WO2014020941A1

WO2014020941A1 - Disc brake

Info

Publication number: WO2014020941A1
Application number: PCT/JP2013/058973
Authority: WO
Inventors: 俊山崎
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2012-07-31
Filing date: 2013-03-27
Publication date: 2014-02-06
Also published as: JP5914662B2; CN104246271A; JPWO2014020941A1; CN104246271B

Abstract

The present invention is configured so that, in a state where the outer periphery of a tube of one of a first member and a second member that constitute a pin is brought into contact with the inner periphery of a bracket hole, one member of the first member and the second member is press fitted into an insertion part of the other member, and that in a state where a bracket is being sandwiched by a flange of the first member and a flange of the second member, the first member and the second member are fixed to the bracket.

Description

Disc brake

The present invention relates to a disc brake for braking a vehicle.
This application claims priority on July 31, 2012 based on Japanese Patent Application No. 2012-170478 for which it applied to Japan, and uses the content here.

A disc brake for braking a vehicle such as a two-wheeled vehicle or a four-wheeled vehicle has a structure in which a pin in which a torque receiving portion and a slide portion are integrally formed is screwed to a bracket (for example, Patent Document 1). reference).

Japanese Utility Model Publication No. 57-139741

The above pins may cause looseness with respect to the bracket, and there is room for improvement in terms of improving reliability.

The present invention provides a disc brake capable of improving reliability.

According to the first aspect of the present invention, the disc brake includes a carrier fixed to the non-rotating portion of the vehicle, a pair of friction pads that are slidably supported by the carrier and disposed on both sides of the disc, A caliper that has a piston that presses one of the friction pads and is slidably supported by the carrier. The carrier includes a bracket formed with a hole penetrating in the disk axial direction and fixed to a non-rotating portion of the vehicle, and a pin extending from the hole in the disk axial direction and fixed. The pin includes a torque receiving portion on which the friction pad slides on one side of the hole and a slide portion on which the caliper slides on the other side. The said pin is comprised by another member of a 1st member and a 2nd member. Each of the first member and the second member is formed with a radially extending flange portion that contacts the periphery of the opening of the hole of the bracket. One of the first member and the second member is formed with a cylindrical portion having an insertion portion that allows the other member to be press-fitted. In the state where the outer peripheral portion of the cylindrical portion of one member of the first member and the second member is in contact with the inner peripheral portion of the hole of the bracket, the insertion portion of the one member In the state where the other member of the first member and the second member is press-fitted, and the bracket is sandwiched between the flange portions of the first member and the second member, the first member A member and the second member are fixed to the bracket.

The first member may include the torque receiving portion, and the second member may include the slide portion.
By pressing the outer peripheral portion of the cylindrical portion of the one member into the inner peripheral portion of the hole of the bracket, the inner peripheral portion of the hole of the bracket and the outer peripheral portion of the cylindrical portion of the one member The degree of coupling may be increased.

According to the second aspect of the present invention, the first member includes the flange portion, the second member extending in an axial direction from the flange portion and inserted into an inner peripheral portion of the hole of the bracket. And a cylindrical portion having the insertion portion allowing the press-fitting of the cylindrical member. The second member is a pin member in which a torque receiving portion is formed on one side, a slide portion is formed on the other side, and the flange portion is formed on the rear side in the insertion direction to the insertion portion.

According to the third aspect of the present invention, the concave portion is provided at a position close to the flange portion in the axial direction in the outer peripheral portion of the cylindrical portion of the one member, and the flange portion of the one member has the A convex portion that abuts the bracket is provided.

According to the disc brake described above, the reliability of the disc brake can be improved.

It is a front view which shows the disc brake of 1st Embodiment which concerns on this invention. It is a side view showing the disc brake of a 1st embodiment concerning the present invention. It is a top 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 sectional side view which shows the disc brake of 2nd Embodiment which concerns on this invention. It is a sectional side view which shows the disc brake of 3rd Embodiment which concerns on this invention. It is side sectional drawing which shows the disc brake of 4th Embodiment which concerns on this invention. It is side sectional drawing which shows the disc brake of 5th Embodiment which concerns on this invention. It is a side view which shows the slide shaft member of the disc brake of 5th Embodiment. It is a sectional side view which shows the assembly process of the carrier of the disc brake of 5th Embodiment. It is a sectional side view which shows the assembly process of the carrier of the disc brake of 5th Embodiment. It is a sectional side view which shows the assembly process of the carrier of the disc brake of 5th Embodiment. It is a sectional side view which shows the assembly process of the carrier of the disc brake of 5th Embodiment. It is a sectional side view which shows the assembly process of the carrier of the disc brake of 5th Embodiment. It is a side view which shows the modification of the slide shaft member of the disc brake of 5th Embodiment.

“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 such as two-wheeled vehicles and four-wheeled vehicles, specifically for motorcycles. As shown in FIGS. 1 to 3, the disc brake 1 includes a disc 2, a carrier 3 disposed on one side in the axial direction of the disc 2, and a caliper 4 supported by the carrier 3 so as to straddle the disc 2. And have. As shown in FIGS. 2 and 3, the disc brake 1 has two

friction pads

5 and 6, and further has

boots

12 and 13. 1 and 3 indicate the direction of rotation of the disk 2 when the vehicle moves forward. In the following description, the inlet side (the right side in FIGS. 1 and 3) in the rotating direction is the disk inlet side and the outlet side is the disk outlet side. Also, the axial direction of the disk 2 is the disk axial direction, the radial direction of the disk 2 is the disk radial direction, and the rotational direction of the disk 2 is the disk rotational direction or the disk circumferential direction.

As shown in FIG. 1, the disk 2 has a disk shape. The disc 2 is provided on a wheel (not shown) of a vehicle that is a braking target of the disc brake 1 and rotates integrally with the wheel.

The carrier 3 is fixed to the non-rotating part of the vehicle. As shown in FIG. 4, the carrier 3 includes a bracket 15 and a slide pin 16 and a dual-purpose pin (pin) 17 that are fixed to the bracket 15 integrally. The slide pin 16 guides the movement of the caliper 4 along the disk axis direction. The dual-purpose pin 17 serves both as a slide pin that guides the movement of the caliper 4 along the disk axis direction and a torque receiving pin that receives the braking torque of the

friction pads

5 and 6.

The bracket 15 is made of an aluminum alloy in the present embodiment. As shown in FIG. 2, the bracket 15 is disposed on the outer side (the right side in FIG. 2 and opposite to the wheel) that is one side of the disk 2, and the non-rotating portion (near the disk 2 of the vehicle) For example, it is fixed to a front fork. As shown in FIG. 1, the bracket 15 has a through hole 18 formed on the base end side, and is attached to a non-rotating portion of the vehicle with an unillustrated axle disposed in the through hole 18. The material of the bracket 15 is not limited to an aluminum alloy, and may be formed using cast iron or the like.

