JP3393657B2 - Brake disc rotor - Google Patents

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 for 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.
4 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. 16 showing the processing data by the styrene particle tracer method and the above. As shown in FIG. 17, which shows a sketch of the flow based on the flow, a flow that has flowed into the inlet opening I into the passage H 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 on the negative pressure surface side of the partition wall F forming the fin, and a wide stagnation Y is generated in the lower part of the partition wall in the passage H forming the bench hole. Therefore, the main flow region MS becomes very narrow, and a quasi-secondary flow SS is generated due to the collision with the upper surface of the partition wall, and the reverse flow RS from the outside is generated at the upper part of the outlet opening.
There was a problem that occurs.

As a result, in the conventional brake disc rotor, the pressure loss of the flow is large because the main flow area MS is narrowed, so that 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 various flows of the conventional brake disc rotor using an oil film observation photograph and an image processed by the tracer method, the present inventors have found that the pressure between the pressure surface and the negative pressure surface of the partition wall forming the fins. Focusing on the technical idea of the present invention that if the flow is formed by utilizing the difference and the separation at the inlet is prevented, the main flow area MS is narrowed, the stagnation area Y is narrowed and the main flow area MS is widened. did.

As a result of further research and development, the inventors of the present invention formed a communication port for pressure recovery in the partition wall to recover the pressure on the suction surface side, thereby removing the above-mentioned conventional separation of the inlet opening. Since the stagnation area Y of the bench hole is reduced and the pressure loss of the flow is reduced, the reduction of the heat transfer coefficient on the surface of the cooling air is reduced to improve the air blowing and cooling efficiency of the rotor and the cooling area. The present invention has been achieved which achieves the purpose of increasing the total heat dissipation in order to expand

[0007]

A brake disc rotor according to the present invention (a first invention according to claim 1) slides with disc-shaped sliding plates which are spaced apart in the axial direction and are arranged on the left and right sides. A plurality of partition walls radially arranged between the plates, a plurality of passages radially formed between the plurality of partition walls, and a plurality of inlet openings which are connected to the plurality of passages and open radially inward and outward. And the outlet opening and a plurality of partition walls at a position of 20% on the center side of the partition walls.
More than 10% and less than 20% of the partition wall in the radial outward direction
With the opening formed over the entire width direction with to separate in the radial direction over the length, it communicates a passage adjacent via the partition wall which is divided into an inlet portion and an outlet portion, before
It passes through a part of the flow along the wall on the pressure side of the entry port.
Those composed of a plurality of communication ports that Ru allowed to flow into stagnation region in the downstream side of the passage was.

[0008] Brake disc rotor of the present invention (second invention described in claim 2), in the first invention, the inlet
A shape in which the thickness of the partition wall on the center side gradually increases
It is formed in .

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 a tip end portion of an inner wall forming an inlet opening of the disc-shaped sliding plate on the inner side has a tip thickness. A chamfer that gradually decreases as it goes to, and the tip of the inlet opening of the disc-shaped sliding plate on the outer side projects 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.

The brake disc rotor of the present invention (the fourth invention according to claim 4) is the brake disc rotor according to the first invention, wherein at least the outer circumference of the inner wall forming the passages of the disk slide plates on the outer side and the inner side is radial. The heat radiation fins are formed by small protrusions having a small width and height.

[0011]

In the brake disc rotor according to the first aspect of the present invention having the above-described structure, a part of the flow flowing near the partition wall out of the flow flowing in from the inlet opening is located in a radial direction from the position of the center 20% of the partition wall.
In the outward direction, over the length of 10% or more and less than 20% of the partition wall
It is separated in the radial direction and passes through the communication port formed in the entire width direction.
By causing the stagnation region to flow into the stagnation region and forming the flow, the stagnation region due to the separation on the suction surface side is narrowed, the main flow region is widened, and the reverse flow at the outlet opening is suppressed.

In the brake disc rotor according to the second aspect of the present invention having the above structure , the tip of the partition wall on the center side of the inlet portion is gradually
Since it is formed in a shape with increasing thickness, the inlet opening
The flow from the mouth is shaped into a gradually increasing thickness.
Flow along the center end of the partition wall of the inlet part
Therefore, the flow that passes through the communication port and flows into the suction surface side of the lower part of the partition wall is effectively formed, and the stagnation area due to separation on the suction surface side is effectively narrowed to widen the main flow area and the outlet opening. This has the effect of suppressing backflow in the.

