JP2010266061A - Disk brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To stabilize postures of both inner side and outer side pads 10a, 11a with respect to a calliper 5a, irrespective of a nonbraking time and a braking time, and to prevent a strange noise and vibration from being generated in pads 10a, 11a parts not only at the nonbraking time but also at the braking time. <P>SOLUTION: A pad spring 14a is assembled in between the both pads 10a, 11a and the calliper 5a. Directions of moments applied to the both pads 10a, 11a at the nonbraking time are made same respectively to directions of moments acting on the both pads 10a, 11a by forces imparted from both energizing parts 33 and both locking parts 34 constituting the pad spring 14a. The postures of the both pads 10a, 11a are thereby maintained in the same state at the nonbraking time and at the braking time, and the problem to be solved is solved thereby. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The disc brake according to the present invention is used for braking an automobile. In particular, the present invention improves the structure of the pad spring to prevent a pair of pads from rattling during non-braking, stabilizes the posture of both pads during braking, and not only during non-braking but also during braking. Also, it is possible to prevent the generation of abnormal noise and vibration at both the pad portions.

  Disc brakes are widely used to brake automobiles. At the time of braking by the disc brake, a pair of pads disposed on both sides in the axial direction of the rotor rotating together with the wheels are pressed against both side surfaces of the rotor by the piston. Conventionally, various types of disc brakes are known. For example, an opposed piston type disc brake having pistons on both sides of a rotor facing each other can be used stably since it can obtain a stable braking force. Patent Document 1 describes an invention relating to such an opposed piston type disc brake.

  21 to 22 show the structure described in Patent Document 1. The disc brake 1 is provided with a caliper 5 composed of an outer body portion 3 and an inner body portion 4 at a position sandwiching the rotor 2, and one or a plurality of outer cylinders 6 and inner cylinders 7 are provided in both the body portions 3 and 4. Each opening is provided in a state of being opposed to each other via the rotor 2. Then, the outer piston 8 and the inner piston 9 are fitted in the outer cylinder 6 and the inner cylinder 7 so as to be fluid-tight and displaceable in the axial direction of the rotor 2 (vertical direction in FIG. 21 and horizontal direction in FIG. 22). Disguise. Further, the outer pad 10 and the inner pad 11 are disposed on the two pad pins 12, 12 spanned between the outer body portion 3 and the inner body portion 4 at a portion radially outward from the outer peripheral edge of the rotor 2. In the suspended state, the rotor 2 can be displaced in the axial direction. For this purpose, guide holes are formed in the outer peripheral edge portions of the pressure plates 13 and 13 of the pads 10 and 11, respectively, and the pad pins 12 and 12 are loosely inserted into the guide holes.

  Further, a pad spring 14 is disposed between the pad pins 12 and 12 and the outer pad 10 and the inner pad 11. The pad spring 14 is formed by joining two metal plates 15a and 15b each having elasticity so as to intersect each other. One of the metal plates 15a is disposed between the pads 10 and 11 in parallel with the circumferential direction of the rotor 2 (left and right direction in FIG. 21). On the other hand, the other metal plate 15b is disposed in the axial direction of the rotor 2 at a substantially central portion with respect to the circumferential direction of the rotor 2 of the pads 10 and 11.

  Further, the one metal plate 15a is bent at both ends with respect to the circumferential direction of the rotor 2 in the shape of a crank inward in the radial direction to form bent portions 16 and 16, respectively. The pad pins 12 and 12 are engaged with the outer peripheral surfaces on the radially inner side. Also, the other metal plate 15b has both end portions in the axial direction of the rotor 2 folded inward to form elastic engagement portions 17 and 17, respectively. Then, the radially inner side surfaces of both the elastic engagement portions 17, 17 are elastically formed at the outer peripheral edge portions of the pressure plates 13, 13 of the both pads 10, 11 in the substantially central portion in the circumferential direction of the rotor 2. Are in contact with each other.

