JP2012042014A - Brake disc rotor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase gross heat radiation by expanding a cooling area while enhancing ventilation cooling efficiency in a bench hole.SOLUTION: The rotor includes a series of divided partition walls 2 which are radially arranged between a slide plates 11 so as to be inclined in a direction opposite to a rotating direction as going radially outward. A plurality of sets of partition walls 2 are formed on a circumference of the slide plate 11 with an angular phase difference of being separated in the direction opposite to the rotating direction. A radius of an envelope circle in which radially outward ends of the divided partition wall 2 situated radially inward are connected to each other, is formed so as to be substantially identical to a radius of an envelope circle in which radially inward ends of the divided partition wall 2 situated radially outward are connected to each other. An angle formed by a longitudinal center line of the divided partition wall 2 arranged radially inward with a radial direction of the slide plate 11 is made larger than an angle formed by a longitudinal center line of the divided partition wall 2 of the slide plate 11 arranged radially outward with the radial direction of the slide plate 11. Each of the divided partition walls 2 is formed so as to be recessed with respect to the rotating direction of the slide plate 11.

Description

  The present invention relates to a brake disc rotor of a disc brake device used in a vehicle or the like.

  As shown in FIGS. 7 and 8, the conventional brake disk rotor forms a plurality of simple radial partition walls BH between disc-shaped sliding plates OD and ID that are spaced apart in the axle direction. An inlet opening IT, an outlet opening OL, and a radial passage VH are formed between the partition walls.

In addition, various improvements in air permeability as shown in Patent Document 1 have been made.

JP-A-5-346126

  In the conventional brake disc rotor, the flow that flows into the passage VH with the rotation of the disc-shaped sliding plate causes separation in the thickness direction of the partition wall BH on the suction surface side of the partition wall BH constituting the fin, A large stagnation SL is generated in the lower part of the partition wall BH in the passage VH, which is a flow path, so that there is a problem that the main flow area MF becomes very narrow and the ventilation is not good.

  Further, in Patent Document 1, as a means for solving this problem, the partition wall is inclined with respect to the radial direction at an angle equal to or smaller than the inflow angle Ψ of the flow that flows when the sliding plate rotates, and the middle of the partition wall is divided. It has been proposed to improve ventilation by providing a gap and allowing a part of the flow to flow toward the suction side.

  However, in the method of Patent Document 1, there is a problem that the effective length of the partition as a blower blade is shortened and the improvement degree of the blowing performance is small because the middle of the partition is divided and a gap is opened.

  The brake disc rotor of the present invention has been made in view of these problems, and the first invention described in claim 1 includes a disc-shaped sliding plate and a double-sliding plate that are spaced apart in the axle direction. It consists of a series of partition walls that radiate between the moving plates, are arranged to incline in the direction opposite to the rotation direction of the sliding plate toward the outer side in the radial direction, and are divided into a plurality of divisions. A plurality of divided partition walls are formed on the circumference of the sliding plate to form a plurality of inlet openings and outlet openings that open from the inside in the radial direction to the outside, and a series of the plurality of divided openings. The divided partition wall is separated from the divided partition wall disposed radially inward by an angular phase difference in the direction opposite to the rotation direction of the sliding plate. A plurality of first divided spaces disposed on the circumference of the sliding plate. Enveloping circle obtained by connecting between the ends of the radially outer are those that are configured to conform substantially with enveloping circle obtained by connecting between the radially inner end of the second split septum.

  According to a second aspect of the present invention, in the first aspect, the series of the divided partition walls divided into a plurality is the center in the longitudinal direction of the divided partition walls disposed radially inward of the disk-shaped sliding plate. The angle formed by the line with respect to the radial direction of the disk-shaped sliding plate is the longitudinal center line of the partition wall arranged radially outward with respect to the radial direction of the disk-shaped sliding plate. It is configured to be formed larger than the angle.

According to a third aspect of the present invention, in the second aspect, the series of divided partition walls divided into a plurality are formed so as to be concave with respect to the rotation direction of the disc-shaped sliding plate. It is configured.

