JP2012122598A - Disk brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk brake which can improve productivity.SOLUTION: A single torque receiving pin 27 which is arranged at a side of a trailing edge of a disk when a vehicle moves forward and extends in an axial direction of the disk over the disk 12 and in which a pair of friction pads 15 and 16 slides is provided at a carrier 13, and in the pair of friction pads 15 and 16, a through hole 115 through which the torque receiving pin 27 is inserted is formed at the disk rotation input side, an engaging section 122 which is engaged with a caliper is formed at a portion other than the through hole 115, and the single torque receiving pin 27 at the trailing side of the disk receives braking torque in a disk rotation direction at the pair of friction pads 15 and 16 during braking when the vehicle moves forward.

Description

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

  A disc brake for braking a vehicle is configured to bring a friction pad into contact with a disc rotating with a wheel by a caliper and perform braking by the frictional resistance. Among such disc brakes, there is a carrier that supports a caliper and receives torque generated in a friction pad during braking (see, for example, Patent Document 1).

Japanese Utility Model Publication No. 53-120052

  In the disc brake, processing and the like are troublesome, and improvement in productivity is demanded.

  An object of this invention is to provide the disc brake which can improve productivity.

  In order to achieve the above object, the present invention provides a torque receiver that is disposed on a carrier on a disk insertion side when the vehicle moves forward, extends in the disk axial direction across the disk, and a pair of friction pads slide. Pins are provided, and the pair of friction pads are configured such that insertion holes through which the torque receiving pins are inserted are formed on the respective disk insertion sides.

  According to the present invention, productivity can be improved.

It is a top view which shows the disc brake of 1st Embodiment which concerns on this invention. It is a front view which shows the disc brake of 1st Embodiment which concerns on this invention. 1 is a side sectional view showing a disc brake of a first embodiment according to the present invention. It is a rear view which shows the disc brake of 1st Embodiment which concerns on this invention. 1 is a plan view showing a disc brake carrier, a pair of friction pads, and a disc according to a first embodiment of the present invention. It is a front view showing a carrier of a disc brake of a 1st embodiment concerning the present invention, a pair of friction pads, and a disc. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a front view showing a carrier, a pad pin, a pair of friction pads and a disc of a disc brake according to a first embodiment of the present invention, and dimensions, forces, and directions of moments of each part. It is a front view which shows an example of the attachment state to the vehicle which shows the disc brake of 1st Embodiment which concerns on this invention. It is a front view which shows another example of the attachment state to the vehicle which shows the disc brake of 1st Embodiment which concerns on this invention. It is a top view which shows the disc brake of 2nd Embodiment which concerns on this invention. It is a front sectional view showing a disc brake of a second embodiment according to the present invention.

“First Embodiment”
A first embodiment according to the present invention will be described below with reference to FIGS.

  The disc brake of the first embodiment is a disc brake for vehicles, specifically for motorcycles. As shown in FIGS. 1 to 4, the disc brake 11 includes a carrier 13 fixed to the vehicle body, a caliper 14 straddling the disc 12 fixed to the wheel, a pair of friction pads 15 and 16, and a pad spring 17. 1 and 3 and a boot 19 shown in FIG. An arrow R shown in each figure indicates the rotation direction of the disk 12 when the vehicle is moving forward, and the following description will be made with the inlet side in this rotation direction as the disk inlet side and the outlet side as the disk outlet side. The axial direction of the disk 12 is the disk axial direction, the radial direction of the disk 12 is the disk radial direction, and the rotational direction of the disk 12 is the disk rotational direction or the disk circumferential direction.

  The disk 12 has a disk shape, and is provided on a wheel (not shown) of a vehicle that is a braking target of the disk brake 11 and rotates together with the wheel.

  The carrier 13 is shown in FIGS. 1 and 4, which are fixed to the mounting bracket 25, the guide pin 26 shown in FIG. 3 that is fixed to the mounting bracket 25, and the mounting bracket 25. And a torque receiving pin 27.

  As shown in FIG. 1, the mounting bracket 25 is disposed on the outer side (the side opposite to the wheel) that is one side of the disk 12 and is fixed to a non-rotating portion of the vehicle. As shown in FIGS. 2 and 4, the mounting bracket 25 includes a base portion 31 extending in the disc rotation direction, and a radial direction extending outward in the disc radial direction from the end portion of the base portion 31 on the disc insertion side. And an extending portion 32. The base portion 31 is formed with an attachment hole 33 at the end on the disk entry side and an attachment hole 34 on the disk delivery side, penetrating in the disk axial direction. In the mounting bracket 25, the carrier 13 is mounted on the vehicle with a mounting bolt (not shown) in which a fixing portion 35 around the mounting hole 33 and a fixing portion 36 around the mounting hole 34 are screwed into the mounting holes 33 and 34, respectively. Fixed to the non-rotating part.

