JPH05346126A - Brake disc rotor - Google Patents

Abstract

PURPOSE:To improve the air-blasting and cooling efficiency of a rotor by suppressing the pressure loss of the flow in a bench hole and the reduction of the surface heat transfer coefficient of the cooling air, and to increase the total heat radiating quantity by increasing the cooling area. CONSTITUTION:A brake disc rotor is provided with sliding plates 11, 12 on the inner and the outer sides which are continuously arranged by keeping the space in the axial direction of the axle, a plurality of fins 2 consisting of an inlet part 21 arranged in a radial and inclined manner relative to the radial direction and an outlet part 22 inclined at a smaller angle from the inlet part 21, a plurality of bench holes 4 which are radially partitioned by the fins 2, an inlet opening 31 and an outlet opening 32 which are respectively open inwardly and outwardly in the radial direction, and communicating ports 5 which are formed in the respective fins 2, and are communicated with the adjacent bench holes 4. The brake disc rotor consists of a round part 61 formed at the inner radius part of a sliding plate 11, a direction changing part 62 formed in the radius part of the sliding plate 12, and a plurality of compact heat- radiating fins 71-74 formed on the outer circumferential part of the inner wall of the sliding plates 11, 12.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake disc rotor of a disc brake device used in vehicles and the like.

[0002]

2. Description of the Related Art A conventional brake disc rotor is shown in FIG.
0 and disk-shaped sliding plates OP and IP as shown in FIG.
A plurality of partition walls F are simply formed between the partition walls, and an inlet opening I, an outlet opening O, and a radial passage H are formed between the partition walls.

[0003]

The above-mentioned conventional brake disc rotor, which is apparent from the observation of the oil film for analyzing the flow in the passage, is shown in FIG. 12 showing the processing data by the styrene particle tracer method and the above. As shown in FIG. 13 showing a sketch of a flow based on the flow, a flow that has flowed into the passage H at the inlet opening I at an angle of about 50 degrees from the velocity triangle of the circumferential velocity component and the radial velocity component at the inlet opening,
Separation occurs in the thickness direction of the partition F on the negative pressure surface side of the partition F forming the fin, and a wide stagnation Y occurs in the lower part of the partition in the passage H forming the bench hole. Therefore, the main river basin M
There is a problem that S becomes very narrow, a quasi-secondary flow SS is generated due to collision with the upper surface of the partition wall, and a backflow RS from the outside is generated in the upper portion of the outlet opening.

As a result, in the conventional brake disc rotor, since the main flow area MS is narrowed and the pressure loss of the flow is large, the surface heat transfer coefficient in the passage area of the cooling air is reduced, and the air blowing and cooling efficiency of the rotor is poor. At the same time, there is a problem that the total amount of heat radiation is reduced because the cooling area is reduced.

Therefore, as a result of analyzing the various flows of the conventional brake disc rotor by using an oil film observation photograph and an image processed by the tracer method, the present inventors have found that the partition angle of the partition wall constituting the fin is separated. If the angle is set to suppress and the flow is formed by using the pressure difference between the pressure surface and the negative pressure surface of the partition wall to prevent separation at the inlet, the main flow area MS is narrowed. The stagnation area Y is narrowed. Basin M
We focused on the technical idea of the present invention that S may become wider.

As a result of further research and development, the inventors of the present invention have arranged the partition wall with an inclination of an angle equal to or smaller than the inflow angle of the flow to prevent the occurrence of separation in the vicinity of the inlet opening, and to apply pressure to the partition wall. By forming a communication port for recovery, the pressure on the suction side is recovered to prevent separation of the above-mentioned conventional inlet opening, reduce the stagnation region Y of the bench hole, and reduce the pressure loss of the flow. The present invention achieves the object of increasing the total amount of heat radiated to expand the cooling area while improving the air blowing and cooling efficiency of the rotor by reducing the decrease in the heat transfer coefficient of the surface of the cooling air. ..

