JP2012172740A - Pad clip assembling structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pad clip assembling structure capable of adjusting loading direction of an urging force applied to a brake pad and ratio of the force without changing a structure of pad clips.SOLUTION: The assembling structure of the pad clip which urges an outer pad supported on a pair of slide pins to the slide pins. The pad clip has a support portion which clamps a pressure plate constituting the outer pad, a base portion arranged along a plate surface of the pressure plate, and a spring part which contacts a slide pin to cause the urging force. A seat, which is a side for mounting the support portion of the pad clip, is provided on the outer pad. By setting an angle θ formed by a first straight line lalong the radial direction of a rotor passing the center of circular arc portions constituting penetration holes and a second straight line lpassing the center and intersecting the seat perpendicularly, the structure is made to change the ratio between the component force in the radial direction of the rotor and that in the rotor circumferential direction, in the urging force by the pad clip.

Description

  The present invention relates to a disc brake device, and more particularly to an assembly structure of a pad clip in a floating disc brake device in which a brake pad is pin-slid.

  As a floating type disc brake device of a type in which the brake pad is slid into a pin, ones having configurations as disclosed in Patent Document 1 and Patent Document 2 are known. In the disc brake device having such a configuration, although not shown, a spring called a pad clip is provided, and the brake pad supported by the slide pin is pressed.

  A slight gap is provided between the through hole (penetrating portion) provided in the brake pad and the slide pin in view of its configuration. For this reason, if the brake pad is simply supported by the slide pin, it vibrates in the radial direction and circumferential direction of the rotor due to vibration during vehicle running, inertia force during braking, torque, etc. A sound (click sound) is generated.

  For this reason, the brake pad is pressed against the slide pin via the pad clip, and movement (backlash) in the radial direction, the circumferential direction, or both of the rotor is suppressed.

JP-A-55-142127 JP-T-2006-520448

  In general, in a disc brake device having a configuration as disclosed in Patent Literature 1 and Patent Literature 2, a large pad clip is provided between the caliper and the brake pad, so that the brake pad can be used as a base point of the caliper. The structure is pushed down toward the radially inner periphery.

  However, when such a structure is adopted, the direction of the urging force against the brake pad is determined by the configuration of the pad clip. Further, the brake pad is always given a biasing force toward the radially inner periphery of the rotor.

  On the other hand, the vibration and torque applied to the brake pad are not constant, and the direction is not always constant. For this reason, the disc brake device has a structure that can handle various characteristics such as those that have a strong rattle noise reduction effect, those that have a strong crunch noise reduction effect, and those that have both characteristics. However, it is difficult to meet the demand with the structure of the conventional disc brake device.

  Therefore, in the present invention, a pad clip assembly structure capable of adjusting the load direction of the urging force applied to the brake pad and the ratio of the force is solved without changing the configuration of the pad clip. The purpose is to provide.

  In order to achieve the above object, the pad clip assembly structure according to the present invention comprises a brake pad supported by a pair of slide pins constituting a disc brake device through a through hole formed in a pressure plate. An assembly structure of a pad clip to be urged to, wherein the pad clip includes a support portion that sandwiches a pressure plate that constitutes the brake pad, and a base portion that is disposed along a plate surface of the pressure plate, A spring portion that abuts on the slide pin and generates an urging force, the brake pad is provided with a seat that is a side for attaching a support portion of the pad clip, and an arc portion that constitutes the through hole is provided. A first straight line passing through the center along the radial direction of the rotor and a second straight line passing through the center and perpendicular to the seat; By setting the angle formed, characterized by being configured to vary the ratio of the rotor radial and rotor circumferential component force in the biasing force of the pad clip.

Moreover, in the assembly structure of the pad clip having the above-described characteristics, the angle of the seat can be set so that the angle formed by the first straight line and the second straight line is less than 45 degrees. .
According to such a structure, the force applied in the radial direction of the rotor is stronger than the force applied in the circumferential direction of the rotor.

In the assembly structure of the pad clip having the above-described characteristics, the angle of the seat can be set so that the angle formed by the first straight line and the second straight line is 45 degrees.
With such a structure, the force applied in the radial direction of the rotor and the force applied in the circumferential direction are balanced.

Furthermore, in the assembly structure of the pad clip having the above characteristics, the angle of the seat may be set so that an angle formed by the first straight line and the second straight line is larger than 45 degrees. it can.
According to such a structure, the force applied in the circumferential direction of the rotor is stronger than the force applied in the radial direction of the rotor.

  According to the assembly structure of the pad clip having the above-described characteristics, it is possible to adjust the load direction of the urging force applied to the brake pad and the ratio of the force without changing the configuration of the pad clip.