In the brake disc rotor of the third invention having the above-mentioned structure, the inner side sliding plate has the chamfered portion formed at the inner wall distal end thereof, and the outer side sliding plate has the protruding portion formed at the inner wall distal end thereof. This has the effect of smoothly changing the direction of the incoming flow at the inlet opening.

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

[0015]

According to the brake disc rotor of the first aspect of the present invention, which has the above-described operation, a part of the flow flowing near the partition wall is separated from the partition wall.
The partition wall is radially outward from the position of 20% on the center side.
A flow is formed by passing through a communication opening that is formed in the radial direction over a length of 10% or more and less than 20% and is formed over the entire width direction to flow into the stagnation region on the negative pressure surface side of the lower part of the partition wall. This narrows the stagnation area due to separation on the suction surface side, widens the main flow area in the passage, and suppresses the reverse flow at the outlet opening, reducing the pressure loss of the flow and reducing the heat on the surface of the cooling air. By reducing the decrease in the transfer rate, the effects of improving the air blowing / cooling efficiency of the rotor and increasing the total heat radiation amount in order to expand the cooling area are achieved.

In the brake disc rotor according to the second aspect of the present invention, which has the above-described operation, the flow introduced from the inlet opening gradually increases in thickness.
Inside the partition wall of the inlet portion formed in a shape that increases
Since it flows along the tip of the core side, the flow that passes through the communication port and flows into the suction surface side under the partition wall is effectively formed, and the stagnation area due to the separation on the suction surface side is effectively narrowed to reduce the main flow area. By increasing the width and suppressing the backflow at the outlet opening, the air blowing and cooling efficiency of the rotor is improved more effectively than in the first aspect of the invention, and the total amount of heat radiation is increased in order to expand the effective cooling area. Has the effect.

In the brake disc rotor according to the third aspect of the present invention, which has the above-described action, the direction of the flow flowing in by the chamfered portion and the projecting portion is smoothly changed to the radial direction 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 radiation area is increased by the small protrusions constituting the heat radiation fin, the total heat radiation amount is further increased.

[0019]

Embodiments of the present invention will now be described 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. 8 and 9. 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 9.

(Structure of the First Embodiment) A brake disc rotor 1 of the first embodiment has inner and outer sliding plates 11 arranged side by side in the axial direction of an axle (not shown).
And 12, a plurality of fins 2 forming a partition wall radially arranged between the sliding plates 11 and 12, and a sliding plate 11
And 12 and a plurality of openings 31 and 32 that are open inward and outward in the radial direction, and sliding plates 11 and 1
2, a plurality of bench holes 4 forming a passage formed by the partition wall 2 adjacent to each other, a communication port 5 formed in each fin 2 for communicating adjacent bench holes, and an inner wall tip portion of the inner side sliding plate. A rounded portion 61 that constitutes a chamfered portion is formed, and a direction changing portion 62 that constitutes a protrusion at the tip of the outer side sliding plate and the bench holes 4 of the inner side and outer side sliding plates are formed. The heat radiation fins 7 are arranged radially on the inner wall of the heat sink.

The outer side sliding plate 12 is formed integrally with the inner side sliding plate via a step portion 13 and a boss portion 14 having a fixing hole. Outer side sliding plate 1
2 and the sliding plate 11 on the inner side linearly increase in thickness outwardly 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 and inner sliding plates.
It is integrally molded radially in the range of mm.

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 1.
Since the fins 2 are 4 mm in height and 9 mm in height at the outlet opening 32, and the fins 2 are radially formed, the cross-sectional area thereof is substantially constant.

As shown in FIG. 3, the communication port 5 has a length of 6 mm, and the fin 2 is divided into an inlet portion 21 and an outlet portion 22. The tip end 21E of the inlet portion 21F of the fin immediately preceding in the rotational direction 21E.
And the tip of the communication port 5 (the rear end 21 of the inlet portion 21 of the fin 2
R) and the neutral line N of the bench hole 4 are arranged at an angle of 50 degrees, that is, 0.24L to 0.39L from the tip of the inner peripheral side of the fin 2 (fin 2 has a total length of 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),
As shown in FIG. 4, the fin length on the inner circumference side is short, and the flow having an inflow angle of 40 to 50 degrees directly passes through the communication port, and on the suction surface of the fin 22 on the outer circumference side of the adjacent downstream bench hole. Since the separation and the stagnation area Y occur, the inflow loss at the inlet portion increases, the flow rate decreases, and the cooling performance deteriorates. On the contrary, when 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 as shown in FIG. 5, but the pressure difference is caused by the spreading loss of the bench hole 4. Since this decreases, the pressure recovery effect becomes smaller, separation occurs at the inlet, a stagnation region is formed on the inner peripheral fin negative pressure surface side, and the flow rate and cooling performance deteriorate. At 0.5 L or more, since the length of the fins on the outer peripheral side becomes short, the energy difference inside and outside the hole that determines the ventilation capacity of the bench hole tends to be small, and the passing flow rate tends to decrease. From the balance with the pressure recovery effect (flow rate increase effect) due to the above, 0.7 L was set as the limit. When a good cooling effect is required, it depends on the arrangement interval of the fins and the number of revolutions, but is within a desirable range of 0.
It is recommended to use 2L to 0.5L. The first embodiment is 0.
It is set to 24L to 0.39L.

