JP4691443B2 - brake disc - Google Patents

Description

  The present invention relates to a brake disc for a disc brake.

  A brake disc, which is a main component of the disc brake device, includes an annular braking body (also referred to as a braking member or a sliding member) and an attachment member for mounting on an axle provided in the central region of the braking body. It is configured. In general, in a brake disk, when the braking body thermally expands due to frictional heat during braking, the annular braking body is firmly restrained by the mounting member, and therefore the braking body in the direction of the rotation axis of the braking body. There is known a phenomenon in which a moment is generated and the braking body is deformed so as to be inclined in the axial direction (this phenomenon is referred to as “heat collapse”). The thermal collapse causes uneven wear on the brake disc, which in turn causes unstable braking torque and unpleasant brake vibration during braking. For this reason, various measures for preventing thermal collapse as much as possible have been proposed.

  The disk plate for a disk brake disclosed in Patent Document 1 is “a connecting pin through which an end portion of a mounting member separated from a braking member is superimposed on an inner peripheral portion of an annular braking member, and the both members pass through them. ”, One or both of the holes of both members through which the connecting pin is inserted are elongated holes in the radial direction” (see the claims of the utility model registration). That is, as shown in FIGS. 2 and 3 of Patent Document 1, the hole 6 for the connecting pin 7 is elongated in the radial direction, so that the restraint by the mounting member during thermal expansion of the braking member is alleviated. The brake member can be easily thermally expanded outwardly in the radial direction of the disk to prevent the brake member from falling over.

  However, according to page 4 of the specification of Patent Document 1, “the brake pin 1 and the attachment member 5 are fixedly connected to each other by a connection pin 7 such as a caulking pin inserted through the connection hole 4 and the long hole 6, The plate is made up. " That is, in addition to the existence of the intended clearance between the long hole 6 formed so as to be long in the radial direction of the disk plate and the connecting pin 7, the connecting hole 4 and the connecting pin 7 simply inserted through the connecting hole 4 are provided. A clearance is unavoidably present between the two. For this reason, when braking or accelerating the vehicle, not only a vibration continuous contact occurs between the inner wall of the long hole of the member provided with the long hole 6 and the connecting pin 7, but an abnormal noise is generated. Similarly, a continuous vibration contact is generated between the inner wall of the member provided with the hole 4 and the connecting pin 7, and an abnormal noise is generated.

  Thus, when the connecting pin 7 is exposed to vibration continuous contact not only with the long hole 6 but also with the connecting hole 4, the surface of the connecting pin 7 and the inner wall surface of the other hole (particularly the connecting hole 4) are damaged. Or it may be worn out and the clearance may unintentionally expand. As a result, the continuous vibration contact between the connecting pin 7 and in particular the inner wall surface of the connecting hole 4 is promoted, and a vicious circle occurs in which the generation of abnormal noise increases more and more. The present invention has been made in view of such circumstances.

Japanese Utility Model Publication No. 61-104842 (full text description and drawings)

  SUMMARY OF THE INVENTION An object of the present invention is to provide a brake disc that employs a configuration in which a predetermined clearance is secured between a brake body and a mounting member so as to prevent thermal collapse of the brake body due to frictional heat during braking. The purpose is to suppress the generation of abnormal noise at times, etc., as compared with the conventional case. A further object of the present invention is to provide a brake disc that solves the disadvantages and problems associated with adopting a configuration in which a coupling pin is press-fitted into a mounting member in order to suppress the occurrence of abnormal noise during braking or the like. It is to provide.

The invention according to claim 1 is a brake disk comprising an annular braking body, a mounting member disposed at the center of the braking body, and a plurality of coupling pins involved in coupling of the braking body and the mounting member. The pin has a brake member side shaft portion located on the brake member side and an attachment member side shaft portion located on the attachment member side, and an inner peripheral portion of the brake member surrounds the rotation axis (C) of the brake disc. A peripheral flange portion is provided, and the inner peripheral flange portion has an inner diameter (D1) that extends in parallel with the rotation axis (C) and that is larger than the outer diameter (D3) of the brake member side shaft portion of the coupling pin. A plurality of connecting pin insertion holes are formed, and an outer peripheral flange portion that surrounds the rotation axis (C) of the brake disc and can be joined to the inner peripheral flange portion of the brake body is provided on the outer peripheral portion of the mounting member. The outer peripheral A plurality of coupling pin press-fitting holes extending in parallel with the rotation axis (C) and having an inner diameter (D2) smaller than the outer diameter (D4) of the mounting member side shaft of the coupling pin are formed in the flange portion. The inner peripheral flange portion of the braking body is formed with an inner peripheral flange joint surface orthogonal to the rotational axis (C), and the outer peripheral flange portion of the mounting member has the rotational axis ( C) and an outer peripheral flange joint surface that is orthogonal to the brake member and that can be joined to the inner peripheral flange joint surface of the braking body is formed, and the outer peripheral flange portion of the mounting member is further provided with an outer peripheral flange of a coupling pin press-fitting hole By adopting a shape in which the periphery of the joint surface side opening is partially stealed, a recessed portion around the press-fitting hole that is recessed with respect to the outer peripheral flange joint surface is formed, and the inner peripheral flange portion of the braking body and the Peripheral flange of mounting member In the state where the connecting portion is joined, the connecting pin press-fitting hole of the outer peripheral flange portion is press-fitted into the connecting pin side shaft portion of the connecting pin, and the braking pin side shaft portion of the connecting pin is inserted into the connecting pin insertion hole of the inner peripheral flange portion. A brake disc characterized in that the brake body and the mounting member are coupled by directly or indirectly engaging the brake body side end portion of the coupling pin with the inner peripheral flange portion of the brake body. is there.

  According to the first aspect, the coupling pin is press-fitted in parallel with the rotation axis (C) of the brake disk with respect to the coupling pin press-fitting hole of the outer peripheral flange portion of the mounting member and the coupling pin insertion hole of the inner peripheral flange portion of the brake member. After the insertion, the attachment member and the braking body are coupled by directly or indirectly locking the end of the coupling pin on the braking body side to the inner peripheral flange portion of the braking body. In this coupling structure, the inner diameter (D1) of the coupling pin insertion hole of the inner peripheral flange portion of the braking body is set to be larger than the outer diameter (D3) of the braking body side shaft portion of the coupling pin, and the inner wall surface of the coupling pin insertion hole and A predetermined clearance is secured between the connecting pins. Due to the presence of this clearance, the braking body is allowed to thermally expand in the radial direction during braking, and thermal collapse of the braking body is prevented or suppressed.