  The disc brake 1 configured as described above sends pressure oil into the outer cylinder 6 and the inner cylinder 7 at the time of braking, and the outer pad 10 and the inner piston 9 are used to lining 18 the outer pad 10 and the inner pad 11. , 18 are pressed against both inner and outer side surfaces of the rotor 2. Further, when the brake is released, both the pads 10 and 11 are pulled away from the side surface of the rotor 2 by the elastic force applied from the both elastic engagement portions 17 and 17 constituting the pad spring 14. On the other hand, at the time of non-braking, the both elastic engagement portions 17 and 17 apply a force inward in the radial direction to the two pads 10 and 11, and the pressure plates 13 and 13 of both the pads 10 and 11 By pressing a part of the guide holes formed in the outer peripheral edge portions against the outer peripheral surfaces of the pad pins 12 and 12 inserted through the guide holes, the pads 10 and 11 are rattled against the caliper 5. To prevent.

  In the case of the structure described in Patent Document 1 described above, by pressing both the pads 10 and 11 radially inward by the both elastic engaging portions 17 and 17 constituting the pad spring 14, It is intended to prevent rattling of the pads 10 and 11 during non-braking. However, when such a structure is adopted, the direction of the moment applied to both the pads 10 and 11 due to the friction between the side surface of the rotor 2 and the linings 18 and 18 during braking (couple rotation direction) And the pressing direction of the pad spring 14 is either the turn-in side (the side where the rotor 2 enters when moving forward) or the turn-out side (the side where the rotor 2 comes out when moving forward) of the pads 10 and 11. On the other hand, it is reversed. For this reason, the postures of both the pads 10 and 11 become unstable during braking, and are formed on the side edge portions of the pressure plates 13 and 13 constituting both the pads 10 and 11 and the caliper 5 side with braking. The generated torque receiving surface comes into contact with vigor, and abnormal noise (clonk noise) is likely to occur. Furthermore, in the case of the structure described in Patent Document 1, rattling in the circumferential direction of the pads 10 and 11 cannot be sufficiently prevented. For this reason, there is a possibility that abnormal noise is not sufficiently prevented during non-braking. In addition, a clonk noise is likely to occur at the start of braking.

  On the other hand, in Patent Document 2, as shown in FIG. 23, the pad 19 is rotated by the pad spring 14 a in the Fx direction which is the rotation direction of the rotor 2 (see FIGS. 21 to 22), and the diameter of the rotor 2. The structure which presses each to the Fy direction which is a direction is described. However, even in the case of such a structure described in Patent Document 2, the pressing direction does not coincide with the moment applied to the pad 19 during braking. Also, in any of the inventions described in Patent Documents 1 and 2, since the pad is supported by the two pad pins 12 and 12, the pad spring causes the moment to act on the pad during braking in the same direction. When energized, on the contrary, there is a possibility that rattling occurs in this pad.

JP-A-9-89018 Japanese Patent No. 3487030

  In view of the circumstances as described above, the present invention stabilizes the postures of both the inner side and outer side pads with respect to the caliper regardless of whether the brake is not applied or not applied, so that not only during non-braking but also during braking. It was invented to prevent the generation of abnormal noise and vibration at both pad portions.

Each of the disc brakes according to the present invention (described in claim 1 and claim 6) has a pair of pads, a caliper, a pad pin, and a torque receiving surface, as in the conventional disc brakes described above. And a pad spring.
Both of these pads are provided with a rotor rotating together with the wheel.
The caliper includes pistons that support the pads so as to be movable in the axial direction of the rotor, and press the pads against both side surfaces of the rotor.
The torque receiving surface is disposed on the caliper delivery side and supports torque acting on both pads during braking.
Further, the pad pin is arranged in a state where it is stretched in the axial direction of the rotor at a part of the caliper and radially outside the outer peripheral edge of the rotor. And it is each inserted in the guide hole provided in the pressure plate which comprises the said both pads.
Further, the pad spring is provided between the two pads and the caliper, and prevents rattling of these pads during non-braking.

