs. Then, the ventilated rotor rotates in the normal direction (the direction in which the vehicle rotates when the vehicle moves forward).
In order to reduce the separation flow region formed in the ventilation hole when rotating in the ventilated rotor, in the ventilated rotor described in the above-mentioned publication, the inner peripheral side rib is formed between two adjacent outer peripheral side ribs. It was arranged at a position slightly deviated forward in the forward rotation direction from the intermediate position. Further, the above-mentioned publication also discloses a structure in which the inner peripheral ribs and the outer peripheral ribs are inclined so that their radial outer ends face forward in the normal rotation direction in order to reduce the separation flow region. I have.

[0005]

However, in the ventilated rotor described in the above-mentioned publication, the ribs are appropriately arranged in consideration of the forward rotation direction of the ventilated rotor. However, the structure of the ventilated rotor for the left wheel of the vehicle and the structure of the ventilated rotor for the right wheel are in a plane-symmetric relationship, and they cannot be shared, which has been an obstacle to reducing the manufacturing cost.

The present invention has been made in view of the problems to be solved by the conventional technology, and can be shared by the left and right wheels of the vehicle to reduce the cost. It is an object of the present invention to provide a ventilated rotor capable of reducing the ventilation resistance of the cooling air, increasing the flow rate and flow velocity of the cooling air, and thereby obtaining a better cooling effect.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, a pair of opposed sliding plates are provided.
In a ventilated rotor for a disc brake in which a ventilation hole is formed by being connected via a plurality of ribs extending radially, an inner peripheral surface of the sliding plate has an uneven surface in which unevenness is arranged in a circumferential direction.

According to a second aspect of the present invention, there is provided a ventilated rotor according to the first aspect,
The plurality of ribs are arranged such that their radially inner ends are located near recesses or protrusions on the inner peripheral surface of the sliding plate.

According to a third aspect of the present invention, there is provided a ventilated rotor according to the first aspect of the invention.
The plurality of ribs are composed of at least two types of a long rib and a short rib, and the long ribs and the short ribs are arranged alternately and radially so that radial outer end positions are aligned,
The inner peripheral surface of the sliding plate is the irregular surface along a line connecting the vicinity of the radially inner end of the long rib and the vicinity of the radially inner end of the short rib.

According to a fourth aspect of the present invention, in the ventilated rotor according to the first to third aspects, the center of the slope between the concave portion and the convex portion on the inner peripheral surface of the sliding plate is concave. I didn't.

According to a fifth aspect of the present invention, in the ventilated rotor according to the first to fourth aspects, a corner of the inner peripheral surface of the sliding plate on the ventilation hole side is chamfered. .

Here, in the invention according to claim 1,
During the rotation of the ventilated rotor, the airflow flowing in the rotor inner peripheral portion in the direction opposite to the rotation direction flows into the respective ventilation holes after flowing on the uneven surface of the inner peripheral surface of the sliding plate. The direction is a direction substantially orthogonal to the uneven surface when viewed from the axial direction. That is, when the inner peripheral surface of the sliding plate is a normal cylindrical surface, the direction of the cooling air flowing into the ventilation hole from the inner peripheral side of the rotor is determined by the vector pointing in the opposite direction to the rotor rotation direction and the centrifugal force. In contrast to the direction in which the vector is combined, that is, the direction along the vector that faces outward in the radial direction while facing backward in the rotation direction, the direction according to the invention according to claim 1 is determined in the ventilation hole. The direction in which the cooling air flows can be easily adjusted.

If a plurality of ribs are provided, for example, according to the second aspect of the present invention, the cooling air flows into the ventilation holes while minimizing interference between the radially inner ends of the ribs and the cooling air. Since the separation flow area can be reduced and the flow path width can be increased, the flow rate and flow velocity of the cooling air in the ventilation holes increase. Similarly, in the invention according to claim 3, the cooling air can flow into the ventilation hole while minimizing the interference between the radially inner end of the rib and the cooling air, and the separation flow region can be reduced. Since the flow width can be increased by decreasing the flow rate, the flow rate and the flow velocity of the cooling air in the ventilation hole increase.