  Further, according to this coupling structure, the inner diameter (D2) of the coupling pin press-fitting hole of the outer peripheral flange portion of the mounting member is set to be smaller than the outer diameter (D4) of the mounting member side shaft portion of the coupling pin. It is press-fitted into the connecting pin press-fitting hole of the flange. In other words, the coupling pin and the mounting member are tightly integrated in the coupling pin press-fitting hole, and there is a gap inside the coupling pin press-fitting hole that allows the coupling pin to be finely moved or displaced in the radial direction and the circumferential direction. Does not exist. For this reason, vibration continuous contact does not occur between the coupling pin press-fitting hole and the coupling pin during braking or acceleration of the vehicle, and therefore no abnormal noise is generated due to such vibration continuous contact. As described above, since vibration continuous contact cannot occur at least between the mounting member and the coupling pin, the occurrence of abnormal noise based on the vibration continuous contact is a braking in which the clearance is intentionally secured in the coupling pin insertion hole. It stays only in abnormal noise based on the continuous vibration contact between the body and the connecting pin. Therefore, according to this brake disk, the occurrence of abnormal noise during braking or the like is suppressed more than in the past.

Further , according to claim 1 , even when the inner peripheral flange joint surface of the inner peripheral flange portion of the braking body is joined to the outer peripheral flange joint surface of the outer peripheral flange portion of the mounting member, the coupling pin press-fitting hole of the outer peripheral flange portion of the mounting member A clearance space based on the press-fitting hole peripheral recess is secured around the outer peripheral flange joint surface side opening. For this reason, the coupling pin is press-fitted into the coupling pin press-fitting hole of the outer peripheral flange portion from the side opposite to the outer peripheral flange joint surface toward the outer peripheral flange joint surface. Even if swell deformation due to the influence of the press-fitting of the connecting pin occurs around the portion, the swell deformation is accommodated in the gap space based on the concave portion around the press-fitting hole. Therefore, the flatness of the outer peripheral flange joint surface of the mounting member is not hindered by the influence of the coupling pin press-fitting (that is, no unevenness is generated), and the outer peripheral flange portion of the mounting member and the inner peripheral flange portion of the braking body are not The joining is performed accurately and reliably, the braking body is accurately positioned with respect to the mounting member, and the surface runout accuracy of the sliding surface of the braking body is enhanced.

According to a second aspect of the invention, the brake disk according to claim 1, together with the coupling pin is made of metal, in addition to the brake-side shaft portion and the mounting member side shaft portion, the end portion of the mounting member side The mounting member side shaft portion has a flat head having a diameter larger than the outer diameter (D4), and the end portion on the braking body side has a cylindrical caulking portion that is thin enough to be bent. Inserting the connecting pin of the inner peripheral flange portion of the braking body when the shaft side of the mounting member side of the connecting pin is press-fitted into the connecting pin press-fitting hole of the outer peripheral flange portion of the member and the flat head is engaged with the outer peripheral flange portion Bending the cylindrical caulking portion of the coupling pin protruding from the hole so as to push it out in the radial direction, the caulking portion is directly or indirectly engaged with the inner peripheral flange portion of the braking body, and attached to the braking body. It is characterized by caulking the member.

According to the second aspect of the present invention, the coupling pin is bent so as to push and expand the cylindrical caulking portion of the coupling pin in the radial direction in a state where the coupling pin is press-fitted and inserted into the outer peripheral flange portion of the mounting member and the inner peripheral flange portion of the braking body. The brake body and the mounting member are caulked and coupled via the coupling pin. At that time, the mounting member outer peripheral flange portion and the brake inner peripheral flange portion are strongly tightened between the flat head of the coupling pin that engages with the outer peripheral flange portion of the mounting member and the crimped crimped portion. The caulking connection between the brake body and the mounting member is realized with the flange portion in close contact.

According to a third aspect of the present invention, in the brake disk according to the second aspect , a conical spring is attached to the cylindrical caulking portion of the coupling pin, and the caulking portion is bent so as to be pushed and expanded in the radial direction of the coupling pin. The disc spring is pressed against the inner peripheral flange portion of the braking body.

According to the third aspect , the brake body is urged toward the mounting member by the action of the disc spring pressed against the inner peripheral flange portion of the brake body by the bent crimping portion, and the inner periphery and the outer peripheral flange portion are in close contact with each other. In this state, the caulking connection between the braking body and the mounting member is realized (that is, the braking body side end portion of the coupling pin is indirectly locked to the inner peripheral flange portion of the braking body via the disc spring). Further, even when the brake body is thermally expanded due to heat generated during braking, excessive stress is applied between the brake body and the coupling pin due to the elastic deformation of the disc spring in response to the thermal expansion. While avoiding, the close state between the brake body and the mounting member is maintained.

According to a fourth aspect of the present invention, there is provided a brake disc comprising: an annular braking body; an attachment member disposed at the center of the braking body; and an even number of coupling pins involved in coupling of the braking body and the attachment member. The coupling pin has a brake body side shaft portion located on the brake body side and an attachment member side shaft portion located on the attachment member side, and an inner peripheral portion of the brake body surrounds the rotation axis (C) of the brake disc. An inner peripheral flange portion is provided, and the inner peripheral flange portion extends in parallel with the rotation axis (C) and has an inner diameter (D1) that is larger than the outer diameter (D3) of the brake member side shaft portion of the coupling pin. An even number of connecting pin insertion holes are formed, and an outer peripheral flange portion that surrounds the rotational axis (C) of the brake disc and can be joined to an inner peripheral flange portion of the brake body on the outer peripheral portion of the mounting member Is provided outside The flange portion is formed with an even number of coupling pin press-fitting holes extending in parallel with the rotation axis (C) and having an inner diameter (D2) smaller than the outer diameter (D4) of the coupling pin side shaft portion of the coupling pin. A group of even-numbered coupling pin insertion holes formed in the inner peripheral flange portion of the braking body, and a group of even-numbered coupling pin press-fitting holes formed in the outer peripheral flange portion of the mounting member. The holes constituting one group are equally spaced at a predetermined interval (L) along the circumferential direction of the corresponding flange portion, whereas the group of the even number of coupling pin insertion holes and the even number Each of the holes constituting the other group of the one group of the coupling pin press-fitting holes is shorter than the predetermined interval (L) by a predetermined length (m) along the circumferential direction of the corresponding flange portion. The interval (L−m) and the predetermined length than the predetermined interval (L) m) are arranged at unequal intervals so that long intervals (L + m) that are longer than each other appear alternately, and the outer peripheral flange in the state where the inner peripheral flange portion of the braking body and the outer peripheral flange portion of the mounting member are joined. The coupling member press-fitting hole of the coupling pin is press-fitted into the coupling pin press-fitting hole, and the braking-body-side shaft portion of the coupling pin is inserted into the coupling pin insertion hole of the inner peripheral flange portion, so that the braking-body-side end of the coupling pin The brake disc is characterized in that the brake member and the mounting member are joined by directly or indirectly engaging the inner peripheral flange portion of the brake member.

