JP2007071296A - Disk brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure of a pad back plate of a disk brake device which can reduce a partial abrasion of a part of friction material. <P>SOLUTION: A caliper of the disk brake device comprises the part of friction material 20a, a pad back plate 22a having a pair of guide parts 30 and also a support surface to support the part of friction material 20a, a piston, and a chassis fixing mount 12. A guide center line M of the guide parts 30 is formed in the pad back plate 22a so that the center line M can practically cross a pressing line N in the pressing direction which passes through the pressing center point of the piston. The pad back plate 22a is depressed by a disk rotor, while sliding in the torque receiving groove 32 inside. A sliding resistance generated by the tangent force at a braking time in the torque receiving groove 32 by this configuration marks roughly the same figure up or down the guide part center line M and the pad back plate 22a is depressed by the disk rotor substantially in parallel in the pressing direction. As a result, partial abrasion of the part of friction material is reduced. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an improvement in a pad backing metal that supports a friction material of a disk brake device, particularly a disk brake device.

  As one of braking devices for braking a vehicle, there is a disc brake device. This disc brake is composed of a disc rotor and a caliper that rotate together with the wheels. The caliper has a housing portion that forms an outer shape and functions as a cylinder, and a mount that includes a torque receiving surface that fixes the caliper itself to the vehicle body and receives braking torque generated during braking. The housing portion includes a piston, and includes a pair of friction materials arranged with a disc rotor interposed therebetween, and a pair of pad backing plates that respectively support the friction materials. Convex-shaped guide portions are formed at both ends of the pad back metal, and are engaged with grooves that form a torque receiving surface of the mount to support the pad back metal on the mount. In the disc brake device having such a configuration, when hydraulic pressure is introduced between the housing portion and the piston, the guide portion slides in the groove and moves to the disc rotor side, and the friction material is pressed against the disc rotor to thereby apply a braking force. Can be generated.

  The friction material has, for example, a fan shape, and the pad back metal has, for example, substantially the same shape or a rectangular shape so as to support the friction material. The friction material is dragged by the disk rotor while coming into contact with the disk rotor at the time of braking and is dragged by the disk rotor.For example, when traveling forward, a tangential force is generated forward, and this tangential force is transmitted through the guide portion of the pad back metal. Acts on the torque receiving surface of the mount. The pad back metal is pressed against the torque receiving surface by a tangential force generated by the braking torque of the friction material at the same time as it moves toward the disk rotor by the cylinder.

Conventionally, in order to suppress abnormal noise generated during braking of a disc brake device, so-called "brake squealing" and vibration, if the pad back metal is pressed against the torque receiving surface with a large force so as not to vibrate, it will inevitably vibrate. There is an idea that squealing and braking are reduced. For example, in the disc brake device disclosed in Patent Document 1, the guide portion of the pad back metal is intentionally offset from the center of pressing of the cylinder toward the center of the disc rotor. In this case, the rotational moment generated in the friction material by the tangential force during braking is in the same direction as the rotational moment generated in the friction material by the braking force. As a result, the pad backing metal and the friction material rotate in the rotational direction of the disk rotor, and the rotational restraining force of the pad backing metal and the friction material increases. That is, brake squeal and vibration are suppressed by the pad back metal pressing against the torque receiving surface with a large force.
JP-A-8-135696

  However, since the pad backing metal moves toward the disk rotor while being strongly pressed against the torque receiving surface during braking, when the guide part of the pad backing metal is offset from the center of the cylinder pressing toward the center of the disk rotor, A sliding resistance is generated in the direction away from the disk rotor at the lower guide portion. Therefore, a rotational moment is generated such that the upper side of the pad back metal and the friction material (the outer peripheral side of the disc rotor) is inclined toward the disc rotor. As a result, there is a problem that the upper side of the friction material is pressed more strongly by the disc rotor than the lower side, causing uneven wear of the friction material.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a disc brake device having a pad back metal that can reduce the inclination of the pad back metal when the pad back metal is pressed against the disk rotor. It is in.