[0007]

DISCLOSURE OF THE INVENTION A brake disc rotor according to the present invention (a first invention according to claim 1) slides with a disc-shaped sliding plate which is arranged on the left and right and is spaced apart in the axle direction. A plurality of partition walls radially arranged between the plates, at least the inner peripheral side portion of which is inclined at an angle equal to or less than the inflow angle of the flow; a plurality of passages radially formed between the plurality of partition walls; It comprises a plurality of inlet openings and outlet openings which communicate with the passages and are opened inward and outward in the radial direction, and a plurality of communication openings which are formed in the plurality of partition walls and allow adjacent passages to communicate with each other through the partition walls. ..

A brake disc rotor according to the present invention (a second invention according to claim 2) is the brake disk rotor according to the first invention, wherein the outer peripheral side portion of the partition wall is inclined toward the wake behind rotation.

The brake disc rotor of the present invention (the third invention according to claim 3) is the brake disc rotor according to the first invention, wherein the thickness of the tip of the inner wall forming the inlet opening of the disc-shaped sliding plate on the inner side is the tip. The chamfered portion gradually decreases as it goes to, and the tip end portion which constitutes the inlet opening of the disc-shaped sliding plate on the outer side is projected radially inward from the disc-shaped sliding plate on the inner side. At the same time, a protrusion is formed whose thickness gradually increases toward the tip.

In the brake disc rotor of the present invention (the fourth invention according to claim 4), in the second invention, at least the outer peripheral portion of the inner wall forming the passages of the disk slide plates on the outer side and the inner side. Radiating fins formed by small protrusions having a small width and height that are radial and are substantially parallel to the partition wall are formed.

[0011]

In the brake disc rotor according to the first aspect of the present invention having the above-described structure, the angle between the partition wall and the flow that has flowed at a certain inlet angle is relatively smaller than that of the conventional partition wall. In addition to preventing the occurrence of separation at the inlet opening, part of the flow that flows near the partition wall of the flow that has flowed in from the inlet opening passes through the communication port and flows into the negative pressure surface side under the partition wall to form a flow. By
This has the effects of preventing separation on the suction surface side, narrowing the stagnation area, widening the main flow area, and suppressing backflow at the outlet opening.

In the brake disc rotor according to the second aspect of the present invention having the above-mentioned structure, the outer peripheral side portion of the partition wall is inclined toward the wake after rotation, so that the flow passing through the communication port flows along the partition wall of the outer peripheral side portion. Also in the outer peripheral side portion, the main flow region is widened by effectively preventing separation on the suction surface side and narrowing the stagnation region.

In the brake disc rotor according to the third aspect of the present invention having the above structure, the inner side of the inner sliding plate has the chamfered portion and the outer side sliding plate has the inner wall having the protruding portion. This has the effect of smoothly changing the direction of the inflow at the inlet opening.

In the brake disc rotor according to the fourth aspect of the present invention having the above-described structure, since the small protrusions forming the heat radiation fins are formed along the flow in the place where the flow is fast, the heat radiation area is increased and the fin action is achieved. ..

[0015]

In the brake disc rotor of the first aspect of the invention having the above-described operation, the inner peripheral side portion of the sloping partition wall and the communication port widen the main flow region in the passage and suppress the backflow of the outlet opening. By reducing the pressure loss of the flow and reducing the decrease in the heat transfer coefficient on the surface of the cooling air, it is possible to improve the air blowing and cooling efficiency of the rotor and to increase the total heat dissipation to expand the cooling area. Play.

In the brake disc rotor according to the second aspect of the present invention, which has the above-described operation, the outer peripheral side portion of the partition wall is inclined toward the post-rotation flow side. By suppressing the backflow, it is possible to further improve the air blowing / cooling efficiency of the rotor as compared with the first aspect of the invention, and to increase the total heat radiation amount in order to expand the effective cooling area.

In the brake disc rotor according to the third aspect of the present invention, which has the above-mentioned operation, the flow direction of the inflow is smoothly changed to the radial direction by the chamfered portion and the projecting portion at the inlet opening, so that the separation on the suction surface side of the partition wall is prevented. The effect of suppressing is exhibited.