According to the brake disk of the fourth aspect , in addition to the same effects as the brake disk according to the first aspect, the following effects can be obtained. That is, among the group of even-numbered coupling pin insertion holes in the braking body peripheral flange portion and the group of even-numbered coupling pin press-fitting holes in the mounting member outer peripheral flange portion, each hole constituting one group corresponds to it. Along the circumferential direction of the flange portion, the holes are arranged at equal intervals (L), and the holes constituting the other group are arranged at short intervals (Lm) and long intervals along the circumferential direction of the corresponding flange portion. By arranging them at unequal intervals so that (L + m) appears alternately, the braking body side shaft portion of the coupling pin inserted into each coupling pin insertion hole of the peripheral flange portion in the braking body is in relation to the coupling pin insertion hole. This creates a situation where it is eccentrically placed in the circumferential direction. More specifically, as shown in FIG. 8, of the even number (N) of the coupling pin insertion holes (17A, 17B), half (N / 2) of the coupling pin insertion holes (17A) located every other one. In FIG. 3, the brake member side shaft portion (33) of the connecting pin is eccentric to the front side in the direction of rotation of the brake member, and the other half (N / 2) of the connecting pin insertion holes (17B) are located in the other half. A situation occurs in which the brake body side shaft portion (33) is eccentric to the rear side in the braking body rotation direction. In particular, in the half of the coupling pin insertion holes (17A) in which the brake body side shaft portion (33) of the coupling pin is eccentric to the front side in the braking body rotation direction, the insertion holes (17A) of these insertion holes (17A) are closer to the front in the braking body rotation direction. The brake member side shaft portion (33) of the coupling pin is substantially in contact with or extremely close to the inner wall portion on the side, and the relative displacement of the coupling pin (30) in the braking member rotation direction is restricted as much as possible. For this reason, even when braking with the disc brake mounted on an actual vehicle, even if an inertial force is exerted between the brake body and the mounting member to relatively displace one in the circumferential direction with respect to the other. The circumferential relative displacement hardly occurs between the braking body and the mounting member. Therefore, almost no collision noise caused by the circumferential relative displacement between the braking body and the mounting member is generated, and damage due to the collision is avoided as much as possible.

In order for the brake disk of claim 4 to exhibit the above-mentioned operation and effect most effectively, the predetermined length (m) is set so that the inner diameter (D1) of the coupling pin insertion hole and the coupling pin side of the coupling pin. It is set to the difference from the outer diameter (D3) of the shaft portion (ie, m = D1-D3), or the difference between the inner diameter of the coupling pin insertion hole and the outer diameter of the coupling pin-side shaft portion of the coupling pin (D1-D3) ) And a value close to the difference (D1-D3) is preferable. The number of the coupling pins, the coupling pin insertion holes, and the coupling pin press-fitting holes is particularly preferably “an even number (or number) of six (or number) or more”.

According to a fifth aspect of the present invention, in the brake disk according to the fourth aspect, an inner peripheral flange joint surface that is orthogonal to the rotation axis (C) is formed on the inner peripheral flange portion of the braking body. The outer peripheral flange portion of the mounting member is formed with an outer peripheral flange joint surface that is orthogonal to the rotation axis (C) and that can be joined to the inner peripheral flange joint surface of the braking body. Further, the outer peripheral flange part of the outer peripheral flange part of the connecting pin press-fitting hole has a shape in which the periphery of the outer peripheral flange joint surface side opening part is partially stealed so that a concave part around the press-fitted hole is recessed with respect to the outer peripheral flange joint surface. It is formed.

According to the brake disk of the fifth aspect, the same effect as the brake disk according to the first aspect is obtained.

[Additional remarks] Further preferable aspects and additional constituent elements of the present invention are listed below.
-In Claims 1-5 , a braking body is comprised with cast iron and an attachment member is comprised with aluminum or its alloy.
The contents of claims 2 and 3 are made dependent on claims 4 and 5 .

According to the brake disk according to any one of claims 1 to 5 , a predetermined clearance is secured between the coupling pin insertion hole of the braking body and the coupling pin to allow the braking body to thermally expand in the radial direction during braking. This can prevent or suppress the thermal collapse of the braking body, and press the coupling pin into the coupling pin press-fitting hole of the mounting member to eliminate the room for the fine movement or displacement of the coupling pin. Generation of sound can be suppressed as compared with the conventional case.

According to the brake disk of the fourth aspect of the present invention, a predetermined clearance that allows the braking body to thermally expand in the radial direction during braking is secured between the coupling pin insertion hole of the braking body and the coupling pin. In addition, the brake body side shaft portion of the coupling pin inserted into each coupling pin insertion hole of the peripheral flange portion in the braking body creates an eccentric arrangement in the circumferential direction with respect to the coupling pin insertion hole. Even if an inertial force is applied between the brake body and the mounting member to cause relative displacement in the circumferential direction between the brake body and the mounting member, the circumferential relative displacement between the brake body and the mounting member is almost It has a structure that does not occur. For this reason, while preventing or suppressing the thermal collapse of the braking body, it is possible to avoid as much as possible the generation of a collision sound caused by the circumferential relative displacement between the braking body and the mounting member and the damage caused by such a collision. it can.

In particular, according to the brake disk according to claim 1, 2, 3, and 5 , the outer peripheral flange portion of the mounting member has a shape in which the periphery of the peripheral flange joint surface side opening portion of the coupling pin press-fitting hole is partially stealed. By forming the concave portion around the press-fitting hole that is recessed with respect to the outer peripheral flange joint surface, the flatness of the outer peripheral flange joint surface of the mounting member is not hindered by the influence of the coupling pin press-fitting, and the mounting member The outer peripheral flange portion and the inner peripheral flange portion of the braking body can be joined accurately and reliably.