  In order to solve the above-described problems, the present invention provides a friction material disposed to face a friction sliding surface of a disk rotor that rotates with a wheel, and a support surface that supports a surface of the friction material that does not face the disk rotor. And a pad back metal having a pair of guide portions having a predetermined vertical width on both end surfaces of the support surface, and pressing the non-support surface of the pad back metal in a direction substantially parallel to the rotation axis of the disk rotor A pressing means for pressing the friction material against the friction sliding surface of the disk rotor; and a guide portion of the pad backing metal, and the pad backing metal is pressed by the pressing means so that the friction material is applied to the disk rotor. A vehicle body fixing mount having a torque receiving surface that receives a braking torque generated in the friction material when contacted, and the guide portion has two longitudinal widths of the pair of guide portions. A center line of the guide portion connecting the dividing points is formed on the pad back metal so as to substantially intersect with a pressing line in a pressing direction passing through the center of pressing when the pressing means presses the non-supporting surface of the pad back metal. It is characterized by being.

  Here, the vertical width of the guide portion is a width defined by the engagement lower end position and the engagement upper end position of the torque receiving surface to be engaged. According to this aspect, the rotational moment due to the sliding resistance force in the direction away from the disk rotor generated at the guide portion during braking is balanced above and below the pressing line of the pressing means. Therefore, the pad back metal presses the disc rotor substantially in parallel with the pressing direction of the pressing means. As a result, uneven wear of the friction material is reduced. In addition, since the sliding resistance generated in the guide portion when the pad backing metal approaches the disk rotor is balanced above and below the pressing line of the pressing means, the pad backing metal moves toward the disk rotor almost parallel to the pressing direction, and friction The material comes into contact with the disk rotor in a parallel posture. As a result, the friction material and the disk rotor are pressed in a parallel posture after contact, and uneven wear of the friction material is reduced.

  Further, in order to solve the above-mentioned problems, the present invention supports a friction material disposed to face a friction sliding surface of a disk rotor that rotates together with a wheel, and a surface of the friction material that does not face the disk rotor. A pad backing plate having a supporting surface and a pair of guide portions having a predetermined vertical width on both end surfaces orthogonal to the supporting surface; and a non-pad backing plate in a direction substantially parallel to the rotation axis of the disk rotor. A pressing means that presses the support surface and presses the friction material against the friction sliding surface of the disk rotor, and a guide portion of the pad backing metal, and the pad backing metal is pressed by the pressing means and the friction material is A vehicle body fixing mount having a torque receiving surface that receives a braking torque generated in the friction material when contacting the disk rotor, and the guide portion has a longitudinal width that is the maximum of the friction material. 1/3 or less of the vertical width, and the formation position is between the height of 1/3 of the maximum vertical width and the height of 2/3 based on the lower end position of the friction material on the end surface of the pad back metal. It is characterized by being.

  When the disc rotor is tilted and rotated, for example, in a state where the friction material starts to contact the friction sliding surface on the outer peripheral side of the disc rotor, the friction material and the disc rotor are already in contact with each other and pressed on the inner peripheral side. Consider the case where the material is compressed. In this case, it was found that the center of gravity of the reaction force due to compression is 1/3 from the inner peripheral side end face of the friction material maximum longitudinal width. Therefore, if the sliding frictional force generated in the guide portion by the reaction force toward the frictional sliding surface is generated on the outer peripheral side from the position 1/3 from the inner peripheral side end face of the friction material maximum longitudinal width, the outer peripheral side of the friction material is It has been found that a rotational moment is generated that presses against the frictional sliding surface of the disk rotor. As a result, the posture of the friction material is corrected in a direction parallel to the disk rotor. On the contrary, consider a case where the friction material is already in contact with the friction rotor and compressed on the outer periphery side in a state where the friction material starts to contact the friction sliding surface on the inner periphery side of the disk rotor. In this case, it was found that the center of gravity of the reaction force due to compression is 1/3 from the outer peripheral side end face of the friction material maximum longitudinal width. Therefore, if the sliding frictional force generated in the guide portion due to the reaction force toward the frictional sliding surface is generated on the inner peripheral side from the position of the outer peripheral side of the friction material maximum longitudinal width, the inner peripheral side of the friction material. It has been found that a rotational moment is generated that presses against the frictional sliding surface of the disk rotor. As a result, the posture of the friction material is corrected in a direction parallel to the disk rotor. Therefore, the vertical width of the guide portion is set to 1/3 or less of the maximum vertical width of the friction material, and between the height of 1/3 of the maximum vertical width and the height of 2/3 based on the lower end position of the friction material. By positioning, even when the disc rotor is tilted and rotated, the posture of the friction material is corrected so that the friction material approaches parallel to the disc rotor, and uneven wear can be reduced. The maximum vertical width of the wear material is a width defined by the innermost peripheral end portion and the outermost peripheral end portion of the friction material.