  The brake disk rotor according to the first aspect of the present invention having the above-described configuration is configured so that the divided partition walls arranged radially between the disc-shaped sliding plates arranged apart from each other in the axle direction move toward the outer side in the radial direction. It is arranged to be inclined in the direction opposite to the rotation direction of the moving plate, and the first divided partition wall is directed in the flow inflow direction, so that an effect of facilitating the flow of the fluid is obtained.

  Furthermore, the flow taken in from the first divided partition is captured by the second divided partition located radially outward of the first divided partition. The second divided partition wall is configured to be spaced apart from the first divided partition wall with an angular phase difference in the direction opposite to the rotation direction of the sliding plate. The flow along the one partition wall is separated from the first partition wall so as to wrap around the end of the first partition wall in the radial direction, and is captured by the second partition wall. The contact time can be extended, and frictional heat between the brake disc rotor and the brake pad can be effectively taken into this fluid through the partition wall during braking, and the generated frictional heat can be effectively released. There is an effect.

  In addition, the envelope circle connecting the radially outer ends of the first divided partition walls, which are plural sets on the circumference of the disk-shaped sliding plate, connects the radially inner ends of the second partitioned partition walls. Since it is almost coincident with the envelope circle, a sufficient effective length can be obtained as a blower blade of the partition wall, and sufficient ventilation performance can be secured, so by dividing the partition wall and leaving a space on the partition line, There exists an effect that there is no problem like patent document 1 that effective length becomes short and there is little improvement degree of ventilation performance.

  Furthermore, as described above, the second divided partition is arranged to be spaced apart with an angular phase difference in the direction opposite to the rotation direction of the sliding plate with respect to the first divided partition. Of the flow taken in from the first partition wall by the rotation of the sliding plate, the flow on the rear side in the rotation direction of the first partition wall is partly divided by the radially inner end of the second partition wall. There exists an effect that it can merge with the flow of the front of a two-partition partition effectively.

  The brake disc rotor according to the second invention having the above-described configuration is such that the angle formed by the longitudinal center line of the first divided partition with respect to the radial direction of the disk-shaped sliding plate is such that the second divided partition is the disk-shaped slide. Since it is formed to be larger than the angle formed with respect to the radial direction of the moving plate, it is difficult to stagnate the flow on the back of the first divided partition, which is shorter than the partition without partition. In addition, the flow that is separated from the first divided partition and is captured by the second divided partition so that the flow wraps around the end at the radially outer end of the first divided partition is not disturbed. It is effective that it is taken in more smoothly.

  In addition, the flow taken in from the first partition wall draws a concave shape (U shape) with respect to the rotation direction of the disk-shaped sliding plate, and the stagnation of the flow generated on the back surface of the partition wall functioning as a rotary blade. Since it is in a state of overhanging the area, there is an effect that it becomes difficult to stagnate.

  In addition, the flow separated from the first divided partition wall so as to wrap around the end portion of the first divided partition wall in the radial direction and trapped in the second divided partition wall is directed radially outward. Therefore, the flow is smoothly rectified by the second divided partition wall without disturbing the flow.

  Furthermore, the flow on the back surface in the rotational direction of the first partition wall is effectively diverted by the radially inner end of the second partition wall as this angle gradually decreases as it goes radially outward. After that, there is an effect that a part thereof can be effectively joined to the flow in front of the second divided partition wall.

In the brake disc rotor according to the third aspect of the present invention having the above-described configuration, each partition wall is formed so as to be concave with respect to the rotation direction of the disc-shaped sliding plate, so that the flat partition wall rotates. The stagnation area of the flow behind the bulkhead can sometimes be concave and overhang, making it difficult to stagnate due to the flow behind the bulkhead functioning as a rotor blade, and wrap around the end of the outlet opening to the next bench hole. There is an effect that it is possible to effectively suppress the reverse flow toward the flow.