  A basic embodiment (FIGS. 1 to 6) and an additional embodiment (FIGS. 8 to 10) in which the present invention is embodied in a ventilated brake disc will be described with reference to the drawings.

[Basic Embodiment (FIGS. 1 to 6)]
As shown in FIG. 1, the brake disc includes an annular braking body 10, a mounting member 20 disposed at the center of the braking body 10, and a plurality of coupling pins 30.

  As shown in FIG. 1 and FIGS. 2 (A) and 2 (B), the annular braking body 10 is formed by integrally casting cast iron (for example, flake graphite cast iron) by casting. The braking body 10 includes a first annular disc portion 11 and a second annular disc portion 12 that are connected to each other by a plurality of connecting ribs 13 that extend radially between the annular disc portions 11 and 12. They are connected, and have a ventilated structure in which air passages 14 extending radially are secured between adjacent connecting ribs 13. The outer side surfaces of the first and second annular disk portions 11 and 12 serve as braking surfaces (sliding surfaces) that make frictional contact with the brake caliper brake brake.

  An inner peripheral flange portion 15 is provided on the inner peripheral portion of the first annular disc portion 11 so as to surround the central axis C (also the rotation axis C of the brake disc) of the brake body 10 over the entire circumference. ing. An inner peripheral flange joint surface 16 a is formed on the inner peripheral flange portion 15 on the side facing the mounting member 20, and an inner peripheral flange locking surface 16 b is formed on the opposite side. A plane including at least the inner peripheral flange joint surface 16a is orthogonal to the central axis C. In addition, a plurality of connecting pin insertion holes 17 (12 in this example) are arranged and formed in the inner peripheral flange portion 15 at equiangular intervals (30 ° intervals in this example) with the central axis C as the center. . Each coupling pin insertion hole 17 extends in parallel with the central axis C and penetrates the inner peripheral flange portion 15. The inner diameter of the coupling pin insertion hole 17 is D1 (for example, D1 = 7.20 mm).

  As shown in FIG. 1 and FIGS. 3A and 3B, the mounting member 20 is formed by integrally molding an aluminum alloy by casting. The mounting member 20 includes a disc-shaped axle mounting flange 21, a short cylindrical cylindrical wall 22 provided on the outer peripheral edge of the flange 21, and an outer periphery provided in a bowl shape around the cylindrical wall 22. And a flange portion 23. The axle mounting flange 21 extends in a direction (radial direction) orthogonal to the central axis (rotation axis C) common to the mounting member 20 and the braking body 10. The cylindrical wall 22 extends rearward from the outer peripheral edge of the axle mounting flange 21 in parallel with the rotation axis C. The axle mounting flange 21 is formed with a central large hole 24 for passing the axle at the center position, and a plurality of bolt insertion holes 25 (four in this example) are equiangular at positions surrounding the central large hole 24. Arranged and formed at intervals.

  The outer peripheral flange portion 23 of the mounting member 20 protrudes radially outward over the entire circumference in the vicinity of the rear end portion of the cylindrical wall 22 and surrounds the central axis C. An outer peripheral flange joint surface 26a is formed on the outer peripheral flange portion 23 on the side facing the braking body 10, and an outer peripheral flange locking surface 26b is formed on the opposite side. A plane including at least the outer peripheral flange joint surface 26a is orthogonal to the central axis C. The outer peripheral flange joint surface 26 a can be joined to the inner peripheral flange joint surface 16 a of the braking body 10.

  A plurality of coupling pin press-fitting holes 27 (12 in this example) are arranged and formed in the outer peripheral flange portion 23 of the mounting member 20 at equal angular intervals (30 ° intervals in this example) with the central axis C as the center. Yes. Each coupling pin press-fit hole 27 extends parallel to the central axis C and penetrates the outer peripheral flange portion 23. The inner diameter of the coupling pin press-fitting hole 27 is D2 (for example, D2 = 7.40 mm). The distance from the central axis C of the mounting member 20 to each coupling pin press-fitting hole 27 matches or substantially coincides with the distance from the central axis C of the braking body 10 to each coupling pin insertion hole 17. The brake member 10 inner peripheral flange portion 15 and the outer peripheral flange portion 23 of the mounting member 20 can be joined to each other while the hole 17 and the connecting pin press-fitting hole 27 are matched or substantially matched (see FIG. 1).

  As shown in FIGS. 1, 3, and 4, the outer peripheral flange portion 23 of the mounting member 20 further includes a press-fitting hole peripheral recess 28 around the opening on the outer peripheral flange joint surface 26 a side of each coupling pin press-fitting hole 27. Is formed. The press-fitting hole peripheral concave portion 28 is formed in a shape recessed with respect to the outer peripheral flange joint surface 26a by partially stealing the outer peripheral flange portion 23 on the outer peripheral flange joint surface 26a side.

  As shown in FIG. 1 and FIGS. 5A and 5B, the coupling pin 30 is a hollow pipe-shaped stainless steel pin having a through hole 31 penetrating the center in the axial direction. In particular, as shown in FIG. 5 (B), the coupling pin 30 includes a caulking portion 32 that is an end portion that is positioned on the braking body 10 side during use, a braking body side shaft portion 33 that is positioned closer to the braking body 10 side, It has the attachment member side axial part 34 located near the member 20 side, and the flat head 35 which is an edge part located in the attachment member 20 side at the time of use.

  The caulking portion 32 is configured as a cylindrical portion that is relatively thin (smaller and thinner than the outer diameter D3 of the brake-body-side shaft portion 33) at one end of the coupling pin 30, and the degree of thinness (thickness) is caulking. It can be bent without difficulty by a machine. The outer diameter of the brake member side shaft portion 33 of the coupling pin 30 is D3 (for example, D3 = 7.00 mm), and the outer diameter of the mounting member side shaft portion 34 is D4 (for example, D4 = 7.42 mm). In the present embodiment, D3 <D4. The inner diameter D1 of the connecting pin insertion hole 17 is set to be larger than the outer diameter D3 of the brake member side shaft portion 33 of the connecting pin. The inner diameter D2 of the coupling pin press-fitting hole 27 is set to be slightly smaller than the outer diameter D4 of the mounting member side shaft portion 34 of the coupling pin.

  The flat head portion 35 has a larger diameter than the outer diameter D4 of the attachment member side shaft portion 34, and is configured as the thickest ring-shaped portion at the other end portion of the coupling pin 30. The flat head 35 functions as a restricting portion that abuts on the outer peripheral flange engaging surface 26b of the mounting member 20 and restricts the axial sliding of the coupling pin 30.