The inner pin mounting hole 20 is formed in the bracket 15 at an intermediate position in the disk radial direction. An outer pin mounting hole (hole) 21 is formed at the outer end of the bracket 15 in the disk radial direction. As shown in FIG. 4, the inner pin mounting hole 20 is formed so as to penetrate the bracket 15 in the disk axial direction, and a female screw 22 is formed on the inner peripheral portion. The outer pin mounting hole 21 is also formed so as to penetrate the bracket 15 in the disk axial direction, and a female screw 23 is formed on the inner peripheral portion.

The slide pin 16 is composed of a bolt member 26 and a collar 27. The bolt member 26 has a hexagonal column-shaped head portion 28 that can be engaged with a tool and a cylindrical shaft portion 29, and is provided on an outer peripheral portion of a predetermined range on the opposite side of the head portion 28 of the shaft portion 29. A male screw 30 is formed. The collar 27 has a cylindrical shape, and the shaft portion 29 of the bolt member 26 is fitted therein, and covers the shaft portion 29.

The bolt member 26 is screwed to the female screw 22 of the inner pin mounting hole 20 of the bracket 15 with a male screw 30 with the shaft portion 29 inserted into the collar 27. The bolt member 26 screwed in this way holds the collar 27 between the head 28 and the bracket 15. As a result, it is fixed to the bracket 15 together with the collar 27. The slide pin 16 composed of the bolt member 26 and the collar 27 is attached to the bracket 15 in this way. In this state, it extends from the bracket 15 to the opposite side (outer side) from the bracket 15 in a posture along the disc axial direction as a whole. The slide pin 16 has a collar 27 fitted in the boot 13, and an outer peripheral surface of the collar 27 is covered with the boot 13. The slide pin 16 supports the caliper 4 through the boot 13 so as to be movable in the disk axial direction.

The dual-purpose pin 17 is fixed to the bracket 15. The dual-purpose pin 17 includes a slide shaft member (second member, one member) 35 extending from the outer pin mounting hole 21 of the bracket 15 to the outer side in the disk axial direction, and a disk from the outer pin mounting hole 21 of the bracket 15 to the disk. The torque receiving shaft member (first member, the other member) 36 extending to the inner side in the axial direction is constituted by two separate members.

The slide shaft member 35 is made of a material different from that of the aluminum alloy bracket 15. In the present embodiment, the slide shaft member 35 is specifically made of steel. The slide shaft member 35 includes, in order from one end in the axial direction, a cylindrical tube portion 40 having a hole-shaped insertion portion 39 having an inner peripheral surface that is a cylindrical surface at the center in the radial direction, and larger than the outer peripheral portion of the tube portion 40. An annular flange portion 41 having a diameter and a columnar slide portion 42 having a smaller diameter than the cylindrical portion 40 are provided. In other words, the slide shaft member 35 is formed with the flange portion 41 at the intermediate portion in the axial direction. The flange portion 41 is formed to extend radially outward from the cylindrical portion 40 and the slide portion 42 on both sides in the axial direction.

The insertion part 39 of the cylinder part 40 is a part which accept | permits press injection of the torque receiving shaft member 36 so that it may mention later. The insertion part 39 opens to the side opposite to the slide part 42 in the axial direction, and is formed with a depth within the range of the cylindrical part 40. A male screw 43 is formed on the outer peripheral portion of the cylindrical portion 40. The flange portion 41 is chamfered at the outer peripheral portion on the slide portion 42 side in the axial direction. The axial length of the cylindrical portion 40 is slightly shorter than the axial length of the outer pin mounting hole 21 of the bracket 15. The cylinder part 40, the flange part 41, and the slide part 42 are all coaxially arranged with the central axes thereof matched.

The torque receiving shaft member 36 is made of the same steel as the slide shaft member 35 in the present embodiment. The torque receiving shaft member 36 includes, in order from one end in the axial direction, a cylindrical torque receiving portion 50, an annular flange portion 51 having a larger diameter than the torque receiving portion 50, and a cylindrical shape having a smaller diameter than the torque receiving portion 50. And a fitting shaft portion 52. In other words, the torque receiving shaft member 36 is formed with a flange portion 51 at an axially intermediate portion, and the flange portion 51 extends radially outward from the torque receiving portions 50 and the fitting shaft portions 52 on both axial sides. It is formed out. The slide shaft member 35 and the torque receiving shaft member 36 may be formed of a material having a smaller expansion coefficient than that of the bracket 15, and the same material is not necessarily used.

The axial length of the fitting shaft portion 52 is equal to or less than or equal to the axial length of the insertion portion 39 of the slide shaft member 35. The fitting shaft portion 52 is fitted to the insertion portion 39 of the slide shaft member 35 with an interference fit as will be described later. Therefore, the outer diameter of the fitting shaft portion 52 is larger than the inner diameter of the insertion portion 39 by the tightening allowance dimension. The torque receiving portion 50, the flange portion 51, and the fitting shaft portion 52 are all coaxially arranged so that the central axes coincide with each other.

The slide shaft member 35 is attached to the bracket 15 by bringing the outer peripheral portion of the cylindrical portion 40 into contact with the inner peripheral portion of the outer pin mounting hole 21. Specifically, the male screw 43 on the outer peripheral portion of the cylindrical portion 40 is screwed into the female screw 23 on the inner peripheral portion of the outer pin mounting hole 21 of the bracket 15 from the side opposite to the disk 2. The slide shaft member 35 is attached to the bracket 15 by such screwing. At that time, the slide shaft member 35 is in contact with the surface around the opening of the outer pin mounting hole 21 on the surface opposite to the disk 2 of the bracket 15 at the end surface 55 where the flange portion 41 extends in the direction perpendicular to the axis. . Thereby, the slide shaft member 35 is fixed to the bracket 15 such that the slide portion 42 extends from the bracket 15 to the side opposite to the disk 2 along the disk axial direction. As described above, the axial length of the cylindrical portion 40 is shorter than the axial length of the outer pin mounting hole 21. For this reason, in a state where the flange portion 41 is in contact with the bracket 15 at the end surface 55, the cylindrical portion 40 does not protrude from the outer pin attachment hole 21 to the disk 2 side.

As described above, the fitting shaft portion 52 of the torque receiving shaft member 36 has a surface side facing the disk 2 in the insertion portion 39 of the slide shaft member 35 attached to the outer pin mounting hole 21 of the bracket 15. It is press-fitted from. Thus, the bracket 15 is attached via the slide shaft member 35. At that time, the torque receiving shaft member 36 comes into contact with the periphery of the opening of the outer pin mounting hole 21 on the surface of the bracket 15 on the disk 2 side at the end surface 56 in which the flange portion 51 extends in the axis orthogonal direction. Thereby, the torque receiving shaft member 36 is fixed to the slide shaft member 35 such that the torque receiving portion 50 extends from the bracket 15 to the disk 2 side along the disk axial direction.