Further, in the invention according to claim 4, the air flowing along the inner peripheral surface of the sliding plate goes around the slope between the concave portion and the convex portion of the inner peripheral surface of the sliding plate, and the ventilation hole is formed. When the cooling air flows into the ventilation holes, the width of the cooling air flowing into the ventilation holes is further increased because the width of the cooling air flows into the ventilation holes due to the influence of the slope having a concave central portion. The depression on the slope between the concave portion and the convex portion on the inner peripheral surface of the sliding plate may be formed by combining a plurality of flat surfaces, or may be formed by a concave curved surface.

Further, in the invention according to claim 5,
Since the ventilation resistance at the corners of the inner peripheral surface of the sliding plate is reduced, the air can flow more smoothly from the inner peripheral surface side of the sliding plate into the ventilation hole. The corner of the inner peripheral surface of the sliding plate may be rounded so as to be round, or may be chamfered with an oblique plane.

[0016]

As described above, according to the present invention, the direction in which the cooling air flows into the ventilation hole can be easily adjusted, so that the arrangement of each rib constituting the ventilation hole can be adjusted. By appropriately setting the uneven shape of the inner peripheral surface of the sliding plate, it is possible to obtain a good cooling effect by increasing the flow rate and flow velocity of the cooling air in the ventilation hole, and it is necessary to consider the rotation direction. Since it has no structure, it can be shared by the left and right wheels of the vehicle, which is advantageous in reducing the manufacturing cost.

In particular, according to the second and third aspects of the present invention, it is possible to surely increase the flow rate and flow rate of the cooling air in the ventilation hole by the interaction with the uneven surface on the inner peripheral surface of the sliding plate. And a better cooling effect can be obtained.

Further, according to the invention of claim 4, since the bias of the cooling air in the ventilation hole can be further reduced, the cooling effect is further improved. According to the fifth aspect of the present invention, since the flow of air into the ventilation hole becomes smoother, the flow rate and flow velocity of the cooling air can be further increased.

[0019]

Embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 to 5 show a first embodiment of the present invention, and FIG. 1 is a perspective view of a ventilated rotor 1 according to the present invention.

First, the structure will be described. The ventilated rotor 1 includes an outer sliding plate 2 disposed on the outer side in the vehicle width direction and an inner sliding direction in parallel with the sliding plate 2. And a central portion of the sliding plates 2 and 3 has a large opening, and an inner peripheral portion of the outer sliding plate 2 has: A cylindrical portion 4 used for attachment to an axle is fixed coaxially. A plurality of holes 4a for bolt insertion are formed in the bottom 4A of the cylindrical portion 4.

Between the pair of sliding plates 2 and 3, two types of ribs 5 and 6 having different lengths are interposed radially at equal intervals along the radial direction. The sliding plates 2 and 3 are integrated via the members 5 and 6.

Here, the ribs 5, 6 are long and narrow prism-shaped members having both ends finished in a semi-cylindrical shape. One of the ribs 5,..., 5 is relatively long, and the other ribs 6,. , 6 are relatively short, and as shown in FIG. 2, which is a plan view of each rib 5, 6 hidden behind the sliding plate 3, see FIG.
The long ribs 5, ..., 5 and the short ribs 6, ..., 6 are arranged alternately and radially so that their radially outer ends are aligned on a concentric circle. Since the positions of the radially outer ends of the ribs 5 and 6 having different lengths are aligned, the radially inner ends of the ribs 5 and 6 are irregular.

Then, the irregular ribs 5,
The inner peripheral surface of the sliding plate 3 on the inner side is an uneven surface 3A so as to be along the line connecting the radially inner ends of the sliding plates 6. That is, the convex portion 3a is located at a position slightly inward of the radially inner ends of the long ribs 5,..., 5 and slightly more radially than the radially inner ends of the short ribs 6,. So that the concave portion 3b is located at the position where it enters inside the direction
An uneven surface 3A is formed. Therefore, the radially inner end of the long rib 5 is located near the convex portion 3a, more specifically, near the convex portion 3a or the concave portion 3b alternately arranged in the circumferential direction. The ribs 5 and 6 are arranged so that the radially inner end of the short rib 6 is located at the end of the rib. In addition, between each convex part 3a and each concave part 3b, it is the slope 3c which consists of a plane.