It is a figure which shows the plane form of the disc brake device which can apply the assembly structure of the pad clip which concerns on invention. It is a figure which shows the front form of the disc brake apparatus which can apply the assembly | attachment structure of the pad clip which concerns on invention. It is a figure which shows the right side surface form of the disc brake apparatus which can apply the assembly | attachment structure of the pad clip which concerns on invention. It is a right lower surface side perspective view of the disc brake device which can apply the assembly structure of the pad clip concerning an invention. It is a figure which shows the structure of the slide pin and engaging part in the disc brake apparatus which concerns on embodiment. It is a perspective view which shows the engagement state of an outer pad and a pad clip. Relation pitch P ₂ of the pitch P ₁ and the slide pin holes in the outer pad of the disc brake device according to the embodiment, and is a diagram for explaining a state at the time of braking torque loads. It is a side perspective view which shows the structure of a pair of pad clip. It is the perspective view seen from the spring part side which shows a structure of a pair of pad clip. It is a figure which shows the pressing form of the outer pad with respect to the slide pin in the disc brake apparatus which concerns on embodiment. Is a diagram illustrating an example for describing the assembly structure of a pad clip according to the embodiment, when the angle θ is 45 ° between the first straight line l ₀ which passes through the center of the through hole and a second straight line l ₁ It is a figure which shows the example of. Is a diagram illustrating an example for describing the assembly structure of a pad clip according to the embodiment, the first straight line l ₀ which passes through the center of the through hole and a second straight line l ₁ angle θ is less than 45 ° It is a figure which shows the example of a case. Is a diagram illustrating an example for describing the assembly structure of a pad clip according to the embodiment, the angle θ is larger than 45 ° with the first straight line l ₀ which passes through the center of the through hole and a second straight line l ₁ It is a figure which shows the example of a case. It is a figure for demonstrating the operation | movement relationship between the slide pin by the side of rotor rotation in the disc brake device which concerns on embodiment, and the through-hole of an outer pad. It is a figure which shows an example of the structure by which the couple which arises in an outer pad at the time of braking in the embodiment becomes the direction opposite to the rotor rotation direction. It is a figure which shows an example of the structure by which the couple which arises in an outer pad at the time of braking in the embodiment becomes the same direction as the rotor rotation direction. It is a figure which shows the pressing form of the outer pad with respect to a slide pin in case the couple produced in an outer pad at the time of braking reversely in embodiment. It is a figure which shows the front form in the other example of the disc brake apparatus which can apply the assembly structure of the pad clip which concerns on invention. Other relationships exemplary pitch P ₁ of the through-holes in the outer pad of the disc brake device according to the the slide pin pitch P _2, and is a diagram for explaining a state at the time of braking torque loads. It is a figure which shows the pressing form of the outer pad with respect to the slide pin in the disc brake apparatus which concerns on other embodiment. It is a figure which shows the pressing form of the outer pad with respect to a slide pin in case the couple produced in an outer pad at the time of braking reversely in other embodiment.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the pad clip assembly structure of the present invention will be described in detail below with reference to the drawings. First, with reference to FIG. 1 to FIG. 4, a disc brake device to which the pad clip assembly structure of the present invention can be applied will be described. 1 is a plan view showing an example of a disc brake device to which the assembly structure of the pad clip of the present invention can be applied, FIG. 2 is a front view, and FIG. 3 is a right side view. FIG. 4 is a perspective view from the lower right side.

  The disc brake device 10 basically includes a support 38, slide pins 24 (24a, 24b) that engage with the support 38, a caliper 12 that engages with the slide pin 24, and brake pads (an inner pad 52 and an outer pad 58). Configured as

  The support 38 functions as a torque receiver that fixes the disc brake device 10 to the vehicle and receives the braking torque of a rotor (not shown) that rotates with the wheels. The support 38 includes a pair of torque receiving portions 40 (40a, 40b) provided to engage the slide pin 24, which will be described in detail later, and a support bridge portion 46 that connects the pair of torque receiving portions 40. The overall shape is substantially U-shaped.

  A screw hole 42 (see FIG. 5) for engaging the slide pin 24 is provided on the distal end side of the torque receiving portion 40. An attachment hole 44 for fixing the support 38 to a vehicle or the like is provided at a joint portion between the torque receiving portion 40 and the support bridge portion 46. In addition, substantially U-shaped concave portions 48 are formed at opposing positions on the opposing side surfaces of the pair of torque receiving portions 40. The recess 48 serves as a slide rail for holding and sliding an inner pad 52 (brake pad), which will be described in detail later.

  The slide pin 24 is screwed into a screw hole 42 provided in the torque receiving portion 40 of the support 38 described above, and serves as a slide rail for the caliper 12 and the outer pad 58 (brake pad), which will be described in detail later. During braking, the outer pad 58 also serves as a torque receiver.