  In the brake disc of this embodiment, the same number of disc springs 41 and flat washers 42 as the coupling pins 30 are used in addition to the coupling pins 30 (see FIG. 1). As shown in FIG. 6, the disc spring 41 includes a tapered umbrella-shaped ring-shaped main body portion 41 a and a flange-shaped straight ring portion 41 b formed on the inner peripheral portion of the main body portion 41 a.

  The brake disc of this embodiment is assembled as shown in FIG. That is, the outer peripheral flange of the mounting member 20 with respect to the inner peripheral flange joint surface 16a of the braking body 10 while the connecting pin insertion hole 17 of the braking body 10 and the connecting pin press-fitting hole 27 of the mounting member 20 are matched or substantially matched. The joining surface 26a is joined. Then, the coupling pin 30 is inserted into the holes (27, 17) from the outer peripheral flange locking surface 26b side of the mounting member toward the inner peripheral flange locking surface 16b side of the braking body, and the coupling pin The coupling pin 30 is inserted firmly until the flat head 35 of the 30 comes into contact with the outer peripheral flange locking surface 26b. Then, the mounting member side shaft portion 34 of the coupling pin 30 is press-fitted into the coupling pin press-fitting hole 27, and the coupling pin 30 is integrated with the outer peripheral flange portion 23 of the mounting member 10. Further, the brake member side shaft portion 33 of the coupling pin 30 is disposed in the coupling pin insertion hole 17, and the crimping portion 32 passes through the coupling pin insertion hole 17 and protrudes toward the inner peripheral flange locking surface 16 b side.

  After the disc spring 41 and the flat washer 42 are fitted on the cylindrical caulking portion 32 protruding from the coupling pin insertion hole 17, the cylindrical caulking portion 32 is pushed outward in the radial direction by using a caulking machine. Bend to widen (see partially enlarged view in FIG. 1). As the crimping portion 32 is pushed and spread, the outer peripheral end of the disc spring 41 is pressed against the inner peripheral flange locking surface 16b via the flat washer 42, and the disc spring 41 is elastically deformed appropriately. Then, the disc spring 41 is configured such that the straight ring portion 41 b of the disc spring 41 is sandwiched between the flat washer 42 and the step portion located at the boundary between the cylindrical caulking portion 32 of the coupling pin 30 and the brake body side shaft portion 33. Positioning. Thus, the caulking portion 32 of the coupling pin 30 is indirectly locked to the inner peripheral flange locking surface 16b of the braking body 10 via the flat washer 42 and the disc spring 41, so that the braking body via the coupling pin 30 is obtained. 10 and the mounting member 20 are caulked and the assembly of the brake disc is completed.

  In the completed brake disc, the disc spring 41 that is appropriately elastically deformed presses the inner peripheral flange engaging surface 16b, so that the inner peripheral flange portion 15 (and hence the braking body 10) is The flange portion 23 (and hence the attachment member 20) continues to be appropriately biased. Further, the outer peripheral flange portion 23 and the inner peripheral flange portion 15 are strongly tightened between the flat head portion 35 of the coupling pin 30 that engages with the outer peripheral flange portion 23 of the mounting member 20 and the crimped caulking portion 32. Therefore, the intimate state of both flange portions is maintained. Further, even when the braking body 10 is thermally expanded due to heat generated during braking, the disc spring 41 is elastically deformed in response to the thermal expansion, so that excessive stress acts between the braking body 10 and the coupling pin 30. The close state between the braking body 10 and the mounting member 20 is maintained while avoiding this.

[Effects of basic embodiment]
According to the present embodiment, the inner diameter D1 of the coupling pin insertion hole 17 of the inner peripheral flange portion 15 of the braking body 10 is set larger than the outer diameter D3 of the braking body side shaft portion 33 of the coupling pin 30, and the coupling pin insertion hole A clearance corresponding to a difference in both diameters (D1-D3) is secured between the inner wall surface 17 and the coupling pin 30 (see FIG. 1). Due to the presence of this clearance, the brake body 10 is allowed to thermally expand in the radial direction during braking, so that the thermal collapse of the brake body 10 can be prevented or suppressed.

  According to this embodiment, the inner diameter D2 of the coupling pin press-fitting hole 27 of the outer peripheral flange portion 23 of the mounting member 20 is set smaller than the outer diameter D4 of the mounting member side shaft portion 34 of the coupling pin 30, and the coupling pin 30 is It is press-fitted into the connecting pin press-fitting hole 27. That is, there is no gap inside the coupling pin press-fitting hole 27 that allows the coupling pin 30 to be finely moved or displaced in the radial direction and the circumferential direction. For this reason, vibration continuous contact does not occur between the coupling pin press-fitting hole 27 and the coupling pin 30 during braking or acceleration of the vehicle. Since vibration continuous contact cannot occur at least between the mounting member 20 and the coupling pin 30, the occurrence of abnormal noise based on the vibration continuous contact is a braking in which the clearance is intentionally secured in the coupling pin insertion hole 17. Only abnormal noise based on vibrational continuous contact between the body 10 and the coupling pin 30 remains. Therefore, it is possible to suppress the occurrence of abnormal noise during braking or the like.

  According to the present embodiment, a clearance space based on the press-fitting hole peripheral recess 28 is secured around the opening on the outer peripheral flange joint surface 26a side of the coupling pin press-fitting hole 27 of the outer peripheral flange 23 of the mounting member 20 ( (See FIG. 1). Therefore, the coupling pin 30 is pressed into the coupling pin press-fitting hole 27 from the outer peripheral flange locking surface 26b side toward the outer peripheral flange joint surface 26a. As a result, the outer peripheral flange joint surface 26a side of the coupling pin press-fit hole 27 is obtained. Even if swell deformation due to the influence of the coupling pin press-fitting occurs around the opening, the swell deformation remains in the press-fitting hole peripheral recess 28 (see FIG. 4). Therefore, the outer peripheral flange joint surface 26a of the mounting member 20 is not uneven and does not lose its flatness due to the influence of the coupling pin press-fitting. That is, despite the adoption of a press-fitting structure in which the relatively large-diameter coupling pin 30 is press-fitted into the relatively small-diameter coupling pin press-fitting hole 27, the adverse effect of the coupling pin press-in appears on the outer peripheral flange joint surface 26a. There is nothing. Therefore, according to the present embodiment, the inner peripheral flange portion 15 of the braking body 10 and the outer peripheral flange portion 23 of the mounting member 20 are joined accurately and reliably, and the braking body 10 is accurately positioned with respect to the mounting member 20. In addition, the surface runout accuracy of the sliding surface of the braking body 10 is increased.