In the brake disc rotor of the fourth aspect of the invention having the above-mentioned operation, since the heat dissipation area is increased by the small projections along the flow forming the heat dissipation fins, the total heat dissipation amount is further increased.

[0019]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) The brake disc rotor of the first embodiment is applied to a disc brake device for an automobile, and is arranged inside each wheel WH as shown in FIGS. 6 and 7. The air sucked from the suction port S of the dust cover DC is introduced into the bench hole of the rotor, which will be described in detail with reference to FIGS. 1 to 7.

(Structure of the First Embodiment) A brake disc rotor 1 of the first embodiment has inner and outer sliding plates 1 which are arranged side by side in the axial direction of an axle WS (in FIG. 7) with a space therebetween.
1 and 12, a plurality of fins 2 forming a partition wall which are arranged between the sliding plates 11 and 12 in a radial direction of the disk, and radially inward between the sliding plates 11 and 12. A plurality of openings 31 and 32 opening to the outside
A plurality of bench holes 4 forming a passage formed by the sliding plates 11 and 12 and the adjacent partition wall 2, a communication port 5 formed in each fin 2 for communicating adjacent bench holes, and an inner side A direction changing portion 62 that forms a rounded portion 61 that constitutes a chamfered portion at the tip of the inner wall of the sliding plate and forms a protrusion at the tip of the outer sliding plate, and the inner and outer sliding plates. The heat dissipation fins 7 are radially arranged on the inner wall of each of the bench holes 4.

As shown in FIG. 2, the outer slide plate 12 is formed integrally with the inner slide plate through a step portion 13 and a boss portion 14 having a fixing hole. The outer side sliding plate 12 and the inner side sliding plate 11 linearly increase in thickness as they go outward in the radial direction, and linearly decrease the height of the bench hole 4.

The fin 2 has a thickness of 4.5 mm and has a radius of 165 mm to a radius of 275 between the outer side and inner side sliding plates.
It is integrally molded radially in the range of mm. That is, the inlet portion 21 corresponding to the inner peripheral side portion is formed with an inclination of 30 degrees with respect to the straight line N connecting the tip 21E and the center (not shown) of the disc as shown in FIG. The outlet portion 22 corresponding to the side portion is formed with an angle smaller than 30 degrees of the inlet portion and inclined by 20 degrees with respect to a straight line connecting the tip 21G of the inlet portion and the center of the disk. This is a so-called two-stage fin structure that effectively secures the action.

That is, the inlet portion 21 and the outlet portion 2
The arrangement angle of 2 is determined according to the inflow angle of the flow into the rotor, and since the flow generally flows in the range of 30 to 70 degrees, the angle is equal to or slightly smaller than that. It will be set to an angle. Fin 2 entrance part 2
The arrangement angle of 1 and the outlet part 22 is best along the inflow angle of the flow with a small inflow loss, but if it is small within a certain range with respect to the inflow angle of the flow, it is an undesired region as a partial flow. However, the inflow loss is relatively small because the inlet cross-sectional area is enlarged, and it is effective when the number of fins is large (when the fin interval is narrow). On the contrary, there is an undesired region as a part of the flow even if it is large within a certain range with respect to the inflow angle of the flow. small. As a result, the arrangement angle of the fins 2 may be set within a certain angle range according to the inflow angle of the flow.

In the bench hole 4, the thickness of the sliding plates 12 and 11 on the outer side and the inner side increases linearly as it goes outward in the radial direction, and the height at the inlet opening 31 is 14 mm and at the outlet opening 32. Since the fin 2 has a height of 9 mm and the fins 2 are formed in a radial shape, the cross-sectional area thereof is formed substantially constant.

The communication port 5 has a length of 6.6 as shown in FIG.
mm, the fin 2 has a length of 15 mm for the inlet portion 21 and the length 34
and a line connecting the front end 21E of the inlet part 21F of the fin immediately before in the rotational direction and the front end of the communication port 5 (the rear end 21R of the inlet part 21 of the fin 2) and the inlet part 22. A straight line N connecting the tip 21E of 21 and the center of the disc
It is arranged at a position of an angle of 50 degrees with (radial direction of the disk), that is, 0.28L from the tip of the inner peripheral side of the fin 2.
Is formed at a position of 0.39L from the position of (1) (the entire length from the front end to the rear end of the fin 2 is L).