  In the mounting bracket 25, a guide pin mounting hole 38 is formed at one position through the disk axial direction at an intermediate position of the base portion 31 in the disk rotation direction, in other words, between the mounting hole 33 and the mounting hole 34. ing. Further, the mounting bracket 25 is formed with a torque receiving pin mounting hole 39 shown in FIG. 4 at one end in the disk axial direction at the end of the radially extending portion 32 on the outer side in the disk radial direction. The center of the torque receiving pin mounting hole 39 is disposed outside the disk 12 in the disk radial direction. Further, the torque receiving pin mounting hole 39 is disposed on the outer side in the disk radial direction than the guide pin mounting hole 38 and on the disk insertion side.

  The mounting bracket 25 is formed, for example, by punching a metal plate by press molding, and the mounting holes 33 and 34, the guide pin mounting hole 38, and the torque receiving pin mounting hole 39 are cut into the mounting bracket 25. Etc. are formed. The mounting bracket 25 is not subjected to bending processing on the plate material, and has a constant thickness with no protrusions in the plate thickness direction.

  As shown in FIGS. 3 and 5, the guide pin 26 has, in order from one end in the axial direction, a small-diameter fixed shaft portion 42, an intermediate shaft portion 43 having a larger diameter than the fixed shaft portion 42, and a larger diameter than the intermediate shaft portion 43. The flange portion 44 and a guide shaft portion 45 having a smaller diameter than the intermediate shaft portion 43 are provided. The guide pin 26 is made of metal, and only one guide pin 26 is provided in the carrier 13.

  The fixed pin portion 42 is fitted and fixed to the guide pin mounting hole 38 of the mounting bracket 25 so that the guide pin 26 protrudes to the opposite side (outer side) from the disk 12 as a whole. In the state of being attached to the mounting bracket 25 as described above, the guide pin 26 protrudes from the mounting bracket 25 to the side opposite to the disk 12 along the disk axial direction.

  As shown in FIG. 5, the torque receiving pin 27 includes, in order from one end in the axial direction, a torque receiving shaft portion 48 having a circular cross section having a constant diameter, and a fixed shaft portion (fixing portion) 49 having a larger diameter than the torque receiving shaft portion 48. And an intermediate shaft portion 50 having a larger diameter than the fixed shaft portion 49, a flange portion 51 having a larger diameter than the intermediate shaft portion 50, and a guide shaft portion 52 having a smaller diameter than the fixed shaft portion 49. The torque receiving pin 27 is made of metal, and only one is provided in the carrier 13.

  The torque receiving pin 27 has a fixed shaft portion 49 fitted and fixed in the torque receiving pin mounting hole 39 of the mounting bracket 25. When the torque receiving pin 27 is attached to the mounting bracket 25 in this manner, the center of the torque receiving pin 27 is disposed radially outside of the disk 12, and one torque receiving shaft portion is aligned along the disk axial direction. The 48 side extends to the disk 12 side across the disk 12, and the other guide shaft portion 52 side extends to the opposite side of the disk 12. In other words, the torque receiving pin 27 extends from the mounting bracket 25 to the disk 12 side and both sides opposite to the disk 12, and from the outer side, which is one surface side of the disk 12, to the inner side, which is the other surface side of the disk 12. Extends beyond the disk 12. Depending on the formation position of the torque receiving pin mounting hole 39, the torque receiving pin 27 is arranged on the disk insertion side in the carrier 13, as shown in FIG. Has been placed.

  As shown in FIG. 1, the caliper 14 is slidable in the disk axial direction with respect to the carrier 13 by a guide shaft portion 52 of the torque receiving pin 27 and a guide shaft portion 45 of the guide pin 26 as shown in FIG. It is a so-called pin slide type caliper. As shown in FIG. 2, the caliper 14 includes a caliper body 55, two pistons 56 and 57, and a pad pin 58.

  The caliper body 55 is formed by being integrally formed by casting from an aluminum alloy or the like, and then being cut. As shown in FIG. 1 to FIG. 1 and a guide pin 26 shown in FIG. 3 are slidably attached. The caliper body 55 includes a cylinder portion 62 disposed on the outer side of the carrier 13, a bridge portion 63 extending from the outer side of the cylinder portion 62 in the disk radial direction to the inner side of the disk 12, and a bridge It has a claw portion 64 extending radially inward of the disk 12 so as to face the cylinder portion 62 from the inner end portion of the portion 63.

  As shown in FIG. 2, a sliding guide portion 66 is formed in the cylinder portion 62 so as to protrude inward in the radial direction of the disc from an intermediate position in the circumferential direction of the disc. A sliding guide 67 is formed so as to protrude to the turn-in side. A guide pin support hole 68 shown in FIG. 3 is formed in the sliding guide portion 66 so as to penetrate in the disk axial direction. A torque receiving pin support hole 69 shown in FIG. It is formed from the 12 side to the midway position in the disk axial direction.

As shown in FIG. 3, the above-described boot 18 is fitted in the guide pin support hole 68 of the cylinder portion 62, and the sliding guide portion 66 is guided by the guide shaft portion of the guide pin 26 via the boot 18. 45 is slidably supported. Further, as shown in FIG. 1, the guide shaft portion 52 of the torque receiving pin 27 is fitted into the torque receiving pin support hole 69 of the cylinder portion 62, and the sliding guide portion 67 is connected to the torque receiving pin 27. The guide shaft portion 52 is slidably supported.
Note that the sliding guide portion 66 and the sliding guide portion 67 perform sliding guidance by inserting the guide shaft portion 45 and the torque receiving pin 27 into the inside, but the present invention is not limited to this. The portion 66 and the sliding guide portion 67 may be formed in a pin shape so that a hole is provided in the center portion of the guide shaft portion 45 and the torque receiving pin 27 and inserted.

