JP2013072501A - Disk brake apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk brake apparatus that achieves the weight reduction and the reduction in manufacturing costs of the disk brake apparatus while configured to directly receive braking torque of the outer brake pad by a support.SOLUTION: The disk brake apparatus includes a caliper held to a support via a guide pin so as to be slidable in the rotor axial direction, and is configured such that an outer brake pad is loosely fitted and held to a claw part of the caliper. The support includes: a pair of rotor pass parts respectively provided protruding from each of a pair of inner torque receiving parts so as to straddle a rotor; and a pair of outer torque receiving parts each provided at the tip side of the rotor pass part. The width between the pair of outer torque receiving parts and the width of the outer brake pad in the circumferential direction of the rotor are determined so that a gap provided in the circumferential direction of the rotor in the loosely fitted state of the outer brake pad with respect to the claw part is larger than a gap provided between the outer brake pad and the outer torque receiving parts.

Description

  The present invention relates to a caliper floating type disc brake device that is applied to a disc brake device and receives a braking torque by a support.

  As a caliper floating type disc brake device that receives a braking torque by a support, the one disclosed in Patent Document 1 is known. As shown in FIG. 26, the disc brake device disclosed in Patent Document 1 is configured based on a support 2, brake pads 3 a and 3 b held by the support 2, and a caliper 4. In the disc brake device 1 shown in FIG. 26, only the torque receiving portion of the support 2 that holds the brake pads 3a and 3b is directly configured to receive the braking torque (the pressing force of the brake pad) at the time of braking.

  For this reason, on the outer side of the support 2, a bridge 2 a that connects the torque receiving portion arranged on the output side of the rotor 9 and the torque receiving portion arranged on the introduction side is provided. Measures are taken to increase

  However, when the bridge 2a is provided on the outer side of the support 2 as in the disc brake device 1 disclosed in Patent Document 1, the weight of the disc brake device increases as the size of the disc brake device increases. .

On the other hand, Patent Disclosures 2 and 3 disclose disc brake devices that eliminate the outer side bridge in the support and are reduced in size and weight.
In the disc brake device disclosed in Patent Document 2, as shown in FIG. 27, the brake pad 3 a disposed on the outer side of the rotor 9 is engaged with the recess 4 a 1 formed in the claw portion 4 a constituting the caliper 4. Convex portion 3a1. The form of the support 2 is asymmetrical between the rotor inlet side and the rotor outlet side, and only the torque receiving portion 2b located on the rotor outlet side when the vehicle moves forward is arranged on the outer side across the rotor. It is configured.

  In the disc brake device 1a having such a feature, the braking torque generated when the vehicle moves forward is received by the torque receiving portion constituting the support 2 on both the inner side and the outer side. On the other hand, the braking torque generated when the vehicle moves backward is received by the torque receiving portion of the support 2 on the inner side, and is transmitted to the caliper 4 via the convex portion 3a1 formed on the outer brake pad on the outer side, and is supported via the caliper 4. 2 will be transmitted.

  Further, as shown in FIG. 28, the disc brake device disclosed in Patent Document 3 also has a configuration in which the outer brake pad 3 a is unevenly fitted to the claw portion 4 a constituting the caliper 4. In the disc brake device 1b disclosed in Patent Document 3, as shown in FIG. 29, the gap A between the guide pin 5a on the rotor turn-in side and the slide sleeve 6a on which the guide pin 5a slides, and the rotor The relationship between the clearance B between the guide pin 5b on the delivery side and the slide sleeve 6b and the clearance C between the outer peripheral portion of the slide sleeve 6b and the ear portion (protruding outer edge portion) of the outer brake pad 3a is expressed as A <B <C. With this relationship, the number of locations serving as torque receiving portions for the outer brake pad 3a is increased stepwise in accordance with the strength of the braking torque.

  Specifically, at the time of initial braking, a braking torque is received and transmitted to the support 2 by the contact between the guide pin 5a on the rotor turn-in side and the slide sleeve 6a. When the braking torque increases, the guide pin 5b on the rotor delivery side and the slide sleeve 6b also come into contact with each other and receive the braking torque at two locations on the rotor delivery side and the delivery side. When the braking torque further increases, the outer peripheral surface of the rotor delivery-side slide sleeve 6b comes into contact with the ear portion of the outer-side brake pad 3a, and the braking torque is received at three points. Thereby, even if it is a case where the outer side bridge part is not provided in the support 2, it becomes possible to suppress the distortion of the caliper 4 and the support 2 at the time of braking to the minimum.

Japanese Patent Laid-Open No. 10-30659 JP 2000-104764 A JP-A-10-26152

  Among the disc brake devices configured as described above, the disc brake device disclosed in Patent Document 2 is configured to delete not only the outer bridge portion of the support but also the rotor path portion straddling the rotor. It can be said that the disc brake device is excellent in terms of reduction in size and weight. However, the configuration in which the braking torque at the time when the vehicle advances in the outer brake pad is received only by the torque receiving portion on the rotor delivery side may cause distortion in the support. In addition, the configuration in which the form of support is asymmetrical between the inlet side and the outlet side of the rotor requires that different types of supports be used on the left and right sides of the vehicle when assembled to the vehicle, which complicates inventory management. And, there is a risk that the manufacturing cost will increase.