The allowable arrangement position of the communication port 5 depends on the inflow angle of the flow into the bench hole 4, but within the range of 0.1 L (70 degrees at the above angle) to 0.7 L (30 degrees). However, if it is too close to the inlet opening 31 (0.1 L or less),
The fin length on the inner circumference side is short, and the flow that has flowed in at an inflow angle of 40 to 50 degrees passes directly through the communication port. Since it occurs, the inflow loss at the inlet increases, the flow rate decreases, and the cooling performance deteriorates. Conversely, if it is too close to the outlet opening 32 (0.7 L or more), the occurrence of peeling on the outer peripheral side is suppressed and the stagnation area is reduced,
Since the pressure difference is reduced due to the spreading loss of the bench hole 4, the pressure recovery effect is reduced, and peeling occurs at the inlet.
A stagnation region is formed on the negative pressure surface side of the inner circumferential fin, resulting in deterioration of the flow rate and cooling performance. At 0.5 L or more, since the length of the fins on the outer peripheral side becomes short, the energy difference in the outer peripheral area of the hole that determines the ventilation capacity of the bench hole becomes small, and the passing flow rate tends to decrease. From the balance with the pressure recovery effect (flow rate increase effect) due to, the limit was set to 0.7L. If a good cooling effect is required, 0.2L to 0.5L, which is a desirable range depending on the fin arrangement interval and the number of rotations, may be adopted.
The first embodiment is set to 0.28L to 0.39L.

The allowable length of the communication port 5 is 2 mm to 15 mm, but if it is short, the effect as a pressure recovery port decreases, and if it is long, the effective length of the fin becomes short, the effect as a blade (blower) is obtained. As the optimum length range is 4 mm to 8 mm. In the first embodiment, the thickness is set to 6.6 mm in consideration of manufacturing.

The radius portion 61 at the inner wall tip of the inner side sliding plate 11 is chamfered at 45 degrees as shown in FIG. 2, and the minimum thickness portion is set to 5 mm from the viewpoint of strength. ing.

The direction changing portion 62 of the outer side sliding plate 12
As shown in FIG. 2, the inner wall should be projected inward in the radial direction from the inner sliding plate 11 and the inner wall should be gradually thickened as it goes inward to form a concave arc shape with a height of 4 mm. Thus, the flow in the axial direction of the rotor 1 is changed to the flow outward in the radial direction by cooperation with the rounded portion 61, and the flow is made to flow into the bench hole 4 via the inlet opening 31.

As shown in FIGS. 3 and 4, the radiating fin 7 has a long radiating fin 71 integrally formed along the fin 2 at a portion near the pressure side of the fin 22 on the outer peripheral side, and the central portion of the bench hole 4 is formed. Also, short radiating fins 72 and 73 are integrally formed along the fin 2 in the portion of the fin 22 close to the suction surface side, so that the heat radiating effect is enhanced without increasing the resistance of the flow in the bench hole 4. is there.

(Operation of the First Embodiment) In the brake disc rotor of the first embodiment having the above-mentioned structure, as shown in FIG. 2, the radius portion 61 and the direction changing portion 62 in the inlet opening 31 are provided.
The flow of the axial direction is smoothly converted into the flow of the radial direction by the cooperation with and the flow is made into the bench hole 4 at an inflow angle of 30 degrees as shown in FIG. By forming a smooth flow along the wall surface on the pressure surface side without causing separation in the vicinity of the opening of the portion 21 and letting a part thereof pass through the communication port 5 and flow into the next bench hole 4, In addition to promoting reattachment of the flow separated at the side portion, the occurrence of separation on the suction surface side of the outlet portion 22 of the fin 2 is suppressed, and the stagnation region 41 is reduced to wide the main flow region 4
Form 2.