The allowable length of the communication port 5 is 2 mm to 15 mm, but if the length is short, the effect as a pressure recovery port is reduced, and if the length is long, the length of the fin is shortened, so that the effect as a blade (blower) is obtained. 4mm as the optimum length range
It will be ~ 6mm. In the first embodiment, considering the manufacturing point of view, the thickness is set to 6 mm.

As shown in FIG. 2, the radius portion 61 at the tip of the inner wall of the sliding plate 11 on the inner side has chamfered corners of 45 degrees, 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 radially inward 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 4 mm raised shape. 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 6, the radiating fins 7 have long radiating fins 71 and 72 radially integrally formed on the outer peripheral side near the fins 2, respectively, and are short in the central portion of the bench hole 4. Radiating fins 73 and 74 are integrally formed in a radial pattern, and the heat radiation effect is enhanced without increasing the resistance of the flow in the bench hole 4.

(Operation of the First Embodiment) As shown in FIG. 2, the brake disc rotor of the first embodiment having the above-described structure has the rounded portion 61 and the direction changing portion 62 in the inlet opening 31.
The flow in the axial direction is smoothly converted into the flow in the radial direction by the cooperation with the air flow, and the flow is made to flow into the bench hole 4 at an inflow angle of 40 to 50 degrees as shown in FIG.
A part of the flow along the wall surface on the pressure surface side of 1 passes through the communication port 5 and flows into the next bench hole 4, thereby suppressing the occurrence of separation on the suction surface side of the fin 2 and suppressing the stagnation region 4
1 is reduced to form a wide main watershed 42. This is
It is also clear from the tracer particle processing data by the styrene particle tracer method that traces the floating styrene particles following the flow shown in FIG. 7 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 result, and is suitable for mainstream observation. ing.

(Effect of First Embodiment) In the brake disc rotor of the first embodiment having the above-described operation, as shown in FIG. 3, the generation of the stagnation region 41 due to the separation of the fin 2 on the suction surface side is suppressed, Since the wide main flow region 42 is formed in the most desirable form by suppressing the generation of the conventional quasi-secondary flow, the reverse flow at the conventional outlet opening can also be suppressed, the pressure loss of the flow is minimized, and the heat of the surface of the cooling wind is minimized. By reducing the decrease in the transmissibility, the blowing and cooling efficiency of the rotor 1 is improved, and the total amount of heat radiation is increased in order to expand the effective cooling area.

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, increasing the flow velocity is important for improving the cooling capacity. In other words, in the first embodiment, since the passage resistance can be reduced and the flow velocity can be increased, the heat radiation amount and the cooling capability are improved.

Since the cooling capacity is proportional to the heat radiation area,
It is important to increase the heat dissipation area.
Since it was possible to effectively secure the heat dissipation area within the limited heat dissipation area and to widen the area of high heat dissipation efficiency, the cooling capacity could 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, it is possible to effectively suppress the separation of the flow generated near the tip of the inner wall of the inner side sliding plate 11.

Further, in the brake disc rotor 1 of the first embodiment, as shown in FIGS. 3 and 6, four small heat radiation fins 71 to 74 are provided on the inner wall on the outer peripheral side of the inner side and outer side sliding plates. Since it is formed, there is an effect that the heat radiation effect is effectively enhanced without increasing the resistance of the flow in the bench hole 4.

In the brake disc rotor 1 of the first embodiment, as shown in FIG. 1, the fins 2 are radially formed and are symmetrically arranged, so that the brakes for the left and right wheels of the automobile are constituted by the same rotor. Because of the design,
A single production line is sufficient, and it has the effect of significantly reducing costs and management.

Further, in the first embodiment, since the length of the communication port 5 is set to the optimum 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 efficiently suppressed. There is an effect that can be done.