The shape of the uneven surface 3A will be described in more detail. As shown in FIG.
The convex portion 3a and the concave portion 3b forming A have a circumferentially symmetric shape with respect to each straight line 1A extending in the radial direction of the ventilated rotor 1 and passing through the center of the ribs 5, 6. That is, paying attention to two slopes 3c ^* and 3c ^* between one concave portion 3b ^* and two convex portions 3a ^* and 3a ^* on both sides thereof, the center of the rib 6 close to the one concave portion 3b ^* is focused. Considering a straight line 1B orthogonal to the passing straight line 1A and intersecting the slopes 3c ^* , 3c ^* , the straight line 1B
B and the angle theta ₁ between one slope 3c ^*, are the same angle as the angle theta ₂ between the straight line 1B and the other inclined surface 3c ^*. When such a straight line 1B is considered with respect to another straight line 1A, the straight line 1B and the slopes 3 on both sides are considered.
Two angles formed by c and 3c are equal.

As described above, the ventilated rotor 1 of the present embodiment has a structure that does not consider the direction of rotation. A ventilation hole 7 is formed between each of the ribs 5 and 6 so that an inner peripheral side and an outer peripheral side of the ventilated rotor 1 communicate with each other through each ventilation hole 7 to allow cooling air to escape. Has become.

Next, the operation of this embodiment will be described. 4 and 5 are views for explaining the operation of the present embodiment. FIG. 4 is a perspective plan view in which main parts are enlarged as in FIG.
FIG. 5 is an enlarged perspective view of a main part. In the following description, only two ventilation holes 7A and 7B formed on both sides of one short rib 6 will be noted, and the description of the other ventilation holes 7 will be omitted because they are duplicated. Further, the rotation direction of the ventilated rotor 1 is indicated by an arrow R in FIG. 4, but since the operation of the ventilated rotor 1 does not change depending on the rotation direction, the rotation direction R is either the normal rotation direction or One of the reverse directions. Then, the ventilation hole on the rear side along the rotation direction R with respect to the one short rib 6 is defined as a ventilation hole 7A, and the ventilation hole on the front side along the rotation direction R with respect to the one short eve 6 is a ventilation hole. 7B.

[0027] That is, the ventilated rotor 1 is rotated together with the axle, and at the same time the air flow F _X of relatively opposite direction to the rotation direction R in the inner peripheral portion occurs, ventilation holes 7A under the influence of centrifugal force, Cooling air F ₁ and F ₂ flowing from the inner peripheral side to the outer peripheral side in 7B are also generated. That is, the airflow F _X is flowing along the uneven surface 3A is an inner peripheral surface of the sliding plate 3, the sliding plate 3 there under the influence of centrifugal force from
And flows into the ventilation holes 7A or 7B to form cooling air F ₁ and F ₂ .

[0028] Then, the air flow F _X is ventilation holes 7
Cooling air F ₁ which is formed by flowing around the corners of the inclined surface 3c forming the inlet of A ventilation hole 7 while aiming at a direction substantially orthogonal in plan view with respect to the inclined surface 3c
A flows into A. For this reason, the cooling air F ₁
Flows into the ventilation hole 7A almost without interfering with the radial inner end. That is, the ventilation resistance at the inflow port of the ventilation hole 7A is low.

When the cooling air F ₁ flows into the ventilation hole 7A, the direction of the flow does not change significantly.
That for flowing into the ventilation hole 7A unchanged large with respect to the direction of the airflow F _x, bench at a speed close to the synthesis velocity of the flow velocity and centrifugal force of the airflow F _x determined by the rotational speed of the ventilated rotor 1 It passes through the inside of the ration hole 7A. Also from the point that this high flow velocity can be maintained, the ventilation resistance in the ventilation hole 7A can be reduced.

Furthermore, in order to high flow rates of the cooling air F ₁ ventilation hole 7A as described above can be maintained, a strong vortex flow in the separated flow region 8A is formed on the side closer to the rib 6 of the ventilation holes 7A V _X is formed. Therefore, among the separated flow region 8A, since the latter part of the ventilation holes 7A is sucked into the rotation of the vortex V _X, channel width B ₁ of the second half of the ventilation hole 7A is to expand. As a result, the ventilation resistance of the outflow portion of the ventilation hole 7A is also reduced.

[0031] Thus, since the airflow resistance of the ventilation holes 7A are reduced over the entire until the outlet from the inlet, air volume and flow rate of the cooling air F ₁ which passes through the ventilation hole 7A is It will rise.