As described above, the dual-purpose pin 17 in which the slide shaft member 35 and the torque receiving shaft member 36 are integrated by press-fitting is in a state where the

flange portions

41 and 51 on both sides in the axial direction are in contact with the bracket 15 at the same time and the bracket 15 is sandwiched between them. Thus, it is fixed to the bracket 15. In other words, the dual-purpose pin 17 is formed by dividing the

flanges

41 and 51 that sandwich the bracket 15 from both sides in the disk axial direction into the slide shaft member 35 and the torque receiving shaft member 36 which are separate members. Yes. In a state of being fixed to the bracket 15, the dual-purpose pin 17 includes a torque receiving portion 50 on one side and a slide portion 42 on the other side across the outer pin mounting hole 21 of the bracket 15. 50 is the same axis with the center axes of each other coincident.

When the fitting shaft portion 52 is press-fitted to the vicinity of the bottom portion of the insertion portion 39 of the slide shaft member 35 in a state where the end surface 55 of the flange portion 41 is in contact with the bracket 15 without a gap, the end surface 56 of the flange portion 51 is inserted. The axial length of the bracket 15 is set so that the bracket 15 contacts the bracket 15 without a gap. Further, the fitting shaft portion 52 is press-fitted into the insertion portion 39 with a tightening margin, so that it is screwed into the outer diameter of the cylindrical portion 40 of the slide shaft member 35, that is, the female screw 23 of the outer pin mounting hole 21 of the bracket 15. The diameter of the male screw 43 is enlarged so that the radial gap with the female screw 23 is reduced or eliminated. Thereby, the coupling | bonding degree of the inner peripheral part of the outer side pin attachment hole 21 of the bracket 15 and the outer peripheral part of the cylinder part 40 of the slide shaft member 35 can be raised.

In the state of being fixed to the bracket 15 as described above, the center of the dual-purpose pin 17 is arranged on the outer side in the radial direction than the disk 2 as shown in FIG. As shown in FIG. 4, the dual-purpose pin 17 extends in the direction of the disk axis, with one torque receiving portion 50 side extending across the disk 2 to the disk 2 side, and the other slide portion 42 side opposite to the disk 2. To extend. As shown in FIG. 1, the dual-purpose pins 17 are arranged on the disk delivery side in the carrier 3, and are arranged on the disk delivery side and on the disk radial direction outer side than the slide pins 16. As will be described later, the torque receiving portion 50 shown in FIG. 4 is a portion where the

friction pads

5 and 6 slide, and the slide portion 42 is a portion where the caliper 4 slides.

The caliper 4 is supported by the carrier 3 so as to be slidable in the disk axial direction by the slide portion 42 of the dual-purpose pin 17 and the slide pin 16. The caliper 4 is a so-called pin slide type caliper. As shown in FIG. 1, the caliper 4 includes a caliper body 60, a piston 61, and a pad pin 62.

In the present embodiment, the caliper body 60 is formed by being integrally formed by casting from an aluminum alloy or the like and then being cut. The caliper body 60 is slidably attached to the slide portion 42 and the slide pin 16 of the dual-purpose pin 17 shown in FIG. 4 of the carrier 3 while straddling the disk 2 as shown in FIGS. The caliper body 60 includes a cylinder portion 65 disposed on the outer side of the carrier 3, a bridge portion 66 extending from the outer side in the disk radial direction of the cylinder portion 65 to the inner side so as to exceed the outer side in the radial direction of the disk 2, and a bridge A claw portion 67 extending radially inward of the disk 2 is provided so as to face the cylinder portion 65 from the inner end portion of the portion 66. In other words, the caliper body 60 is formed with a claw portion 67 and a cylinder portion 65 that are provided so as to face the bridge portion 66 disposed across the disc 2 with the disc 2 interposed therebetween.

As shown in FIG. 1, a sliding guide part 70 is formed in the cylinder part 65 so as to protrude inward in the disk radial direction from an intermediate position in the disk circumferential direction. In addition, a sliding guide portion 71 is formed in the cylinder portion 65 so as to protrude from the outer side in the disc radial direction to the disc delivery side. As shown in FIG. 4, a slide pin support hole 72 is formed in the slide guide portion 70 so as to penetrate in the disk axial direction. In the sliding guide portion 71, a dual-purpose pin support hole 73 is formed from the disk 2 side to an intermediate position in the disk axial direction.

A cylindrical portion 78 described later of the boot 13 is fitted into the slide pin support hole 72 of the cylinder portion 65. The sliding guide portion 70 is slidably supported by the collar 27 of the slide pin 16 through the boot 13. The slide portion 42 of the dual-purpose pin 17 is fitted in the dual-purpose pin support hole 73 of the cylinder portion 65. The sliding guide portion 71 is slidably supported by the sliding portion 42.

The boot 12 is made of rubber. The boot 12 covers a portion between the slide guide portion 71 and the flange portion 41 of the slide portion 42 of the slide shaft member 35. The boot 12 has a bellows shape so as to expand and contract when the sliding guide portion 71 moves relative to the slide portion 42. One end portion of the boot 12 is locked to the sliding guide portion 71, and the other end portion is locked to the flange portion 41 of the slide shaft member 35.

The boot 13 is also made of rubber. The boot 13 covers the collar 27 of the slide pin 16. The boot 13 has an intermediate cylindrical portion 78 fitted in the slide pin support hole 72 of the slide guide portion 70, and moves on the collar 27 of the slide pin 16 together with the slide guide portion 70. In the boot 13, both sides of the cylindrical portion 78 are

bellows portions

79 and 80 that expand and contract when the cylindrical portion 78 moves relative to the slide pin 16. One end of the boot 13 is locked to the outer peripheral portion of one end of the collar 27 of the slide pin 16 and the other end is locked to the outer peripheral portion of the other end of the collar 27.

A bottomed bore 85 is formed in the cylinder portion 65 as shown in FIG. The bore 85 is formed along the disk axial direction so as to open toward the claw portion 67 shown in FIG. As shown in FIG. 1, a pipe connection hole 86 communicating with the bore 85 is formed along the disk radial direction on the disk entry side of the cylinder portion 65. A brake pipe (not shown) is connected to the pipe connection hole 86. Further, an air bleeding bleeder plug 87 communicating with the bore 85 is attached to the disk delivery side of the cylinder portion 65. The piston 61 is slidably fitted into the bore 85 of the cylinder portion 65.

As shown in FIG. 3, on the bridge portion 66 side in the disc axial direction of the cylinder portion 65, a turn-in side projecting portion 90 that protrudes toward the disc feed-in side on the outer side in the disc radial direction is formed. On the bridge portion 66 side in the disc axial direction of the claw portion 67, a turn-in side projecting portion 91 that protrudes toward the disc feed-in side is formed on the outer side in the disc radial direction.

The pad pin 62 is fitted into a through-hole 92 extending in the disk axis direction formed in the turn-in side protrusion 90 of the caliper body 60 and a through-hole 93 extending in the disk axis direction formed in the turn-in side protrusion 91. . The pad pin 62 extends so as to connect the turn-in side protrusion 90 and the turn-in side protrusion 91 in this fitted state. The pad pin 62 is disposed so as to straddle the disk 2 along the disk axial direction, on the outer side in the disk radial direction than the disk 2 and on the disk entry side with respect to the bridge portion 66.