  Here, as shown in FIG. 3, the boot 18 is made of rubber, and includes a locking portion 72 locked to the intermediate shaft portion 43 and the flange portion 44 of the guide pin 26, a telescopic bellows portion 73, It has a cylindrical part 75 that is fitted in the guide pin support hole 68 and has a sliding hole 74 inside, and a lid part 76 that covers the opposite side of the guide shaft part 45 from the flange part 44. The boot 18 is held in the guide pin support hole 68 of the caliper 14 by the cylindrical portion 75, and can slide the guide shaft portion 45 of the guide pin 26 of the carrier 13 in the sliding hole 74 inside the cylindrical portion 75. To fit.

  The boot 19 shown in FIG. 1 is also made of rubber, and the locking portion 80 shown in FIG. 1 that is locked to the intermediate shaft portion 50 and the flange portion 51 of the torque receiving pin 27 shown in FIG. And a telescopic bellows portion 81 that covers the guide shaft portion 52 protruding from 69.

  As described above, the caliper body 55 is supported by the guide pins 26 and the torque receiving pins 27 provided on the carrier 13 so as to be slidable in the direction along the disk axial direction. In other words, the torque receiving pin 27 extends from a fixed shaft portion 49 that is a fixed portion to the carrier 16 in a direction away from the disk 12 in the disk axis direction, and is a portion of the guide shaft that slidably supports the caliper 14. Part 52.

  In the cylinder portion 62, two bottomed bores 87 and 88 are formed side by side in the disc rotation direction along the disc axial direction so as to open toward the claw portion 64 as shown in FIG. . A pipe connection hole 89 communicating with these is formed along the disk radial direction between the bore 87 on the disk introduction side and the bore 88 on the disk delivery side, and a brake (not shown) is formed in the pipe connection hole 89. Piping is connected. An air bleeding bleeder plug 90 communicating with the bore 88 is attached to the disk delivery side of the cylinder portion 62. As shown in FIG. 4, the claw portion 64 has recesses 91 and 92 for allowing a cutting tool to pass when the bores 87 and 88 are machined. It is formed on the inlet side and the disk outlet side.

  As shown in FIG. 1, on the bridge part 63 side in the disk axial direction of the cylinder part 62, a delivery side projecting part 95 projecting from the bridge part 63 is formed on the disk delivery side outside the disk radial direction. Also on the side of the bridge portion 63 in the disc axial direction of the claw portion 64, a delivery side projection 96 that projects from the bridge portion 63 on the disc delivery side on the outer side in the disc radial direction is formed.

  The pistons 56 and 57 are slidably fitted into the bores 87 and 88 of the cylinder portion 62 as shown in FIG. In this fitted state, the pistons 56 and 57 are arranged side by side with respect to the caliper body 55 in the disk rotation direction. The pistons 56 and 57 are made of metal.

  As shown in FIG. 1, the pad pin 58 is fitted into a through-hole extending in the disk axial direction provided in the delivery-side projection 95 and the delivery-side projection 96 of the caliper body 55. A guide shaft 101 having a circular cross section with a constant diameter is disposed between the delivery-side projection 95 and the delivery-side projection 96 in the combined state. The pad pin 58 is made of metal and extends along the disk axial direction, and the guide shaft portion 101 is disposed so as to straddle the disk 12 on the outer side in the disk radial direction than the disk 12 and on the disk delivery side from the bridge portion 63. ing. Here, a line connecting the center of the pad pin 58 and the center of the torque receiving pin 27 shown in FIG. 7 in a state where the caliper body 55 is supported by the carrier 13 so as to be slidable in the direction along the disk axial direction. The line connecting the center position of this line and the center of the disk 12 (hereinafter referred to as the disk center) is orthogonal.

  As shown in FIG. 1, the pair of friction pads 15 and 16 are disposed on both surfaces of the disk 12 and are supported by the torque receiving shaft portion 48 of the torque receiving pin 27 and the guide shaft portion 101 of the pad pin 58. is there. Specifically, the friction pad 15 is disposed on the outer side which is one surface side of the disk 12, and the friction pad 16 is disposed on the inner side which is the other surface side of the disk 12.

  As shown in FIG. 3, the outer friction pad 15 includes a friction material 106 that generates frictional resistance by contacting the disk 12, and a metal plate-like back metal 107 that holds the friction material 106. ing.