  On the other hand, according to the disc brake device disclosed in Patent Document 3, the torque receiving portion is increased stepwise according to the braking torque, and as a result, the rotor on the outer side brake pad is turned on and off. Both are configured to receive braking torque. For this reason, the distortion which arises in a caliper or a support can be suppressed small, and the support used on the right and left of a vehicle can be made the same.

  However, the disc brake device configured as disclosed in Patent Document 3 is configured to receive the braking torque by eliminating the sliding gap between the guide pin and the slide sleeve. For this reason, there is a concern about deterioration in caliper sliding characteristics due to an increase in sliding resistance and accompanying brake performance.

  Accordingly, an object of the present invention is to provide a disc brake device capable of reducing the weight of the disc brake device and reducing the manufacturing cost while adopting a configuration in which the braking torque in the outer brake pad is directly received by the support.

  In order to achieve the above object, a disc brake device according to the present invention includes a caliper that is supported so as to be slidable in the rotor axial direction with respect to a support via a guide pin, and is arranged on the outer side of the claw portion of the caliper. A disc brake device configured to loosely fit and hold a brake pad, wherein the support is disposed on an inner side of the rotor and is disposed on a rotor entrance side and an exit side, and an inner brake The rotor so as to straddle the rotor from each of an inner side torque receiving portion that receives braking torque by the pad, an inner side bridge portion that connects the pair of inner side torque receiving portions, and the pair of inner side torque receiving portions. A pair of rotor path portions projecting in the axial direction of the rotor, and the outer side brake pad at the tip side of the rotor path portion. A pair of outer side torque receiving portions that receive torque is provided, and the outer side brake pad is in a loosely fitted state with respect to the claw portion, rather than a gap provided between the outer side brake pad and the outer side torque receiving portion. A disc brake device characterized in that a width between the pair of outer side torque receiving portions and a width in the circumferential direction of the rotor at the outer side brake pad are determined so that a gap in a circumferential direction becomes large.

  In the disc brake device having the above-described characteristics, the outer side torque receiving portion preferably has a torque receiving surface formed by flat processing the rotor path portion.

  By having such a feature, it is possible to simplify the cutting process during manufacturing. Specifically, broaching with a special tool is not necessary. In addition, between the disc brake devices having different rotor diameters, it becomes easy to apply the change in the amount of deviation in the rotor radial direction on the torque receiving surface, so that it is easy to share the brake pad shape.

  In the disc brake device having the above-described characteristics, the outer brake pad and the claw portion may be loosely fitted by providing a convex portion on the outer brake pad and a concave portion on the claw portion.

  In such a configuration, the convex portion of the outer brake pad can be formed by press working, and the through hole can be formed by cutting. On the other hand, when this is reversed, a special cutting process for forming a convex part inside a nail | claw part is needed.

  Further, in the disc brake device having the above-described features, the convex portion has an elliptical or elliptical plan view configuration in which the major axis is directed in the radial direction of the rotor and the minor axis is oriented in the circumferential direction, It is preferable that the concave portion has a circular shape having a diameter longer than the major axis in plan view.

  By having such a feature, the movement in the rotor circumferential direction can be given a greater degree of freedom than in the radial direction while restricting the movement of the outer brake pad in the rotor radial direction.

  Furthermore, in the disc brake device having the above-described features, the convex portion has a circular shape in plan view, and the concave portion has an elliptical shape in which the major axis is oriented in the circumferential direction of the rotor and the minor axis is oriented in the radial direction. Or it may have an elliptical plan view form, and the length of the short axis may be longer than the diameter of the circle.

  Also by having such a feature, the movement in the circumferential direction of the rotor can be given a greater degree of freedom than in the radial direction while restricting the movement of the outer brake pad in the radial direction of the rotor, as in the above configuration. it can.

  According to the disc brake device having the above-described features, the disc brake device can be reduced in weight and the manufacturing cost can be reduced while the braking torque in the outer brake pad is directly received by the support.