As shown in FIG. 2, the friction pad 5 on the outer side of the

friction pads

5 and 6 is disposed between one surface of the disk 2 and the piston 61. The friction pad 5 has a lining 95 that abuts against the disk 2 to generate a frictional resistance, and a back plate 96 to which the lining 95 is attached to one surface and the pressing force from the piston 61 is transmitted to the other surface. ing. As shown in FIG. 3, the back plate 96 is formed with a through hole 97 on the disk feed-in side and a through hole 98 on the disk feed-out side. In the friction pad 5, the torque receiving portion 50 of the dual-purpose pin 17 of the carrier 3 is inserted into the through-hole 98, and the pad pin 62 of the caliper 4 is inserted into the through-hole 97. It is slidably supported in the direction.

As shown in FIG. 2, the inner friction pad 6 is disposed between the other surface of the disk 2 and the claw portion 67. The friction pad 6 has a mirror-symmetric shape with respect to the outer friction pad 5. The friction pad 6 has a lining 100 that abuts against the disk 2 to generate a frictional resistance, and a back plate 101 to which the lining 100 is attached to one surface and the pressing force from the claw portion 67 is transmitted to the other surface. is doing. As shown in FIG. 3, the back plate 101 has a through hole 102 formed on the disk feed-in side and a through-hole 103 formed on the disk feed-out side. In the friction pad 6, the torque receiving portion 50 of the dual-purpose pin 17 of the carrier 3 is inserted into the through-hole 103, and the pad pin 62 of the caliper 4 is inserted into the through-hole 102, and the disc shaft is inserted into the dual-purpose pin 17 and the pad pin 62. It is slidably supported in the direction. Therefore, the pair of

friction pads

5 and 6 are disposed on both surfaces of the disk 2.

When the brake fluid is introduced into the bore 85 of the cylinder portion 65 shown in FIG. 1 from the pipe connection hole 86, the caliper 4 moves forward in the direction of the disk 2 with respect to the cylinder portion 65, and the piston 61 shown in FIG. One of the

pads

5 and 6 is pressed toward the disk 2. Then, the friction pad 5 comes into contact with one surface of the disk 2 to generate a reaction force. With this reaction force, the caliper 4 causes the

slide guide portions

70 and 71 shown in FIG. The cylinder portion 65 is moved in a direction away from the disk 2 while sliding the slide pin 16 of the carrier 3 and the slide portion 42 of the dual-purpose pin 17 through the hole 73. Then, the claw portion 67 brings the other friction pad 6 into contact with the other surface of the disk 2. In this manner, the caliper 4 brakes the rotation of the disk 2, that is, the wheel by pressing the

friction pads

5 and 6 against the disk 2 from both sides by the claw portion 67 and the piston 61.

In the disc brake described in Patent Document 1 described above, a pin is attached to the bracket so as to protrude on both sides thereof, and a caliper is slidably fitted to a slide portion on one axial direction of the pin. The friction pad is supported by the torque receiving portion on the opposite side. In the structure in which the slide portion and the torque receiving portion are coaxial in this way, when the pin is attached to the bracket, the male screw formed at the intermediate position in the axial direction of the pin is screwed into the female screw of the bracket. However, if the male screw of the pin is screwed into the female screw of the bracket, the screwing may be loosened by repeatedly receiving the braking torque from the friction pad. The pins are also press-fitted into the bracket, but in this case, especially when different types of materials, such as press-fitting steel pins into aluminum alloy brackets, have different expansion rates, braking There is a possibility that the hole of the bracket to which the pin is attached expands due to the temperature rise due to heat generation and the pin is loosened with respect to the bracket.

On the other hand, according to the first embodiment described above, the male screw of the slide shaft member 35 which is one of the slide shaft member 35 having the slide portion 42 and the torque receiving shaft member 36 having the torque receiving portion 50. 43 is screwed into the female screw 23 of the outer pin mounting hole 21 of the bracket 15, and the fitting shaft portion 52 of the other torque receiving shaft member 36 is press-fitted into the insertion portion 39 of the slide shaft member 35 to integrate them. Like to do. Therefore, even if the dual-purpose pin 17 repeatedly receives the braking torque from the

friction pads

5 and 6, the slide shaft member 35 and the torque receiving shaft member 36 are integrated by press-fitting inside the outer pin mounting hole 21 of the bracket 15. Since the dual-purpose pin 17 and the bracket 15 are fixed in the radial direction, the possibility of loosening of the dual-purpose pin 17 with respect to the bracket 15 is reduced, and the looseness and rattling of the dual-purpose pin 17 with respect to the bracket 15 are suppressed, and both The degree of coupling can be increased. Therefore, the reliability of the disc brake 1 can be improved.

In addition, when the slide shaft member 35 and the torque receiving shaft member 36 are integrated by press-fitting, the bracket 15 is attached to the pins 17 for both ends by the flange portions 41 and the flange portions 51 of the slide shaft member 35 and the torque receiving shaft member 36, respectively. The structure is sandwiched in the axial direction. For this reason, since the dual-purpose pin 17 is fixed to the bracket 15 in the axial direction of the dual-purpose pin 17, the possibility that the dual-purpose pin 17 is loosened with respect to the bracket 15 is reduced, and the dual-purpose pin 17 is loosened relative to the bracket 15. And rattling can be suppressed. Therefore, the reliability of the disc brake 1 can be improved.

Further, the structure in which the bracket 15 is sandwiched between the flange portion 41 and the flange portion 51 in the axial direction of the dual-purpose pin 17 is caused by heat generated during braking when the bracket 15 made of aluminum alloy and the dual-purpose pin 17 made of steel are used. Even if the temperature rises, the bracket 15 tries to thermally expand in the axial direction of the dual-purpose pin 17, so that the flange portion 41 and the flange portion 51 act to hold down this thermal expansion. For this reason, the possibility of loosening the dual-purpose pin 17 with respect to the bracket 15 is reduced, and the looseness and rattling of the dual-purpose pin 17 with respect to the bracket 15 can be suppressed. Therefore, the reliability of the disc brake 1 can be improved.

The torque receiving shaft member 36 has a torque receiving portion 50 on which the

friction pads

5 and 6 slide, and the slide shaft member 35 has a sliding portion 42 on which the caliper 4 slides. For this reason, even if the torque receiving portion 50 and the slide portion 42 are provided on the torque receiving shaft member 36 and the slide shaft member 35 which are separate members, they can be arranged linearly, and the disc brake can be made compact. Can do.