  Further, in the above aspect, the guide portion has a guide portion center line connecting the bisectors of the longitudinal widths of the pair of guide portions when the pressing means presses the non-supporting surface of the pad backing metal. The pad backing metal is formed so as to substantially cross a pressing line in the pressing direction passing through the pressing center point. According to this aspect, it is possible to effectively reduce the uneven wear of the friction material.

  According to the disc brake device of the present invention, uneven wear of the friction material can be reduced.

  Hereinafter, an embodiment of the present invention (hereinafter referred to as an embodiment) will be described with reference to the drawings.

  The caliper of the disc brake device according to the present embodiment includes a friction material, a pad back metal having a pair of guide portions, a pressing means, and a vehicle body fixing mount. . Then, the sliding friction generated in the guide part of the pad backing metal is formed on the pad backing metal so that the guide center line of the guide part substantially intersects the pressing line in the pressing direction passing through the pressing center point of the pressing means. The force becomes equal above and below the pressing line, and the pad backing metal can be pressed almost parallel to the pressing direction. As a result, uneven wear of the friction material can be reduced. Further, the vertical width of the guide portion is set to 1/3 or less of the maximum vertical width of the friction material, and the formation position thereof is 1/3 of the maximum vertical width on the end surface of the pad backing metal with reference to the lower end position of the friction material. Set between height and 2/3 height. Thereby, even when the disk rotor is tilted and rotated, the friction material can be corrected so as to approach the disk rotor in parallel, and uneven wear can be reduced.

  FIG. 1 is a side view of a floating caliper 10 constituting the disc brake device of the present embodiment, and FIG. 2 is a sectional view taken along line AA in FIG. FIG. 3 is a cross-sectional view taken along line BB in FIG. As shown in FIG. 1, the caliper 10 according to the present embodiment is roughly divided into a vehicle body fixing mount (mounting) 12 for fixing the caliper itself to a vehicle body (not shown), and a brake pad that is pressed by the disk rotor to generate a braking force. 14 and a cylinder portion 16 that functions as a pressing means for driving the brake pad 14. As shown in FIG. 2, the disk rotor 18 that rotates together with the wheels exists between the pair of brake pads 14. The side surfaces 18 a and 18 b of the disk rotor 18 constitute a friction sliding surface, and a pair of brake pads 14 are disposed opposite to each other with the disk rotor 18 interposed therebetween. The brake pad 14 includes a friction material 20 that directly contacts the side surfaces 18 a and 18 b of the disk rotor 18, and a pad back metal 22 that supports the back side of the friction material 20, that is, the side that does not contact the disk rotor 18.

  The caliper 10 is attached to the vehicle body via a vehicle body fixing mount 12 so as to be displaceable in the left-right direction. As shown in FIG. 2, a bottomed hole 24 is formed in the cylinder portion 16 of the caliper 10, and a piston 26 is slidably fitted into the hole 24. A port (not shown) is provided at the bottom of the hole 24 and is connected to a master cylinder (not shown) via a hydraulic pipe. When the driver operates the brake pedal, the brake oil from the master cylinder flows into the port and drives the piston 26.

  When the brake oil flows into the port, the piston 26 slides from the non-operating state shown in FIG. 2 in the direction of the arrow R, that is, the pressing direction of the piston 26, and the friction material 20a is moved to the side surface of the disk rotor 18 via the pad back metal 22a. Press to 18a. When the friction material 20a is pressed against the disk rotor 18, the piston 26 stops sliding. Even after the piston 26 stops sliding, if the brake oil flows into the port, the hydraulic pressure in the hole 24 further increases. As a result, the stopped piston 26 reversely presses the inner surface of the hole 24, presses the cylinder housing 16a constituting the cylinder portion 16 in the direction of the arrow L, that is, in the reverse direction of the arrow R, and as the hydraulic pressure increases, The cylinder housing 16a is displaced in the arrow L direction.