  As shown in FIG. 5, the back plate 107 of the friction pad 15 includes a main plate portion 108 to which the friction material 106 is fixed to the surface on the disk 12 side, and a main plate portion 108 on the outer side in the disk radial direction as shown in FIG. From the disk entry side, the end protrusion 109 projecting obliquely to the disk entry side and the disk radial direction outside, and the disk delivery side and the disk radial direction from the disk delivery side outside the disk radial direction of the main plate portion 108 It has the edge part protrusion part 110 which protrudes diagonally outside. Further, the back metal 107 of the friction pad 15 includes a protrusion 111 that protrudes radially outward from the end protrusion 109 side of the outer edge of the main plate 108 in the radial direction of the disk and an end protrusion of the outer edge of the main plate 108 in the radial direction of the disk. And a protrusion 112 protruding radially outward from the 110 side.

  A polygonal insertion hole 115 having rounded corners approximating a square shape is formed in the end protrusion 109 on the disk insertion side so as to penetrate in the disk axis direction. That is, in the friction pad 15, the insertion hole 115 is formed on the disk insertion side. The insertion hole 115 is at the center in the disk circumferential direction (the center in the left-right direction in the figure) on the inner side in the disk radial direction, along the disk axial direction, and the center of the friction material 106 (hereinafter referred to as the pad center) and the disk center. A plane portion 116 (the lower plane portion in FIG. 6) along the direction orthogonal to the connecting line, and a line at the center in the circumferential direction of the disc on the outer side in the disc radial direction, along the disc axial direction, and connecting the pad center and the disc center. A plane portion 117 (the plane portion on the upper side in FIG. 6) along the direction orthogonal to the plane, and a plane along the line in the disc radial direction on the disc entry side, along the disc axial direction, and along the line connecting the pad center and the disc center Portion 118 (the flat portion on the right side in FIG. 6) and the flat portion 119 (FIG. 6) along the disc axial direction at the disc delivery side and along the disc axial direction and along the line connecting the pad center and the disc center. And a left flat portion of) and. Then, the torque receiving shaft portion 48 of the torque receiving pin 27 is inserted into the insertion hole 115. At this time, the insertion holes 115 are circular torque receivers at the four flat portions 116 to 119. It can come into contact with the shaft portion 48.

  The end protrusion 110 is formed with a long engagement hole (engagement portion) 122 extending in the disk axial direction along the disk circumferential direction. That is, the engagement hole 122 is formed in the friction pad 15 on the disk delivery side, which is a part other than the insertion hole 115. The engagement hole 122 has a flat surface portion 123 (a flat surface portion on the lower side in FIG. 6) along the disk axial direction and along the direction perpendicular to the line connecting the pad center and the disk center. A flat portion 124 (the upper flat portion in FIG. 6) along the direction of the disk axis along the disk axis direction and perpendicular to the line connecting the pad center and the disk center, and the disk shaft on the disk entry side A curved surface portion 125 (a curved surface portion on the right side in FIG. 6) that forms a semicircle along the direction, and a curved surface portion 126 (a curved surface portion on the left side in FIG. 6) that forms a semicircular shape along the disk axial direction on the disk delivery side. ). Then, the guide shaft portion 101 of the pad pin 58 is inserted into the engagement hole 122, and at this time, the flat surface portion 123 and the surface portion 124 that is parallel to the flat portion 123 are circular in the circular pad pin 58. The shape can be brought into contact with the guide shaft portion 101. In addition, the engagement hole 122 is provided with a predetermined gap on both sides in the disk rotation direction so that the curved surface portions 125 and 126 do not contact the pad pin 58. It should be noted that this gap need only be provided at least on the disk entry side. In the state supported by the torque receiving pin 27 and the pad pin 58, the pair of friction pads 15 and 16 has a line connecting the center of the engagement hole 122 and the center of the insertion hole 115 connecting the center of the pad and the center of the disk. Along the direction orthogonal to

  Here, as shown in FIG. 7, the engagement hole 122 has a torque that is approximately twice the distance between the center of the torque receiving pin 27 and the center of the circumferential length of the friction pad 15 in the friction pad 15. It is formed at a position away from the center of the receiving pin 27. Specifically, the friction pad 15 has a center in the circumferential direction of the disk that is aligned with a center of a line segment connecting the insertion hole 115 and the engagement hole 122 in the circumferential direction of the disk.

  As described above, the outer friction pad 15 has the insertion hole 115 formed on the disk insertion side slidably supported by the torque receiving shaft portion 48 of the torque receiving pin 27 of the carrier 13, and the disk unwinding. The engagement hole 122 formed on the side is supported by the guide shaft portion 101 of the pad pin 58, and the torque receiving shaft portion 48 and the guide shaft portion 101 guide the sliding in the disk axis direction. The friction pad 15 comes into contact with the pad spring 17 shown in FIG. 3 at the protrusions 111 and 112, and is biased obliquely toward the inner side in the disk radial direction and the disk delivery side by the pad spring 17.

  The inner friction pad 16 forms a mirror surface with respect to the outer friction pad 15 via the disk 12.

  That is, the inner side friction pad 16 uses a back metal 107 common to the outer side friction pad 15, and the friction material 106 common to the outer side friction pad 15 is placed on the reverse side of the back metal 107. It is configured to be fixed. That is, the back metal 107 is a common component shared by the outer friction pad 15 and the inner friction pad 16.