“Second Embodiment”
Next, the second embodiment will be described mainly based on FIG. 5 with a focus on the differences from the first embodiment. 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 disc brake 1A of the second embodiment, a carrier 3A having a dual-purpose pin (pin) 17A partially different from the dual-purpose pin 17 of the first embodiment and a bracket 15 similar to the first embodiment is used. . The dual-purpose pin 17A of the second embodiment includes a slide shaft member (second member, the other member) 35A extending from the outer pin mounting hole 21 of the bracket 15 to the outer side in the disk axial direction, and an outer pin of the bracket 15 A torque receiving shaft member (first member, one member) 36A extending from the mounting hole 21 toward the inner side in the disk axial direction is constituted by two separate members.

The slide shaft member 35A is also made of steel. The slide shaft member 35A includes, in order from one end in the axial direction, a cylindrical fitting shaft portion 52A, a flange portion 41 having a diameter larger than that of the fitting shaft portion 52A and the same as that of the first embodiment, and a fitting shaft portion. The slide portion 42 has a diameter larger than 52A and is the same as that of the first embodiment. In other words, the slide shaft member 35A is formed with a flange portion 41 extending outward in the radial direction from the fitting shaft portion 52A and the slide portion 42 on both sides in the axial direction at the intermediate portion in the axial direction. The fitting shaft portion 52A, the flange portion 41, and the slide portion 42 are all coaxially arranged at the same center.

The torque receiving shaft member 36A is also made of steel. The torque receiving shaft member 36A includes, in order from one end in the axial direction, a torque receiving portion 50 similar to that in the first embodiment, a flange portion 51 similar to that in the first embodiment, and an inner peripheral surface in the radial center and a cylindrical surface. A cylindrical tube portion 40A having a hole-shaped insertion portion 39A having a diameter smaller than that of the flange portion 51 and larger than that of the torque receiving portion 50. In other words, the torque receiving shaft member 36A is formed with a flange portion 51 that extends radially outward from the torque receiving portions 50 and the cylindrical portion 40A on both axial sides at the axially intermediate portion. The insertion portion 39A of the cylinder portion 40A is a portion that allows the slide shaft member 35A to be press-fitted as will be described later. The insertion portion 39A opens to the opposite side of the axial torque receiving portion 50, and is formed with a depth within the range of the tubular portion 40A. The axial length of the tubular portion 40A is shorter than the axial length of the outer pin mounting hole 21 of the bracket 15. The axial length of the insertion portion 39A of the tubular portion 40A is equal to or greater than or equal to the axial length of the fitting shaft portion 52A of the slide shaft member 35A. A male screw 43A is formed on the outer peripheral portion of the cylindrical portion 40A. As will be described later, the fitting shaft portion 52A of the slide shaft member 35A is fitted into the insertion portion 39A with an interference fit. Therefore, the inner diameter of the insertion portion 39A is smaller than the outer diameter of the fitting shaft portion 52A. The cylindrical portion 40A, the flange portion 51, and the torque receiving portion 50 are all coaxially arranged at the same center.

The torque receiving shaft member 36A is attached to the bracket 15 by bringing the outer peripheral portion of the cylindrical portion 40A into contact with the inner peripheral portion of the outer pin mounting hole 21. Specifically, the male screw 43A on the outer peripheral portion of the cylindrical portion 40A is screwed into the female screw 23 on the inner peripheral portion of the outer pin mounting hole 21 of the bracket 15 from the disk 2 side. The torque receiving shaft member 36 A is attached to the bracket 15 by such screwing. At that time, in the torque receiving shaft member 36A, the flange portion 51 is in contact with the periphery of the outer pin mounting hole 21 on the surface on the disk 2 side of the bracket 15 at the end surface 56 along the axis orthogonal direction. In this case, in a state where the flange portion 51 is in contact with the bracket 15 at the end surface 56, the tubular portion 40 A does not protrude from the outer pin attachment hole 21 to the side opposite to the disk 2.

The fitting shaft portion 52A is press-fitted from the side opposite to the disk 2 into the insertion portion 39A of the torque receiving shaft member 36A that is attached to the outer pin attachment hole 21 of the bracket 15 as described above. Thus, the slide shaft member 35A is attached to the bracket 15 via the torque receiving shaft member 36A. At that time, the slide shaft member 35A comes into contact with the periphery of the outer pin mounting hole 21 on the surface opposite to the disk 2 of the bracket 15 at the end surface 55 in which the flange portion 41 extends in the direction perpendicular to the axis. Further, the fitting shaft portion 52A is press-fitted into the insertion portion 39A with an allowance, thereby increasing the diameter of the male screw 43A of the cylindrical portion 40A of the torque receiving shaft member 36A.

As described above, in the dual-purpose pin 17A in which the slide shaft member 35A and the torque receiving shaft member 36A are integrated by press-fitting, the

flange portions

41 and 51 on both axial sides are attached to the bracket 15 in the same manner as the dual-purpose pin 17 of the first embodiment. At the same time, the bracket 15 is sandwiched and fixed to the bracket 15. In the state of being fixed to the bracket 15 as described above, in the dual-purpose pin 17A, the slide portion 42 is fitted into the dual-purpose pin support hole 73 of the caliper 4 and the torque receiving portion 50 is the friction pad 5, as in the first embodiment. 6 through

holes

98 and 103.

“Third Embodiment”
Next, the third embodiment will be described mainly with reference to FIG. 6 with a focus on differences from the first embodiment. 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 disc brake 1B of the third embodiment, a carrier 3B having a bracket 15B and a dual-purpose pin (pin) 17B that are partially different from the bracket 15 and the dual-purpose pin 17 of the first embodiment is used. The bracket 15B of the third embodiment is formed with an outer pin attachment hole (hole) 21B having an inner peripheral portion having a cylindrical surface shape without female threads. The dual-purpose pin 17B of the third embodiment has a slide shaft member (second member, one member) 35B different from the first embodiment, and a torque receiving shaft member 36 similar to the first embodiment. Yes.

The slide shaft member 35B of the third embodiment is also made of steel, and in order from one end in the axial direction, the cylindrical portion 40B, the flange portion 41 similar to the first embodiment, and the slide portion 42 similar to the first embodiment, have. An insertion portion 39 similar to that of the first embodiment is formed at the center in the radial direction of the cylindrical portion 40B. The cylinder part 40B, the flange part 41, and the slide part 42 are all coaxially arranged with their centers aligned. The cylindrical portion 40B has a cylindrical surface shape in which the outer peripheral portion is not formed with external threads. As will be described later, this outer peripheral portion is fitted into the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B with an interference fit. Therefore, the outer diameter of the cylinder portion 40B is larger than the inner diameter of the outer pin mounting hole 21B by the tightening allowance dimension.

The slide shaft member 35B is attached to the bracket 15B by bringing the outer peripheral portion of the cylindrical portion 40B into contact with the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B. Specifically, the slide shaft member 35B is attached to the bracket 15B by the cylindrical portion 40B being press-fitted into the inner peripheral portion of the outer pin attachment hole 21B from the opposite side to the disk 2 at the outer peripheral portion. At that time, the flange portion 41 is in contact with the outer surface of the outer pin mounting hole 21B on the surface opposite to the disk 2 of the bracket 15B at the end surface 55 along the axis orthogonal direction. That is, the contact of the outer peripheral portion of the cylindrical portion 40B of the slide shaft member 35B with the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B press-fits the outer peripheral portion of the cylindrical portion 40B into the inner peripheral portion of the outer pin mounting hole 21B. Is done. In addition, the axial direction length of the cylinder part 40B is also shorter than the axial direction length of the outer side pin attachment hole 21B.