[Additional Embodiment (FIGS. 8 to 10)]
In the brake disk according to the basic embodiment shown in FIGS. 1 to 6, twelve connecting pin insertion holes 17 are formed in the inner peripheral flange portion 15 of the braking body 10 at equiangular intervals (30 ° intervals) about the central axis C. On the other hand, twelve coupling pin press-fitting holes 27 are arranged at equiangular intervals (30 ° intervals) around the central axis C in the outer peripheral flange portion 23 of the mounting member 20. Is formed. That is, as shown in FIG. 7A, the twelve connecting pin insertion holes 17 are along a virtual circle (PCD) passing through the center of each insertion hole 17 in the inner peripheral flange portion 15 of the braking body 10. At equal intervals L. Similarly, the twelve coupling pins 30 that are respectively press-fitted into the twelve coupling pin press-fit holes 27 are virtual circles (PCD) that pass through the centers of the press-fit holes 27 in the outer peripheral flange portion 23 of the mounting member 20. Are equally spaced at the same predetermined interval L. Immediately after assembling the mounting member 20 to the braking body 10 using the twelve coupling pins 30, as shown in FIG. 7A, each coupling pin insertion hole 17 of the inner peripheral flange portion 15 and its In the situation in which the centers of the coupling pin 30 inserted through the insertion hole 17 are substantially coincident with each other and the concentric circles are disposed, and one of the two is eccentric with respect to the other. Absent.

  However, in each coupling pin insertion hole 17, the inner diameter D <b> 1 of the coupling pin insertion hole 17 is provided on both sides of the coupling pin on the braking body side shaft portion 33 (at the front side and the rear side with respect to the rotation direction of the braking body 10). And a clearance corresponding to a half of the difference between the outer diameter D3 of the brake member side shaft portion 33 (that is, (D1-D3) / 2). For this reason, relative braking in the circumferential direction occurs between the brake body 10 and the mounting member 20 during braking after the brake disk is mounted on the actual vehicle, and an irritating collision sound may occur at that time. . That is, when braking is applied in a state where the brake disc is mounted on the vehicle, the brake body 10 receives rotation of the brake pad by the brake caliper, and the brake body 10 tries to stop rotating. Each of the coupling pins 30 that are press-fitted and fixed tends to continue to rotate in the rotational direction of the braking body 10 based on inertia. As a result, as shown in FIG. 7B, the brake body side shaft portion 33 of each coupling pin is displaced in the rotation direction of the braking body 10 in each coupling pin insertion hole 17, and in each coupling pin insertion hole 17. It collides with the hole inner wall located on the front side in the direction of rotation of the braking body. At this time, there is a problem that an unpleasant collision sound such as “click” is generated, and this sound makes the passenger uncomfortable. Further, when the brake member side shaft portion 33 of the coupling pin collides with the inner wall portion of the coupling pin insertion hole 17, both the coupling pin 30 side and the coupling pin insertion hole 17 side are damaged, or the coupling pin 30 is caused by repeated collisions. And the inner wall portion of the connecting pin insertion hole 17 may gradually increase, which may further increase unpleasant collision noise.

  The brake disc of the additional embodiment shown in FIGS. 8 to 10 solves the above-mentioned problems. The following description will focus on differences from the basic embodiment.

  In the outer peripheral flange portion 23 of the mounting member 20 constituting the brake disk of the additional embodiment, as in the case of FIG. 3A of the basic embodiment, twelve coupling pin press-fitting holes 27 have the central axis C. Are arranged and formed at equiangular intervals (30 ° intervals). That is, the twelve coupling pin press-fitting holes 27 are along a virtual circle (PCD) passing through the center of each press-fitting hole 27 in the outer peripheral flange portion 23 of the mounting member 20, that is, in the circumferential direction of the outer peripheral flange portion 23. Are equally spaced at a predetermined distance L. Accordingly, when the brake disk is assembled, a total of twelve coupling pins 30 that are press-fitted into the respective coupling pin press-fitting holes 27 are also arranged at regular intervals L along the circumferential direction of the outer peripheral flange portion 23 (FIG. 8). reference). In addition, the outer peripheral flange portion 23 of the mounting member 20 in the additional embodiment is provided with a plurality of press-fitting hole peripheral recesses 28 as in the basic embodiment.

  On the other hand, in the inner peripheral flange portion 15 of the braking body 10 constituting the brake disk of the additional embodiment, as shown in FIGS. 8 and 9, twelve coupling pin insertion holes 17A and 17B are provided around the periphery. Arranged and formed at unequal intervals in the direction. More specifically, among the 12 hole intervals between the 12 coupling pin insertion holes 17A and 17B, a short interval (Lm) is adopted for every other 6 hole intervals. Long intervals (L + m) are adopted for the remaining six hole intervals located every other one. That is, the twelve coupling pin insertion holes 17A and 17B are arranged at unequal intervals so that short intervals (L−m) and long intervals (L + m) appear alternately along the circumferential direction of the inner peripheral flange portion 15. Yes.

  Here, the short interval (L−m) is an interval shorter than the predetermined interval L by a predetermined length m, and the long interval (L + m) is an interval longer than the predetermined interval L by the predetermined length m. Say. The predetermined interval L means a distance along the circumferential direction between two adjacent coupling pins 30 in the plurality of coupling pins 30 that are press-fitted and integrated with the mounting member 20. Ideally, the predetermined length m is most preferably set to m = (D1−D3). However, in consideration of tolerances indispensable for assembly, in reality, m <(D1−D3). ) Is preferable.

  As shown in FIG. 8, m = (D1-D3) or m is (D1-D3) at a place where the interval between two adjacent coupling pin insertion holes 17A, 17B is set to a short interval (L-m). ) And close to (D1-D3), the coupling pin insertion hole 17A located on the front side of the braking body rotation direction causes the braking body side shaft portion 33 of the coupling pin to be connected to the coupling pin insertion hole. It almost abuts on or comes close to the inner wall portion on the front side of the braking body rotation direction of 17A. On the other hand, in the coupling pin insertion hole 17B located on the rear side of the braking body rotation direction, the braking body side shaft portion 33 of the coupling pin substantially contacts the inner wall portion of the coupling pin insertion hole 17B on the rear side in the braking body rotation direction. Close or close.