The cross-sectional view which follows the AA line of the brake disc rotor which shows the Example of this invention A longitudinal sectional view showing a brake disc rotor of an embodiment Cross-sectional view showing a part of the brake disc rotor of the embodiment Cross-sectional view showing the flow in the brake disc rotor of the embodiment The perspective view which abbreviate | omitted one part which shows the state with which the brake disc rotor of the Example was mounted in the vehicle Sectional drawing which shows the state with which the brake disc rotor of the Example was attached to the vehicle Cross-sectional view taken along line B-B in FIG. 8 showing a conventional brake disc rotor A longitudinal sectional view showing a conventional brake disc rotor Sectional view showing the flow of a conventional brake disc rotor Conceptual diagram showing the flow state when a cylindrical obstacle is placed in a part of the steady flow

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  FIG. 5 shows an automobile to which the present invention is applied as viewed from below in a lifted-up state. The frictional heat generated by braking is cooled by introducing the air sucked from the air intake IL of the dust shield DS arranged inside each wheel DW into the bench hole of the rotor. This will be described in detail.

  The brake disc rotor 1 according to the embodiment has a disc-like inner and outer sliding plates 11 and 12 disposed in the axial direction of the axle AS shown in FIG. A plurality of fins constituting a series of divided partition walls arranged radially in the radial direction of the disk, a plurality of openings 31 and 32 opened radially inward and outward between the sliding plates 11 and 12, It consists of a plurality of bench holes 4 constituting a passage formed by the sliding plates 11 and 12 and the adjacent fins 2 and a communication port 5 formed in each fin 2 and connecting the adjacent bench holes.

  As shown in FIG. 2, the sliding plate 12 on the vehicle outer side is integrally formed with a mounting plate 14 having a fastening hole through a step portion 13 together with the sliding plate 11 on the vehicle inner side.

  The fins 2 have a thickness of 5 mm and are integrally formed radially between the outer and inner sliding plates in a radius range of 120 mm to 190 mm. That is, as shown in FIG. 3, the air inlet portion 21 corresponding to the inner peripheral side portion is formed with an inclination of θ1 degree with respect to a straight line C connecting the tip 21E and the center of the disc (not shown). The intermediate portion 22 is formed with an inclination of θ2 degrees smaller than the angle θ1 of the inlet portion 21 with respect to the straight line connecting the tip 22E and the center of the disc, and the outlet portion 23 corresponding to the outer peripheral portion. Is inclined at θ3 degrees, which is smaller than the angle θ2 of the intermediate portion 22, with respect to a straight line connecting the tip 23E and the center of the disc.

  In the embodiment, θ1 is set to 50 degrees, θ2 is set to 20 degrees, and θ3 is set to 5 degrees. However, the arrangement angles of the inlet portion 21, the intermediate portion 22, and the outlet portion 23 are set in the rotor. The inflow angle should be determined according to the inflow angle of the flow, and the inflow angle varies depending on the rotational speed of the rotor. In general, for an automobile, the arrangement angle of the inlet portion 21 is preferably in the range of 30 to 70 degrees. Therefore, it is preferable to set the angle according to that. The arrangement angle of the outlet portion 23 is set within a range of 0 degrees to 15 degrees so that the action as a blower blade on the pressure surface side becomes more effective, and the arrangement angle of the intermediate section 22 is efficient without stagnation of the flow. It is preferable to set an intermediate angle between the inlet portion 21 and the outlet portion 23 in order to allow the flow to flow.

  Each fin 21, 22, 23 is formed in a concave shape having a radius of 100 mm with respect to the rotation direction of the brake disc rotor. Further, the radially outer ends 21T and 22T of the fins 21 and 22 are formed in a semicircular shape. In addition to the reason that the semicircular shape of the fins 21 and 22 is easier to manufacture, the cylindrical shape is obtained when a cylindrical obstacle is placed on a part of the steady flow as is apparent from FIG. Focusing on the fact that the flow can be guided to a region that does not reach when there is no obstacle with the formation of the flow PF that wraps around, the flow around the end portions 21T and 22T is guided to the fins 22 and 23 without stagnation. It is.