  As a result, the back metal 107 of the friction pad 16 on the inner side is also fixed to the friction material 106 on the surface of the main plate portion 108 on the disk 12 side. As shown in FIG. An insertion hole 115 is formed in the end protruding portion 109 protruding to the side, an engagement hole 122 is formed in the end protruding portion 110 protruding from the main plate portion 108 to the disk delivery side, and radially outward from the main plate portion 108. Each of the protrusions 111 and 112 projecting from each other is formed.

  The inner friction pad 16 also receives the same torque receiving force as that for supporting the outer friction pad 15 so that the insertion hole 115 formed on the disk insertion side can come into contact with the flat portions 116 to 119. The circular torque receiving shaft portion 48 of the pin 27 is inserted, and can be brought into contact with the flat portions 123 and 124 in the engagement hole 122 formed on the disk delivery side which is a portion other than the insertion hole 115. Thus, the circular guide shaft portion 101 of the same pad pin 58 that supports the outer friction pad 15 is inserted while forming a predetermined gap on both sides of the disk rotation direction. In one torque receiving pin 27, a torque receiving shaft portion 48, which is a portion where the pair of friction pads 15, 16 slide, has a circular shape.

  Also in the friction pad 16, as shown in FIG. 7, the engagement hole 122 has a torque receiving pin that is approximately twice the distance between the center of the torque receiving pin 27 and the center of the circumferential length of the friction pad 16. 27 is formed at a position away from the center of 27. Specifically, the friction pad 16 has the center in the circumferential direction of the disk aligned with the center of the line segment connecting the insertion hole 115 and the engagement hole 122 in the circumferential direction of the disk.

  As described above, the inner friction pad 16 is also supported by the torque receiving shaft portion 48 of the torque receiving pin 27 of the carrier 13 so that the insertion hole 115 formed on the disk insertion side is slidable. The exit-side engagement hole 122 is supported by the guide shaft portion 101 of the pad pin 58, and the torque receiving pin 27 and the pad pin 58 guide the sliding in the disk axis direction. In addition, the back metal 107 of the inner friction pad 16 is also biased obliquely by the pad spring 17 toward the inner side in the disk radial direction and the disk delivery side by the pad spring 17.

  Further, the carrier 13 is provided with one torque receiving pin 27 on which the pair of friction pads 15 and 16 slide on the disk insertion side. The pair of friction pads 15 and 16 are provided with the respective disk rotations. An insertion hole 115 through which the torque receiving pin 27 is inserted is formed on the entry side, and an engagement hole 122 that is an engagement portion that engages with the caliper 14 is formed at a portion other than the insertion hole 115. Both the outer side friction pad 15 and the inner side friction pad 16 are not supported by the mounting bracket 25, and the torque receiving pin 27 attached to the mounting bracket 25 and the pad pin attached to the caliper 14. Only 58 is supported. A claw portion 64 of the caliper 14 is arranged on the side of the inner friction pad 16 opposite to the disc 12, and a cylinder portion 62 of the caliper 14 is arranged on the side of the outer friction pad 15 opposite to the disc 12. Will be.

  In the disc brake 11 having the above configuration, when brake fluid is introduced into the bores 87 and 88 from a brake pipe (not shown) through the pipe connection hole 89 of the cylinder portion 62 of the caliper 14 when the vehicle moves forward, The pistons 56 and 57 are advanced toward the claw 64 by the hydraulic pressure. Then, the pistons 56 and 57 protrude toward the disk 12 in the disk axial direction, and press the outer friction pad 15 which is one of the pair of friction pads 15 and 16. As a result, the outer friction pad 15 slides on the guide shaft portion 101 of the torque receiving pin 27 and the torque receiving shaft portion 48 of the pad pin 58 and comes into contact with the disk 12. On the other hand, by the reaction force, the caliper body 55 slides on the guide shaft portion 45 of the guide pin 26 and the guide shaft portion 52 of the torque receiving pin 27 so as to move the claw portion 64 to the disk 12 side. The friction pad 16 is pressed. As a result, the inner friction pad 16 slides on the guide shaft portion 101 of the torque receiving pin 27 and the torque receiving shaft portion 48 of the pad pin 58 and comes into contact with the disk 12. In this way, the pair of friction pads 15 and 16 provided on both surfaces of the disk 12 are brought into contact with the disk 12, and the disk 12, that is, the wheel is braked by the frictional resistance.

  During braking when the vehicle is moving forward, braking torque is generated from the disk entry side to the disk delivery side on the pair of friction pads 15 and 16, and this braking torque in the disk rotation direction is applied to the disk. One torque receiving pin 27 is received from the flat portions 117 and 118 of the insertion hole 115 in contact therewith. On the other hand, the pad pin 58 of the caliper 14 supports the pair of friction pads 15 and 16 by the engagement hole 122 that is long in the disk rotation direction. The engagement hole 122 and the pad pin 58 include the disk rotation direction. Is provided with a predetermined gap so as not to receive braking torque from the pair of friction pads 15 and 16. That is, the disc brake 11 is a pull type disc brake that receives the braking torque during braking on the disc entry side, and the braking torque generated in the pair of friction pads 15 and 16 during braking when the vehicle is moving forward. Only one torque receiving pin 27 on the disk insertion side receives it.