  As shown in FIG. 5, the slide pin has a sliding portion of the outer pad 58 on the distal end side and a sliding portion of the caliper 12 on the proximal end side with the threaded portion 30 with the support 38 as a base point. . For this reason, the slide pin 24 has a bolt head 26 for tightening, a caliper sliding portion 28, a screwing portion 30, and an outer pad sliding portion 32. As will be described in detail later, the caliper 12 according to the present embodiment engages with the slide pin 24 through a through hole 22 provided in the arm portion 20, and between the through hole 22 and the slide pin 24. A sleeve 34 and a boot 36 are provided. The sleeve 34 ensures the sliding amount of the caliper 12. On the other hand, the boot 36 has a damping function between the sleeve 34 and the through hole 22 while preventing dust from adhering to the sliding portion between the sleeve 34 and the through hole 22.

  The caliper 12 is configured based on the caliper main body 14, the claw portion 18, the caliper bridge portion 16, and the arm portion 20. The caliper body 14 is disposed on the inner side of a rotor (not shown), and is provided with at least a cylinder (not shown) and a piston 15. The hydraulic fluid flows into the cylinder by the brake operation, and the piston 15 is pushed out through the hydraulic fluid that has flowed in, thereby pressing the pressure plate 54 in the inner pad 52 to be described in detail later. A bellows-like piston boot (not shown) is provided between the opening of the cylinder and the tip of the piston 15 to prevent dust from adhering to the sliding portion.

  The claw portion 18 is disposed on the opposite side of the caliper body 14 via the rotor, that is, on the outer side of the rotor, and plays a role of supporting an outer pad 58 described later in detail. The claw portion 18 extends toward the inner side in the rotor radial direction with a caliper bridge portion 16 described later in detail as a base point. For this reason, the nail | claw part 18 and the caliper main body 14 are provided in the position which opposes via a rotor. Further, in the disc brake device 10 according to the present embodiment, the through holes 18a and 18a are provided on both the rotor entrance side and the exit side of the claw part 18, and an outer pad 58, which will be described in detail later, is attached to the inner wall of the claw part 18. It is set as the structure which can be unevenly fitted.

  The arm portion 20 is an engaging portion that extends from the caliper body 14 to both end sides (rotor entry side and exit side). A through hole 22 (see FIG. 5) for engaging the caliper sliding portion 28 in the slide pin 24 is provided on the distal end side of the arm portion 20, and the slide pin 24 is connected to the through hole 22. Engagement is achieved.

  The disc brake device 10 according to this embodiment includes an inner pad 52 that slides in a recess 48 provided in the support 38 and an outer pad 58 that slides on slide pins 24a and 24b as brake pads. Both the inner pad 52 and the outer pad 58 are basically composed of pressure plates 54 and 60 and linings 56 and 62 that are friction members attached to the pressure plates 54 and 60.

  The pressure plate 54 in the inner pad 52 has a plate main body formed in a substantially fan shape by a metal flat plate that is slightly larger than the lining 56, and ears (not shown) protruding from both ends of the plate main body. By loosely fitting the ears of the pressure plate 54 into the recesses 48 formed in the support 38, the inner pad 52 can slide in the axial direction of the rotor. A pad clip 50 made of a metal plate is provided in the concave portion 48 of the support 38 to reduce sliding resistance when the inner pad 52 slides in the rotor axial direction and to prevent dragging during traveling. ing.

  As shown in FIG. 6, the pressure plate 60 in the outer pad 58 has a plate body 60a formed in a substantially fan shape by a metal plate that is slightly larger than the lining 62, and the plate body 60a is used as a base point at both ends of the plate body 60a. The arm portion 60b is provided so as to project substantially in a V shape, and the through hole 66 (66a, 66b) is formed on the distal end side of the arm portion 60b. The outer pad 58 can slide on the slide pin 24 by inserting the outer pad sliding portion 32 of the slide pin 24 through the through hole 66 of the arm portion 60b. Further, on the contact surface of the outer pad 58 with the claw portion 18 opposite to the lining attachment surface of the pressure plate 60, a pair of convex portions 64 are provided at positions corresponding to the through holes 18 a provided in the claw portion 18 of the caliper 12. Is formed. By fitting the pair of convex portions 64 into the through holes 18 a (concave portions) of the claw portion 18, the caliper 12 can be stably held with respect to the outer pad 58.

  In addition, the outer pad 58 according to this embodiment is provided with a second clip 68 on the contact surface of the pressure plate 60 with the claw portion 18. The second clip 68 is a clip having a pair of spring portions 72 extending from both sides with the central portion as a base portion 70. The second clip 68 functions by fixing the base portion 70 to the pressure plate 60. The base 70 is fixed at the center position between the pair of convex portions 64 provided on the pressure plate 60. Note that examples of fixing means for the base portion 70 include caulking and screwing.