  As shown in FIG. 8, m = (D1−D3) or m is less than (D1−D3) at a place where the interval between two adjacent coupling pin insertion holes 17A and 17B is set to a long interval (L + m). In addition, by setting the value close to (D1-D3), in the coupling pin insertion hole 17B located on the front side in the braking body rotation direction, the braking body side shaft portion 33 of the coupling pin is connected to the coupling pin insertion hole 17B. Almost abuts or comes close to the inner wall on the rear side in the rotation direction of the braking body. On the other hand, in the coupling pin insertion hole 17A located on the rear side in the braking body rotation direction, the braking body side shaft portion 33 of the coupling pin substantially contacts the inner wall portion on the front side in the braking body rotation direction of the coupling pin insertion hole 17A. Close or close.

  Assume that the brake is applied after the disc brake of the additional embodiment in which the braking body 10 and the mounting member 20 are coupled as shown in FIG. Even in such a case, in the six connecting pin insertion holes 17A located at every other position, the brake member side shaft portion 33 of the connecting pin is substantially in contact with the inner wall portion of each insertion hole 17A on the front side in the braking member rotation direction. In a state of close proximity, the relative displacement of the coupling pin 30 in the braking body rotation direction is restricted as much as possible. In addition, even in the six coupling pin insertion holes 17B that are located at every other position, the braking body side shaft portion 33 of the coupling pin is substantially in contact with or in close proximity to the inner wall portion on the rear side in the braking body rotation direction of each insertion hole 17B. In this state, there is almost no collision between the inner wall portion of the coupling pin insertion hole 17B and the brake pin side shaft portion 33 of the coupling pin due to relative displacement. Accordingly, even during braking, relative displacement in the circumferential direction between the braking body 10 and the mounting member 20 hardly occurs, and the above-mentioned harsh collision noise during braking is hardly generated.

  When the predetermined length m is set to a value less than (D1-D3) and close to (D1-D3), not m = (D1-D3), as shown in the enlarged view of FIG. In addition, in the coupling pin insertion hole 17A or 17B, relative to the relatively narrow clearance C1 on both sides of the coupling body side shaft portion 33 of the coupling pin (the front side and the rear side with respect to the rotation direction of the braking body 10). A wide clearance C2 can be obtained. Incidentally, when m = (D1-D3), C1 = 0 and C2 = (D1-D3). When two narrow clearances C1 and C2 are generated in this way, for example, the inner diameter D1 of the coupling pin insertion holes 17A and 17B is 7.20 mm, and the outer diameter D3 of the braking body side shaft portion 33 of the coupling pin 30 is 7.00 mm. In this case, it is preferable to limit the narrow clearance to about C1 = 0.02 to 0.03 mm (that is, about 10 to 15% of D1−D3 = 0.20 mm). When the narrow clearance C1 becomes too large compared to (D1-D3), the twelve coupling pin insertion holes 17A, 17B are arranged along the circumferential direction of the inner peripheral flange portion 15 with a short interval (Lm) and a long interval ( L + m) are arranged at unequal intervals so that they appear alternately, the meaning of preventing relative displacement in the circumferential direction between the braking body 10 and the mounting member 20 at the time of braking is lessened, and an unpleasant collision sound at the time of braking is suppressed. Or it is difficult to reduce.

  [Modification] In the above-described additional embodiment, the twelve connecting pin insertion holes 17 in the inner peripheral flange portion 15 of the braking body 10 are arranged at unequal intervals. Instead of this, the twelve coupling pin insertion holes 17 in the inner peripheral flange portion 15 of the braking body 10 are equally spaced at a predetermined interval L, while the twelve coupling pin press-fits in the outer peripheral flange portion 23 of the mounting member 20 are arranged. The holes 27 may be arranged at unequal intervals so that short intervals (L−m) and long intervals (L + m) appear alternately along the circumferential direction of the outer peripheral flange portion 23. Even in such a case, the same effects as those of the additional embodiment can be obtained.

  [Modification] In the basic and additional embodiments described above, the outer diameter D4 of the mounting member side shaft portion 34 is larger than the outer diameter D3 of the braking body side shaft portion 33 of the coupling pin 30 (D3 <D4). It may be a coupling pin such that = D4. In the present invention, D3 <D1 and D2 <D4 may be satisfied.

  [Modifications] In the basic and additional embodiments, the coupling pin 30 having the through hole 31 passing through the center of the pin is used. However, if at least the caulking portion 32 that is the brake-body-side end portion of the coupling pin is cylindrical. The other parts (33, 34, 35) may be configured as solid bodies.

  [Modifications] In the basic and additional embodiments described above, the disc spring 41 and the flat washer 42 are omitted, and the caulking portion 32 of the coupling pin 30 is directly locked to the inner peripheral flange locking surface 16b of the braking body 10. By doing so, the brake body 10 and the mounting member 20 may be connected by caulking. Alternatively, only the flat washer 42 may be omitted.

  [Modification] In the above basic embodiment, the number of the coupling pins 30, the coupling pin insertion holes 17 and the coupling pin press-fitting holes 27 is an even number or pieces (specifically, twelve pieces or pieces). It is good also as a piece (for example, 11 or 13). Even in that case, the same effects as the above-described basic embodiment can be obtained.

Sectional drawing of the radial direction of a brake disc, and the expanded sectional view of the part. (A) is a front view of a braking body, (B) is sectional drawing in the AA of (A). (A) is a rear view of an attachment member, (B) is sectional drawing in the BB line of (A). The perspective view which expands and shows a part of outer periphery flange of an attachment member. (A) is a rear view of a coupling pin, (B) is sectional drawing in the EE line of (A). (A) is a rear view of a disc spring, (B) is sectional drawing in the FF line of (A). It is the partial front view which showed a part of inner peripheral flange part of the braking body in basic embodiment in the linear strip | belt state, (A) is the partial front view at the time of an assembly | attachment, (B) is the part at the time of braking Front view. The partial front view which showed a part of inner peripheral flange part of the braking body in additional embodiment in the linear strip | belt state. The partial front view which shows a part of braking body in additional embodiment. The partial enlarged front view which expands and shows a part of inner peripheral flange part of the braking body in additional embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Ring-shaped braking body, 15 ... Inner peripheral flange part, 16a ... Inner peripheral flange joint surface, 16b ... Inner peripheral flange locking surface, 17, 17A, 17B ... Connecting pin insertion hole, 20 ... Mounting member, 23 ... Outer periphery Flange part, 26a ... outer peripheral flange joint surface, 26b ... outer peripheral flange locking surface, 27 ... coupling pin press-fitting hole, 28 ... press-fitting hole peripheral recess, 30 ... coupling pin, 32 ... caulking part (brake body side end of coupling pin) 33 ... Brake body side shaft portion, 34 ... Mounting member side shaft portion, 35 ... Flat head (attachment member side end portion of the coupling pin), 41 ... Belleville spring, 42 ... Flat washer, C ... Center axis (rotation axis) .