Further, cooling air F ₁ flowing into the ventilation hole 7A has become difficult to interfere with the end portion of the rib 6,
Moreover since passage width B ₁ by vortex V _X from Tsu is adapted to expand, because separated flow region 8A in the ventilation holes 7A are decreased, touches the cooling air F ₁ of the ventilation holes 7A inner surface As a result, the ratio of the surface area where heat dissipation is expected is increased. Furthermore, so that the heat dissipation is also promoted from the side of the rib 6 in the ventilation holes 7A by a strong vortex V _X.

From the above, a high cooling effect is obtained in the ventilation hole 7A, and the ventilated rotor 1
This improves the heat dissipation. On the other hand, the cooling air F ₂ airflow F _X is formed by flowing around the corners of the inclined surface 3c forming the inlet of the ventilation holes 7B, while aiming to a direction substantially orthogonal in plan view with respect to the inclined surface 3c Bench It flows into the ration hole 7B. That is, the cooling air F
₂ is greatly bent at the corner of the slope 3c,
B flows into the ventilation hole 7B in a state in which the angle β is relatively large without the angle B. More specifically, cooling air F ₂ is oriented is changed so as to approach the radial direction (direction parallel to the ribs 5, 6) to flow into the ventilation hole 7B. For this reason, the cooling air F ₂ flows into the ventilation hole 7B without substantially interfering with the radially inner end of the short rib 6, so that the ventilation resistance at the inflow port of the ventilation hole 7B decreases. I have.

When the direction of the cooling air F ₂ approaches the direction parallel to the ribs 5 and 6, the separation flow region 8B formed along the side surface of the long rib 5 in the ventilation hole 7B is reduced. since made, channel width B ₂ of the ventilation holes 7B is enlarged.

[0035] Thus, since it reduced in a wide range even airflow resistance of ventilation holes 7B over the outlet from the inlet, so that the air volume and flow rate of the cooling air F ₂ which passes through the ventilation hole 7B rises become.

Further, if reducing flow separation region 8B of the ventilation hole 7B is the percentage of the surface area of heat dissipation can be expected by the cooling air F ₂ touches of ventilation holes 7B inner surface increases.

As described above, a high cooling effect is obtained even in the ventilation hole 7B, and the heat radiation of the ventilated rotor 1 is improved. FIGS. 6 and 7 are diagrams for explaining the flow of cooling air in the ventilated rotor 1 having a structure in which no unevenness is formed on the inner peripheral surface of the sliding plate 3 as a comparison object with the present embodiment. , FIG. 6 corresponds to FIG. 4, and FIG. 7 corresponds to FIG. Note that the same components as those in the present embodiment are denoted by the same reference numerals. However, the ventilation holes formed between the long ribs 5 are ventilation holes 7C.

That is, even in the ventilated rotor 1 having such a structure, the airflow F _X flowing along the inner peripheral surface 3B of the sliding plate 3 in the direction opposite to the rotation direction R on the inner peripheral side thereof. caused to flow into the ventilation hole 7C wraps around the corner of the inner peripheral surface 3B is its airflow F _X. Cooling air flowing into the ventilation hole 7C interferes with the ends of the ribs 6, diverted to the cooling air F ₃ flowing into the ventilation hole 7A, and the cooling air F ₄ flowing into the ventilation hole 7B I do.

At this time, when the cooling air F ₃ flows into the ventilation hole 7A due to the interference with the end of the rib 6, the direction of the cooling air F ₃ can be largely changed so as to approach the rib 5; the airflow resistance increases, moreover, the ventilation holes 7A relatively passage width B ₁ short width of the separated flow region 8A is formed on the side surface of the rib 6 is increased within becomes narrow.

[0040] Therefore, air volume and flow rate of the cooling air F ₃ which passes through the ventilation hole. 7A becomes lower than in the case of the present embodiment is the good cooling effect can not be expected. FIG. 8 shows an experiment in which the flow velocity of the cooling air passing through the ventilation holes 7A was measured for the structure of the present embodiment in which the inner peripheral surface of the sliding plate 3 was uneven and a comparative object in which the sliding surface was cylindrical. Is a graph showing the results of the above, and it is also clear from the experimental results that the structure of the present embodiment can obtain a higher flow velocity.

