JP2008025667A - Rotor for disc brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotor for a disc brake allowing assembly and disassembly between an inner rotor and an outer rotor to be easily and rapidly executed without using a special tool. <P>SOLUTION: This rotor 10 for a disc brake employs a structure fastening the inner rotor 20 to the outer rotor 40 through a plurality of fastening parts 32 and 50 respectively arranged at positions where the outer periphery of the inner rotor 20 faces the inner periphery of the outer rotor 40. The fastening members 32 and 50 have projecting parts transmitting torque added at least to the inner rotor 20 to the outer rotor 40, and are provided with one filament material as a fastening member 60 penetrating the fastening members 32 and 50 in the circumferential direction of the rotor 10. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a disc brake rotor, and more particularly to a floating type rotor.

  There are roughly two types of disc brake rotors. There are a type called a solid type and a type called a floating type. The solid rotor is composed of a single steel plate, and does not require a process such as assembly when forming the rotor. Therefore, it is characterized by high productivity and low cost production. Have. On the other hand, the floating type rotor is composed of at least three types of constituent members such as an inner rotor and an outer rotor, and a fastening member that fastens the inner rotor and the outer rotor. Floating type rotors can be reduced in weight by changing the constituent material of the inner rotor and outer rotor, have good heat dissipation, can suppress distortion generated in the rotor during braking, and have floating characteristics Therefore, it has characteristics such as good compatibility with the pad during braking, and is excellent in performance as a disc brake rotor.

  At present, in consideration of the characteristics of each type as described above, a floating type brake system is increasingly adopted as a brake system giving priority to performance, and various improvements have been added.

For example, a disc brake rotor disclosed in Patent Document 1 employs a configuration in which an inner rotor and an outer rotor are fastened by a pin called a floating pin. Patent Document 1 is characterized in that the configuration of the washer that presses the disc spring for preventing rattling between the inner rotor and the outer rotor, and the arrangement of the disc spring itself are changed. On the other hand, the disc brake rotor disclosed in Patent Document 2 employs a configuration in which an inner rotor and an outer rotor are fastened using a circular can-shaped spring called a ring spring. Here, the configuration using the ring spring has an advantage that the number of parts can be reduced compared to the configuration using the floating pin, and the rotor can be assembled quickly.
Japanese Patent No. 2568526 JP 2003-343619 A

  All of the disk brake rotors disclosed in Patent Documents 1 and 2 are premised on that a sufficient and sufficient tightening property is required to fasten the inner rotor and the outer rotor. For this reason, when assembling the rotor, a jig for crimping the floating pin and a jig for fitting the ring spring into a predetermined position are necessary. Maintenance of the rotor itself such as disassembly and assembly, and replacement of damaged parts It was not considered. That is, when the outer rotor is worn, it has been customary to replace the entire rotor even when the inner rotor is not damaged.

  By the way, disc brakes are currently used in various moving objects, and in addition to conventional automobiles and motorcycles, they are also used in bicycles. In such moving bodies, the inner rotor and outer rotor are assembled and disassembled from the viewpoint of switching the braking performance according to the usage environment and reducing the cost of replacement parts by improving the exchangeability of single consumable parts. Some disc brake rotors are desired which can be easily performed.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to solve the above-described problems and to provide a disc brake rotor that can easily and quickly assemble and disassemble an inner rotor and an outer rotor without using a special jig. To do.

  In order to fix the inner rotor and the outer rotor, it is only necessary to suppress circumferential movement and axial movement. Therefore, the disc brake rotor according to the present invention for achieving the above object includes the inner rotor and the outer rotor via a plurality of fastening portions respectively provided at positions facing the outer periphery of the inner rotor and the inner periphery of the outer rotor. The disc brake rotor is configured to fasten the fastening portion, and the fastening portion has a convex portion that transmits at least the rotational force applied to the inner rotor to the outer rotor, and the linear portion penetrates the fastening portion in the circumferential direction of the rotor. It is characterized by having materials.

  In the disc brake rotor having the above-described configuration, the convex portion is a fitting structure including a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor, Among the fastening portions, the inner rotor side convex portion is formed with a through-hole along the circumferential direction of the rotor, and the outer rotor side convex portion is cut with reference to different main surfaces with respect to the pair of convex portions. It is preferable that a notch or a groove is formed so as to be positioned on an extension line of the through hole, and the linear member is configured to penetrate the through hole and the notch or the groove.

  Further, in the disc brake rotor having the above-described configuration, the convex portion has a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor, and the fastening portion Forms a through hole penetrating the inner rotor side convex portion and the outer rotor side convex portion along the circumferential direction of the rotor, and the linear member is a through hole formed in both convex portions of the inner rotor and the outer rotor. It is good also as a structure which penetrates.