Claims (5)

In a brake disc comprising an annular braking body, a mounting member disposed at the center of the braking body, and a plurality of coupling pins involved in coupling of the braking body and the mounting member,
The coupling pin has a brake member side shaft portion located on the brake member side and an attachment member side shaft portion located on the attachment member side,
An inner peripheral flange portion surrounding the rotation axis (C) of the brake disc is provided on an inner peripheral portion of the brake body, and the inner peripheral flange portion extends in parallel with the rotation axis (C) and is coupled to the brake disc. A plurality of connecting pin insertion holes having an inner diameter (D1) larger than the outer diameter (D3) of the shaft on the brake body side of the pin are formed,
The outer peripheral portion of the mounting member is provided with an outer peripheral flange portion that surrounds the rotation axis (C) of the brake disc and can be joined to the inner peripheral flange portion of the brake body. The outer peripheral flange portion has a rotation axis ( A plurality of coupling pin press-fitting holes extending in parallel with C) and having an inner diameter (D2) smaller than the outer diameter (D4) of the mounting member side shaft portion of the coupling pin;
An inner peripheral flange joint surface that is orthogonal to the rotation axis (C) is formed on the inner peripheral flange portion of the braking body,
The outer peripheral flange portion of the mounting member is formed with an outer peripheral flange joint surface that is orthogonal to the rotation axis (C) and that can be joined to the inner peripheral flange joint surface of the brake member,
The outer peripheral flange portion of the mounting member further has a press-fitting hole that is recessed with respect to the outer peripheral flange joint surface by forming a shape that partially steals the periphery of the outer peripheral flange joint surface side opening of the coupling pin press-fitting hole. A peripheral recess is formed,
While the inner peripheral flange portion of the braking body and the outer peripheral flange portion of the mounting member are joined, the mounting member side shaft portion of the coupling pin is press-fitted into the coupling pin press-fitting hole of the outer peripheral flange portion, and the inner peripheral flange The brake body side shaft portion of the coupling pin is inserted into the coupling pin insertion hole of the portion, and the brake body side end portion of the coupling pin is directly or indirectly engaged with the inner peripheral flange portion of the brake body, A brake disc, wherein the mounting member is coupled. The coupling pin is made of metal, and in addition to the brake member side shaft portion and the mounting member side shaft portion, the end on the mounting member side has a flat diameter larger than the outer diameter (D4) of the mounting member side shaft portion. It has a head and has a cylindrical caulking portion that is thin enough to be bent at the end on the brake body side,
When the mounting member side shaft portion of the connecting pin is press-fitted into the connecting pin press-fitting hole of the outer peripheral flange portion of the mounting member and the flat head is engaged with the outer peripheral flange portion, the inner peripheral flange portion of the braking body is connected. By bending the cylindrical caulking portion of the coupling pin protruding from the pin insertion hole so as to push and expand in the radial direction, the caulking portion is directly or indirectly engaged with the inner peripheral flange portion of the braking body, and the braking body The brake disk according to claim 1 , wherein the mounting member and the mounting member are caulked. A disc spring is attached to the cylindrical crimping portion of the coupling pin, and the disc spring is pressed against the inner peripheral flange portion of the braking body by a crimping portion that is bent so as to be pushed and expanded in the radial direction of the coupling pin. The brake disk according to claim 2 . In a brake disc including an annular braking body, an attachment member arranged at the center of the braking body, and an even number of coupling pins involved in coupling of the braking body and the attachment member,
The coupling pin has a brake member side shaft portion located on the brake member side and an attachment member side shaft portion located on the attachment member side,
An inner peripheral flange portion surrounding the rotation axis (C) of the brake disc is provided on an inner peripheral portion of the brake body, and the inner peripheral flange portion extends in parallel with the rotation axis (C) and is coupled to the brake disc. An even number of connecting pin insertion holes having an inner diameter (D1) larger than the outer diameter (D3) of the shaft on the brake body side of the pin are formed,
The outer peripheral portion of the mounting member is provided with an outer peripheral flange portion that surrounds the rotation axis (C) of the brake disc and can be joined to the inner peripheral flange portion of the brake body. The outer peripheral flange portion has a rotation axis ( C) and an even number of coupling pin press-fitting holes extending in parallel to the coupling pin and having an inner diameter (D2) smaller than the outer diameter (D4) of the mounting member side shaft portion;
One group of a group of even-numbered coupling pin insertion holes formed in the inner peripheral flange portion of the braking body and a group of even-numbered coupling pin press-fitting holes formed in the outer peripheral flange portion of the mounting member Are arranged at equal intervals (L) along the circumferential direction of the corresponding flange portion, whereas the even number of coupling pin insertion holes and the even number of couplings Each of the holes constituting the other group of the pin press-fitting holes has a short interval (L) shorter than the predetermined interval (L) by a predetermined length (m) along the circumferential direction of the corresponding flange portion. -M) and the long intervals (L + m) longer than the predetermined interval (L) by the predetermined length (m) are alternately arranged so as to appear alternately,
While the inner peripheral flange portion of the braking body and the outer peripheral flange portion of the mounting member are joined, the mounting member side shaft portion of the coupling pin is press-fitted into the coupling pin press-fitting hole of the outer peripheral flange portion, and the inner peripheral flange The brake body side shaft portion of the coupling pin is inserted into the coupling pin insertion hole of the portion, and the brake body side end portion of the coupling pin is directly or indirectly engaged with the inner peripheral flange portion of the brake body, A brake disc, wherein the mounting member is coupled. An inner peripheral flange joint surface that is orthogonal to the rotation axis (C) is formed on the inner peripheral flange portion of the braking body,
The outer peripheral flange portion of the mounting member is formed with an outer peripheral flange joint surface that is orthogonal to the rotation axis (C) and that can be joined to the inner peripheral flange joint surface of the brake member,
The outer peripheral flange portion of the mounting member further has a press-fitting hole that is recessed with respect to the outer peripheral flange joint surface by forming a shape that partially steals the periphery of the outer peripheral flange joint surface side opening of the coupling pin press-fitting hole. The brake disk according to claim 4 , wherein a peripheral recess is formed.

Images