  A claw portion 28 is formed on the non-cylinder forming side of the cylinder housing 16a. As the cylinder housing 16a is displaced in the direction of arrow L, the claw portion 28 causes the friction material 20b to pass through the pad back metal 22b to the disc rotor 18. Is pressed against the side surface 18b. Therefore, the disk rotor 18 is pressed and clamped by the pair of friction materials 20a and 20b, and the disk rotor 18 can be braked efficiently.

  As shown in FIG. 3, the pad backing metal 22 a that supports the friction material 20 a has a pair of guide portions 30 that are formed on both end surfaces of the friction material 20 a of the pad backing metal 22 a and have a predetermined vertical width P. ing. This guide portion 30 is engaged with a torque receiving groove 32 functioning as a torque receiving surface formed on the vehicle body fixed mount 12 side in a loosely fitted state. Here, the vertical width P of the guide portion 30 is a width defined by the engagement lower end position and the engagement upper end position of the torque receiving groove 32 with which the guide portion 30 is engaged. When the friction material 20a is brought into contact with the rotating disk rotor 18, the friction material 20a is dragged by the disk rotor 18 and receives a tangential tangential force, that is, braking torque with respect to the disk rotor 18 (see FIG. 2). ). This tangential force is received by the torque receiving groove 32 of the vehicle body fixing mount 12 through the pad back metal 22a. In other words, the torque receiving groove 32 contacts the end surface portion of the pad backing metal 22a on the outlet side of the friction material 20a with respect to the rotation direction of the disk rotor 18 when the pad backing metal 22a is pressed, and receives the tangential force of the friction material 20a. For example, in FIG. 3, when the disk rotor 18 (not shown) rotates counterclockwise, the torque receiving groove 32a receives the braking torque of the guide portion 30 that engages with the torque receiving groove 32a. Conversely, when the disk rotor 18 (not shown) rotates in the clockwise direction, the torque receiving groove 32b receives the braking torque of the guide portion 30 that engages with the torque receiving groove 32b. As a result, a good braking force can be ensured both when the vehicle is moving forward and when the vehicle is moving backward.

  By the way, when the friction material 20 a is pressed against the rotating disk rotor 18 by the piston 26, the guide portion 30 of the pad back metal 22 a is pressed against the torque receiving groove 32 of the vehicle body fixed mount 12 by a tangential force generated during braking. At the same time, the pad back metal 22 a is pressed toward the disk rotor 18 by the piston 26. Therefore, a sliding resistance force in the direction opposite to the pressing direction is generated between the guide portion 30 and the torque receiving groove 32. As a result, depending on the position where the guide portion 30 is formed, a rotational moment that causes the friction member 20a to tilt with respect to the disk rotor 18 due to this sliding resistance force is generated, and the pad backing metal 22a has an inner peripheral side and an outer peripheral side. Differences in the pressing force caused uneven wear of the friction material 20a.

  Therefore, in the pad back metal 22 of the disc brake device of the present embodiment, the guide part center line M connecting the bisectors (P1 = P2) of the respective longitudinal widths P of the guide part 30 is the piston 26 as the pressing means. Is substantially crossed with a pressing line N in the pressing direction passing through the pressing center point O. As shown in FIG. 3, the guide portion 30 has a substantially symmetrical shape in the vertical direction with respect to the guide portion center line M. That is, the outer shape of the guide portion 30 is a substantially U-shaped rectangular shape, and the upper end surface (the engagement upper end position of the torque receiving surface) and the lower end surface (the engagement lower end position of the torque receiving surface) are parallel to each other. ing. By adopting such a shape of the guide portion 30, the sliding resistance force generated by the tangential force at the time of braking in the torque receiving groove 32 is substantially the same above and below the guide portion center line M. As a result, the pad backing metal 22 a is pressed against the disk rotor 18 in parallel with the pressing line N of the piston 26. Therefore, the friction material 20a and the disk rotor 18 come into full contact with an equal pressing force, and uneven wear can be reduced.