  Further, in the disc brake rotor having the above-described configuration, the convex portion has a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor, and the fastening portion Among them, the outer rotor side convex portion is formed with a through hole that continuously penetrates the pair of convex portions along the circumferential direction of the rotor, and the inner rotor side convex portion is formed adjacent to the inner rotor side convex portion. It is good also as a structure which forms the notch or groove | channel on the basis of a different surface from so that it may be located on the extension line | wire of the said through-hole, and the said line material penetrates the said through-hole and the said notch or the said groove | channel.

  Similarly, in the disc brake rotor having the above-described configuration, the convex portion has a fitting structure including a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor, and the fastening is performed. The inner rotor-side convex portion and the outer rotor-side convex portion constituting the portion are formed with notches or grooves based on main surfaces on different sides, and the inner rotor-side convex portion and the outer rotor constituting the adjacent fastening portion The side projection has a configuration in which a reference surface that forms the notch or groove is reversed, and the linear member includes notches or grooves formed in the inner rotor side convex portion and the outer rotor side convex portion of the plurality of fastening portions. It is good also as a structure penetrated continuously.

  Furthermore, in the disc brake rotor having the above-described configuration, the convex portion has a fitting structure including a convex portion formed on the outer rotor and a pair of convex portions formed on the inner rotor, Among them, a pair of convex portions formed on the inner rotor side are respectively formed with through holes along the circumferential direction of the rotor, and the outer rotor side convex portion has different main surfaces with respect to one convex portion. A plurality of reference cutouts or grooves may be continuously formed so as to be positioned on an extension line of the through hole, and the linear member may be configured to penetrate the through hole and the cutout or the groove.

  Further, in the disc brake rotor having the above-described features, a thin portion thinner than the thickness of the inner rotor-side convex body is formed on the contact surface of the inner rotor-side convex portion of the fastening portion with the outer rotor-side convex portion. A configuration is good.

In the disc brake rotor having the above-described configuration, it is preferable that the wire rod is a single member that continuously penetrates all of a plurality of fastening portions provided in the inner rotor and the outer rotor in the circumferential direction.
Furthermore, when the disc brake rotor is configured as described above, it is desirable that the ends of the wire rods arranged through the fastening portion be fastened together.

  In the case of the disc brake rotor having the above-described characteristics, the assembly and disassembly of the inner rotor and the outer rotor can be performed only by inserting / removing the wire rod that penetrates the fastening portion in the circumferential direction. For this reason, the assembly and disassembly of the inner rotor and the outer rotor can be performed easily and quickly without using a special jig.

  Further, by forming a thin wall portion on the contact surface of the inner rotor side convex portion of the fastening portion with the outer rotor side convex portion, the wear of the contact surface reaches the entire contact surface. For this reason, even when the contact surface of the inner rotor is worn, there is no step on the contact surface, and the rotational force can be reliably transmitted to the outer rotor.

  In addition, when the wire material is a single member, the number of members constituting the rotor can be reduced as compared with the case where a fastening member (wire material) is provided for each fastening portion. For this reason, it becomes possible to assemble and disassemble the inner rotor and outer rotor more simply and quickly.

  Furthermore, since it was set as the structure which fastens the edge parts (front-end | tip and rear-end | tip) of the filament material comprised by the said one member, while being able to prevent the removal of a filament material, the front-end | tips are axial directions. Interference with an adjacent member due to shifting to can be avoided. Furthermore, since it is possible to effectively prevent omission and interference, it is possible to use in a high speed range.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of a disc brake rotor according to the present invention will be described below in detail with reference to the drawings. In addition, embodiment shown below is only some embodiment which concerns on this invention, and the technical scope of this invention is not restrained only by the following embodiment.

  First, a first embodiment of the disc brake rotor according to the present invention will be described with reference to FIGS. 1 is a diagram showing the overall configuration of the rotor according to the present embodiment, FIGS. 2 to 4 are diagrams showing individual components of the rotor, and FIG. 5 is a partially enlarged perspective view when the rotor is assembled. is there. The rotor 10 according to this embodiment includes an inner rotor 20, an outer rotor 40, and a fastening member 60 that fastens the inner rotor 20 and the outer rotor 40. The rotor 10 according to the present embodiment is assumed to be attached to a two-wheeled vehicle, but may be adapted as a disc brake rotor for other moving bodies.

  The inner rotor 20 adopts the configuration shown in FIG. 2A is a left side view of the inner rotor, FIG. 2B is a front view of the inner rotor, and FIG. 2C is a cross-sectional view taken along line AA in FIG. 2B. The inner rotor 20 is configured by machining a single plate material into a desired shape. As the constituent member, it is economical to use aluminum or an alloy mainly composed of aluminum, but other members may be used as long as they are lightweight and highly rigid.