Next, as in the first embodiment, the torque receiving shaft member 36 is press-fitted into the insertion portion 39 of the slide shaft member 35B from the disk 2 side at the fitting shaft portion 52. At that time, the flange portion 51 is brought into contact with the periphery of the outer pin mounting hole 21B on the surface on the disk 2 side of the bracket 15B at the end surface 56 along the axis orthogonal direction. Thus, when the fitting shaft portion 52 is press-fitted into the insertion portion 39 with a tightening margin, the outer diameter of the tubular portion 40B of the slide shaft member 35B, that is, the tubular portion press-fitted into the outer pin mounting hole 21B of the bracket 15B. The diameter of 40B becomes large, and the fastening margin with the outer side pin attachment hole 21B is expanded. Thereby, the coupling | bonding degree of the inner peripheral part of the outer side pin attachment hole 21B of the bracket 15B and the outer peripheral part of the cylinder part 40B of the slide shaft member 35B can be raised.

As described above, the dual-purpose pin 17B in which the slide shaft member 35B and the torque receiving shaft member 36 are integrated by press-fitting is similar to the dual-purpose pin 17 of the first embodiment in that the

flange portions

41 and 51 on both axial sides are attached to the bracket 15B. At the same time, the bracket 15B is sandwiched and fixed to the bracket 15. In the state of being fixed to the bracket 15 as described above, in the dual-purpose pin 17B, the slide portion 42 is fitted into the dual-purpose pin support hole 73 of the caliper 4 and the torque receiving portion 50 is the friction pad 5, as in the first embodiment. 6 through

holes

98 and 103.

According to the third embodiment described above, the outer peripheral portion of the cylindrical portion 40B of the slide shaft member 35B is press-fitted into the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B. For this reason, it is not necessary to thread the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B and the outer peripheral portion of the cylindrical portion 40B of the slide shaft member 35B, and the processing cost can be reduced.

Although illustration is omitted, the third embodiment may be applied to the second embodiment. That is, the inner peripheral portion of the outer pin mounting hole 21 of the bracket 15 of the second embodiment is formed into a cylindrical surface shape, and the outer peripheral portion of the cylindrical portion 40A of the torque receiving shaft member 36A is formed into a cylindrical surface shape, and these are press-fitted with a tightening margin. You may do it.

“Fourth Embodiment”
Next, the fourth embodiment will be described mainly on the basis of FIG. 7 with a focus on differences from the first and third embodiments. In addition, about the site | part which is common in 1st, 3rd embodiment, it represents with the same name and the same code | symbol.

As in the third embodiment, the disc brake 1C of the fourth embodiment has a bracket 15B in which an outer pin mounting hole 21B having a cylindrical surface shape without a female thread is formed. A carrier 3C having a dual-purpose pin (pin) 17C partially different from the dual-purpose pin 17B is used.

The dual-purpose pin 17C of the fourth embodiment includes a pin member (second member, the other member) 36C extending from the outer pin mounting hole 21B of the bracket 15 in both the outer side and the inner side in the disc axial direction, It is comprised by two separate members with the shape member (1st member, one member) 35C.

The pin member 36C is also made of steel. The pin member 36 C is, in order from one end in the axial direction, a torque receiving portion 50 similar to the first embodiment, a flange portion 51 similar to the first embodiment, and a cylindrical shape having a smaller diameter than the torque receiving portion 50 and the flange portion 51. The fitting shaft portion 52C and the slide portion 42 which is smaller in diameter than the fitting shaft portion 52C and similar to the first embodiment are provided. In other words, the pin member 36C has a torque receiving portion 50 formed on one side in the axial direction, a fitting shaft portion 52C and a slide portion 42 formed on the other side in the axial direction, and an intermediate portion in the axial direction. Also, a flange portion 51 extending outward in the radial direction is formed. The torque receiving part 50, the flange part 51, the fitting shaft part 52C, and the slide part 42 are all coaxially arranged with their centers aligned.

The cylindrical member 35C is also made of steel. The cylindrical member 35C includes a flange portion 41 similar to that of the first embodiment, and a hole-shaped insertion portion 39C that extends in the axial direction from the flange portion 41 and has a cylindrical inner surface at the center in the radial direction. And a cylindrical tube portion 40C. As will be described later, the insertion portion 39C is a portion that allows the pin member 36C to be press-fitted, and is formed through the cylindrical member 35C in the axial direction so as to open on both sides in the axial direction. The axial length of the cylinder portion 40 C extending from the flange portion 41 is shorter than the axial length of the outer pin mounting hole 21 B of the bracket 15. The axial length of the insertion portion 39C is equal to the axial length of the fitting shaft portion 52C of the pin member 36C. The cylindrical portion 40C and the flange portion 41 are all coaxially arranged with their centers aligned.

The cylinder portion 40C has a cylindrical surface shape in which the outer peripheral portion is not formed with external threads. As will be described later, this outer peripheral portion is fitted into the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B with an interference fit. Therefore, the outer diameter of the cylinder portion 40C is larger than the inner diameter of the outer pin attachment hole 21B by the tightening allowance.

The cylindrical member 35C is attached to the bracket 15B by bringing the outer peripheral portion of the cylindrical portion 40C into contact with the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B. Specifically, the cylindrical member 35C is attached to the bracket 15B by press-fitting the cylindrical portion 40C into the inner peripheral portion of the outer pin mounting hole 21B from the opposite side to the disk 2 at the outer peripheral portion. At that time, the flange portion 41 is in contact with the outer surface of the outer pin mounting hole 21B on the surface opposite to the disk 2 of the bracket 15B at the end surface 55 along the axis orthogonal direction. That is, the contact of the outer peripheral portion of the cylindrical portion 35C of the cylindrical member 35C with the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B is such that the cylindrical member 35C is brought into contact with the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B. This is performed by press-fitting the outer peripheral portion of the cylindrical portion 40C.

Next, the pin member 36C is press-fitted into the insertion portion 39C of the cylindrical member 35C from the disc 2 side at the fitting shaft portion 52C. At that time, the flange portion 51 formed on the rear side in the insertion direction to the insertion portion 39C is an end surface 56 along the direction orthogonal to the axis, and contacts the surface around the outer pin mounting hole 21B on the surface of the bracket 15B on the disk 2 side. Abut. Thus, the fitting shaft portion 52C is press-fitted into the insertion portion 39C with a tight margin, whereby the outer diameter of the tubular portion 40C of the tubular member 35C, that is, the tubular portion press-fitted into the outer pin mounting hole 21B of the bracket 15B. The diameter of 40C becomes large and the interference with the outer pin mounting hole 21B is expanded.