It is a front view of the disc brake device concerning an embodiment. It is a right side sectional view of the disc brake device concerning an embodiment. It is a fragmentary sectional top view of the disc brake device concerning an embodiment. It is a rear view of the disc brake device concerning an embodiment. It is a lower right perspective view of the disc brake device concerning an embodiment. It is an upper right side perspective view of the disc brake device concerning an embodiment. It is a front view of the support in the disc brake device concerning an embodiment. It is a right view of the support in the disc brake device concerning an embodiment. It is a top view of the support in the disc brake device concerning an embodiment. It is a rear view of the support in the disc brake device concerning an embodiment. It is a front view of the caliper in the disc brake device concerning an embodiment. It is a right view of the caliper in the disc brake device concerning an embodiment. It is a rear view of the caliper in the disc brake device concerning an embodiment. It is a front view of an inner side brake pad. It is a right view of an inner side brake pad. It is a rear view of an inner side brake pad. It is a front view of an outer side brake pad. It is AA sectional drawing of an outer side brake pad. It is BB sectional drawing of an outer side brake pad. It is a rear view of an outer side brake pad. It is a perspective view of the outer side brake pad which assembled | attached the butterfly spring. It is a figure for demonstrating the relationship of the clearance gap between a support, an outer side brake pad, and a caliper. It is a rear view which shows the structure of the outer side brake pad at the time of making a convex part into an elliptical shape. It is a front view which shows the example of the disc brake apparatus which made the through-hole oval and the convex part circular. It is a front view which shows the example of the disc brake apparatus at the time of providing a through-hole in a nail | claw part main body. It is a fragmentary sectional top view which shows the structure of the conventional disc brake apparatus which has an outer side bridge | bridging in a support. It is a fragmentary sectional top view which shows the structure of the conventional disc brake apparatus which made the form of the support an asymmetry. It is a fragmentary sectional top view which shows the structure of the conventional disc brake apparatus which engages an outer side brake pad with a caliper and inputs braking torque to a support via a caliper and a guide pin. It is a figure for demonstrating the magnitude relationship of the clearance gap in the guide pin and guide sleeve in the conventional disc brake apparatus shown in FIG. 28, and an outer side brake pad.

Hereinafter, embodiments of the disc brake device according to the present invention will be described in detail with reference to the drawings.
First, the disc brake device according to the first embodiment will be described with reference to FIGS. Here, FIG. 1 is a front view of the disc brake device according to the present embodiment. FIG. 2 is a right side sectional view of the disc brake device according to the present embodiment. FIG. 3 is a partial sectional plan view of the disc brake device according to the present embodiment. FIG. 4 is a rear view of the disc brake device according to the present embodiment. FIG. 5 is a lower right perspective view of the disc brake device according to the present embodiment. Furthermore, FIG. 6 is a right upper perspective view of the disc brake device according to the present embodiment. 7 to 22 are drawings of each element constituting the disc brake device according to the present embodiment, and details will be described later.

  The disc brake device 10 according to the present embodiment is configured based on a support 12, a caliper 30, an inner side brake pad 60, an outer side brake pad 80, and a rotor 100. Here, the rotor 100 (not shown in its entirety) is a ring-shaped friction plate that rotates together with wheels (not shown), and the friction surface is sandwiched between an inner brake pad 60 and an outer brake pad 80, which will be described in detail later. Thus, a frictional force is generated on the sliding surface, the rotation of the wheel is suppressed, and a braking force is obtained.

  As shown in FIGS. 7 to 10, the support 12 includes a pair of inner side torque receiving portions 14a and 14b, an inner side bridge portion 28, rotor path portions 22a and 22b, and a pair of outer side torque receiving portions 24a and 24b. Configured as a base. 7 is a front view of the support, FIG. 8 is a right side view, FIG. 9 is a plan view, and FIG. 10 is a rear view.

  Both the inner side torque receiving portions 14a and 14b and the outer side torque receiving portions 24a and 24b receive a braking torque from an inner side brake pad 60 or an outer side brake pad 80, which will be described in detail later, and play a role of generating a braking force.

  The inner side torque receiving portions 14a and 14b are respectively arranged on the rotor entrance side and the exit side along the circumferential surface of the rotor. Between the inner side torque receiving portion 14b disposed on the rotor revolving side and the inner side torque receiving portion 14a disposed on the rotor retreating side, an inner side bridge portion 28 is provided to connect both from the front. The projection surface is configured to be substantially U-shaped (see, for example, FIG. 7).

  Mounting holes 16, guide holes 18a and 18b, and torque receiving surfaces 20a and 20b are formed in the inner side torque receiving portions 14a and 14b. The attachment hole 16 is a hole for fixing the support 12 to the vehicle. In the present embodiment, the attachment hole 16 is provided on the lower side of the pair of inner side torque receiving portions 14a and 14b. By providing a plurality of mounting holes 16, it is possible to prevent rotation of the fixed support 12. The mounting hole 16 is formed with a thread and forms a body of a female screw hole.

  The guide holes 18a and 18b are bag holes into which guide pins 50a and 50b for sliding a caliper 30 whose details will be described later in the rotor axial direction can be inserted. The guide holes 18a and 18b are provided at locations on the outer peripheral side of the rotor 100 in a state where the disc brake device 10 is assembled. Further, the guide holes 18a and 18b are perforated to the rotor path portions 22a and 22b arranged on the outer peripheral side of the rotor 100, thereby preventing dust from adhering to the guide pins 50a and 50b, and the guide pins 50a and 18b. A sliding amount of 50b can be ensured.

  The torque receiving surfaces 20a and 20b are cutting surfaces formed on opposing surfaces of the inner side torque receiving portions 14a and 14b disposed on the turning-in side and the turning-out side of the rotor 100, respectively. In the case of the present embodiment, the torque receiving surfaces 20a, 20b in the inner side torque receiving portions 14a, 14b are provided on the lower side of the locations where the guide holes 18a, 18b are formed, a step portion is provided on the upper portion thereof, and the inner brake pad 60 It was decided to constitute a flank. By causing the torque receiving surfaces 20a and 20b to be formed closer to the connecting portion between the inner side torque receiving portions 14a and 14b and the inner side bridge portion 28, the distortion of the support 12 when braking torque is applied can be suppressed. In addition, the torque receiving surfaces 20a and 20b are only one surface facing each other on the rotor entrance side and the exit side, so that the cutting surface can be only the facing surface.