  A center hole 22 through which a rotating shaft (not shown) for rotating the wheel of the moving body is inserted is provided at the center of the inner rotor 20, and an inner rotor is provided around the center hole 22 such as a wheel hub constituting the wheel. Bolt holes 24 for fixing 20 are provided. In the inner rotor 20 of the present embodiment, a plurality of (seven in this embodiment) main spokes 26, sub-spokes 28, and beams 30 are provided on the outer periphery of the bolt holes 24. The main spokes 26 and the sub spokes 28 are both arranged radially from the outer periphery of the center hole 22. However, since the sub spokes 28 are arranged with a lead angle with respect to the center hole 22, A configuration intersecting with the spokes 26 is adopted. Here, since the main spoke 26 and the sub-spoke 28 are formed on the same plane, the sub-spoke 28 functions as a side of the main spoke 26. By adopting such a configuration, it is possible to distribute the force generated during braking to the sub-spoke 28 side, and it is possible to prevent a situation in which the main spoke 26 is deformed by a force in the rotation direction.

  Further, in the inner rotor 20 of the present embodiment, the sub-spoke 28 is configured to be narrower than the main spoke 26 in order to reduce the weight. The main spoke 26 is formed so that the thickness of the central portion 26a is reduced and the cross-sectional structure in the radial direction is H-shaped, and it is possible to achieve both weight reduction and retention of rigidity against bending. It is configured. The beam 30 is disposed on the front end side of the main spoke 26 and connects the adjacent main spokes 26 to each other so as to improve the rigidity against the force acting in the rotation direction.

  Further, a fastening portion 32 that is a convex portion for fastening with the outer rotor 40 is provided at the distal end portion of the main spoke 26 and on the outer peripheral side of the beam 30. A through hole 34 for inserting a fastening member 60, which will be described in detail later, is formed on the side surface of the fastening portion 32. That is, the through hole 34 is provided along the circumferential direction of the rotor (including the tangential direction). A protrusion 36 is formed on the side surface of the main spoke 26 opposite to the side on which the sub-spoke 28 is disposed. By forming the projecting portion 36, it becomes possible to receive the impact and friction generated during braking by the projecting portion 36, and it is possible to prevent the main spoke 26 body from being deformed or worn.

  The protrusion 36 is formed thinner than the entire inner rotor 20 or the thickness of the fastening portion 32 main body. By adopting such a configuration, there is play in the axial direction (insertion direction of the rotating shaft inserted through the center hole 22) in the fastening of the inner rotor 20 and the outer rotor 40 (when the floating characteristics are improved). In addition, the protrusion 36 that bears the contact surface with the outer rotor 40 has its entire side surface in contact with the outer rotor 40. For this reason, even if the protrusion 36 is deformed or worn due to impact or friction during braking, the entire protrusion 36 is uniformly formed without causing a step in the deformed portion or the worn portion. It will be worn or deformed. In addition, it is good to form the notch 38 in the front-end | tip part of the main spoke 26, or to chamfer. This is because by performing such processing, interference with the fastening portion 50 in the outer rotor 40 can be prevented.

  Next, the outer rotor 40 will be described with reference to FIG. The outer rotor 40 of the present embodiment is configured by a plate-like member integrally formed with a sliding portion 42 formed in a ring shape and a fastening portion 50 for fastening the inner rotor 20. Stainless steel is often used as a constituent member, but members such as ceramic and carbon may be used. A plurality of through holes 44 arranged regularly or irregularly are provided on the surface of the sliding portion 42. The through holes 44 have functions such as heat radiation generated in the outer rotor 40 during braking, weight reduction, and suppression of distortion generated on the surface of the sliding portion 42 due to thermal expansion.

  The number of fastening portions 50 is the same as the number of main spokes 26 in the inner rotor 20 described above (seven in this embodiment), and is provided on the inner peripheral side of the sliding portion 42. The fastening part 50 is constituted by a pair of convex parts (anchors) arranged at an interval in which the fastening part 32 of the main spoke 26 formed on the inner rotor 20 can be inserted. The anchor of this embodiment can be classified into a main anchor 48 and a sub-anchor 46.

  The main anchor 48 is an anchor that receives a force transmitted by the protrusion 36 formed on the fastening portion 32 of the inner rotor 20, and the sub-anchor 46 is an anchor that receives a force applied in the opposite direction. Since the rotor 10 according to the present embodiment is assumed to be attached to a two-wheeled vehicle, a large force is applied during braking in the traveling direction. For this reason, the width of the main anchor 48 that receives the rotational force directed in the traveling direction is made wider than the width of the sub-anchor 46 so that it can withstand even when a large force is applied to the anchor surface.

  Notches 48 a and 46 a are formed at the tip of the main anchor 48 and the tip of the sub-anchor 46 so as to reduce the thickness of each anchor. The notch portion 48a of the main anchor 48 and the notch portion 46a of the sub-anchor 46 are different from each other as a reference surface when forming the notch portion. That is, if the reference surface of the notch 48a provided in the main anchor 48 is one surface of the outer rotor 40, the reference surface of the notch 46a provided in the sub-anchor 46 is the other surface. With such a configuration, the processed surfaces of the notches 48 a and 46 a provided in the main anchor 48 and the sub-anchor 46 are alternately provided in the axial direction of the rotor 10.