  In the outer pad 58 provided with such a second clip 68, when the outer pad 58 is fixed to the claw portion 18, the convex portion 64 provided on the pressure plate 60 is fitted into the through hole 18 a, and the second clip 68 By sandwiching the portion 18, the outer pad 58 is biased toward the claw portion 18. Thereby, falling of the outer pad 58 can be prevented, and uneven wear of the lining can be prevented. Further, the outer pad 58 is in stable contact with the slide pin 24 by a pair of pad clips 74 which will be described in detail later. For this reason, by urging the claw portion 18 against the outer pad 58 stably held via the slide pin 24, it is possible to prevent and stabilize the caliper 12 from rattling. Note that, as in the second clip 68, by increasing the distance from the base portion 70 to the tip that is the point of action of the spring portion 72, variation in load can be suppressed. In the present embodiment, the concave portion provided on the inner wall of the claw portion 18 is expressed as the through hole 18a. However, the bottomed bag hole may be used instead of the through hole.

Further, in the disk brake apparatus 10 according to the present embodiment, the through hole 66a in the outer pad 58, a center pitch _{P 1} of the 66b, the slide pins 24a, 24b around the pitch _{P 2} and the _P 1 of> _{P 2}
So as to satisfy the relationship, the through-hole 66a, the pitch _{P 1} of 66b are determined. In the case of such a configuration, as shown in FIG. 7, when a low braking torque is generated such as at the initial stage of braking, the inner wall of the through hole 66b contacts only the slide pin 24b arranged on the delivery side, and only the slide pin 24b. A braking torque is applied. On the other hand, when a high braking torque is generated, the slide pin 24b arranged on the delivery side bends in the braking torque load direction, and the inner wall of the through hole 66a contacts the slide pin 24a arranged on the entry side. Thus, the braking torque is distributed to the pair of slide pins 24a and 24b. Thus, by making it possible to disperse the braking torque according to the level of the braking torque, there is no need to reinforce the strength such as increasing the diameter of the slide pin 24, and accompanying an increase in the diameter of the slide pin. An increase in weight or the like can be suppressed.

  The outer pad 58 is provided with a pair of pad clips 74 (first pad clips) on the arm portion 60b. Hereinafter, the structure of the pad clip 74 will be described, and then the assembly structure of the pad clip 74 to the outer pad 58 will be described in detail.

  The pad clip 74 provided on the arm portion 60b urges the slide pins 24a and 24b inserted through the through holes 66a and 66b, and presses the outer pad 58 held by the pad clip 74 in the direction opposite to the urging direction. Take on. As the pad clip 74 according to the present embodiment, the same one is adopted on the turn-in side and the turn-out side of the rotor. As shown in detail in FIGS. 8 and 9, the specific configuration is configured based on a base portion 76, a support portion 80, and a spring portion 82. The base portion 76 is a portion positioned between a support portion 80 and a spring portion 82, the details of which will be described later. In the case of this embodiment, a through hole 78 for inserting the slide pin 24 is provided, and the pressure plate 60 is provided. It is arranged along the surface. The support portion 80 is configured by a plate piece bent from the base portion 76 toward the pressure plate 60 side of the outer pad 58. The support part 80 can clamp the pressure plate 60 in the thickness direction by forming the plate pieces in a substantially U shape (horizontal U shape). The spring portion 82 is a plate piece that is bent and formed in a roll shape from the base portion 76 toward the opposite side to the support portion 80. By pressing the roll portion formed in this way against the slide pin 24, the pressure plate 60 held by the support portion 80 is drawn toward the spring portion 82 side. That is, by using the pad clip 74 according to the present embodiment, the outer pad 58 can be drawn in the arrangement direction of the spring portion 82 with the slide pin 24 as a base point (earth), It is possible to suppress a cronk sound (click sound) during braking. The pad clip 74 having such a configuration has good workability because the bending direction for forming the support portion 80 and the spring portion 82 is one direction that does not include twist. In addition, since the flat form in the unfolded state is simple and the plate-making property is good, the material yield is good and the manufacturing cost is low.