  The outer side torque receiving portions 24a and 24b have torque receiving surfaces 26a and 26b. The outer side torque receiving portions 24a and 24b in the support 12 according to the present embodiment are configured by extending portions on the front end side of the rotor path portions 22a and 22b in which the guide holes 18a and 18b are bored. By simplifying the configuration of the outer side torque receiving portions 24a and 24b, the support 12 can be reduced in size and weight.

  The torque receiving surfaces 26a, 26b in the outer side torque receiving portions 24a, 24b are plane-cutting the opposing surfaces of the rotor entrance side and the outlet side in the rotor path portions 22a, 22b constituting the outer side torque receiving portions 24a, 24b ( (Flat processing). By forming the torque receiving surfaces 26 a and 26 b in this manner, the surface that needs to be processed is only one surface that comes into contact with the outer brake pad 80. For this reason, even when the radius of the rotor 100 changes, the contact portions of the torque receiving surfaces 26a and 26b and the contact surfaces 92a and 92b of the outer brake pad 80 are only shifted in the rotor radial direction. It is easy to make the pad shape common.

  In the support 12 configured as described above, the inner side torque receiving portions 14a and 14b and the outer side torque receiving portions 24a and 24b have only one processed surface by cutting. This makes it easy to process with general-purpose equipment, eliminates the need for broaching with special tools such as conventional grooving and milling, improves processability, and reduces processing time and costs. Can do.

  As shown in FIGS. 11 to 13, the caliper 30 is configured based on a caliper body 32, claw portions 44 a and 44 b, and a bridge portion 42. 11 shows a front view of the caliper, FIG. 12 shows a right side view of the caliper, and FIG. 13 shows a rear view of the caliper.

  The caliper body 32 is disposed on the inner side of the rotor 100 and includes a cylinder 34 and arm portions 38a and 38b. As shown in FIG. 2, the cylinder 34 is provided with a groove for providing an oil seal 34a and a dust seal 34b, and a cup-shaped piston 36 is disposed therein. The piston 36 is disposed with the cup bottom facing the bottom side of the cylinder 34. With such a configuration, the piston 36 is pushed out to the rotor 100 side as the hydraulic oil flows into the cylinder 34. The cylinder 34 is preferably disposed at a position facing the sliding surface of the rotor 100 in a state where the caliper 30 is assembled to the support 12. This is because loss and bias are less likely to occur in the transmission of force to the inner brake pad 60 that presses against the rotor 100.

  The arm portions 38 a and 38 b are base points when the caliper 30 is assembled to the support 12, and extend from the outer wall of the cylinder 34 as a base point so as to form a pair on both the inlet side and the outlet side of the rotor 100. Yes. Female screw holes 40a and 40b for screwing guide pins 50a and 50b, which will be described in detail later, are formed at the distal ends of the arm portions 38a and 38b. Since the guide pins 50a and 50b are inserted into the guide holes 18a and 18b described above, the caliper 30 can be slid in the axial direction, so that the center pitch of the guide holes 18a and 18b in the support 12 and the arm The center pitches of the female screw holes 40a and 40b in the portions 38a and 38b are configured so as to coincide with each other.

  The guide pins 50a and 50b are pins provided with sliding portions 52a and 52b, fixing portions 54a and 54b, and bolt heads 56a and 56b (see FIG. 3). The sliding portions 52a and 52b have a diameter slightly smaller than the diameter of the guide holes 18a and 18b in the support 12, and the length may be at least the sliding distance of the caliper 30. As a result, the guide pins 50a and 50b can be inserted into and slid into the guide holes 18a and 18b. The fixing portions 54a and 54b have male screws that can be screwed into the female screw holes 40a and 40b provided in the arm portions 38a and 38b. With such a configuration, the guide pins 50a and 50b can be fixed to the arm portions 38a and 38b by tightening via the bolt heads 56a and 56b. Needless to say, the diameters of the sliding portions 52a and 52b are smaller than the fixing portions 54a and 54b due to the structure of the assembly. In the present embodiment, a constricted portion 58 is formed at the boundary position between the sliding portions 52a and 52b and the fixed portions 54a and 54b, and the boot 59 covers between the inlets of the guide holes 18a and 18b and the constricted portion 58 in the assembled state. It is set as the structure which provides. The boot 59 is a covering member formed in an accordion shape by an elastic member such as rubber, and extends and retracts in the axial direction of the rotor 100 in accordance with the sliding of the guide pins 50a and 50b, thereby entering and exiting the guide holes 18a and 18b. It plays the role which prevents that dust adheres to the sliding parts 52a and 52b which do.