  The envelope circle connecting the radially outer ends 21T of the inlet portion 21 and the envelope circle connecting the radially inner ends 22E of the intermediate portion 22 are formed with substantially the same dimensions. Further, by forming the radii of the envelope circles 22T and 23E in the same manner, it becomes a three-stage fin structure formed so that the action as the blowing blade on the pressure surface side of the intermediate portion 22 and the outlet portion 23 becomes more effective. ing.

  The flow that flows so as to wind the end portion 21T radially outward of the fin 21 smoothly flows along the fin 22 that is radially outward, minimizing the stagnation generated in the gap between the partition walls 21T and 22E, A part of the flow on the back surface of the fin 21 can join the flow on the front surface of the fin 22 through the gap between the partition walls. The gap between the partition walls is set to 6 mm, but 4 mm to 8 mm is preferable for obtaining an effect without obstructing the air flow in the bench hole. The gap between the partition walls of the next fins 22 and 23 has the same structure, and the same effect can be obtained.

  In this embodiment, the lengths of the fins 21, 22, and 23 in the radial direction are set to be substantially the same. Accordingly, since the fin 21 has a large angle with the center of the disk, its actual length is the longest, and the flow can be taken in efficiently.

  The above-described embodiments have been illustrated for the purpose of explanation, and the present invention is not limited to them. Modifications and modifications are possible as long as they do not contradict the technical idea of the present invention that can be recognized by those skilled in the art from the description of the scope of claims. Addition is possible.

  The present invention is not limited to the brake disk rotor, but can be applied to industrial equipment having a function as a blower.

DESCRIPTION OF SYMBOLS 1 Brake disc rotor 2 Fin 4 Bench hole 5 Communication port 11 Inner side sliding plate 12 Outer side sliding plate 21 Inlet part fin 22 Middle part fin 23 Outlet part fin 31 Inlet opening 32 Outlet opening 41 Stagnation area 42 Main flow area

  The present invention relates to a brake disc rotor of a disc brake device used in a vehicle or the like.

  As shown in FIGS. 7 and 8, the conventional brake disk rotor forms a plurality of simple radial partition walls BH between disc-shaped sliding plates OD and ID that are spaced apart in the axle direction. An inlet opening IT, an outlet opening OL, and a radial passage VH are formed between the partition walls.

In addition, various improvements in air permeability as shown in Patent Document 1 have been made.

JP-A-5-346126

  In the conventional brake disc rotor, the flow that flows into the passage VH with the rotation of the disc-shaped sliding plate causes separation in the thickness direction of the partition wall BH on the suction surface side of the partition wall BH constituting the fin, A large stagnation SL is generated in the lower part of the partition wall BH in the passage VH, which is a flow path, so that there is a problem that the main flow area MF becomes very narrow and the ventilation is not good.

  Further, in Patent Document 1, as a means for solving this problem, the partition wall is inclined with respect to the radial direction at an angle equal to or smaller than the inflow angle Ψ of the flow that flows when the sliding plate rotates, and the middle of the partition wall is divided. It has been proposed to improve ventilation by providing a gap and allowing a part of the flow to flow toward the suction side.

  However, in the method of Patent Document 1, there is a problem that the effective length of the partition as a blower blade is shortened and the improvement degree of the blowing performance is small because the middle of the partition is divided and a gap is opened.

The brake disc rotor of the present invention has been made in view of these problems, and the present invention according to claim 1 is directed to a disc-shaped sliding plate that is spaced apart in the axle direction, It consists of a series of partition walls that radiate between the plates and are inclined in the direction opposite to the rotation direction of the sliding plate toward the outer side in the radial direction. A plurality of sets of partition walls are formed on the circumference of the sliding plate to form a plurality of inlet openings and outlet openings that open from the inside in the radial direction to the outside, and a series of divisions divided into the plurality of divisions. The partition wall is arranged such that the partition wall disposed outside the radial method with respect to the partition wall disposed inward in the radial direction is spaced apart with an angular phase difference in the direction opposite to the rotation direction of the sliding plate. A plurality of first partition walls provided on the circumference of the sliding plate Enveloping circle obtained by connecting between the ends of the radially outwardly is one that is configured to conform substantially with enveloping circle obtained by connecting between the radially inner end of the second split septum.