In particular, in the disc brake according to the first aspect of the present invention, the covering portion that covers the radially outer side of the extending side portions of the two pads is provided on the extending side portion of the outer peripheral portion of the caliper. Is provided.
Of the two pressure plates, a locking hole is provided in the turn-in side portion, and a biased protrusion is provided in the outer peripheral edge portion of the output side portion.
Further, the pad pin is provided only (only one) at the entrance side portion.
Further, the pad spring is formed by bending one wire having elasticity, and includes an engaging portion, a pair of urging portions disposed substantially parallel to the engaging portion, A pair of locking portions formed by bending both ends of the wire in the axial direction of the rotor.
The engaging portion is engaged with an engaging recess formed on the inner peripheral surface of the cover portion, and the two urging portions are elastically formed on the side surfaces of the energized projections of the two urging projections. In the state of contact, both the locking portions are locked to the both locking holes, so that the line of action is applied from the two biasing portions to the turn-in side surface of the two biased protrusions. Is the direction in which the torque receiving portion provided at the delivery side edge of the pressure plates is pressed against the torque receiving surface, and the radial direction of the rotor from the rotation center of the pads. A force in a direction away from the outside is applied, and a force directed outward in the radial direction of the rotor is applied from the both locking portions to the both locking holes.
As a result, the direction of the moment applied to the two pads during braking and the direction of the moment acting on both the pads by the force (pressing force) applied from the two urging portions and the two locking portions are made the same. The rattling of these two pads is prevented.

In the disc brake according to the sixth aspect of the present invention, a biased protrusion is provided on the outer peripheral edge portion of the turn-in side portion of the pressure plates.
Further, the pad pin is provided only (only one) at the entrance side portion.
Further, the pad spring is formed by bending a metal plate having elasticity, and is provided with a locking plate portion for locking to the outer peripheral surface of the caliper and both the biased protrusions. A pair of urging plate portions to be urged, and a bending portion provided between the urging plate portions and the locking plate portion are provided.
The locking plate portion is locked to the outer peripheral surface of the caliper entry side portion, and the two biasing projection portions are connected to the two biasing projection portions while the bending portion is bent. The direction of the line of action of the two energizing plate portions from the energizing side surfaces of the two energized protrusions is directed to the extruding side. A force directed radially outward of the rotor is applied.
As a result, the direction of the moment applied to the two pads during braking and the direction of the moment acting on both the pads by the force (pressing force) applied from the two urging plate portions are the same, and the Prevents rattling.

  In the present specification and claims, unless otherwise specified, “axial direction” refers to the axial direction of the rotor, and similarly, “radial direction” refers to the radial direction of the rotor. The “circumferential direction” refers to the circumferential direction (= rotation direction) of the rotor. Further, unless otherwise specified, the “outward side” refers to the forward side when the rotor advances, and the “inward side” similarly refers to the forward side when the rotor advances.

  When the invention described in claim 1 as described above is carried out, the both locking portions are preferably mounted in a state in which a pad spring is assembled between the pads as in the invention described in claim 2. Are elastic in the direction away from each other.

  Further, when the invention described in claims 1 to 2 is carried out, it is preferable that, as in the invention described in claim 3, the two urging portions are connected to the front end portion or the intermediate portion of the two urged protrusions. A gap is provided between the two urging portions and a portion of the outer peripheral edge portions of the two pressure plates adjacent to the turn-in side of the two urging projections. .

  Further, when the invention described in claims 1 to 3 is carried out, it is preferable that, as in the invention described in claim 4, the circumferences of the two pads on the turn-in side surface of each of the biased protrusions. The inclination angle with respect to the radial direction at the central position in the direction is made larger than the inclination angle with respect to the radial direction of the turn-in side surface of the engagement recess.