Further, the cooling air F ₄ flowing into the ventilation hole 7B can be largely changed in direction so as to approach the rib 5 when flowing into the ventilation hole 7B due to interference with the end of the rib 6. The ventilation resistance at the inflow port of the ventilation hole 7B is large, and the separation flow region 8 formed on the side surface of the long rib 5 in the ventilation hole 7B.
Relatively passage width B ₂ width B is increased becomes narrow.

[0042] Therefore, air volume and flow rate of the cooling air F ₄ which passes through the ventilation hole. 7B becomes lower than in the case of the present embodiment is the good cooling effect can not be expected. FIG. 9 shows an experiment in which the flow rate of the cooling air passing through the ventilation holes 7B was measured for the structure of the present embodiment in which the inner peripheral surface of the sliding plate 3 was uneven and a comparative object in which the sliding surface was cylindrical. Is a graph showing the results of the above, and it is also clear from the experimental results that the structure of the present embodiment can obtain a higher flow velocity.

FIG. 10 shows the angle β of cooling air flowing into the ventilation hole 7B and the internal angle of the sliding plate 3 in the structure of the present embodiment in which the inner peripheral surface of the sliding plate 3 is uneven. It is a graph which shows the result of the experiment which measured the inflow angle (beta) of the cooling air into the ventilation hole 7C in the comparative object which made the peripheral surface into a cylindrical surface, and also from this experiment result, the structure of this Embodiment shows Indicates that the inflow angle β is large. The inflow angle β is too large (nearly at right angles), because thereby the ventilation resistance of the inlet of the ventilation hole 7B is small, achieve high cooling effect correspondingly by cooling air F ₂ which passes through the ventilation hole 7B It is done.

The ventilated rotor 1 of the present embodiment can provide the above-described excellent cooling effect regardless of the direction of rotation. It can be. Therefore, it can greatly contribute to a reduction in manufacturing cost.

FIGS. 11 and 12 are views showing a second embodiment of the present invention, and are perspective plan views in which main parts are enlarged similarly to FIG. The same members and parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, the structure of the present embodiment is substantially the same as the structure of the first embodiment, and the difference is that the slope 3
The only difference is that the center of c is recessed. More specifically,
In this embodiment, the straight line L ₁ extending from the recess 3b to the convex portion 3a, and a straight line L ₂ extending toward the recess 3b from the convex portion 3a, is the intersection with cross at substantially the center portion of the inclined surface 3c radius by assuming so biased to outwardly to form an inclined surface 3c in the plane and a plane along a straight line L ₂ along the line L _1, and recessed central portion of the inclined surface 3c.

With such a configuration, as shown in FIG. 12, the cooling air flowing into the ventilation hole 7A from the inner peripheral side further approaches the rib 5 side when going around the corner of the slope 3c. a cooling air F _11, so divided into a cooling air F ₁₂ further closer to the rib 6 side. Similarly, the cooling air flowing into the ventilation hole 7B from the inner peripheral side is inclined 3
When flowing around the corner of c, the cooling air F ₂₁ further closer to the rib 6 side, so divided into a cooling air F ₂₂ further approaches the ribs 5 side. That is, when the cooling air flowing into the ventilation holes 7A and 7B goes around the corner of the slope 3c, the width thereof naturally expands.

As a result, the ventilation holes 7A and 7
The flow of the cooling air in B is further uniformed, and heat can be removed from a wider area in the ventilation holes 7A and 7B, so that a better cooling effect can be obtained. Other functions and effects are the same as those in the first embodiment.

In this embodiment, the slope 3c is composed of two planes. However, the present invention is not limited to this. The slope 3c is composed of three or more planes so that the center portion is concave. You may make it.

FIGS. 13 and 14 are views showing a third embodiment of the present invention, and are perspective plan views in which main parts are enlarged as in FIG. The same members and parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, the structure of the present embodiment is substantially the same as the structure of the above-described second embodiment, except that the slope 3
The only difference is that c is a curved surface, so that its center is depressed.

[0052] With such a structure, as shown in FIG. 14, the cooling air F ₁ flowing from the inner circumferential side ventilation holes 7A, when wrap around corners of the inclined surface 3c, to widen It will, likewise, the cooling air F ₂ flowing from the inner circumferential side ventilation holes 7B, when wrap around corners of the inclined surface 3c, so widen.

As a result, similarly to the second embodiment, the flow of the cooling air in the ventilation holes 7A and 7B is further uniformed, and the ventilation holes 7A and 7B
Heat can be removed from a wider area in the inside, and a better cooling effect can be obtained. Other functions and effects are the same as those in the first embodiment.