The series of split barrier ribs divided into Oite the plurality to the present invention, the longitudinal center line the disc-shaped sliding radially inwardly disposed a split septum of the disc-shaped slide plate The angle formed with respect to the radial direction of the plate is formed so that the longitudinal center line of the partition wall disposed radially outward is larger than the angle formed with respect to the radial direction of the disk-shaped sliding plate. It is configured.

Furthermore, the series of divided partition walls divided into a plurality are configured so as to be concave with respect to the rotational direction of the disc-shaped sliding plate.

The brake disc rotor according to the present invention having the above-described configuration is configured such that the divided partition walls radially disposed between the disk-shaped sliding plates spaced apart in the axle direction slide in the radial direction. It is arranged so as to be inclined in the direction opposite to the rotation direction of the plate, and the first divided partition wall is directed in the flow inflow direction, so that an effect of facilitating the flow of the fluid is obtained.

  Furthermore, the flow taken in from the first divided partition is captured by the second divided partition located radially outward of the first divided partition. The second divided partition wall is configured to be spaced apart from the first divided partition wall with an angular phase difference in the direction opposite to the rotation direction of the sliding plate. The flow along the one partition wall is separated from the first partition wall so as to wrap around the end of the first partition wall in the radial direction, and is captured by the second partition wall. The contact time can be extended, and frictional heat between the brake disc rotor and the brake pad can be effectively taken into this fluid through the partition wall during braking, and the generated frictional heat can be effectively released. There is an effect.

  In addition, the envelope circle connecting the radially outer ends of the first divided partition walls, which are plural sets on the circumference of the disk-shaped sliding plate, connects the radially inner ends of the second partitioned partition walls. Since it is almost coincident with the envelope circle, a sufficient effective length can be obtained as a blower blade of the partition wall, and sufficient ventilation performance can be secured, so by dividing the partition wall and leaving a space on the partition line, There exists an effect that there is no problem like patent document 1 that effective length becomes short and there is little improvement degree of ventilation performance.

  Furthermore, as described above, the second divided partition is arranged to be spaced apart with an angular phase difference in the direction opposite to the rotation direction of the sliding plate with respect to the first divided partition. Of the flow taken in from the first partition wall by the rotation of the sliding plate, the flow on the rear side in the rotation direction of the first partition wall is partly divided by the radially inner end of the second partition wall. There exists an effect that it can merge with the flow of the front of a two-partition partition effectively.

The brake disk rotor according to the present invention having the above-described configuration is such that the angle formed by the longitudinal center line of the first divided partition with respect to the radial direction of the disk-shaped sliding plate is such that the second divided partition is the disk-shaped sliding. Since it is formed larger than the angle formed with respect to the radial direction of the plate, it is difficult to stagnate the flow on the back of the first divided partition formed in a shorter length in the longitudinal direction by dividing compared to the partition without partition, In addition, the flow separated from the first divided partition so that the flow wraps around the end at the radially outer end of the first divided partition is captured by the second divided partition without being disturbed by the second divided partition. There is an effect that it is captured smoothly.

  In addition, the flow taken in from the first partition wall draws a concave shape (U shape) with respect to the rotation direction of the disk-shaped sliding plate, and the stagnation of the flow generated on the back surface of the partition wall functioning as a rotary blade. Since it is in a state of overhanging the area, there is an effect that it becomes difficult to stagnate.

Further , the flow that is separated from the first divided partition wall so as to wrap around the end portion of the first divided partition wall in the radial direction and that is captured by the second divided partition wall is directed radially outward. Therefore, the flow is smoothly rectified by the second divided partition wall without disturbing the flow.

In addition , the flow on the rear side in the rotation direction of the first divided partition wall is effectively diverted by the radially inner end of the second divided partition wall as this angle gradually decreases as it goes radially outward. After that, there is an effect that a part thereof can be effectively joined to the flow in front of the second divided partition wall.