Further, in the first embodiment, the communication port 5
Is the optimum position of 0.24L (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 peeling can be most effectively suppressed.

(Second Embodiment) In the brake disc rotor of the second embodiment, from the viewpoint of focusing on improving the flow in the bench hole 4, sacrificing the merit of the left-right symmetric type of the first embodiment, In order to more effectively suppress the separation of the flow on the suction surface side of the fin 2 and the occurrence of stagnation, the shapes of the fin and the communication port are changed.

As shown in FIG. 10, the suction surface side tips 21N and 2 of the inlet portion 21 and the outlet portion 22 of the fin 2 are formed.
The thickness gradually increases from 2N, and the flow becomes the suction surface 21 of the fin 2.
N and 22N so as to flow along the streamlined shape, and the rear end 21R of the inlet portion 21 of the fin 2 forming the communication port 5 is formed into an S-shape so that the flow along the rear end 21R is formed by the fin 2 Is arranged so as to be directed along the negative pressure surface 22N of the outlet portion 22 of the above, 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.
The length is about 7 mm.

In the brake disc rotor of the second embodiment having the above-mentioned structure, as shown in FIG. 10, the flow that has flowed into the bench hole 4 is along the suction surface side tip 21N of the inlet portion 21 of the fin 2 having a streamlined shape. Flow is further suppressed as compared with the first embodiment, and the flow that has passed 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 outlet portion 22. Because of the streamlined shape of the negative pressure surface 22N, the flow smoothly flows along the negative pressure surface 22N of the outlet portion 22 of the fin 2, so that the occurrence of separation at the lower portion of the negative pressure surface of the outlet portion 22 of the fin 2 is prevented compared to the first embodiment. This has the effect of more effectively suppressing stagnation.

(Third Embodiment) In the brake disc rotor of the third embodiment, a plurality of communication ports 51 and 52 are formed in the fin as shown in FIG.
The stagnation region 41 is formed by three parts, namely, the first part 23, the central part 23, and the outlet part 22, and is separated by peeling after passing through the first communication port 51.
The second communication port 52 is formed at a position where does not grow, the flow is formed by utilizing the pressure difference, and the separation is prevented, thereby suppressing the expansion of the stagnation region 41 and forming a wider main flow region 42. , Which further improves the blowing and cooling efficiency.

(Fourth Embodiment) As shown in FIG. 10, the brake disc rotor of the fourth embodiment is such that the inlet portion 21 of the fin of the first embodiment is changed to an inlet portion 21S which is a thin fin. By increasing the area of the inlet opening 31 and decreasing the inflow resistance, the blowing and cooling efficiency is further improved.

In the fourth embodiment, in the case of a floating caliper, the pressure is higher at the outer periphery, 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. .

(Fifth Embodiment) As shown in FIG. 11, the brake disc rotor of the fifth embodiment has a first fin 2A having a communication port 5 and an inlet portion 21 and an outlet portion 22, and a communication port. Of the first bench hole 44 and the second bench 2B, in which the tips on the inner peripheral side are formed alternately and the short second fins 2B located closer to the outer periphery than the tips of the first fins are not formed.
The so-called staggered fins that form the bench hole 45 of the fin are formed. Since the number of fins is increased to increase the heat radiation amount and the fin arrangement pitch on the circumference is narrowed, the fin inlet portion 21 The present invention can be applied to an extremely short brake disc or a brake disc rotor in which the communication port cannot be installed.

The above-mentioned embodiments are given as examples 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 go against the idea.

In the first embodiment, the position of the communication port is 0.24L to 0.39L (L is the length from the front end to the rear end of the fin 2). An example was described in which the angle between the line connecting the tip of the fin and the rear end of the fin inlet and the neutral line of the bench hole was set to 50 degrees, but the length of the fin, the width of the bench hole, and the rotor Rotation speed or other position as required between 0.1L and 0.7L, or at the above angle from 30 degrees to 7
It can be set within the range of 0 degree.

The allowable length of the communication port is 2 mm to 15 mm in the rotor size of the first embodiment, and the desirable range is 4 mm to 6 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 viewpoints of the flow rate passing through, the blade action of the fins, etc., and is in the range of 0.1L to 0.2L with respect to the fin length L. It may be set to an appropriate length in.

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, but the rotor size of the first embodiment is considered from the viewpoint of inflow resistance, poor manufacturing and other manufacturing. Can be set to an appropriate thickness of 5 mm or less, and may be set to a height of 5 mm or more as the rotor size increases.