  The pressing direction of the outer pad 58 depends on how the pad clip 74 is attached to the arm portion 60b. For example, in the case of the present embodiment, as shown in FIG. 6, the side of the arm portion 60b extending in a substantially V shape with the plate body 60a as a base point is positioned on the outer side in the rotor radial direction by the support portion 80, The base portion 76 is attached so as to overlap the through holes 66 (66a, 66b). In the case of such an attachment form, the pad clip 74 disposed on the rotor entry side causes the spring portion 82 to contact the slide pin 24a toward the rotor delivery side on the outer side in the rotor radial direction. As a result, the outer pad 58 receives a force pressed against the slide pin 24a toward the rotor turning-in side on the inner side in the rotor radial direction. As a result, in the through hole 66a, the inner peripheral surface located on the rotor outlet side on the outer side in the rotor radial direction is urged to the slide pin 24a. On the other hand, the pad clip 74 disposed on the rotor delivery side brings the spring portion 82 into contact with the slide pin 24b toward the rotor entry side on the outer side in the rotor radial direction. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24b toward the inner side of the rotor in the radial direction of the rotor. As a result, in the through-hole 66b, the inner peripheral surface located on the rotor turn-in side on the outer side in the rotor radial direction is biased toward the slide pin 24b (see FIG. 10).

In the present embodiment, in order to stabilize the assembled form of the pad clip 74, a seat 65 is provided on the side sandwiched by the support portion 80, and the center O of the arc portion (dominant arc) constituting the through hole 66 is moved from the center O to the seat 65. A straight line l ₁ (second straight line) that extends toward the seat 65 intersects the seat 65 perpendicularly. In such a configuration, as shown in FIGS. 11 to 13, a straight line l ₀ (first straight line) along the radial direction of the rotor passing through the center O of the arc portion and a straight line l perpendicular to the seat 65. by changing the angle θ formed by the _1, F _{1 (circumferential} direction) is a component of the urging force of the pad clip 74, it is possible to change the ratio of F 2 _(radial direction). The relationship between the component forces F ₁ and F ₂ associated with the change in the angle θ is as follows. That is, when θ <45 °, F ₁ <F ₂ , and the component force acting in the radial direction is stronger than the component force acting in the circumferential direction. Further, when θ = 45 °, F ₁ = F ₂ , and the component force acting in the circumferential direction and the component force acting in the radial direction are balanced. When θ> 45 °, F ₁ > F ₂ and the component force acting in the circumferential direction becomes stronger than the component force acting in the radial direction.

When the component force acting in the radial direction is stronger than the component force acting in the circumferential direction, the force for suppressing the movement of the outer pad 58 in the radial direction becomes strong. As a result, it is possible to enhance the effect of suppressing rattle noise caused by vibration of the outer pad 58 and the like. On the other hand, when the component force acting in the circumferential direction is stronger than the component force acting in the radial direction, the force that suppresses the movement of the outer pad 58 in the circumferential direction becomes strong. As a result, it is possible to enhance the effect of suppressing the cronk sound (clapping sound) during braking. When F ₁ = F ₂ or F ₁ ≈F ₂ , both effects can be obtained.

  In this way, by changing the angle of the attachment side (seat 65) of the pad clip 74 with respect to the outer pad 58, the load direction of the urging force applied to the outer pad 58 without changing the form and characteristics of the pad clip, and its The proportion of power can be adjusted.

  In the present embodiment, the form of the through hole 66 in the outer pad 58 is as follows. That is, the planar shape of the wall surface on the side where the slide pin 24 is pressed is arcuate, the wall surface on the opposite side to the pressing side is flat, and so-called arcs and strings are combined. In the case of the present embodiment, a horseshoe-shaped through-hole 66 in which a long arc-shaped portion, that is, a combination of a dominant arc and a string, is formed out of two arcs whose circles are divided by strings. In the disc brake device 10 according to the present embodiment, the outer pad 58 is pressed against the slide pin 24 by the pad clip 74. For this reason, a large gap is generated between the slide pin 24 and the wall surface of the through hole 66 located on the side opposite to the side where the slide pin 24 is pressed. When an unnecessarily large gap is provided between the slide pin 24 and the wall surface of the through hole 66, the rattle noise between the slide pin 24 and the through hole 66 increases. Therefore, by narrowing a part of the through-hole 66 so as to fill the gap, unnecessary rattling can be prevented and rattle noise can be suppressed.

  According to the disc brake device 10 having such a configuration, the outer pad 58 fitted to the claw portion 18 is supported on the slide pin 24 by metal touch. For this reason, the caliper 12 locked to the slide pin 24 via the sleeve 34 and the boot 36 can be prevented from falling down, and rattling can be suppressed.

  Next, the operation at the time of braking in the disc brake device 10 having such a configuration will be described. First, when the vehicle driver operates a brake pedal or a brake lever (not shown), the cylinder of the caliper body 14 is filled with hydraulic oil. As the hydraulic oil fills the cylinder, the piston 15 accommodated in the cylinder is pushed out to the rotor side. The piston 15 pushed out from the cylinder presses the pressure plate 54 of the inner pad 52 supported by the torque receiving portion 40 of the support 38 and presses the lining 56 of the inner pad 52 against the sliding surface of the rotor. When the lining 56 of the inner pad 52 is pressed against the rotor, the caliper body 14 receives a reaction force of the pressing force and slides along the slide pin 24 so as to be separated from the rotor. When the caliper main body 14 slides away from the rotor, the claw portion 18 connected to the caliper main body 14 by the caliper bridge portion 16 operates so as to be drawn toward the rotor side. When the claw portion 18 is pulled toward the rotor side, the pressure plate of the outer pad 58 fixed to the claw portion 18 is pressed by the claw portion 18 and slides toward the rotor side along the slide pin 24, and the lining 62 is the rotor sliding surface. Pressed against.