This is also clear from the tracer particle processing data by the styrene particle tracer method, which traces floating styrene particles following the flow shown in FIG. 5 and visualizes the flow. Here, in the styrene particle tracer method, it is possible to obtain the velocity vector in the local area by associating the positions of the suspended particles that are continuously taken in, and it corresponds well with the wind velocity measurement results, and is suitable for mainstream observation. Therefore, the state of the flow in the main flow region 42 and the range of the stagnation region 41 are clearly shown in FIG.

(Effects of the First Embodiment) The brake disc rotor of the first embodiment having the above-described operation has the inlet portion 21 and the outlet portion 2 of the fins 2 inclined as shown in FIG.
2 and the communication port 5 form a smooth flow along the fin 2 to form an inlet portion 21 and an outlet portion 2 of the fin 2.
In order to suppress the generation of the stagnation region 41 due to the peeling of 2,
By suppressing the generation of the conventional quasi-secondary flow, the wide main flow region 42 is formed in the most desirable form to form the uniform flow in the bench hole, so that the reverse flow at the conventional outlet opening can also be suppressed and the pressure loss of the flow can be suppressed. To minimize the decrease in the heat transfer coefficient on the surface of the cooling air,
In addition to improving the ventilation and cooling efficiency of, the effective cooling area is expanded, and the total amount of heat radiation is increased.

That is, the cooling capacity, which is the amount of heat radiation, is the product of the heat radiation area, the heat transfer coefficient, and the temperature difference. In the case of forced convection heat transfer, the heat transfer coefficient is proportional to the 0.5 to 0.8 power of the flow velocity. Therefore, it is important to increase the flow velocity in order to improve the cooling capacity. In other words, in the first embodiment, it is possible to reduce the passage resistance and increase the flow velocity by preventing separation and suppressing the stagnation region and widening the main flow region 42. Since this is done, the amount of heat radiation and the cooling capacity are improved.

Since the cooling capacity is proportional to the heat radiation area,
It is important to increase the heat dissipation area.
By expanding the area of high flow velocity within the limited heat dissipation area, the heat dissipation area can be effectively secured and the area of high heat dissipation efficiency can be widened, so that the cooling capacity can be significantly increased.

Further, in the brake disc rotor 1 of the first embodiment, as shown in FIG. 2, by the cooperation of the rounded portion 61 and the direction changing portion 62 in the inlet opening 31, the flow in the axial direction is smoothly changed in the radial direction. Since it is converted into a flow, the effect of effectively suppressing separation of the flow generated near the tip of the inner wall of the inner side sliding plate 11 is obtained.

Further, in the brake disc rotor 1 of the first embodiment, as shown in FIGS. 3 and 4, four small heat radiation fins 71 to 74 are provided on the inner wall on the outer peripheral side of the inner and outer sliding plates. Since it is formed, there is an effect that the heat radiation effect is effectively enhanced without increasing the flow resistance in the bench hole 4.

Further, in the first embodiment, since the length of the communication port 5 is set to the optimum length of 6.6 mm, the stagnation due to the separation on the suction surface side of the fin 2 due to the flow passing through the communication port 5 is most efficient. The effect that it can be suppressed well is exhibited.

Further, in the first embodiment, the communication port 5
Is the optimum position of 0.28L (50 degrees at the above angle) ~
Since it is arranged at 0.39 L (the total length of the fin 2 is L), the stagnation due to the separation is most effectively suppressed by forming the flow through the communication port 5 utilizing the pressure difference between the both surfaces of the fin 2. There is an effect that can be.

(Second Embodiment) The brake disc rotor of the second embodiment prevents stagnation of the flow on the suction surface side of the fin 2 from the viewpoint of focusing more on improving the flow in the bench hole 4. In order to suppress the generation of the area more effectively,
Particularly, the shapes of the fins and the communication ports are changed.