  The notches 48a and 46a are positioned on the extension line of the through hole 34 when the fastening portion 32 of the inner rotor 20 is fitted between the main anchor 48 and the sub-anchor 46 (including loose fitting). To be provided. For this reason, a gap of about the thickness of the fastening member 60 described in detail later is provided between the processed surface of the cutout portion 48a of the main anchor 48 and the processed surface of the cutout portion 46a of the sub-anchor 46. .

  Next, the fastening member 60 will be described with reference to FIG. The fastening member 60 in the present embodiment is a single filament material formed in a ring shape as shown in FIG. By using the fastening member 60 as one wire rod, the number of parts constituting the rotor 10 can be reduced, and assembling and disassembling workability is improved. As a constituent member of the fastening member 60, stainless steel similar to the outer rotor 40 can be used. Moreover, you may employ | adopt the spring member etc. which can be elastically deformed like a piano wire instead of stainless steel. Further, a knurling process may be applied to the outer periphery of the fastening member 60, which is a wire rod, to play a role of anti-slip. By setting it as such a structure, the mounting | wearing ease of the fastening member 60 can be improved.

  Next, a procedure for assembling the rotor 10 using the inner rotor 20, the outer rotor 40, and the fastening member 60 configured as described above will be described. First, the fastening portion 32 of the inner rotor 20 is fitted between the main anchor 48 and the sub-anchor 46 in the fastening portion 50 of the outer rotor 40. Next, both end portions 60a and 60b of the wire rod constituting the fastening member 60 are relatively shifted, and either one of the end portions 60a (60b) is connected to the fastening portion 32 of the inner rotor 20 and the fastening portion 50 of the outer rotor 40. Insert between them. Insertion of the fastening member 60 into the fastening portions 32, 50 is continuously performed with respect to the plurality of fastening portions 32, 50, and the insertion of the fastening member 60 into all of the fastening portions 32, 50 is completed. Fastening with the outer rotor 40 is completed.

  When inserting the fastening member 60 into the fastening portions 32 and 50 from the main anchor 48 side, as shown in FIG. 5, the fastening member 60 passed through the notch 48 a of the main anchor 48 in the outer rotor 40 is used as the inner rotor. The through holes 34 formed in the 20 fastening portions 32 are inserted. The fastening member 60 inserted through the through-hole 34 passes over the notch (the back side in the drawing) 46a of the sub-anchor 46 of the outer rotor 40 and passes through the fastening portions 32 and 50. As shown in FIG. 5, the fastening portion 50 employs a configuration in which the fastening member 60 is sandwiched between the cutout portion 48 a of the main anchor 48 and the cutout portion 46 a of the sub-anchor 46 formed by different reference surfaces. For this reason, it is possible to prevent the inner rotor 20 and the outer rotor 40 in which the fastening member 60 has been inserted into the through hole 34 from being displaced in the axial direction of the rotor 10.

  In the rotor 10 assembled as shown in FIG. 1A, a pipe member 62 is disposed between the distal ends of the fastening members 60 as shown in FIG. 1B, and the intermediate portion thereof is crimped. It is possible to prevent the fastening member 60 from coming off. When disassembling the inner rotor 20 and the outer rotor 40, either the pipe member 62 or the fastening member 60 is cut, the end of the fastening member 60 is relatively displaced, and the fastening member 60 is fastened to the fastening portions 32, 50. Just pull out from.

  According to the rotor 10 having the above-described configuration, the assembly and disassembly of the inner rotor 20 and the outer rotor 40 can be performed only by inserting and removing the fastening member 60 that is a linear member. Therefore, it becomes possible to carry out simply and quickly without using a special jig. For this reason, it is possible to replace only the outer rotor 40 having a large wear rate due to sliding as a consumable part, and the inner rotor 20 can be reused. Furthermore, since the inner rotor 20 and the outer rotor 40 can be disassembled and assembled easily and quickly, an appropriate outer rotor 40 can be selectively assembled according to the use environment, weather, and the like to obtain a desired braking performance. Is possible.

  In addition, in this embodiment, the crimping by the pipe member 62 was illustrated as the front end process of the fastening member 60. However, as long as the fastening member 60 can be prevented from coming off or falling off due to the displacement of the end portions 60a and 60b. Can be changed as appropriate. For example, the configuration shown in FIGS. 6 and 7 may be used.

  The form shown in FIG. 6 is a joint portion having a male screw 64 formed at one end (for example, 60b) of the fastening member 60 and a female screw that is screwed with the male screw 64 at the other end (for example, 60a). 66 is provided. Since only the joint portion 66 is configured to be rotatable, the end portions 60a and 60b of the fastening member 60 can be joined together. In such a configuration, there is no need to cut the fastening member 60 when the rotor 10 is disassembled, and the fastening member 60 can be reused.