  The claw portions 44 a and 44 b are reaction force receivers that are disposed on the outer side of the rotor 100 and are provided as a pair on the turn-in side and the turn-out side of the rotor 100 so as to sandwich the facing position of the cylinder 34 in the caliper body 32. Overhanging flange portions 46b and 46a are formed on the turn-in side of the claw portion 44b disposed on the turn-in side of the rotor 100 and on the turn-out side of the claw portion 44a disposed on the turn-out side of the rotor 100, respectively. Has been. The flange portions 46a and 46b are provided with through holes 48a and 48b into which the convex portions 88a and 88b of the outer brake pad 80 described later in detail are loosely fitted. By loosely fitting the protrusions 88a and 88b into the through holes 48a and 48b, it is possible to play both the role of holding the outer brake pad 80 and preventing rotation.

  As can be read from FIGS. 11 and 13, the flange portions 46 a and 46 b are provided at a position where the projection surface avoids the cylinder 34 in the caliper body 32, that is, a position that does not overlap the formation position of the cylinder 34. With this configuration, the through holes 48a and 48b can be easily formed from the caliper body 32 side. This is because if the through holes 48a and 48b are formed from the caliper main body 32 side, burrs are not generated when the through holes are formed on the rotor facing surfaces of the flange portions 46a and 46b.

  In addition, the flange portions 46a and 46b are provided on the turn-in side and the turn-out side of the claw portions 44a and 44b, respectively, and the through holes 48a and 48b (including recesses) are provided in the flange portions 46a and 46b. The pitch between the through holes 48a and 48b (including the recesses) can be increased as compared with the configuration in which the through holes and the recesses are directly provided in the claw portions 44a and 44b. As a result, even if the radial play (play) between the convex portions 88a and 88b of the outer brake pad 80 is the same, the outer brake pad 80 has a longer distance from the center of the caliper 30. The backlash in the direction of rotating can be reduced.

  The bridge portion 42 is a connecting portion that connects the caliper main body 32 and the claw portions 44 a and 44 b across the outer periphery of the rotor 100. An opening 42 a is provided at the center of the bridge portion 42, thereby forming a caliper 30 having a so-called open back structure. The opening 42a plays a role of visually radiating frictional heat generated during braking and visually confirming the degree of lining reduction in a brake pad, which will be described in detail later.

  The inner brake pad 60 is a brake pad held by the piston 36 in the caliper body 32. As shown in FIGS. 14 to 16, the inner brake pad 60 is configured based on a pressure plate 62 and a lining 72. 14 is a front view of the inner brake pad, FIG. 15 is a right side view of the inner brake pad, and FIG. 16 is a rear view of the inner brake pad.

  The pressure plate 62 in the inner brake pad 60 has a plate body 62a and ear portions 70a and 70b. The front projection shape of the plate body 62a has an arc shape along the shape of the sliding surface of the rotor 100, and a plurality of concave grooves 64 for preventing displacement of the lining 72 are provided on the lining application surface (example of embodiment). There are two). On the other hand, a convex spring assembly portion 66 for fixing an assembly spring 74 (see FIG. 2) to a surface (hereinafter referred to as the back surface) opposite to the lining application surface (hereinafter referred to as the front surface). Is formed. The spring assembly 66 may be formed by embossing. Abutment surfaces 68a and 68b are formed on the rotor entrance side and the exit side of the plate body 62a, respectively. The contact surfaces 68 a and 68 b play a role of transmitting braking torque to the support 12 by contacting the torque receiving surfaces 20 a and 20 b formed on the support 12. The contact surfaces 68a and 68b of the inner brake pad 60 are provided below the center of gravity of the brake pad so as to face the torque receiving surfaces 20a and 20b of the inner torque receiving portions 14a and 14b.

  The ears 70a and 70b are provided on the upper portions of the contact surfaces 68a and 68b of the plate main body 62a described above so as to protrude to the entrance side and the exit side of the rotor 100, respectively. The support 12 is hooked on the step between the torque receiving surfaces 20a, 20b and the rotor path portions 22a, 22b having the guide holes 18a, 18b.

  The lining 72 is a friction member that makes contact with the sliding surface of the rotor 100. The front projection shape of the lining 72 is a sector shape along the shape of the sliding surface of the rotor 100. The rotor facing surface of the lining 72 is formed flat, and grooves (not shown) for the purpose of discharging dust and radiating heat are formed as necessary. On the facing surface of the plate main body 62a in the lining 72, a convex portion that fits into the concave groove 64 formed in the plate main body 62a is formed. The lining 72 and the plate body 62a may be joined with a heat resistant adhesive or the like.

  As shown in FIG. 2, the inner brake pad 60 having such a basic configuration has an assembly spring 74 assembled to a spring assembly 66 formed on the plate body 62a, and the assembly spring 74 is cup-shaped. The piston 36 is held by the caliper 30 by urging the inner wall of the recess.

  The outer brake pad 80 is a brake pad that is held by a butterfly spring 96 with the through holes 48a and 48b formed in the claw portions 44a and 44b (the flange portions 46a and 46b of the claw portions 44a and 44b) as a base point. Similar to the inner brake pad 60, the outer brake pad 80 is configured based on a pressure plate 82 and a lining 94. 17 to 20 are views showing the configuration of the outer side brake pad, FIG. 17 is a front view of the outer side brake pad, FIG. 18 is a cross-sectional view taken along line AA in FIG. 17, and FIG. FIG. 20 is a rear view of the outer brake pad.