  Further, when the inventions described in claims 1 to 4 are carried out, preferably, as in the invention described in claim 5, between a part of the caliper and the inflow side edge of both the pressure plates. And a pad clip formed by bending a metal plate. And with this pad clip, the force which turned to the radial direction outward of the said rotor is provided with respect to the rounding-in side edge part of the said both pressure plates.

  Further, when carrying out the invention described in claim 6 as described above, it is preferable that, as in the invention described in claim 7, of the pair of biasing plate portions, The portions in contact with the turn-in side surface are inclined in the direction toward the turn-in side as they go away from each other with respect to the axial direction of the rotor. And in the state which assembled | attached the said pad spring between a pair of said pads, the force of the direction which expands the space | interval of the revolving part of these both pads is given with respect to these both pads.

According to the disk brake of the present invention as described above, the postures of both the inner side and the outer side pads with respect to the caliper can be stabilized regardless of whether the brake is applied or not. For this reason, it is possible to prevent abnormal noise and vibration from occurring in both the pad portions not only during non-braking but also during braking (when braking is started).
That is, first, in the case of the invention described in claim 1, the direction of moment (couple rotation direction) applied to both pads due to friction between the side surface of the rotor and the lining constituting both pads during braking. The direction of the moment acting on each of the two pads is made the same by the force applied from the two urging portions and the two engaging portions constituting the wire pad spring.
Further, in the case of the invention described in claim 6, the direction of moment applied to both pads (couple rotation direction) in accordance with the friction between the side surface of the rotor and the lining constituting both pads during braking, and the plate material The direction of the moment acting on both the pads by the force applied from the two urging plate portions constituting the made pad spring is the same.
Therefore, in the case of the present invention, the non-braking postures of the two pads can be kept (restrained) in the same state as the braking posture. Therefore, the postures of the two pads at the time of braking can be stabilized. Thus, even when braking is started, it is possible to prevent the torque receiving portion and the torque receiving surface, or a part of the guide hole and the outer peripheral surface of the pad pin from colliding with each other, thereby preventing generation of an unpleasant cron sound. .
Furthermore, in the case of the invention described in claim 1, since the torque receiving part can be pressed toward the torque receiving surface by the force applied by the both urging parts, Shaking of the direction can be prevented. In addition, since the part of the guide hole can be pressed toward the radially inner peripheral surface of the pad pin by the force applied by the both locking portions, the radial shaking of the two pads is prevented. You can also do it.
In the case of the invention described in claim 6, the torque receiving portion can be pressed toward the torque receiving surface by the force applied by the two urging plate portions, and one of the guide holes can be pressed. The portion can be pressed toward the outer peripheral surface on the radially inner side of the pad pin. For this reason, it is possible to prevent rattling of the two pads in the circumferential direction and to prevent radial shaking of these pads.
Therefore, in the case of the present invention, the postures of these two pads at the time of non-braking can be sufficiently stabilized, and it is possible to effectively prevent the rattling and abnormal noises at these two pad portions.
As a result, in the case of the present invention, the posture of the two pads with respect to the caliper can be stabilized regardless of whether the brake is applied or not applied. The generation of sound and vibration can be prevented.

  Further, according to the invention described in claims 2 and 7, it is possible to prevent the linings of the two pads and the both side surfaces of the rotor from rubbing at the time of non-braking. For this reason, it is possible to reduce the rotational resistance of the wheel to which the rotor is fixed, and to improve the running performance of the automobile including acceleration performance and fuel efficiency performance.

  Further, according to the invention described in claim 3, the radial component force (component force inward in the radial direction) of the force applied by the two urging portions constituting the pad spring made of wire can be suppressed to a small value. For this reason, it is possible to effectively prevent the moment in the direction opposite to the moment applied during non-braking from acting on both the pads. Therefore, the effect of the invention described in claim 1 can be obtained more effectively.