  In the form shown in FIG. 7, a cover portion 68 that prevents the other end portion (for example, 60 b) from shifting in the axial direction is attached to one end portion (for example, 60 a) of the fastening member 60. With such a configuration, when the inner rotor 20 and the outer rotor 40 are assembled and disassembled, the end portions 60a and 60b need only be slightly shifted in the circumferential direction. In addition, as an edge part process of the fastening member 60, the edge part of a filament may be bent in the radial direction of a rotor.

  In the present embodiment, in order to increase the ease of assembling the outer rotor 40 to the inner rotor 20, a through hole 34 is formed in the fastening portion 32 of the inner rotor 20, and a main anchor 48 that constitutes the fastening portion 50 of the outer rotor 40, The sub-anchor 46 is formed with notches 48a and 46a each having a machining surface facing each other. However, the rotor 10 according to the present embodiment includes one in which through holes are formed instead of the notches 48a and 46a formed in the main anchor 48 and the sub-anchor 46 constituting the fastening portion 50 in the outer rotor 40.

  Although not shown, when through holes are provided in the fastening portions 32 and 50 of the inner rotor 20 and the outer rotor 40, it is preferable to taper the openings of the through holes. By setting it as such a structure, a taper part becomes a guide and it becomes possible to guide | fasten the fastening member 60 to a through-hole, and the assembly | attachment ease of the fastening member 60 will improve.

Further, since the inner rotor 20 and the outer rotor 40 are fastened by a single wire rod, the outer rotor 40 is automatically centered with respect to the inner rotor 20 when the rotor 10 rotates.
Further, in the rotor 10 according to the present embodiment, the fastening member 60 used for fastening the inner rotor 20 and the outer rotor 40 is only the wire material, so that the floating characteristics of the outer rotor 40 can be improved, and braking is performed. Familiarity with the pad at the time will improve. Furthermore, since the floating characteristics are high, the drag torque can be kept low even when the outer rotor 40 is shaken or warped.

  Further, the rotor according to the present embodiment may be configured as shown in FIGS. Specifically, the inner rotor 20 or the outer rotor 40 constituting the rotor is provided with a tab for protecting the wire material that is the fastening member 60. 8 shows an example of a form in which a tab 30a is provided on the inner rotor 20, and FIG. 9 is a view showing an example of a form in which a tab 42a is provided on the outer rotor 40. 8 and 9, respectively, (A) is a front view of the rotor, and (B) is a view showing an AA cross section in FIG. 8 (A). Hereinafter, the detailed configuration will be described with reference to the drawings.

  First, an example of a form in which the tab 30a is provided on the inner rotor 20 will be described with reference to FIG. When providing the tab 30a in the inner rotor 20, it is desirable to provide in the beam 30 which connects the adjacent main spokes 26. This is because by providing the tab 30a on the beam 30, in addition to the effect of protecting the fastening member 60, the effect of increasing the rigidity of the beam 30 can also be obtained. As shown in FIG. 8B, the portion constituting the tab 30a is formed to be thinner than the thickness of the portion constituting the beam 30, so that the linear member which is the fastening member 60 on the back side of the tab 30a forming portion. It is possible to arrange.

  By providing such a tab 30 a on the inner rotor 20, it is possible to prevent the fastening member 60 from being damaged even when scattered objects such as stepping stones collide with the rotor 10 from the tab 30 a formation surface side. it can. Further, even when the vehicle itself such as a two-wheeled vehicle falls, it is possible to prevent the projections present on the ground surface from coming into direct contact with the fastening member 60 and the fastening member 60 from being deformed or damaged. it can. Furthermore, even when stress is applied to the fastening member 60 from the side opposite to the surface on which the tab 30a is formed, that is, the fastening member 60 placement surface, the tab 30a serves as a support, and the fastening member It is possible to prevent the 60 from being greatly deformed.

  Next, an example of a form in which the tab 42a is provided on the outer rotor 40 will be described with reference to FIG. When the tab 42 a is provided on the outer rotor 40, it is disposed between the adjacent fastening portions 50. As shown in FIG. 9B, the portion constituting the tab 42a is formed to be thinner than the thickness of the portion constituting the sliding portion 42, so that the line which is the fastening member 60 on the back side of the tab 42a forming portion. It is possible to place strips. Thus, even when the tab 42a is provided on the outer rotor 40, the same effect as that obtained when the tab 42a is provided on the inner rotor 20 as described above can be obtained. In addition, in FIG. 9, a recessed part is provided between the tab 42a and the main anchor 48 which comprises the fastening part 50, and between the tab 42a and the sub anchor 46 which comprises the fastening part 50, and the component division of each part is easy to understand. Indicated. However, even when the concave portion is eliminated and the tab 42a and the main anchor 48, and the tab 42a and the sub-anchor 46 are continuously arranged, it can be regarded as a part of this embodiment.