  Here, as shown in FIG. 8, the disc brake 11 is provided with mounting portions 133 and 134 at the rear ends of the caliper supports 131 and 132 at the lower and upper portions of the rear portion of the front fork 130 that are inclined rearwardly. The bolts are fastened to the fixing portions 35 and 36 of the carrier 13 described above, and are arranged behind the front fork 130. The caliper supports 131 and 132 including the attachment portions 133 and 134 are non-rotating portions of the vehicle that do not rotate like wheels.

  As shown in FIG. 9, a U-shaped carrier 139 having a base portion 136 and extending portions 137 and 138 extending in the same direction from both ends of the base portion 136 is used. A guide pin 26 and a torque receiving pin 27 are provided at the leading ends of the projecting portions 137 and 138, and both ends of the base portion 136 are attached to the mounting portions 143 at the leading ends of the caliper supports 141 and 142 at the front portion of the front fork 140. 144 may be bolted. In this case, a small carrier 139 can be obtained.

  Here, in the above-described disc brake described in Patent Document 1, a T-shaped groove is formed on the disk insertion side of the carrier supporting the caliper when the vehicle advances, and the T-shaped protrusion of the friction pad is formed in this groove. And the torque generated in the friction pad during braking is received by the T-shaped groove of the carrier. In this way, in the case where the braking torque is received on the disk insertion side, the surface pressure during braking can be made uniform due to the decrease in the surface pressure on the disk insertion side, thereby improving the brake noise suppression performance. However, the structure that receives the braking torque by the T-shaped groove of the carrier has a problem that the shape of the groove and the shape of the protrusion of the friction pad are complicated, and the productivity is not good. Further, since the surface pressure of the friction pad during braking is not stable, there is a problem that the friction pad wears unevenly or brake noise is generated.

  According to the disc brake 11 of the first embodiment, the pair of friction pads 15 and 16 are slid by the single torque receiving pin 27 arranged on the disc insertion side of the carrier 13, and this one torque The receiving pin 27 receives a braking torque in the disc rotation direction generated in the pair of friction pads 15 and 16 during braking when the vehicle moves forward. Therefore, since the braking torque is received on the disk insertion side, the self-servo effect does not occur, so the surface pressure on the disk insertion side of the friction pads 15 and 16 during braking can be reduced, and the surface pressure can be made uniform. Accordingly, uneven wear of the friction pads 15 and 16 can be reduced, so that the life of the friction pads 15 and 16 can be increased, the amount of brake operation can be reduced, and the brake operation feeling can be improved. Moreover, brake squeal can be suppressed.

  Further, since one torque receiving pin 27 receives the braking torque in the disk rotation direction generated in the pair of friction pads 15 and 16 during braking when the vehicle moves forward, the structure is simplified and productivity is improved. be able to. In particular, since it is not necessary to form a torque receiving portion on the mounting bracket 25 of the carrier 13, the shape of the mounting bracket 25 can be simplified and the productivity can be improved.

  In addition, since the back metal 107 can be shared by the friction pads 15 and 16, the types of parts can be reduced, and the manufacturing cost and the management cost can be reduced.

  Further, the disc rotation is performed so that the pad pin 58 supported by the caliper 14 and the engagement hole 122 formed on the disc delivery side of each of the pair of friction pads 15 and 16 do not receive the braking torque when the vehicle moves forward. Since the predetermined gap is provided in the direction, the pad pin 58 supports the friction pads 15 and 16 and its role is clarified. Therefore, the caliper 14 including the pad pin 58 can be reduced in size and simplified. Can do.

  Further, the engagement hole 122 is provided in each of the pair of friction pads 15 and 16 by a distance approximately twice as long as the distance between the center of the torque receiving pin 27 and the center of the friction pad 15 and 16 in the circumferential direction. Since the friction pads 15 and 16 are reduced in size, the load on the pad pin 58 can be reduced and the pad pin 58 can be reduced in size.

  Since one torque receiving pin 27 receives the braking torque of the pair of friction pads 15 and 16 at the torque receiving shaft portion 48 which is a circular portion, the entire friction pads 15 and 16 are reduced in size as described above. However, it is possible to easily reduce the load on the pad pin 58 and reduce the size of the pad pin 58.

  That is, as shown in FIG. 7, the disc brake 11 is a pull type in which the torque receiving pin 27 is disposed on the disk insertion side, the torque receiving shaft portion 48 of the torque receiving pin 27 has a round cross section, and friction An angle β formed by the direction of the force F applied to the pads 15 and 16 and the direction of the force Ft applied to the torque receiving pin 27 and an angle β formed by the direction of the force F and the direction of the component force Fd perpendicular to the force Ft. Α <β, and the relationship between the distance Ld between the center of the torque receiving pin 27 and the pad center O and the distance Lp between the center of the torque receiving pin 27 and the center of the pad pin 58 is Ld <Lp. The condition that the direction of the force Fs due to the pressing of the protrusions 111 and 112 by the pad spring 17 is the same direction is satisfied.