  Moreover, according to the invention described in claim 4, it is possible to effectively prevent the pad spring made of the wire from falling off inward in the radial direction. Therefore, it is possible to prevent the inconvenience that the pad spring is dropped when traveling on a rough road, and the quality of the disc brake can be ensured.

  Furthermore, according to the invention described in claim 5, the pad clip provided separately from the pad spring made of wire is directed radially outward of the rotor at the turn-in side edge of the pressure plates. Can give power. For this reason, compared with the case where the said pad clip is not provided, the force given to the said both pads from the said pad spring can be restrained small. Therefore, it is possible to prevent an excessive force from pressing the outlet side edge of the pressure plate toward the caliper by the urging portion constituting the pad spring. As a result, it is possible to prevent the sliding performance of both the pads in the axial direction from being deteriorated.

The orthographic projection figure which shows the 1st example of embodiment of this invention in the state seen from radial direction outward. FIG. 2 is a cross-sectional view of FIG. Similarly, a plan view (A) and a front view (B) showing only the pad spring. FIG. 3 is an enlarged view of the part C in FIG. Similarly, the left half enlarged view of FIG. The same figure as FIG. The orthographic projection figure which shows the 2nd example of embodiment of this invention in the state seen from radial direction outward. The perspective view shown in the state seen similarly from the inner side and radial direction outer side. Similarly, the orthographic view seen from the left side of FIG. Similarly, the knee cross-sectional view of FIG. The perspective view (B) shown in the state which took out only the pad clip, and was seen from the turn-in side and the diameter direction outside, and was seen from the turn-out side and the diameter direction inner side (B). Similarly, a plan view (A), a side view (B), and a front view (C) showing only the pad clip. The orthographic projection figure which shows the 3rd example of embodiment of this invention in the state seen from radial direction outward. The perspective view shown in the state seen similarly from the outer side and radial direction outer side. The orthographic view shown in the state similarly seen from the outer side. The orthographic view shown in the state seen from the right side of FIG. FIG. 14 is a sectional view of the hoof of FIG. 13. Similarly the G part enlarged view of FIG. Similarly, only the pad spring is taken out and shown in an orthographic view (A) as viewed from the turning-in side in FIG. 17, a cross-sectional view (B) along the head in FIG. An orthographic projection (C) shown. FIG. 14 is an enlarged view of the part in FIG. 13. The orthographic projection figure which looked at one example of the disk brake conventionally known from the outer diameter side of the rotor. FIG. 22 is a cross-sectional view taken along the line II in FIG. 21. The figure similar to FIG. 2 which shows another example of conventional structure.

[First example of embodiment]
FIGS. 1-6 has shown the 1st example of embodiment of this invention corresponding to Claims 1-4. The feature of this example is that both pads 10a, 11a are provided by a caliper 5a and a wire pad spring 14a provided between the outer pad 10a and the inner pad 11a which are a pair of pads described in the claims. A moment in the same direction as the moment applied during braking is applied to the pad 10a and 11a so that the postures of both the pads 10a and 11a are maintained in the same state during non-braking and during braking. The basic structure and operation / effect of the opposed piston type disc brake are substantially the same as those of the conventional structure shown in FIGS. For this reason, illustrations and descriptions of overlapping portions are omitted or simplified, and the following description will focus on the characteristic portions of this example.

  Also in this example, both the pads 10a and 11a are composed of pressure plates 13a and 13a and linings 18a and 18a, respectively, and the rotor that rotates together with the wheels with the linings 18a and 18a facing each other. 2 (see FIGS. 21 to 22).