  As described above, when the tab 30a is disposed on the inner rotor 20 and when the tab 42a is disposed on the outer rotor 40, advantages in terms of safety and weight can be obtained in the following points, respectively. . For example, in the case where the tab 30 a is disposed on the inner rotor 20, the constituent members of the inner rotor 20 are generally lighter than the constituent members of the outer rotor 40. For this reason, even when the size of the tab 30a is somewhat increased to ensure safety, the influence can be reduced in terms of weight.

  On the other hand, the constituent members of the outer rotor 40 are generally more rigid than the constituent members of the inner rotor 20. Therefore, when the tab 42a is provided on the outer rotor 40, the same strength can be maintained even when the thickness of the tab 42a is reduced compared with the case where the tab 30a is provided on the inner rotor 20. The advantage in terms can be obtained.

  From the viewpoint of protection, that is, safety, the size of the tab should be as large as possible or thick. On the other hand, from the viewpoint of weight reduction, it is better to make the tab the minimum necessary size and to make it thin. From such a viewpoint and the viewpoint of the strength of the tab, the size and strength of the tab may be appropriately determined in consideration of aspects such as safety and weight.

  Further, in the above embodiment, the configuration in which the tabs are arranged on the basis of either one of the surfaces is shown in the figure, whether the tab 30a is provided on the inner rotor 20 or the tab 42a is provided on the outer rotor 40. However, the arrangement of the tabs may be alternately provided by reversing the reference plane between adjacent tabs. This is because such a configuration improves the balance between the front and back surfaces of the rotor 10.

  Furthermore, in the above-described embodiment, the configuration in which the tab is provided in only one of the inner rotor 20 and the outer rotor 40 has been described. According to such a configuration, the fastening member 60 can prevent the scattered objects and projections from coming into contact with both side surfaces, so that safety is improved.

  Next, a second embodiment of the disc brake rotor according to the present invention will be described with reference to FIG. Similarly to the rotor 10 according to the first embodiment, the rotor according to the present embodiment is basically composed of an inner rotor, an outer rotor, and a fastening member, and most of the configuration is the rotor 10 according to the first embodiment. The same shall apply. Accordingly, parts having the same function are denoted by reference numerals obtained by adding 100 to the reference numerals in FIG. 1 and detailed description thereof will be omitted.

  The rotor 110 according to the present embodiment is excellent in application when the number of main spokes 126 in the inner rotor 120 is an even number (six in the present embodiment). The difference from the rotor 10 according to the first embodiment is the configuration of the fastening portion 150 in the outer rotor 140.

  Specifically, there are the following structural differences. That is, in the outer rotor 40 according to the first embodiment, the reference surfaces of the notches 48 a and 46 a formed in the main anchor 48 and the sub-anchor 46 constituting one fastening portion 50 are opposite to the front and back of the outer rotor 40. It was. On the other hand, in the outer rotor 140 of this embodiment, the reference surfaces of the notches 148a and 146a formed in the main anchor 148 and the sub-anchor 146 constituting one fastening portion 150 are the same surface, and the adjacent fastening portions 150 are adjacent to each other. The reference planes of the notches 148a and 146a formed in the anchors (main anchor 148 and sub-anchor 146) are reversed.

  Even in such a configuration, the fastening member 160 can be sandwiched between the anchors of the adjacent fastening portions 150 in the axial direction. For this reason, when four or more fastening portions 150 are provided, axial displacement between the inner rotor 120 and the outer rotor 140 can be suppressed, and the same effect as the rotor 10 according to the first embodiment can be obtained. Is possible.

  Next, a third embodiment of the disc brake rotor of the present invention will be described with reference to FIG. Similarly to the rotor 10 according to the first embodiment, the rotor according to the present embodiment is basically composed of an inner rotor, an outer rotor, and a fastening member, and most of the configuration is the rotor 10 according to the first embodiment. The same shall apply. Accordingly, parts having the same function are denoted by reference numerals obtained by adding 200 to the reference numerals in FIG. 1 and detailed description thereof will be omitted. The rotor 210 according to the present embodiment is also applied when the number of main spokes 226 in the inner rotor 220 is an even number (six in this embodiment), similarly to the rotor 110 according to the second embodiment. Is excellent.

The difference between the rotor 210 according to this embodiment and the rotors 10 and 110 according to the first and second embodiments is the configuration of the fastening portion 232 in the inner rotor 220. The inner rotor 220 of the present embodiment is characterized in that a cutout portion 232a is provided instead of the through holes 34 and 134 provided in the fastening portion 232 of the main spoke 226 in the first and second embodiments. To do. The processed surface of the notch 232a is set upside down with respect to the reference surface at the time of processing so that the main spokes 226 are opposite to each other. With such a configuration, the fastening member 260 can be sandwiched between the fastening portions 232 of the adjacent main spokes 226. Further, according to such a configuration of the fastening portion of the inner rotor 220, processing from the side surface of the inner rotor 220 becomes unnecessary, and productivity is improved.
In the form shown in FIG. 11, the main anchor 248 and the sub-anchor 246 constituting the fastening portion 250 of the outer rotor 240 are provided with through holes 249 and 247 instead of the notches.