  The pressure plate 82 includes a plate body 82a and ear portions 90a and 90b. Similar to the inner brake pad 60, a concave groove 84 for attaching the lining 94 is provided on the lining application surface (hereinafter referred to as the surface) of the plate body 82a. On the other hand, a convex spring assembly portion 86 for fixing a butterfly spring 96 for holding the outer brake pad 80 on the surface opposite to the lining application surface (hereinafter referred to as the back surface), and a claw portion Convex portions 88a and 88b are formed to be loosely fitted in through holes 48a and 48b formed in the flange portions 46a and 46b of 44a and 44b.

  In the outer brake pad 80 according to the present embodiment, the shape of the convex portions 88a and 88b is an oval shape. Specifically, the long axis is an axis arranged along the radial direction of the rotor 100 and the short axis is an axis arranged along the circumferential direction. With such a configuration, a gap provided in the radial direction of the rotor 100 and a gap provided in the circumferential direction in relation to the circular through holes 48a and 48b formed in the flange portions 46a and 46b. Can be different. In the case of the convex portions 88 a and 88 b according to the present embodiment, the gap provided in the circumferential direction is larger than the gap provided in the radial direction of the rotor 100. In addition, the spring assembly part 86 and the convex parts 88a and 88b can be formed by embossing. In addition, when the spring assembly part 86 and the convex parts 88a and 88b are formed by embossing, a concave part is formed at the position where the spring assembly part 86 and the convex parts 88a and 88b are formed at corresponding positions on the surface. It will be.

  The ears 90a and 90b are extended from the rotor turn-in side end and the turn-out side end of the plate body 82a toward the turn-in side and the turn-out side, respectively. The outer brake pad 80 forms contact surfaces 92a and 92b on the ears 90a and 90b. For this reason, it is necessary to match the arrangement height of the ear portions 90a and 90b with the torque receiving surfaces 26a and 26b of the outer side torque receiving portions 24a and 24b formed at the tips of the rotor path portions 22a and 22b. Therefore, the ear portions 90a and 90b of the outer brake pad 80 are extended with an inclination toward the radially outer side of the rotor 100, and the entrance side end portion and the delivery side end portion are brought into contact with each other. 92a and 92b. For this reason, the contact surfaces 92a and 92b of the outer brake pad 80 are arranged on the outer peripheral side of the rotor 100, that is, on the outer side in the radial direction from the center of the brake pad.

  Assembling the outer brake pad 80 to the claws 44a and 44b allows the protrusions 88a and 88b to be loosely fitted into the through holes 48a and 48b of the flanges 46a and 46b, and using the butterfly spring 96, the outer brake pad. 80 is applied to the claw portions 44a and 44b. Specifically, the claw portions 44 a and 44 b may be sandwiched between the back surface of the plate body 82 a in the outer brake pad 80 and the butterfly spring 96. As in the present embodiment, the pinch position of the butterfly spring 96 and the loosely fitting position of the convex part 88a, 88b and the loosely fitting position of the convex parts 88a, 88b are shifted in a plane, thereby loosely fitting the convex part 88b, 88b. As compared with the case where the positions coincide with each other, it is possible to obtain an effect that the assembling property is remarkably increased.

Next, the operation at the time of braking in the disc brake device 10 having the above configuration will be described.
First, hydraulic oil is supplied into the cylinder 34 of the caliper body 32 in the caliper 30. As the hydraulic oil is supplied, the piston 36 accommodated in the cylinder 34 protrudes toward the rotor 100 side. By projecting the piston 36, the inner brake pad 60 held by the piston 36 is pressed against the sliding surface of the rotor 100.

  When the inner brake pad 60 is pressed against the sliding surface of the rotor 100, the reaction force is received, and the caliper body 32 moves away from the rotor 100 with the guide pins 50a and 50b as base points. As the caliper body 32 moves, the claw portions 44a and 44b connected by the bridge portion 42 are attracted to the sliding surface side of the rotor 100 on the rotor outer side. Since the outer side brake pad 80 is held by the claw portions 44 a and 44 b, the rotor 100 is sandwiched between both the inner side brake pad 60 and the outer side brake pad 80.

  When the rotor 100 is sandwiched between the inner brake pad 60 and the outer brake pad 80, the inner brake pad 60 and the outer brake pad 80 generate frictional force between the rotor 100 and the rotor 100, respectively. Receive the force in the direction to do. And the inner side brake pad 60 contacts the torque receiving surface 20a of the inner side torque receiving part 14a arrange | positioned at the rotor delivery side, and a braking torque is transmitted to the support 12. FIG.