As shown in FIG. 8, the inlet portion 2 of the fin 2
1 and the suction surface side tips 21N and 22 of the outlet portion 22
The thickness of N gradually increases, and the flow is the suction surface 21N of the fin 2.
And a streamlined shape so as to flow along 22N, and the rear end 21R of the inlet portion 21 of the fin 2 that constitutes the communication port 5 is formed into an S shape, and the flow along the rear end 21R is made to flow along the rear end 21R. It is configured to be directed along the negative pressure surface 22N of the outlet portion 22, and the communication port 5 is disposed at a position of about 0.3L to 0.5L from the tip of the inner peripheral side of the fin 2. I made it about 7 mm.

In the brake disc rotor of the second embodiment having the above-described structure, as shown in FIG. 8, the flow that has flowed into the bench hole 4 is along the suction side tip 21N of the inlet portion 21 of the fin 2 having a streamlined shape. Since it flows as a result, flow separation and stagnation are further suppressed as compared with the first embodiment, and
The flow passing through the communication port 5 has an S-shaped shape at the rear end 21R of the inlet portion of the fin 2 and the suction surface 22 of the outlet portion 22.
Due to the streamlined shape of N, the suction surface 2 of the outlet portion 22 of the fin 2
Since it smoothly flows along 2N, the effect of effectively preventing the occurrence of separation at the lower portion of the negative pressure surface of the outlet portion 22 of the fin 2 and suppressing stagnation is obtained as compared with the first embodiment.

(Third Embodiment) In the brake disc rotor of the third embodiment, as shown in FIG. 9, the inlet portion 21 of the fin of the first embodiment is increased in the installation angle to 40 degrees, and the fin is gradually thinned. Inlet portion 21 which is a fin of increasing thickness
In addition to changing to S, the arrangement angle of the outlet portion 22 is set to 40 degrees which is the same angle as the inlet portion 21S, so that flow separation can be more effectively prevented and the flow in the bench hole can be made more uniform. By increasing the area of the inlet opening 31 and improving the connection between the inlet portion 21S and the outlet portion 22 to reduce the inflow resistance, it is possible to further improve the blowing and cooling efficiency.

In the case of the floating caliper, the third embodiment has a higher pressure on the outer circumference, and therefore the thicker outlet portion 22 of the fins takes charge of the strength, and is particularly effective when increasing the number of fins. ..

The above-mentioned embodiments are given for the purpose of explanation, and the present invention is not limited to them, and the technique of the present invention which can be recognized by those skilled in the art from the description of the claims. Modifications and additions are possible as long as they do not conflict with the idea.

In the first embodiment, the position of the communication port is 0.28L to 0.39L (L is the length from the front end to the rear end of the fin 2). The example in which the angle between the line connecting the tip of the fin and the rear end of the fin and the radial direction and the radial direction is set to 50 degrees has been described, but the length of the fin, the width of the bench hole, the number of rotations of the rotor, etc. are required. Depending on the position between 0.1L and 0.7L,
Alternatively, the angle can be set within the range of 30 degrees to 70 degrees.

In the rotor size of the first embodiment, the allowable length of the communication port is 2 mm to 15 mm, and the desirable range is 4 mm to 7 mm. However, if the rotor size is large, the length is set accordingly. However, the length of the communication port is comprehensively determined from the viewpoint of the flow rate passing through, the blade action of the fin, and other factors, and is in the range of 0.1 L to 0.2 L with respect to the fin length L. You can set it to an appropriate length.

In the above-mentioned first embodiment, an example in which the build-up height of the direction changing portion of the inlet opening is 4 mm has been described. However, in view of manufacturing resistance such as inflow resistance, manufacturing failure, etc., in the rotor size of the first embodiment, Can be set to an appropriate thickness within 5 mm, and may be set to a height of 5 mm or more if the rotor size becomes large.

Although the height of the radiation fin is 1 mm in the first embodiment, it can be any height of 3 mm or less as long as the area of the bench hole is the same as that of the first embodiment. If the area of the bench hole is large, the height may be 30% or less of the height of the bench hole.

[Brief description of drawings]

FIG. 1 is a transverse sectional view taken along the line AA of FIG. 2 showing a brake disc rotor according to a first embodiment of the present invention.