  When the rotor sliding surface is sandwiched between the inner pad 52 and the outer pad 58 by the above-described operation, the inner pad 52 and the outer pad 58 receive a force that rotates in the rotor extending direction due to the frictional force. At this time, the inner pad 52 abuts against the concave portion 48 formed in the torque receiving portion 40 of the support 38 at the ear portion of the pressure plate 54 and generates a braking force by receiving the braking torque generated during braking. On the other hand, the outer pad 58 receives a braking torque by both the slide-side slide pin 24b and the slide-side slide pin 24a, and transmits this to the support 38 fixed to the vehicle body, thereby generating a braking force. As described above, the braking torque in the outer pad 58 is distributed and inputted to the slide pin 24b on the delivery side and the slide pin 24a on the delivery side.

  Further, in the disc brake device 10 according to the present embodiment, since the inner peripheral surface located on the radially outer side of the through hole 66 is pressed against the slide pin 24, the outer pad 58 applies braking torque. When received, on the pulling side (turn-in side), as shown in FIG. 14, the slide pin 24a is moved along the arcuate inner peripheral surface of the through hole 66a (along the locus indicated by the dotted line and the broken line). The pressure plate 60 will shift so as to move. For this reason, there is no situation in which the slide pin 24a suddenly collides with the opposite wall surface at the time of high braking torque load, and the switching from the push anchor to the push + pull anchor is not performed abruptly. Can be stabilized. As a result, the cronk sound (click sound) during braking is suppressed. In the disc brake device 10 according to the present embodiment, since only the inner pad 52 is held by the support 38, the support 38 does not need to be configured to straddle the rotor. For this reason, the cutting time of the support 38 for forming the recess on the outer side can be shortened, and the weight can be reduced.

  In the above embodiment, when the diameter of the dominant arc constituting the through-hole 66 is φD and the diameter of the slide pin 24 is φd (see FIG. 10), Δd that is the difference between φD and φd is the slide pin 24 (above In the case of the embodiment, the slide pin 24b) is determined to be shorter than the shift distance of the outer pad 58 obtained by elastic deformation. With such a configuration, the braking torque can be dispersed within a range in which the slide pin 24 is elastically deformed.

The disc brake device 10 according to the above embodiment has been described on the assumption that the couple (moment) generated in the outer pad 58 during braking works in the direction indicated by the arrow A as shown in FIG. An example of a means for producing a moment in such a direction, a distance from the rotor center axis C ₁ than the distance t ₁ to moment center of the outer pad 58, from the rotor center axis C ₁ to the center of the through hole 66 t ₂ it is possible to include a long case structure, in accordance with this, configuration of the disc brake device 10 according to the embodiment. For this reason, when the assembly structure of the pad clip as described above is adopted, in the through hole 66a serving as the subsequent torque receiver, the slide pin 24a is previously pressed against the pressing wall surface (the rotor radial outer peripheral side) in the through hole 66a. As a result, the generation of a clunk sound (click sound) can be suppressed.

On the other hand, when the couple (moment) generated in the outer pad 58 during braking is reversed as shown by the arrow A ′ (see FIG. 16), the pad is pressed so that the pressing direction of the outer pad 58 against the slide pin 24 is reversed. A clip is attached (a pad clip is not shown). In this case, the relationship between the slide pin 24 and the through hole 66 is as shown in FIG. Specifically, the pad clip 74 (see FIG. 8) disposed on the rotor entry side causes the spring portion 82 to contact the slide pin 24a toward the rotor delivery side on the inner side in the rotor radial direction. . As a result, the outer pad 58 receives a force that is pressed against the slide pin 24a toward the outer side of the rotor in the radial direction of the rotor. As a result, in the through hole 66a, the inner peripheral surface located on the rotor delivery side on the inner side in the rotor radial direction biases the slide pin 24a. On the other hand, the pad clip 74 disposed on the outlet side of the rotor brings the spring portion 82 into contact with the slide pin 24b toward the rotor inlet side on the inner side in the rotor radial direction. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24b toward the outer side of the rotor in the radial direction of the rotor. As a result, in the through-hole 66b, the inner peripheral surface located on the rotor turn-in side on the inner side in the rotor radial direction biases the slide pin 24b. Even in such a configuration, by adjusting the angle of the seat 65 so as to control the angle θ formed by the first straight line l ₀ and the second straight line l ₁ , it is possible to change the ratio of the component force F ₂ acting on the force F ₁ and the radial direction. That is, it is possible to cope with the change only in the assembly structure without changing the form of the pad clip.