  The outer side brake pad 80 also contacts the torque receiving surface 26a of the outer side torque receiving portion 24a disposed on the rotor delivery side at the initial stage of braking. Thereafter, when the braking torque increases, the outer side torque receiving portion 24a provided on the rotor delivery side moves so as to be slightly bent toward the rotor delivery side. When the outer side torque receiving portion 24a provided on the rotor outlet side is slightly bent, the outer side brake pad 80 moves toward the rotor outlet side by the amount of the deflection. Along with this movement, the protrusions 88a and 88b formed on the outer brake pad 80 come into contact with the inner surface of the rotor delivery side of the through holes 48a and 48b formed in the flange portions 46a and 46b. When the convex portions 88a and 88b in the outer brake pad 80 come into contact with the inner peripheral surfaces of the through holes 48a and 48b in the flange portions 46a and 46b, the braking torque is transmitted to the caliper 30 and the caliper 30 moves in the direction of rotating the rotor. .

When the caliper 30 moves in the direction of rotation of the rotor 100, the guide pin 50 b fixed to the arm portion 38 b on the rotor rotation side of the caliper 30 is the inner peripheral surface of the guide hole 18 b formed in the support 12 (rotor rotation side). Contact the inner peripheral surface). Due to this contact, braking torque is transmitted to the support 12.
Since the support 12 is fixed to the vehicle main body via the mounting hole 16, it is possible to receive the braking torque transmitted from the brake pad.

  As described above, in order to distribute the braking torque applied to the outer side torque receiving portions 24a and 24b, the torque receiving surface 26a (26b) of the outer side torque receiving portion 24a (24b) and the outer side brake pad 80 are arranged. The clearance between the contact surface 92a (92b) is A, and the circumferential clearance between the protrusions 88a and 88b of the outer brake pad 80 and the through holes 48a and 48b of the flange portions 46a and 46b of the claw portions 44a and 44b. B, where C is the clearance between the guide pin 50b and the guide hole 18b on the rotor entry side, and ΔA is the amount of deflection of the outer side torque receiving portion 24a when braking torque is applied, respectively, (See FIG. 22).

  First, in the relationship between the gap A and the gap B, the relationship of the gap A <the gap B is satisfied. That is, by having a relationship of gap A <gap B, the contact surface 92a comes into contact with the torque receiving surface 26a before the through holes 48a and 48b and the projections 88a and 88b come into contact with each other.

  Next, (gap B−gap A) has a relationship of being smaller than the deflection amount ΔA (that is, (B−A) <ΔA). By having such a relationship, when the outer side torque receiving portion 24a bends to the rotor outlet side as the braking torque increases, the outer side brake pad 80 moves to the rotor outlet side. Accordingly, the convex portions 88 a and 88 b come into contact with the inner circumferential surface of the rotor delivery side in the through holes 48 a and 48 b, and braking torque is input to the caliper 30.

  Then, (deflection amount ΔA− (gap B−gap A)) is made larger than the gap C (that is, (ΔA− (B−A))> C). With such a relationship, the guide pin 50b comes into contact with the inner peripheral surface of the guide hole 18b within the range of the deflection amount ΔA, and the braking torque is applied to the outer side torque receiving portion 24b (support 12) on the rotor turn-in side. Will be input.

  In the disc brake device 10 having such a configuration and action, in the outer brake pad 80, in the normal braking range, the torque receiving portion (outer side torque receiving portion 24a) on the rotor delivery side receives the braking torque. In the load region, braking torque is also input to the caliper 30 via the convex portions 88a and 88b, and braking torque is also applied to the turning-in side torque receiving portion (outer side torque receiving portion 24b) via the rotor turning-in side guide pin 50b. Will be entered. For this reason, the braking torque is input in a stepwise manner according to the magnitude of the braking torque, and the outer side bridge of the support 12 becomes unnecessary.

  Therefore, in this embodiment, at least the width between the pair of outer side torque receiving portions 24a and 24b and the width in the circumferential direction of the rotor in the outer side brake pad 80 are set so that the gap B is larger than the gap A. It has established.

  Since the outer bridge of the support 12 is not required, the support 12 can be reduced in size and weight, that is, the disc brake device 10 can be reduced in size and weight. Further, the support 12 of the disc brake device 10 according to the present embodiment is provided with the outer side torque receiving portions 24a and 24b at the tip portions of the rotor path portions 22a and 22b. For this reason, compared with the conventional support in which the inner side torque receiving portion, the outer side torque receiving portion, and the rotor path portion have an inverted U-shape in a side view, the casting can be easily formed. Furthermore, the cutting surfaces of the inner side torque receiving portions 14a and 14b and the outer side torque receiving portions 24a and 24b can be only one surface with which the brake pad comes into contact, and the workability is good. In addition, since there is no complicated grooving when the support 12 is cut, complicated control in broaching or milling using a special tool is not required.

  Further, the convex portions 88a and 88b of the outer brake pad 80 are formed into an ellipse having a major axis in the radial direction of the rotor 100 and a minor axis in the circumferential direction, so that the circular through holes 48a and 48b are in the radial direction. The backlash can be reduced and the backlash in the circumferential direction can be increased. For this reason, by adjusting the clearance between the through holes 48a and 48b and the projections 88a and 88b, the timing at which the braking torque for the support 12 is distributedly input can be adjusted.

  In the above embodiment, the convex portions 88a and 88b provided on the outer brake pad 80 are oval, but the shape of the convex portions 88a and 88b is not limited to this, and may be an elliptical shape as shown in FIG. This is because even if the shapes of the convex portions 88a and 88b are elliptical, the same effects as those of the disc brake device 10 according to the above embodiment can be obtained.