  Even with such a configuration, the inner rotor 220 and the outer rotor 240 can be prevented from shifting in the axial direction, similarly to the rotors 10 and 110 according to the first and second embodiments. In the form shown in FIG. 11, the main anchor 248 and the sub-anchor 246 that constitute the fastening portion 250 of the outer rotor 240 are shown to be provided with through holes 249 and 247, but instead of the through holes 249 and 247, Even when the cutout portions 48a and 46a (148a and 146a) as shown in the outer rotors 40 and 140 of FIG. 1 or FIG. 10 are provided, the rotor 210 according to the present embodiment can be considered. . In the case where a notch portion having a configuration like the outer rotor 140 shown in FIG. 10 is provided, the processed surface of the notch portion formed in the fastening portion 232 in the inner rotor 220 and the fastening portion 250 in the outer rotor 240 forming the fitting structure. Are configured in opposite directions.

  Next, a fourth embodiment according to the disk brake rotor of the present invention will be described with reference to FIG. Similarly to the rotor 10 according to the first embodiment, the rotor according to the present embodiment is basically composed of an inner rotor, an outer rotor, and a fastening member, and most of the configuration is the rotor 10 according to the first embodiment. The same shall apply. Accordingly, parts having the same functions are denoted by reference numerals obtained by adding 300 to the reference numerals in FIG. 1, and detailed description thereof will be omitted.

  The difference between the rotor 310 according to this embodiment and the rotor according to the first to third embodiments is in the configuration of the fastening portions 332 and 350. That is, in the above three embodiments, each of the fastening portions is configured to include an anchor including a convex portion on the inner rotor side and a pair of convex portions on the outer rotor side. On the other hand, in the rotor 310 according to the present embodiment, a pair of protrusions formed so as to form a protrusion that is the fastening portion 50 on the outer rotor 340 side and sandwich the protrusion that is the fastening portion 350 on the inner rotor 320 side. It is set as the structure provided with the anchor 332a, 332b which consists of a part.

  By setting it as such a structure, the volume by the side of the inner rotor 320 comprised by the lightweight member can be increased, and the volume by the side of the outer rotor 340 comprised by the weight member can be reduced. For this reason, weight reduction as the rotor 310 whole can be achieved.

  When the configuration of the fastening portions 332 and 350 is as shown in FIG. 12, the fastening portion 350 on the outer rotor 340 side has a plurality of notches 350a, 350b is provided, and it is good to insert the wire material which is the fastening member 360 between the processed surfaces in this notch 350a, 350b. This is because, by adopting such a configuration, it is possible to achieve the same effect as the support of the fastening member 60 by the main anchor 48 and the sub-anchor 46 in the first embodiment.

Other configurations are the same as those of any of the rotors according to the first to third embodiments described above. Even a rotor having such a configuration can achieve the same effects as any of the rotors according to the above embodiments.
In the above-described embodiments, it has been shown that a through hole or a notch is provided in the fastening portion. However, a groove that can guide the fastening member may be provided instead of the notch or the through hole. . For example, in the first embodiment, when a groove is provided in the fastening portion 50 (main anchor 48, sub-anchor 46) of the outer rotor 40 in place of the notches 48a and 46a, as shown in FIG. 14 may be provided with grooves 48b and 46b, or may be provided with grooves 48c (46c) in the axial direction (thickness direction) of the rotor 10, as shown in FIG. As the characteristics of the groove in each configuration, the form shown in FIG. 13 is approximated when a through hole is provided, and the form shown in FIG. 14 is approximated when a notch is provided. Of course, even when a groove is provided in the fastening portion of the inner rotor, two types of grooves can be provided as in the case of the outer rotor. In the case of the inner rotor, when the radial groove is formed, the opening of the groove is positioned on the outer peripheral side of the inner rotor.

  Further, in the rotor 10 according to the first embodiment, when the notches 48a and 46a provided in the main anchor 48 and the sub-anchor 46 constituting the fastening portion 50 of the outer rotor 40 are used as through holes, the fastening member 60 is used. It is good also as a structure which divides | segments for every fastening part.