The brake disk rotor according to the present invention having the above-described configuration is formed so that each divided partition is concave with respect to the rotation direction of the disc-shaped sliding plate. The stagnation area on the back of the partition wall that can be formed is a concave bulge, making it less difficult to stagnate due to the flow on the back of the partition wall that functions as a rotor blade. There is an effect that it is possible to effectively suppress the reverse flow toward the flow.

The cross-sectional view which follows the AA line of the brake disc rotor which shows the Example of this invention A longitudinal sectional view showing a brake disc rotor of an embodiment Cross-sectional view showing a part of the brake disc rotor of the embodiment Cross-sectional view showing the flow in the brake disc rotor of the embodiment The perspective view which abbreviate | omitted one part which shows the state with which the brake disc rotor of the Example was mounted in the vehicle Sectional drawing which shows the state with which the brake disc rotor of the Example was attached to the vehicle Cross-sectional view taken along line B-B in FIG. 8 showing a conventional brake disc rotor A longitudinal sectional view showing a conventional brake disc rotor Sectional view showing the flow of a conventional brake disc rotor Conceptual diagram showing the flow state when a cylindrical obstacle is placed in a part of the steady flow

Hereinafter, embodiments of the present invention will be described with reference to FIGS.

FIG. 5 shows an automobile to which the present invention is applied as viewed from below in a lifted-up state. 1 to FIG. 6 is used to cool the frictional heat generated by braking by introducing the air sucked from the air intake IL of the dust shield DS disposed inside each wheel DW into the bench hole of the brake disc rotor . The details will be described.

The brake disc rotor 1 according to the embodiment has a disc-like inner and outer sliding plates 11 and 12 disposed in the axial direction of the axle AS shown in FIG. A plurality of fins constituting a series of divided partition walls arranged radially in the radial direction of the brake disk rotor , and a plurality of openings 31 and 32 opened radially inward and outward between the sliding plates 11 and 12 And a plurality of bench holes 4 constituting a passage formed by the sliding plates 11 and 12 and the adjacent fins 2, and a communication port 5 formed in each fin 2 and connecting the adjacent bench holes.

  As shown in FIG. 2, the sliding plate 12 on the vehicle outer side is integrally formed with a mounting plate 14 having a fastening hole through a step portion 13 together with the sliding plate 11 on the vehicle inner side.

The fins 2 have a thickness of 5 mm and are integrally formed radially between the outer and inner sliding plates in a radius range of 120 mm to 190 mm. That is, as shown in FIG. 3, the air inlet portion 21 corresponding to the inner peripheral side portion is formed to be inclined by θ1 degree with respect to a straight line C connecting the tip 21E and the center of a brake disk rotor (not shown). . The intermediate portion 22 is formed with an inclination of θ2 degrees smaller than the angle θ1 of the inlet portion 21 with respect to the straight line connecting the tip 22E and the center of the disc, and the outlet portion 23 corresponding to the outer peripheral portion. Is formed with an inclination of θ3 degrees, which is smaller than the angle θ2 of the intermediate portion 22, with respect to a straight line connecting the tip 23E and the center of the brake disc rotor .

In the embodiment, θ1 is set to 50 degrees, θ2 is set to 20 degrees, and θ3 is set to 5 degrees. However, the arrangement angles of the inlet portion 21, the intermediate portion 22, and the outlet portion 23 are set in the brake disc rotor . Although the inflow angle varies depending on the rotation speed of the brake disk rotor , the installation angle of the inlet portion 21 is generally 30 degrees to 70 degrees for automobiles. Since it is known that the range is preferable, it is preferable to set the angle according to it. The arrangement angle of the outlet portion 23 is set within a range of 0 degrees to 15 degrees so that the action as a blower blade on the pressure surface side becomes more effective, and the arrangement angle of the intermediate section 22 is efficient without stagnation of the flow. It is preferable to set an intermediate angle between the inlet portion 21 and the outlet portion 23 in order to allow the flow to flow.