  Moreover, in the said embodiment, although the convex parts 88a and 88b were made oval and the through-holes 48a and 48b were circular, this is an example when emphasizing workability at the time of mass production, for example, as shown in FIG. In addition, even when the protrusions 88a and 88b are circular and the through holes 48a and 48b are oval, the same effects as those of the disc brake device 10 according to the above embodiment can be obtained. Here, the oval through holes 48 a and 48 b are formed with the long axis as the circumferential direction of the rotor 100 and the short axis as the radial direction of the rotor 100. This is because it is possible to give freedom in the circumferential direction while restricting the movement of the convex portions 88a and 88b having a circular front projection shape in the rotor radial direction.

  In the above embodiment, the workability in the caliper 30 is emphasized, and the through holes 48a and 48b for loosely fitting the convex portions 88a and 88b in the outer brake pad 80 are the flange portions 46a and 46b in the claw portions 44a and 44b. 46b was formed. However, the through holes 48a and 48b may be formed in the claw portions 44a and 44b as shown in FIG. 25, and may be bag holes having openings inside the claw portions 44a and 44b.

  In order to solve the problems in the present invention, the loose fitting state between the claw portions 44a and 44b and the outer brake pad 80 is ensured, and the circumferential direction between the outer brake pad 80 and the claw portions 44a and 44b is secured. It suffices if the clearance between the outer side torque receiving portions 24a, 24b and the outer side brake pad 80 in the support 12 is smaller than the backlash. For this reason, the through holes provided in the claw portions 44a and 44b do not necessarily need to be plural, and a loose fit state using the claw portions 44a and 44b main bodies may be ensured. Furthermore, the relationship between the convex portions 88a, 88b and the concave portions (through holes 48a, 48b) in the outer brake pad 80 may be similar to each other.

DESCRIPTION OF SYMBOLS 10 ......... Disc brake device, 12 ......... Support, 14a, 14b ......... Inner side torque receiving part, 16 ......... Mounting hole, 18a, 18b ......... Guide hole, 20a, 20b ......... Torque receiving Surface, 22a, 22b ......... Rotor path, 24a, 24b ......... Outer side torque receiving portion, 26a, 26b ......... Torque receiving surface, 28 ......... Inner side bridge portion, 30 ......... Caliper, 32 ... ... caliper body, 34 ... cylinder, 36 ... piston, 38a, 38b ... arm part, 40a, 40b ... female screw hole, 42 ... bridge part, 44a, 44b ... claw Part, 46a, 46b ......... Flange part, 48a, 48b ......... through hole, 50a, 50b ......... guide pin, 60 ......... inner brake pad, 62 ......... pressure plate 62a ......... plate body, 64 ......... concave groove, 66 ......... spring assembly part, 68a, 68b ...... contact surface, 70a, 70b ......... ear part, 72 ...... lining, 74 ... ..... Assembly spring, 80 ......... Outer brake pad, 82 ... Pressure plate, 82a ... Plate body, 84 ...... Groove, 86 ...... Spring assembly, 88a, 88b ... ...... Projections, 90a, 90b ......... Ears, 92a, 92b ......... Contact surface, 94 ......... Lined, 96 ......... Butterfly spring, 100 ......... Rotor.

Claims (5)

A disc brake device comprising a caliper held so as to be slidable in the rotor axial direction with respect to a support via a guide pin, and configured to hold an outer brake pad loosely fitted on a claw portion of the caliper. There,
The support is disposed on the inner side of the rotor, and is disposed on the rotor turn-in side and the turn-out side so as to receive braking torque from the inner brake pad, and the pair of inner side torques A pair of rotor path portions projecting in the axial direction of the rotor so as to straddle the rotor from each of the inner bridge portion connecting the receiving portions and the pair of inner side torque receiving portions, and the tips of the rotor path portions A pair of outer side torque receiving portions for receiving braking torque by the outer side brake pad on the side,
The clearance in the circumferential direction of the rotor in the loosely fitted state of the outer brake pad with respect to the claw is larger than the clearance provided between the outer brake pad and the outer torque receiving portion. A disc brake device characterized in that a width between a pair of outer side torque receiving portions and a width in a circumferential direction of the rotor in the outer side brake pad are defined.   The disc brake device according to claim 1, wherein the outer side torque receiving portion has a torque receiving surface formed by flattening the rotor path portion.   3. The disc brake device according to claim 1, wherein the outer brake pad and the claw portion are loosely fitted by providing a convex portion on the outer brake pad and a concave portion on the claw portion. The convex portion has a plan view form of an ellipse or an ellipse with a major axis in the radial direction of the rotor and a minor axis in the circumferential direction,
4. The disc brake device according to claim 3, wherein the recess has a circular shape having a diameter longer than the major axis in a plan view. The convex portion has a circular shape in plan view,
The concave portion has a plan view form of an ellipse or an ellipse with a major axis in the circumferential direction of the rotor and a minor axis in the radial direction,
4. The disc brake device according to claim 3, wherein a length of the short axis is longer than a diameter of the circular shape.

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