  Further, a clearance is formed between the guide portion 30 and the torque receiving groove 32 to enable the guide portion 30 to slide. In order to fill this clearance and suppress vibration, for example, a leaf spring 34 having a U-shaped cross section is inserted. Therefore, even when the friction material 20 a is in contact with the disk rotor 18, sliding resistance is generated when the guide portion 30 slides in the torque receiving groove 32. However, by determining the position of the guide portion 30 as described above, the leaf spring 34 is also arranged so that the top and bottom are symmetrical with respect to the guide portion center line M. Therefore, the sliding resistance force generated when the guide portion 30 slides is substantially the same above and below the guide portion center line M. As a result, the pad back metal 22a can be moved in a substantially parallel posture without being tilted with respect to the disk rotor 18 and can start pressing the disk rotor 18, which can contribute to suppression of uneven wear of the friction material 20a. Further, by causing the friction material 20a to approach the disk rotor 18 in parallel, partial contact before the generation of the braking force is prevented, which can contribute to suppression of drag sound of the friction material 20a.

  Incidentally, as shown in FIGS. 4A and 4B, the disc rotor 18 may rotate while swinging left and right. This rotational runout of the disk rotor 18 occurs, for example, when the disk rotor 18 is tilted or attached when the disk rotor 18 is fixed to the axle, or when the disk rotor 18 is deformed due to thermal expansion. In such a case, even when the pad back metal 22a (friction material 20a) is pressed in parallel along the pressing line N of the piston 26, the disk rotor 18 and the friction material 20 are inclined and contacted. For example, as shown in FIG. 4A, the friction material 20a starts to come into contact with the side surface 18a (friction sliding surface) of the disc rotor 18 on the outer peripheral side of the disc rotor 18, and friction has already occurred on the inner peripheral side of the disc rotor 18. Consider a case where the material 20a and the disk rotor 18 are in contact with each other and pressed, and the friction material 20 is compressed. In this case, the center of the reaction force that the friction material 20 receives from the disk rotor 18 was found to be the centroid of the compression region (triangular prism) formed when the disk rotor 18 and the friction material 20a contacted each other. Therefore, in the case of FIG. 4A, the inventor has determined that the center of gravity G of the reaction force F received by the friction material 20 from the disk rotor 18 is 1/2 from the inner peripheral side end surface of the friction material maximum longitudinal width Q of the friction material 20. I found it to be in position 3. At this time, when the end portion of the guide portion 30 is located on the inner peripheral side of the disk rotor 18 from the position of the center of gravity G (broken line hatching in FIG. 4A), a sliding resistance force R0 is generated by the guide portion 30 and friction occurs. A rotational moment that presses the inner peripheral side of the material 20 more strongly against the disc rotor 18 is generated. On the other hand, when the end portion of the guide portion 30 is located on the outer peripheral side of the disk rotor 18 from the position of the center of gravity G (solid hatching in FIG. Rotational moment is generated that more strongly presses the outer peripheral side of the disc against the disc rotor 18. That is, if the sliding friction force generated between the guide portion 30 and the torque receiving groove 32 is generated on the outer peripheral side from the position of the center of gravity G, the outer peripheral side of the friction material 20 is pressed against the friction sliding surface of the disk rotor 18. It was found that the rotational moment can be obtained. As a result, the friction material 20 is strongly pressed against the disk rotor 18 on the outer peripheral side, and the posture can be corrected so that the friction material 20 approaches parallel to the rotation posture of the disk rotor 18.