  Each fin 21, 22, 23 is formed in a concave shape having a radius of 100 mm with respect to the rotation direction of the brake disc rotor. Further, the radially outer ends 21T and 22T of the fins 21 and 22 are formed in a semicircular shape. In addition to the reason that the semicircular shape of the fins 21 and 22 is easier to manufacture, the cylindrical shape is obtained when a cylindrical obstacle is placed on a part of the steady flow as is apparent from FIG. Focusing on the fact that the flow can be guided to a region that does not reach when there is no obstacle with the formation of the flow PF that wraps around, the flow around the end portions 21T and 22T is guided to the fins 22 and 23 without stagnation. It is.

  The envelope circle connecting the radially outer ends 21T of the inlet portion 21 and the envelope circle connecting the radially inner ends 22E of the intermediate portion 22 are formed with substantially the same dimensions. Further, by forming the radii of the envelope circles 22T and 23E in the same manner, it becomes a three-stage fin structure formed so that the action as the blowing blade on the pressure surface side of the intermediate portion 22 and the outlet portion 23 becomes more effective. ing.

  The flow that flows so as to wind the end portion 21T radially outward of the fin 21 smoothly flows along the fin 22 that is radially outward, minimizing the stagnation generated in the gap between the partition walls 21T and 22E, A part of the flow on the back surface of the fin 21 can join the flow on the front surface of the fin 22 through the gap between the partition walls. The gap between the partition walls is set to 6 mm, but 4 mm to 8 mm is preferable for obtaining an effect without obstructing the air flow in the bench hole. The gap between the partition walls of the next fins 22 and 23 has the same structure, and the same effect can be obtained.

In this embodiment, the lengths of the fins 21, 22, and 23 in the radial direction are set to be substantially the same. Accordingly, since the fin 21 has a large angle with the center of the brake disc rotor , its actual length is the longest and the flow can be taken in efficiently.

  The above-described embodiments have been illustrated for the purpose of explanation, and the present invention is not limited to them. Modifications and modifications are possible as long as they do not contradict the technical idea of the present invention that can be recognized by those skilled in the art from the description of the scope of claims. Addition is possible.

  The present invention is not limited to the brake disk rotor, but can be applied to industrial equipment having a function as a blower.

DESCRIPTION OF SYMBOLS 1 Brake disc rotor 2 Fin 4 Bench hole 5 Communication port 11 Inner side sliding plate 12 Outer side sliding plate 21 Inlet part fin 22 Middle part fin 23 Outlet part fin 31 Inlet opening 32 Outlet opening 41 Stagnation area 42 Main flow area

Claims (3)

      Disc-shaped sliding plates arranged apart from each other in the axle direction, and a radial shape between both sliding plates so that they are inclined in the direction opposite to the rotation direction of the sliding plates as they go radially outward. It is composed of a series of partition walls that are arranged and divided into a plurality, and a plurality of sets of the partition walls are formed on the circumference of the sliding plate to open from the radially inner side to the outer side. A brake disc rotor in which a plurality of inlet openings and outlet openings are formed, wherein the series of divided partition walls are radially outward with respect to the divided partition walls disposed radially inwardly. The divided partition walls arranged in the radial direction of the first divided partition wall having a plurality of sets arranged on the circumference of the sliding plate are spaced apart with an angular phase difference in the direction opposite to the rotation direction of the sliding plate. The envelope circle connecting the outer ends is the radial inner side of the second partition wall. Brake disc rotor, characterized in that formed by enveloping circle substantially coincides drawn between parts.       The series of divided partition walls divided into a plurality is divided such that the center line in the longitudinal direction of the partition wall disposed radially inward of the disk-shaped sliding plate is in the radial direction of the disk-shaped sliding plate. The angle formed is formed so that the longitudinal center line of the partition wall disposed radially outward is larger than the angle formed with respect to the radial direction of the disk-shaped sliding plate. Brake disc rotor as described. The brake disk rotor according to claim 2, wherein the plurality of divided partition walls are formed so as to be concave with respect to a rotation direction of the disc-shaped sliding plate.