It is a figure which shows the structure of the rotor for disc brakes concerning 1st Embodiment. It is a figure which shows the structure of the inner rotor of the rotor for disc brakes which concerns on 1st Embodiment. It is a figure which shows the structure of the outer rotor of the rotor for disc brakes which concerns on 1st Embodiment. It is a figure which shows the structure of the fastening member of the rotor for disc brakes which concerns on 1st Embodiment. It is a partial expansion perspective view which shows the fastening part of the rotor for disc brakes concerning 1st Embodiment. It is a figure which shows the example of the terminal process in a fastening member. It is a figure which shows the other example of the terminal process in a fastening member. It is a modification of the disc brake rotor according to the first embodiment and is a view showing a form in which a tab is provided on the inner rotor side. It is a modification of the disc brake rotor according to the first embodiment, and is a view showing a form in which a tab is provided on the outer rotor side. It is a figure which shows the structure of the rotor for disc brakes concerning 2nd Embodiment. It is a figure which shows the structure of the rotor for disc brakes concerning 3rd Embodiment. It is a figure which shows the structure of the rotor for disc brakes concerning 4th Embodiment. It is a figure which shows the example at the time of providing a groove | channel in the radial direction of a rotor in the outer rotor side fastening part. It is a figure which shows the example at the time of providing a groove | channel in the thickness direction of a rotor in the outer rotor side fastening part.

Explanation of symbols

  10 ......... Rotor, 20 ......... Inner rotor, 22 ......... Center hole, 24 ......... Bolt hole, 26 ......... Main spoke, 28 ...... Sub-spoke, 30 ......... Beam, 32 ......... Fastening part 34 ......... Through hole 36 ......... Protrusion part 38 ......... Notch 40 ......... Outer rotor 42 ......... Sliding part 44 ......... Through hole 46 ......... Sub-anchor 46a ......... notch, 48 ......... main anchor, 48a ......... notch, 50 ......... fastener, 60 ... fastener, 60a, 60b ... end, 62 ... ... pipe members.

Claims (9)

A disc brake rotor for fastening the inner rotor and the outer rotor via a plurality of fastening portions respectively provided at positions opposed to the outer periphery of the inner rotor and the inner periphery of the outer rotor;
The fastening portion has at least a convex portion that transmits a rotational force applied to the inner rotor to the outer rotor,
A disc brake rotor comprising a wire rod that penetrates the fastening portion in a circumferential direction of the rotor. The convex portion is a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor,
Among the fastening parts, the inner rotor side convex part is formed with a through hole along the circumferential direction of the rotor, and the outer rotor side convex part is based on different main surfaces with respect to the pair of convex parts. Forming a notch or a groove so as to be located on an extension line of the through-hole,
The disk brake rotor according to claim 1, wherein the linear member is configured to penetrate the through hole and the notch or the groove. The convex portion is a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor,
The fastening portion is formed with a through hole penetrating the inner rotor side convex portion and the outer rotor side convex portion along the circumferential direction of the rotor,
2. The disc brake rotor according to claim 1, wherein the linear member is configured to penetrate through holes formed in both convex portions of the inner rotor and the outer rotor. The convex portion is a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor,
Among the fastening portions, the outer rotor side convex portion forms a through hole that continuously penetrates a pair of convex portions along the circumferential direction of the rotor,
The inner rotor side convex portion is formed so that a notch or a groove based on a surface different from the inner rotor side convex portion formed adjacent to the inner rotor side convex portion is positioned on the extension line of the through hole,
The disk brake rotor according to claim 1, wherein the linear member is configured to penetrate the through hole and the notch or the groove. The convex portion is a fitting structure constituted by a convex portion formed on the inner rotor and a pair of convex portions formed on the outer rotor,
The inner rotor side convex portion and the outer rotor side convex portion constituting the fastening portion are formed with notches or grooves based on main surfaces on different sides, and the inner rotor side convex portion constituting the adjacent fastening portion. And the outer rotor side convex portion is configured to reverse the reference surface forming the notch or groove,
2. The disc brake according to claim 1, wherein the wire rod is configured to continuously pass through notches or grooves formed in the inner rotor side convex portion and the outer rotor side convex portion of the plurality of fastening portions. Rotor. The protrusion is a fitting structure constituted by a protrusion formed on the outer rotor and a pair of protrusions formed on the inner rotor,
Among the fastening portions, a pair of convex portions formed on the inner rotor side are each formed with a through hole along the circumferential direction of the rotor, and the outer rotor side convex portion is mutually connected with respect to one convex portion. A plurality of notches or grooves based on different main surfaces are continuously formed so as to be located on an extension line of the through hole,
The disk brake rotor according to claim 1, wherein the linear member is configured to penetrate the through hole and the notch or the groove.   The thin part thinner than the wall thickness of an inner rotor side convex part main body was formed in the contact surface with the said outer rotor side convex part in the inner rotor side convex part of the said fastening part, The any one of Claim 2 thru | or 6 characterized by the above-mentioned. The rotor for disc brakes according to claim 1.   8. The wire rod according to claim 1, wherein the wire rod is a single member that continuously penetrates all of a plurality of fastening portions provided in the inner rotor and the outer rotor in a circumferential direction. Disc brake rotor as described in 1.   The disk brake rotor according to claim 8, wherein the ends of the wire rods arranged through the fastening portion are fastened to each other.

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