  When these conditions are satisfied, only the force Ft is applied to the torque receiving pin 27 and no moment is applied, so that the load on the torque receiving pin 27 and the insertion hole 115 is small. Further, a force Fp is applied to the pad pin 58 inward in the disk radial direction, and the relationship between the force Ft and the force Fp is Ft >> Fp because of geometrical conditions. Thereby, the pad pin 58 can be reduced in size and simplified. Further, since the force Fs pressing the protrusions 111 and 112 by the pad spring 17 is substantially in the same direction as the force Fp by the pad pin 58, the force Fp necessary for generating the moment M2 around the torque receiving pin 27 is further increased. Small is good. Thereby, the pad pin 58 can be further reduced in size and simplified. In order to reduce the load on the pad pin 58 (downsizing) while reducing the size of the entire friction pads 15 and 16, Lp: Ld = 2: 1 is desirable. That is, the engagement hole 122 is provided in each of the pair of friction pads 15 and 16 by a distance that is approximately twice the distance between the center of the torque receiving pin 27 and the circumferential center of the friction pad 15 and 16. It is good to be formed at a position away from the center of the.

  The pair of friction pads 15 and 16 has a center in the disk circumferential direction, a center of a line segment connecting the insertion hole 115 through which the torque receiving pin 27 is inserted and the engagement hole 122 through which the pad pin 58 is inserted, and the disk circumferential direction. Since the positions coincide with each other, it is possible to reduce the load on the pad pin 58 while reducing the size of the entire friction pads 15 and 16 and to reduce the size of the pad pin 58.

  Further, one torque receiving pin 27 extends from the fixed shaft portion 49 that is a fixed portion to the carrier 13 across the disk 12 in the disk axis direction and receives the braking torque of the pair of friction pads 15 and 16. Contrary to the shaft portion 48, the caliper 14 is slidably supported by the guide shaft portion 52 that extends in a direction away from the disc 12 in the disc axial direction, so that the influence of the braking torque is suppressed. The caliper 14 can be slidably supported by the torque receiving pins 27. Therefore, the structure is further simplified and the productivity can be further improved.

“Second Embodiment”
Next, the second embodiment will be described mainly on the difference from the first embodiment based on FIGS. In addition, about the site | part which is common in 1st Embodiment, it represents with the same name and the same code | symbol.

  In the second embodiment, the caliper 14 is not provided with the pad pin 58 of the first embodiment, and the slide base portion 150 that protrudes toward the disc 12 along the disc axial direction is provided on the delivery side projection portion 95. A slide base 151 that protrudes toward the disk 12 along the disk axial direction is formed on the delivery-side protrusion 96.

  Further, an engaging portion 152 that engages with the slide base portions 150 and 151 of the caliper 14 is formed on the end protruding portion 110 of the common back plate 107 of the friction pads 15 and 16. Then, the engaging portion 152 slides on the slide base portions 150 and 151 along the outer side in the disk radial direction, and as a result, the friction pads 15 and 16 are prevented from rotating and slide. It has become. That is, the pair of friction pads 15, 16 are formed with insertion holes 115 through which the torque receiving pins 27 are inserted on the respective disk insertion sides, and engaging portions 152 that engage with the caliper 14 at portions other than the insertion holes 115. Is formed.

  According to such 2nd Embodiment, since a pad pin becomes unnecessary, a number of parts and manufacturing cost can be reduced.

  According to the disc brake of the above embodiment, the carrier fixed to the non-rotating part of the vehicle, the pair of friction pads slidably supported by the carrier and disposed on both sides of the disc, and the pair of friction pads A disc brake having a piston that presses one of the friction pads and a caliper that is slidably supported by the carrier, wherein the carrier is disposed on a disc entry side when the vehicle moves forward, and the disc One torque receiving pin that extends in the axial direction of the disk and slides between the pair of friction pads is provided, and the pair of friction pads are inserted through the torque receiving pins on the respective disk insertion sides. An insertion hole is formed, and an engagement portion that engages with the caliper is formed in a portion other than the insertion hole, and one torque receiving pin on the disk insertion side is formed. It is characterized by receiving the braking torque of the disk rotational direction generated in the pair of friction pad during braking when the vehicle travels forward. In this way, a pair of friction pads are slid with a single torque receiving pin arranged on the disk insertion side of the carrier, and this single torque receiving pin is used as a pair during braking when the vehicle moves forward. The braking torque generated in the friction pad in the disk rotation direction is received. Therefore, since the torque at the time of braking is received on the disk feed-in side, the self-servo effect does not occur, so the surface pressure on the disk feed-in side of the friction pad during braking can be reduced and the surface pressure can be made uniform. Accordingly, uneven wear of the friction pad can be reduced, so that the life of the friction pad can be extended, the amount of brake operation can be reduced, and the brake operation feeling can be improved. Moreover, brake squeal can be suppressed. In addition, since one torque receiving pin receives a braking torque in the disk rotation direction generated in the pair of friction pads during braking when the vehicle moves forward, the structure is simplified and productivity can be improved. . In particular, since it is not necessary to form a torque receiving portion on the mounting bracket of the carrier, the shape of the mounting bracket can be simplified and productivity can be improved. Since the back metal can be shared by both friction pads, the types of parts can be reduced, and the manufacturing cost and the management cost can be reduced.