In the case of such a configuration, the relationship between the dominant arc and the chord in the through-hole 66 is such that the dominant arc is located on the inner side in the rotor radial direction and the chord is located on the outer side in the radial direction. As an example of means for producing a moment in this direction, as shown in FIG. 16, the distance t ₁ from the rotor center axis C ₁ to moment center of the outer pad 58, from the rotor center axis C ₁ mention may be made long if configuration than the distance t ₂ to the center of the through hole 66.

  Next, another embodiment of the disc brake device to which the pad clip assembly structure of the present invention can be applied will be described with reference to FIG. Note that most of the configuration of the disc brake device 10a according to this embodiment is the same as that of the disc brake device 10 according to the above-described embodiment. Therefore, the same reference numerals are given to the portions having the same configuration, and the detailed description is omitted.

Disc brake device 10a according to the present embodiment is different from the disc brake device according to the embodiment described above, the through hole 66a in the outer pad 58, the center pitch _{P 1} and the slide pin 24a between 66b, a center pitch _{P 2} between 24b Relationship
P ₁ <P ₂
(See FIG. 19).

  Due to such a configuration, at the time of braking, only the slide pin 24a arranged on the turning-in side comes into contact with the through hole 66a during low braking torque load. On the other hand, when the braking torque increases, the slide pin 24a disposed on the turn-in side bends toward the turn-out side (braking torque direction), and the slide pin 24b disposed on the turn-out side contacts the through hole 66b. As a result, the braking torque is dispersed.

  In the present embodiment, the pad clip 74 (see, for example, FIG. 18) arranged on the rotor turn-in side of the pair of pad clips 74 has the spring portion 82 on the inner side in the rotor radial direction with respect to the slide pin 24a. Contact toward the rotor entry side. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24a toward the outer side of the rotor in the radial direction of the rotor. As a result, in the through hole 66a, the inner peripheral surface located on the rotor turn-in side on the inner side in the rotor radial direction biases the slide pin 24a. On the other hand, the pad clip 74 disposed on the rotor delivery side brings the spring portion 82 into contact with the slide pin 24b toward the rotor delivery side on the inner side in the rotor radial direction. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24b toward the outer side of the rotor in the radial direction of the rotor. As a result, in the through hole 66b, the inner peripheral surface located on the rotor delivery side on the inner side in the rotor radial direction is urged toward the slide pin 24b (see FIG. 20).

The pad clip 74 having such an action may have the same form as the pad clip 74 according to the first embodiment described above. The difference from the first embodiment resides in the manner in which the pad clip 74 is attached to the outer pad 58, and the pressing direction of the outer pad 58 against the slide pin 24 can be made different depending on the difference in this attachment manner. Specifically, in the case of the present embodiment, a side located on the inner side in the rotor radial direction of the arm portion 60 b of the pressure plate 60 is sandwiched by the support portion 80. In the disc brake device 10a having such a configuration, the pressing direction of the outer pad 58 is reversed as compared with the disc brake device 10 described above. However, even in such a configuration, by adjusting the angle of the seat 65 so as to control the angle θ formed by the first straight line l ₀ and the second straight line l ₁ , working component force F ₁ and acts in the radial direction can be changed the proportion of component force F _2, is not necessary to form the pad clip is also changed.

  Further, the problem of the gap between the through hole 66 and the slide pin 24 is opposite to that of the disc brake device 10 according to the first embodiment described above. For this reason, in this embodiment, it was set as the structure which provides a flat part in the part located in the rotor radial direction outer side in the through-hole 66. FIG. By setting it as such a structure, there can exist an effect similar to the disc brake apparatus 10 which concerns on 1st Embodiment.

Also in the disc brake device 10a according to the present embodiment, the description has been made on the assumption that the couple (moment) generated in the outer pad 58 during braking works in the direction indicated by the arrow A as shown in FIG. As described above as an example of a means for producing a moment in this direction, than the distance t ₁ from the rotor center axis C ₁ to moment center of the outer pad 58, from the rotor center axis C ₁ of the through-holes 66 distance t ₂ to the center can be cited of the long case configuration. For this reason, when the assembly structure of the pad clip as described above is adopted, in the through hole 66b serving as the subsequent torque receiver, the slide pin 24b is preliminarily placed on the pressing wall surface (rotor radial inner peripheral side) in the through hole 66b. It will be pressed and generation | occurrence | production of a cronk sound (click sound) can be suppressed.