As described above, the dual-purpose pin 17C in which the cylindrical member 35C and the pin member 36C are integrated by press-fitting is similar to the dual-purpose pin 17 of the first embodiment in that the

flange portions

41 and 51 on both axial sides simultaneously contact the bracket 15B. The bracket 15B is in contact with the bracket 15B and is fixed to the bracket 15B. In the state of being fixed to the bracket 15B in this way, in the dual-purpose pin 17C, the slide portion 42 is fitted into the dual-purpose pin support hole 73 of the caliper 4 and the torque receiving portion 50 is the friction pad 5, as in the first embodiment. 6 through

holes

98 and 103.

According to the fourth embodiment described above, the dual-purpose pin 17C has the pin member 36C in which the torque receiving portion 50 is formed on one side and the slide portion 42 is formed on the other side. The processing accuracy of the part 42 can be improved.

“Fifth Embodiment”
Next, the fifth embodiment will be described mainly with reference to FIGS. 8 to 12 focusing on differences from the first and third embodiments. In addition, about the site | part which is common in 1st, 3rd embodiment, it represents with the same name and the same code | symbol.

As shown in FIG. 8, the disc brake 1D of the fifth embodiment has a bracket 15D that is partially different from the bracket 15B of the third embodiment, and is partially different from the dual-purpose pin 17B of the third embodiment. A carrier 3D having pins (pins) 17D is used. The dual-purpose pin 17D of the fifth embodiment includes a slide shaft member (second member, one member) 35D partially different from the slide shaft member 35B of the third embodiment and the same as the first and third embodiments. A torque receiving shaft member 36 is used.

As shown in FIG. 9, the slide shaft member 35D of the fifth embodiment has a flange portion 41D having a configuration in which an annular convex portion 110D is formed on the flange portion 41 of the slide shaft member 35B of the third embodiment. is doing. Specifically, a convex portion 110D is formed on the end surface 55D of the slide shaft member 35D opposite to the slide portion 42 of the flange portion 41D. Further, the slide shaft member 35D has a cylindrical portion 40D having a configuration in which an annular recess 111D is formed on the outer peripheral portion of the cylindrical portion 40B of the slide shaft member 35B of the third embodiment. Specifically, a recess 111D is formed in the slide shaft member 35D at a position close to the axial flange portion 41D of the outer peripheral portion of the cylinder portion 40D. Here, the close position means a position where the material of the bracket 15D can flow in by plastic flow by a metal flow described later. The cylindrical portion 40D, the flange portion 41D, the slide portion 42, the convex portion 110D, and the concave portion 111D are all coaxially arranged with their centers aligned.

The assembly of the slide shaft member 35D and the torque receiving shaft member 36 to the bracket 15B will be described with reference to FIGS. 10A, 10B, and 11A to 11C. As shown in FIGS. 10A to 10B, the cylindrical portion 40D of the slide shaft member 35D is fitted into the inner peripheral portion of the outer pin mounting hole 21B of the bracket 15B with a gap fit at the outer peripheral portion. As shown in FIG. 10B, this fitting is performed until the convex portion 110D of the slide shaft member 35D contacts the bracket 15B, and in this state, the flange portion 41D of the slide shaft member 35D is pressed against the bracket 15B. Then, as shown in FIG. 11A, an annular fitting concave portion 112D is formed at the convex portion 110D of the flange portion 41D to generate plastic flow, so-called metal flow, and the material of the bracket 15D becomes the concave portion 111D of the cylindrical portion 40D. It flows in. As a result, the bracket 15D of the fifth embodiment in which the annular fitting convex portion 113D is formed is formed, and the slide shaft member 35D is stronger than the press-fitting of the third embodiment with respect to the bracket 15D. Fixed.

That is, the concave portion 111D is provided on the outer peripheral portion of the cylindrical portion 40D of the slide shaft member 35D, and the convex portion 110D that contacts the bracket 15D is provided on the flange portion 41D. Therefore, the bracket 15D of the fifth embodiment has an outer pin mounting hole (hole) 21D having a configuration in which the fitting convex portion 113D is formed instead of the outer pin mounting hole 21B, compared to the bracket 15B of the third embodiment. The difference is that the fitting recess 112D is formed around the outer pin mounting hole 21D.

In the state attached to the bracket 15D as described above, the slide shaft member 35D has an end surface 55D in which the flange portion 41D extends along the direction orthogonal to the axis, and the outer pin attachment hole 21D on the surface opposite to the disk 2 of the bracket 15D. Abuts against the surroundings per surface.

Next, as shown in FIGS. 11B to 11C, the torque receiving shaft member 36 is press-fitted into the insertion portion 39 of the slide shaft member 35D at the fitting shaft portion 52 as in the first embodiment. At that time, the flange portion 51 is brought into contact with the periphery of the outer pin mounting hole 21D of the surface on the disk 2 side of the bracket 15D at the end surface 56 along the axis orthogonal direction. In this way, the fitting shaft portion 52 is press-fitted into the insertion portion 39 with a tight margin, whereby the outer diameter of the tube portion 40D of the slide shaft member 35D, that is, the tube portion press-fitted into the outer pin mounting hole 21D of the bracket 15D. The diameter of 40D becomes large and the tightening allowance with the outer side pin attachment hole 21D is expanded.

As described above, the dual-purpose pin 17D in which the slide shaft member 35D and the torque receiving shaft member 36 are integrated by press-fitting is similar to the dual-purpose pin 17 of the first embodiment in that the

flange portions

41D and 51 on both axial sides are attached to the bracket 15D. At the same time, the bracket 15D is sandwiched and fixed to the bracket 15D. With the dual-purpose pin 17D fixed to the bracket 15D in this way, as shown in FIG. 8, the slide portion 42 is fitted into the dual-purpose pin support hole 73 of the caliper 4, and the torque receiving portion 50 is connected to the

friction pads

5, 6 The through

holes

98 and 103 are inserted.

According to the fifth embodiment described above, when the convex portion 110D of the flange portion 41D of the slide shaft member 35D is crimped to the bracket 15D so as to form the fitting concave portion 112D, the fitting concave portion 112D is formed. The material of the bracket 15D flows into the concave portion 111D of the outer peripheral portion of the cylindrical portion 40D of the slide shaft member 35D by the metal flow generated when the fitting is performed, and the fitting convex portion 113D is formed. Therefore, it is not necessary to thread the inner peripheral portion of the outer pin mounting hole 21D of the bracket 15D and the outer peripheral portion of the cylindrical portion 40D of the slide shaft member 35D, and the processing cost can be reduced. Further, the slide shaft member can be firmly fixed to the bracket, rather than press-fitting the slide shaft member into the bracket.