  The engagement portion is an engagement hole formed on the disk delivery side of each of the pair of friction pads when the vehicle advances, and through which a pad pin supported by the caliper is inserted. The pad pin is characterized in that a predetermined gap is provided in the disk rotation direction so as not to receive a braking torque when the vehicle moves forward. In this way, the pad pin supported by the caliper and the engagement holes formed on the respective disk delivery sides of the pair of friction pads have a predetermined disc rotation direction so as not to receive braking torque when the vehicle moves forward. Since the gap is provided, the pad pin supports the friction pad and its role is clarified. Therefore, the caliper including the pad pin can be reduced in size and simplified.

  Further, the engaging portion is separated from the center of the torque receiving pin by a distance of approximately twice the distance between the center of the torque receiving pin and the circumferential center of the friction pad. The engagement hole is formed in a position where the pad pin supported by the caliper is inserted. In this way, the engaging portion is located at a position away from the center of the torque receiving pin by a distance that is approximately twice the distance between the center of the torque receiving pin and the center of the friction pad in the circumferential direction. Since it is formed, it is possible to reduce the load on the pad pin while reducing the size of the entire friction pad, and to reduce the size of the pad pin.

  Further, the pair of friction pads is characterized in that the center in the disk circumferential direction coincides with the center of a line segment connecting the insertion hole and the engagement hole in the disk circumferential direction. As described above, the pair of friction pads has a center in the disk circumferential direction, and the center of the line segment connecting the insertion hole through which the torque receiving pin is inserted and the engagement hole through which the pad pin is inserted, and the position in the disk circumferential direction are the same. Therefore, it is possible to reduce the load on the pad pin while reducing the size of the entire friction pad and to reduce the size of the pad pin.

  The one torque receiving pin is characterized in that a portion where the pair of friction pads slide is circular. Thus, since one torque receiving pin receives the braking torque of a pair of friction pads at a circular portion, the load on the pad pin is reduced and the pad pin is reduced in size while reducing the size of the entire friction pad as described above. Can be easily achieved.

  Further, the torque receiving pin has a portion that extends in a direction away from the disk in a disk axial direction from a fixing portion to the carrier and slidably supports the caliper. In this manner, the torque receiving pin is separated from the disk in the disk axial direction, as opposed to the portion receiving the braking torque of the pair of friction pads extending from the fixing portion to the carrier across the disk in the disk axial direction. Since the caliper is slidably supported at the portion extending in the direction, the caliper can be slidably supported by the torque receiving pin while suppressing the influence of the braking torque. Therefore, the structure is further simplified and the productivity can be further improved.

DESCRIPTION OF SYMBOLS 11 Disc brake 12 Disc 13 Carrier 14 Caliper 15, 16 Friction pad 27 Torque receiving pin 48 Torque receiving shaft part (part where a friction pad slides)
49 Fixed shaft (fixed part)
52 Guide shaft (site that supports caliper slidably)
56, 57 Piston 58 Pad pin 115 Insertion hole 122 Engagement hole (engagement part)
131, 132, 141, 142 Caliper support (non-rotating part)
152 engaging part

Claims (6)

A carrier fixed to a non-rotating portion of the vehicle; a pair of friction pads supported on the carrier so as to be slidable; and a piston that presses one of the friction pads; In a disc brake having a caliper that is slidably supported by the carrier,
The carrier is provided with a torque receiving pin that is arranged on the disk entry side when the vehicle moves forward, extends in the disk axial direction across the disk, and the pair of friction pads slide.
The pair of friction pads are formed with insertion holes through which the torque receiving pins are inserted on the respective disk insertion sides, and are formed with engaging portions that engage with the calipers at portions other than the insertion holes,
One of the torque receiving pins on the disk entry side receives a braking torque in the disk rotation direction generated in the pair of friction pads during braking when the vehicle moves forward.   The engagement portion is an engagement hole that is formed on the disk delivery side of each of the pair of friction pads when the vehicle moves forward, and through which a pad pin supported by the caliper is inserted. The engagement hole, the pad pin, The disc brake according to claim 1, wherein a gap is provided in the disc rotation direction so as not to receive a braking torque when the vehicle moves forward.   The engaging portion is positioned at a distance from the center of the torque receiving pin by approximately twice the distance between the center of the torque receiving pin and the circumferential center of the friction pad on each of the pair of friction pads. The disc brake according to claim 1, wherein the disc brake is an engagement hole through which a pad pin supported by the caliper is inserted.   3. The pair of friction pads, wherein the center in the disk circumferential direction is coincident with the center of a line segment connecting the insertion hole and the engagement hole in the disk circumferential direction. 3. Disc brake according to 3.   The disc brake according to any one of claims 1 to 4, wherein the one torque receiving pin has a circular shape at a portion where the pair of friction pads slide.   6. The torque receiving pin according to claim 1, wherein the torque receiving pin has a portion that extends in a direction away from the disk in a disk axial direction from a fixed portion to the carrier and supports the caliper in a slidable manner. Disc brake according to any one of the above.

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