  Similarly, as shown in FIG. 4B, the friction material 20 a starts to contact the side surface 18 a (friction sliding surface) of the disk rotor 18 on the inner peripheral side of the disk rotor 18. Consider a case where the friction material 20 and the disk rotor 18 are already in contact with each other and pressed, and the friction material 20a is compressed. In this case, the center of gravity G of the reaction force F received by the friction material 20a from the disk rotor 18 is 1/3 from the outer peripheral side end surface of the friction material 20 in the maximum longitudinal width Q of the friction material 20 as shown in FIG. I found it as well. At this time, when the end portion of the guide portion 30 is located on the outer peripheral side of the disk rotor 18 from the position of the center of gravity G (broken line hatching in FIG. 4B), a sliding resistance R0 is generated by the guide portion 30, and the friction material A rotational moment is generated that more strongly presses the outer peripheral side of the disk 20 against the disk rotor 18. On the other hand, when the end portion of the guide portion 30 is located on the inner peripheral side of the disk rotor 18 from the position of the center of gravity G (solid hatching in FIG. 4B), a sliding resistance force R1 is generated by the guide portion 30, and the friction material A rotational moment is generated that strongly presses the inner peripheral side of 20 against the disk rotor 18. That is, if the sliding frictional force generated between the guide portion 30 and the torque receiving groove 32 is generated on the inner peripheral side from the position of the center of gravity G, the inner peripheral side of the friction material 20a is made the friction sliding surface of the disk rotor 18. It has been found that a rotational moment can be obtained that presses against. As a result, the friction material 20 is strongly pressed against the disk rotor 18 on the inner peripheral side, and the posture can be corrected so that the friction material 20 approaches parallel to the rotation posture of the disk rotor 18.

  From the above, the vertical width of the guide portion 30 is set to 1/3 or less of the maximum vertical width Q of the friction material 20, and the height of the maximum vertical width Q of the friction material 20 is 1/3 based on the lower end position of the friction material 20. By positioning between 2/3 (1/3 from the upper end position of the friction material 20), the friction material 20a is parallel to the disk rotor 18 even when the disk rotor 18 is tilted and rotated. Posture correction is performed so that As a result, it becomes possible to equalize the pressing force on the outer peripheral side and the inner peripheral side of the disc rotor 18 and reduce uneven wear. Further, by setting the vertical width of the guide portion 30 to 1/3 or less of the maximum vertical width Q of the friction material 20, the pad back metal 22a is in contact with and away from the disk rotor 18 with the guide portion center line M as the center. It can be rotated relatively easily. As a result, the posture correction of the friction material 20a is easily performed.

  Furthermore, the guide part 30 configured as described above may be arranged so that the guide part center line M of the guide part 30 substantially intersects the pressing line N of the piston 26 as described with reference to FIG. it can. In this case, regardless of the rotation state of the disk rotor 18, it becomes possible to equalize the pressing force on the outer peripheral side and the inner peripheral side of the disk rotor 18, and to reduce uneven wear. The vertical width of the guide portion 30 can be set to an arbitrary width as long as it is 1/3 or less of the maximum vertical width of the friction material 20, but the lower limit of the vertical width is a minimum considering the braking torque. It is necessary to set to a dimension that can ensure the mechanical strength.

  In the above example, the guide part 30 of the pad backing metal 22a on the cylinder part 16 side has been described. However, the same configuration can be applied to the guide part 30 of the pad backing metal 22b on the opposite side of the disk rotor 18. Similar effects can be obtained. The pad backing metal 22b on the opposite side of the disk rotor 18 is pressed by the claw portion 28 as described above. Therefore, if the guide part 30 is arranged so that the guide part center line M of the guide part 30 substantially intersects with the press line passing through the pressing center point of the claw part 28, the pad backing metal 22b is pressed parallel to the press line. Can be realized. Further, the vertical width of the guide portion 30 is set to 1/3 or less of the maximum vertical width of the friction material 20b, and the formation position thereof is 1 / of the maximum vertical width on the end surface of the pad back metal 22b with reference to the lower end position of the friction material 20b. It is preferable that the height is between 3 and 2/3. As a result, after the contact between the disk rotor 18 and the friction material 20b, the posture of the pad back metal 22b (friction material 20b) can be corrected, and uneven wear of the friction material 20b can be reduced.