FIG. 2 is a vertical cross-sectional view showing a brake disc rotor of the first embodiment.

FIG. 3 is a cross-sectional view showing the flow in the brake disc rotor of the first embodiment.

FIG. 4 is a cross-sectional view showing a radiation fin in a bench hole of the first embodiment.

FIG. 5 is a cross-sectional view showing the flow in the brake disc rotor of the first embodiment based on tracer particle processing data.

FIG. 6 is a partially cutaway perspective view showing a state where the brake disc rotor of the first embodiment is mounted on a vehicle.

FIG. 7 is a sectional view showing a state where the brake disc rotor of the first embodiment is attached to a wheel.

FIG. 8 is a sectional view showing the brake disc rotor and flow of the second embodiment.

FIG. 9 is a sectional view showing a brake disc rotor and a flow of a third embodiment.

FIG. 10 is a view showing a conventional brake disc rotor.
It is a cross-sectional view taken along line BB of FIG.

FIG. 11 is a vertical sectional view showing a conventional brake disc rotor.

FIG. 12 is a sectional view showing a flow in a conventional brake disc rotor by tracer particle processing data.

FIG. 13 is a sectional view showing a flow in a conventional brake disc rotor.

[Explanation of symbols]

 1 Brake Disc Rotor 2 Fin 4 Benchhole 5 Communication Port 7 Radiating Fin 11 Inner Side Sliding Plate 12 Outer Side Sliding Plate 21 Inlet Part 22 Outlet Part 31 Inlet Opening 32 Outlet Opening 41 Stagnation Area 42 Main Watershed 61 Earl Section 62 Direction Converter 71, 72, 73 Radiating fin

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takashi Shimazu, Nagakute-cho, Aichi-gun, Aichi Prefecture, Nagachoji, 1 at 41 Yokomichi Toyota Central Research Institute Co., Ltd. (72) Haruo Katagiri, Aichi-gun, Nagakute-machi, Aichi-gun 1 in 41 Central Road, Nagatoji (1) Inside Toyota Central Research Institute Co., Ltd. (72) Shigeru Sakamoto 1 Toyota-cho, Toyota City, Aichi Prefecture Toyota Motor Corporation (72) Hidetoshi Shimizu 1-cho, Toyota City, Aichi Prefecture In Toyota Motor Co., Ltd. (72) Inventor Akio Inatomi, 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (72) Inventor, Masashi Ishihara 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (72 ) Inventor Tohru Shinoda No. 1 Tenno, Takaoka Shinmachi, Toyota City, Aichi Prefecture Aisin Takaoka Co., Ltd.

Claims (4)

[Claims] 1. Disc-shaped sliding plates which are spaced apart from each other in the axial direction on the left and right sides, and are radial between the sliding plates, and at least the inner peripheral side portion is inclined at an angle equal to or smaller than an inflow angle of the flow. A plurality of partition walls arranged in a radial direction, a plurality of passages formed radially between the plurality of partition walls, and a plurality of inlet openings and outlet openings that communicate with the plurality of passages and are opened radially inward and outward. A brake disc rotor comprising: a plurality of partition walls; and a plurality of communication ports that communicate adjacent passages through the partition walls. 2. The brake disc rotor according to claim 1, wherein an outer peripheral side portion of the partition wall is inclined toward a wake after rotation. 3. The chamfered portion according to claim 1, wherein a thickness of a tip portion of an inner wall forming an inlet opening of the disc-shaped sliding plate on the inner side gradually decreases toward the tip, and a chamfered portion on the outer side is formed. The tip that forms the inlet opening of the disc-shaped sliding plate is made to project radially inward from the disc-shaped sliding plate on the inner side, and a protrusion that gradually increases in thickness toward the tip is formed. Brake disc rotor characterized by having done. 4. A small projection having a small width and a height substantially parallel to a partition wall, which is radial at least at an outer peripheral portion of an inner wall forming a passage of the outer and inner disk-shaped sliding plates. A brake disc rotor characterized in that a heat radiation fin composed of is formed.