On the other hand, when the couple (moment) generated in the outer pad 58 during braking is reversed as shown by the arrow A ′ (see FIG. 16), the pad is pressed so that the pressing direction of the outer pad 58 against the slide pin 24 is reversed. A clip is attached (a pad clip is not shown). This is because in the case of a so-called pulling anchor, after the through hole 66a receives a braking torque, the outer pad 58 rotates in the couple generation direction with the through hole 66a as a base point. In this case, the relationship between the slide pin 24 and the through hole 66 is as shown in FIG. The urging by the pad clip 74 (see FIG. 8) according to the first embodiment common to the present embodiment will be described as an example. The pad clip 74 arranged on the rotor entrance side is attached to the slide pin 24a. On the other hand, the spring part 82 is brought into contact with the rotor entering side on the outer side in the rotor radial direction. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24a toward the rotor outlet side on the inner side in the rotor radial direction. As a result, in the through hole 66a, the inner peripheral surface located on the rotor turn-in side on the outer side in the rotor radial direction is biased toward the slide pin 24a. On the other hand, the pad clip 74 disposed on the rotor delivery side brings the spring portion 82 into contact with the slide pin 24b toward the rotor delivery side on the outer side in the rotor radial direction. As a result, the outer pad 58 receives a force that is pressed against the slide pin 24b toward the inner side of the rotor in the radial direction of the rotor. As a result, in the through hole 66b, the inner peripheral surface located on the rotor outlet side on the outer side in the rotor radial direction is urged toward the slide pin 24b. Even in such a configuration, as described above, by adjusting the angle of the seat 65 so as to control the angle θ formed by the first straight line l ₀ and the second straight line l ₁ , it is possible to change the ratio of the component force F ₂ acting on the component force F ₁ and the radially acting in the circumferential direction.

As shown in FIG. 21, in such a configuration, the relationship between the dominant arc and the chord in the through-hole 66 is relatively such that the dominant arc is located on the outer side in the rotor radial direction and the chord is located on the inner side in the radial direction. It will be. As an example of the means for generating the moment in such a direction, as shown in FIG. 16, the distance t ₁ from the rotor center axis C ₁ to the center of the moment of the outer pad 58 is the rotor center, as described above. A configuration in which the distance is longer than the distance t ₂ from the axis C ₁ to the center of the through hole 66 can be given.

10 ......... Disc brake device, 12 ......... Caliper, 14 ......... Caliper body, 15 ......... Piston, 16 ......... Caliper bridge part, 18 ......... Claw part, 20 ...... Arm part, 22 ......... Through hole, 24 (24a, 24b) ......... Slide pin, 26 ......... Bolt head, 28 ......... Caliper sliding part, 30 ......... Screw part, 32 ......... Outer pad sliding part 34 ......... Sleeve, 36 ......... Boot, 38 ......... Support, 40 (40a, 40b) ......... Torque receiving part, 42 ......... Screw hole, 44 ......... Installation hole, 46 ......... Support bridge part 48 ......... recess, 50 ......... pad clip, 52 ......... inner pad, 54 ......... pressure plate, 56 ......... lining, 58 ......... outer pad, 60 ......... pressure plate, 60a ......... Rate body, 60b .... Arm part, 62 ... ... Lining, 64 ... ... Projection part, 66 (66a, 66b) ... ... Through hole, 68 ... ... Second clip, 70 ... ... Base part, 72 ......... Spring part, 74 ......... Pad clip, 76 ......... Base part, 78 ......... Through hole, 80 ......... Support part, 82 ......... Spring part.

Claims (4)

A pad clip assembly structure for biasing a brake pad supported by a pair of slide pins constituting a disc brake device through a through-hole formed in a pressure plate to the slide pins,
The pad clip includes a support portion that holds a pressure plate that constitutes the brake pad, a base portion that is disposed along a plate surface of the pressure plate, and a spring portion that abuts against the slide pin and generates a biasing force. And
The brake pad is provided with a seat that is a side for attaching the support portion of the pad clip,
By setting an angle between a first straight line along the rotor radial direction passing through the center of the arc portion constituting the through hole and a second straight line passing through the center and perpendicular to the seat, the pad An assembly structure of a pad clip, characterized in that the ratio of the component force in the rotor radial direction and the rotor circumferential direction in the urging force by the clip is changed.   The pad clip assembly structure according to claim 1, wherein the angle of the seat is set so that an angle formed by the first straight line and the second straight line is less than 45 degrees.   2. The pad clip assembling structure according to claim 1, wherein the angle of the seat is set so that an angle formed by the first straight line and the second straight line is 45 degrees.   2. The pad clip assembling structure according to claim 1, wherein the angle of the seat is set so that an angle formed by the first straight line and the second straight line is greater than 45 degrees.

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