  The shape of the caliper 10 shown in FIG. 1 to FIG. 3 is an example, and other configurations and shapes are arbitrary as long as the guide portion center line M of the guide portion 30 substantially intersects with the pressing line N of the piston 26. The same effects as in the present embodiment can be obtained. Further, the vertical width P of the guide portion 30 is 1/3 or less of the maximum vertical width of the friction material 20, and the formation position thereof is 1 on the end surface of the pad back metal 22 with the maximum vertical width of 1 based on the lower end position of the friction material 20. If it is between the height of / 3 and the height of 2/3, other structures and shapes can be changed arbitrarily, and the same effect as this embodiment can be acquired.

  In this embodiment, the floating type is shown as an example of the caliper of the disc brake device. However, the pad back metal of this embodiment is also applied to a fixed type caliper that presses the pad back metal on both sides of the disc rotor with the dedicated piston. The configuration can be applied, and similar effects can be obtained. In the present embodiment, the guide portion has a convex shape and the torque receiving surface has a groove shape. However, the guide portion side may have a concave shape, and the torque receiving side may have a convex shape. Obtainable.

  The present invention is not limited to the above-described embodiments, and various modifications such as design changes can be added based on the knowledge of those skilled in the art. The configuration shown in each figure is for explaining an example, and any configuration that can achieve the same function can be changed as appropriate, and the same effect can be obtained.

It is a side view of the caliper of the disc brake device concerning this embodiment. It is AA sectional drawing of FIG. It is sectional drawing in line segment BB of FIG. The vertical width of the guide portion of the pad backing metal is 1/3 or less of the maximum vertical width of the friction material, and the formation position is 2/3 from the height of 1/3 of the maximum vertical width based on the lower end position of the friction material. It is explanatory drawing explaining being between heights.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Caliper, 12 Car body fixed mount, 14 Brake pad, 16 Cylinder part, 16a Cylinder housing, 18 Disc rotor, 20 Friction material, 22 Pad back metal, 24 Hole, 26 Piston, 28 Claw part, 30 Guide part, 32 Torque receiving groove 34 Leaf spring, M guide center line, N pressing line.

Claims (3)

A friction material disposed opposite to the friction sliding surface of the disk rotor rotating with the wheel;
A pad backing metal having a support surface that supports a surface of the friction material that does not face the disk rotor, and a pair of guide portions having a predetermined vertical width on both end surfaces of the support surface;
A pressing means for pressing the non-supporting surface of the pad backing metal in a direction substantially parallel to the rotation axis of the disk rotor, and pressing the friction material against the friction sliding surface of the disk rotor;
A vehicle body fixed mount having a torque receiving surface that engages with a guide portion of the pad back metal and receives a braking torque generated in the friction material when the pad back metal is pressed by the pressing means and the friction material comes into contact with the disk rotor; ,
Including
The guide portion has a guide portion center line connecting the bisectors of the longitudinal widths of the pair of guide portions, and the guide portion passes through the pressing center point when the pressing means presses the non-supporting surface of the pad backing metal. The disc brake device is formed on the pad back metal so as to substantially cross a direction pressing line. A friction material disposed opposite to the friction sliding surface of the disk rotor rotating with the wheel;
A pad back metal having a support surface that supports a surface of the friction material that does not oppose the disk rotor, and a pair of guide portions having a predetermined vertical width on both end surfaces orthogonal to the support surface;
A pressing means for pressing the non-supporting surface of the pad backing metal in a direction substantially parallel to the rotation axis of the disk rotor, and pressing the friction material against the friction sliding surface of the disk rotor;
A vehicle body fixed mount having a torque receiving surface that engages with a guide portion of the pad back metal and receives a braking torque generated in the friction material when the pad back metal is pressed by the pressing means and the friction material comes into contact with the disk rotor; ,
Including
The guide portion has a vertical width of 1/3 or less of the maximum vertical width of the friction material, and the formation position thereof is 1 end of the maximum vertical width on the end surface of the pad back metal with reference to the lower end position of the friction material. A disc brake device characterized by being between a height of / 3 and a height of 2/3.   The guide portion has a guide portion center line connecting the bisectors of the longitudinal widths of the pair of guide portions, and the guide portion passes through the pressing center point when the pressing means presses the non-supporting surface of the pad backing metal. 3. The disc brake device according to claim 2, wherein the pad back metal is formed so as to substantially intersect with a direction pressing line.

Images