In addition, as shown in FIG. 12, in 5th Embodiment, it replaces with the flange part 41 in which the cyclic | annular convex part 110D of slide-shaft member 35D was formed, and it is the some intermittently arrange | positioned circularly by end surface 55D '. A cylindrical portion 40D having a flange portion 41D ′ formed with a hemispherical convex portion 110D ′ and having a plurality of hemispherical concave portions 111D ′ intermittently arranged in an annular shape instead of the annular concave portion 111D. It is also possible to use a slide shaft member 35D 'having a configuration of'. In this case as well, the convex portion 110D 'is caulked to enter the bracket 15D, and a part of the bracket 15D enters the concave portion 111D' by the metal flow.

Although not shown, the fifth embodiment may be applied to the third embodiment applied to the second embodiment. That is, the inner peripheral portion of the outer pin mounting hole 21 of the bracket 15 of the second embodiment is formed into a cylindrical surface shape, and the outer peripheral portion of the cylindrical portion 40A of the torque receiving shaft member 36A is formed into a cylindrical surface shape, and the flange of the torque receiving shaft member 36A. An annular convex portion 110D is formed on the end surface 56 of the portion 51, an annular concave portion 111D is formed on the outer peripheral portion of the cylindrical portion 40A, and a plurality of hemispherical convex portions are formed on the end surface 56 of the flange portion 51 of the torque receiving shaft member 36A. It is also possible to form a plurality of hemispherical concave portions 111D ′ on the outer peripheral portion of the cylindrical portion 40A.

In the first to fifth embodiments, a carrier fixed to a non-rotating portion of a vehicle, a pair of friction pads slidably supported on the carrier and disposed on both sides of the disk, and a pair of friction pads A caliper that has a piston that presses one of the friction pads and is slidably supported by the carrier, and the carrier is formed with a hole penetrating in the disk axial direction to form a non-rotating portion of the vehicle. A bracket that is fixed, and a pin that extends and is fixed in the axial direction of the disk from the hole, the pin including a torque receiving portion on which the friction pad slides on one side of the hole, and the other In the disc brake including the slide portion on which the caliper slides, the pin is constituted by a separate member of the first member and the second member, and each of the first member and the second member Said A radially extending flange is formed that contacts the periphery of the opening of the hole of the racket, and one of the first member and the second member is press-fitted with the other member. A cylindrical portion having an insertion portion to allow is formed, and the insertion portion of the one member is in the state where the outer peripheral portion of the cylindrical portion of the one member is in contact with the inner peripheral portion of the hole of the bracket. The first member and the second member are fixed to the bracket in a state where the other member is press-fitted and the bracket is sandwiched between the flange portions of the first member and the second member. It is characterized by that. Accordingly, the other member is press-fitted into the insertion portion of one of the first member and the second member to integrate them, and the respective flange portions of the first member and the second member Since the bracket is sandwiched between the first member and the second member, loosening of the first member and the second member with respect to the bracket can be suppressed. Therefore, it is possible to provide a disc brake capable of improving reliability.

Since the first to third and fifth embodiments are characterized in that the first member has the torque receiving portion and the second member has the slide portion, the torque receiving portion and the slide portion Can be arranged linearly even if they are provided as separate members, and the disc brake can be made compact.

In the third and fourth embodiments, the outer peripheral portion of the cylindrical portion of the one member is press-fitted into the inner peripheral portion of the hole of the bracket, whereby the inner peripheral portion of the hole of the bracket and the one member Since the degree of coupling with the outer peripheral portion of the cylindrical portion is increased, the processing cost can be reduced.

In the fourth embodiment, the first member extends in the axial direction from the flange portion and the flange portion, and is inserted into the inner peripheral portion of the hole of the bracket to allow press-fitting of the second member. A cylindrical member having the insertion portion, and the second member has a torque receiving portion formed on one side and a slide portion formed on the other side, and is inserted into the insertion portion. Since it is a pin member in which the flange portion is formed on the rear side in the direction, the processing cost can be reduced.

In the fifth embodiment, a concave portion is provided at a position close to the flange portion in the axial direction on the outer peripheral portion of the cylindrical portion of the one member, and the flange portion of the one member is a convex portion that comes into contact with the bracket. Since the portion is provided, when the convex portion of the flange portion of one member is swaged into the bracket, the bracket enters the concave portion in the outer peripheral portion of the one member by metal flow. Therefore, the processing cost can be reduced.

1,1A-1D Disc brake 2

Disc

3,3A-3D Carrier 4

Caliper

5,6

Friction pad

15,15B,

15D Bracket

17,17A-17D Dual use pin
21, 21B, 21D Outer pin mounting hole (hole)
35, 35B, 35D Slide shaft member (second member, one member)
35A slide shaft member (second member, other member)
35C cylindrical member (first member, one member)
36 Torque bearing member (first member, other member)
36A Torque bearing member (first member, one member)
36C Pin member (second member, other member)
39, 39C

Insertion part

40, 40A to 40D, 40D '

Tube part

41, 41D, 41D', 51 Flange part 42 Slide part 50 Torque receiving part 61 Piston 110D Convex part 111D Concave part

Claims

A carrier fixed to a non-rotating part of the vehicle;
A pair of friction pads slidably supported by the carrier and disposed on both sides of the disk;
A caliper that has a piston that presses one of the friction pads and is slidably supported by the carrier;
The carrier is
A bracket that is formed in the disk axial direction and is fixed to a non-rotating part of the vehicle;
A pin that extends from the hole in the axial direction of the disk and is fixed,
In the disc brake, the pin includes a torque receiving portion on which the friction pad slides on one side of the hole and a slide portion on which the caliper slides on the other side.
The pin is composed of separate members of a first member and a second member,
Each of the first member and the second member is formed with a radially extending flange portion in contact with the periphery of the opening of the hole of the bracket,
One member of the first member and the second member is formed with a cylindrical portion having an insertion portion that allows press-fitting of the other member,
The first member is press-fitted into the insertion portion of the one member while the outer peripheral portion of the cylindrical portion of the one member is in contact with the inner peripheral portion of the hole of the bracket, And a disc brake in which the first member and the second member are fixed to the bracket in a state where the bracket is sandwiched between the flange portions of the second member.
2. The disc brake according to claim 1, wherein the first member has the torque receiving portion, and the second member has the slide portion.
By pressing the outer peripheral portion of the cylindrical portion of the one member into the inner peripheral portion of the hole of the bracket, the inner peripheral portion of the hole of the bracket and the outer peripheral portion of the cylindrical portion of the one member The disc brake according to claim 1 or 2, wherein the degree of coupling is increased.
The first member includes the flange portion and the insertion portion that extends in an axial direction from the flange portion and is inserted into an inner peripheral portion of the hole of the bracket to allow press-fitting of the second member. A tubular member having a tubular portion,
The second member is a pin member in which a torque receiving portion is formed on one side, a slide portion is formed on the other side, and the flange portion is formed on the rear side in the insertion direction to the insertion portion. Item 4. The disc brake according to item 1 or 3.
A concave portion is provided at a position close to the flange portion in the axial direction on the outer peripheral portion of the cylindrical portion of the one member, and a convex portion that comes into contact with the bracket is provided on the flange portion of the one member. The disc brake according to any one of claims 1 to 4.