FIGS. 15 and 16 are views showing a fourth embodiment of the present invention. FIG. 15 is a perspective plan view in which main parts are enlarged similarly to FIG. 4, and FIG. FIG. 3 is a sectional view taken along line AA. The same members and parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, in the present embodiment, as shown in FIG. 16 in particular, the corner 3d on the ventilation holes 7A and 7B side of the uneven surface 3A which is the inner peripheral surface of the sliding plate 3 is chamfered. It has a round shape. Other configurations are the same as those of the first embodiment.

With such a configuration, the ventilation resistance at the inflow ports of the ventilation holes 7A and 7B is further reduced, so that the cooling air flows from the inner peripheral side of the ventilated rotor 1 into the ventilation holes 7A and 7B. And the flow of the cooling air can be prevented from being separated when the cooling air passes through the corner 3d, so that the air volume and flow velocity of the cooling air further increase, and a good cooling effect can be obtained. Other functions and effects are the same as those in the first embodiment.

In this embodiment, the corner 3d
The same operation and effect can be obtained by chamfering, for example, along an oblique plane without rounding. In the above embodiments, the ribs 5 and 6 having different lengths are used.
However, the present invention is not limited to this. For example, ribs having the same length may be provided such that the positions of the radially inner end portions thereof are close to the convex portions 3a and the concave portions 3b as in the above embodiments. The same operation and effect as those of the above embodiments can be obtained.

[Brief description of the drawings]

FIG. 1 is a perspective view illustrating a configuration of a first exemplary embodiment of the present invention.

FIG. 2 is a perspective plan view showing the configuration of the first embodiment.

FIG. 3 is an enlarged view of a main part of FIG. 2;

FIG. 4 is a transparent enlarged plan view illustrating the operation of the first embodiment.

FIG. 5 is a perspective view illustrating the operation of the first embodiment.

FIG. 6 is an enlarged perspective plan view illustrating the operation of a comparative example.

FIG. 7 is a perspective view illustrating the operation of a comparative example.

FIG. 8 is a graph showing a result of an experiment for measuring a flow velocity of cooling air in a ventilation hole.

FIG. 9 is a graph showing a result of an experiment for measuring a flow velocity of cooling air in a ventilation hole.

FIG. 10 is a graph showing a result of an experiment for measuring an inflow angle of cooling air into a ventilation hole.

FIG. 11 is a perspective plan view showing the configuration of the second embodiment.

FIG. 12 is an enlarged perspective plan view illustrating the operation of the second embodiment.

FIG. 13 is a perspective plan view showing the configuration of the third embodiment.

FIG. 14 is an enlarged perspective plan view illustrating the operation of the third embodiment.

FIG. 15 is a perspective plan view showing the configuration of the fourth embodiment.

FIG. 16 is a sectional view taken along line AA of FIG.

[Explanation of symbols]

 Reference Signs List 1 ventilated rotor 2, 3 sliding plate 3A uneven surface 3a convex portion 3b concave portion 3c slope 5 rib (long rib) 6 rib (short rib) 7, 7A, 7B ventilation hole

Claims (5)

[Claims] 1. A ventilated rotor for a disc brake having a ventilation hole formed by connecting a pair of opposed sliding plates via a plurality of radially extending ribs, wherein an inner periphery of the sliding plate is provided. A ventilated rotor, wherein the surface is an uneven surface in which unevenness is arranged in a circumferential direction. 2. The ventilated rotor according to claim 1, wherein the plurality of ribs are disposed such that radially inner ends thereof are located near concave portions or convex portions on an inner peripheral surface of the sliding plate. . 3. The plurality of ribs are composed of at least two types of long ribs and short ribs, and the long ribs and the short ribs are arranged alternately and radially so that the outer end positions in the radial direction are aligned. 2. The uneven surface of the sliding plate along a line connecting the vicinity of the radially inner end of the long rib and the vicinity of the radially inner end of the short rib. 3.
The ventilated rotor as described. 4. The ventilated rotor according to claim 1, wherein a central portion of the slope between the concave portion and the convex portion on the inner peripheral surface of the sliding plate is concave. 5. The ventilated rotor according to claim 1, wherein a corner of the inner peripheral surface of the sliding plate on the ventilation hole side is chamfered.