Although the height of the radiation fin is 1 mm in the first embodiment, it can be set to any height of 3 mm or less if 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 transverse cross-sectional view showing the flow in the brake disc rotor of the first embodiment.

FIG. 4 is a cross-sectional view showing a flow in an example in which a communication port is formed at a position of 70 degrees.

FIG. 5 is a cross-sectional view showing a flow in an example in which a communication port is formed at a position of 30 degrees.

FIG. 6 is a cross-sectional view showing a heat radiation fin in a bench hole of the first embodiment.

FIG. 7 is a cross-sectional view showing the flow in the brake disc rotor of the first embodiment based on tracer particle processing data.

FIG. 8 is a partially cutaway perspective view showing a state in which the brake disc rotor of the first embodiment is mounted on a vehicle.

FIG. 9 is a sectional view showing a state in which the brake disc rotor of the first embodiment is attached to a wheel.

FIG. 10 is a sectional view showing the brake disc rotor and flow of the second embodiment.

FIG. 11 is a sectional view showing the brake disc rotor and flow of the third embodiment.

FIG. 12 is a sectional view showing a brake disc rotor and a flow of a fourth embodiment.

FIG. 13 is a sectional view showing the brake disc rotor and flow of the fifth embodiment.

FIG. 14 shows a conventional brake disc rotor.
It is a cross-sectional view taken along the line BB of FIG.

FIG. 15 is a vertical sectional view showing a conventional brake disc rotor.

FIG. 16 is a sectional view showing a flow in a conventional brake disc rotor by tracer particle processing data.

FIG. 17 is a sectional view showing a flow in a conventional brake disc rotor.

[Explanation of symbols]

1 brake disc rotor Two fins 4 bench hall 5 communication ports 7 radiating fins 11 Inner side sliding plate 12 Outer side sliding plate 21 entrance 22 Exit part 31 entrance opening 32 Exit opening 41 Stagnation area 42 Main watershed 61 R 62 Direction changer 71, 72, 73, 74 Radiating fin

Continuation of the front page (72) Takashi Shimazu, Takachi, Aichi-gun, Nagakute-cho, Aichi-gun, Nagatogi, Yoko 41, No. 1 at Toyota Central Research Institute, Inc. (72) Inventor Haruro Katagiri, Aichi-gun, Nagakute-cho, Aichi, Japan, 41 Address 1 Toyota Central Research Institute Co., Ltd. (72) Inventor Akio Inatomi 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Automobile Co., Ltd. (72) Inventor Masafumi Ishihara 1 Toyota Town, Aichi Prefecture Toyota Motor Co., Ltd. (72) Inventor Masayoshi Katagiri 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (72) Inventor Shigeru Sakamoto 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (72) Inventor, Tohru Shinoda Aisin Takaoka Co., Ltd., Tenno 1 Takaoka-Shinmachi, Toyota City, Aichi Prefecture (56) References Showa 53-106581 (JP, U) Showa 55-89832 (JP, U) Showa 58-102840 (JP) , U) Actually open 63-146237 (JP, U) Actually open 59-51224 (JP U) (58) investigated the field (Int.Cl. ^7, DB name) F16D 65/12

Claims (4)

(57) [Claims] 1. A disk-shaped sliding plate which is spaced apart in the axle direction on the left and right sides, a plurality of partition walls radially arranged between the sliding plates, and radially formed between the plurality of partition walls. A plurality of passages, a plurality of inlet openings and outlet openings that communicate with the plurality of passages and open inward and outward in the radial direction, and a plurality of partition walls in the radial direction outside the position of 20% on the center side of the partition walls.
On the other hand, the partition walls are separated from each other in the semi-diametrical direction over a length of 10% or more and less than 20%, and openings are formed over the entire width direction, with the partition wall divided into an inlet portion and an outlet portion. To connect the adjacent passages ,
Allow a part of the flow along the wall on the pressure side to pass and to let the flow on the downstream side.
A brake disc rotor, characterized in that it consists of a plurality of communication ports that Ru allowed to flow into a stagnation area within the road. 2. The thickness according to claim 1, wherein the tip of the partition wall on the center side of the inlet portion gradually increases in thickness.
The brake disc rotor is characterized in that it is formed into a shape . 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 protruding portion whose thickness gradually increases toward the tip is formed. Brake disc rotor characterized by doing. 4. The heat dissipating fin according to claim 1, wherein the heat dissipating fins are formed by small protrusions having a small radial width and height at least at the outer periphery of the inner wall forming the passages of the outer and inner disc-shaped sliding plates. Brake disc rotor characterized by doing.