  The caliper 5a supports the pads 10a and 11a so as to be movable in the axial direction of the rotor 2 (the vertical direction in FIG. 1 and the front and back direction in FIG. 2), and the pads 10a and 11a are supported by the rotor. 2 and outer and inner pistons 8 and 9 (see FIG. 22) for pressing against both side surfaces. In the case of this example, the caliper 5a includes an outer for oil-tightly fitting the pistons 8 and 9, and an outer and inner body portions 3a and 4a provided with inner cylinders 6 and 7 (see FIG. 22). The end of the turn-in side (the side where the rotor 2 enters when moving forward, the right side of FIGS. 1 and 2) and the end of the turn-out side (the side where the rotor 2 comes out when moving forward, the left side of FIGS. 1 and 2), It is connected and fixed by connecting parts 20a and 20b. In the case of this example, the lengths of both the connecting portions 20a and 20b in the rotation direction of the rotor 2 are longer at the outlet side connecting portion 20b than at the inlet side connecting portion 20a. And the part which covers the radial direction outer side of the delivery side part of both said pads 10a and 11b among this connection part 20b on this delivery side is made into the cover part 21. As shown in FIG. Such a caliper 5a is supported and fixed to the vehicle body side (knuckle of the suspension device) by a pair of mounting seats 22a and 22b provided in the inner body portion 4a.

  The pads 10a and 11a are suspended by a single pad pin 12a. The pad pin 12a is disposed in a state of being partly extended in the axial direction of the rotor 2 at a part of the caliper 5a as described above and radially outside the outer peripheral edge of the rotor 2. In other words, the pad pin 12a is arranged at a portion closer to the center of the body portions 3a and 4a and slightly closer to the center than the connection portion 20a on the turn-in side. Then, the portions near both ends of the intermediate portion of the pad pin 12a are loosely inserted into the guide holes 23 provided in the pressure plates 13a and 13a constituting both the pads 10a and 11a so as to freely displace relative displacements in the axial direction. Thus, in the case of this example, there is only one pad pin 12a. Unlike the conventional structure shown in FIGS. 21 to 23, no pad pin is provided on the delivery side. The guide hole 23 is a long hole in the rotation direction of the rotor 2, and the pad pin 12 a is inserted through the middle portion of the guide hole 23 in the length direction.

  In the case of this example, both the pads 10a, at the time of braking, are disposed on the radially inward portion of the rotor 2 among the outlet side (left side in FIGS. 1 and 2) portions of the outer body portion 3a and the inner body portion 4a. Torque receiving surfaces 24 for supporting torque acting on 11a are formed respectively. For this reason, in the case of this example, as shown in FIGS. 2 and 5, wall portions 25 projecting toward each other are formed on the side portions facing each other on the delivery side of the body portions 3 a and 4 a, respectively. Each is provided. Further, a concave groove 26 is formed in each of the intermediate portions in the radial direction of the both wall portions 25. The both concave grooves 26 are opened in both circumferential sides of the both wall portions 25 and the surfaces facing the rotor 2, and are substantially orthogonal to the side surfaces of the both wall portions 25 on the turn-in side. In addition, these wall portions 25 are formed over the entire thickness direction (the left-right direction in FIGS. 2 and 5). In addition, of the side surfaces on the turn-in side of both the wall portions 25, a portion on the inner diameter side than the both concave grooves 26 is a flat surface 27 for torque support. The two torque bearing flat surfaces 27 and the inner diameter side surfaces of the two concave grooves 26 serve as the two torque receiving surfaces 24.

  On the other hand, the protrusions 28 are respectively provided in the radially intermediate portions of the output side edges of the pressure plates 13a, 13a constituting the pads 10a, 11a so as to protrude to the output side. Further, a flat surface 29 is formed on the inner diameter side portion of the both projecting portions 28 of the outlet side edge portions of the pressure plates 13a and 13a. In the case of this example, the inner diameter side surfaces and both flat surfaces 29 of both the protrusions 28 are used as the torque receiving portions 30. In addition, the two protrusions 28 and the two flat surfaces 29 are smoothly and continuously connected to each other by a concave insertion portion 31 that is curved to the entrance side. Then, with both the pads 10a and 11a being disposed at predetermined positions of the caliper 5a, the two protrusions 28 are loosely engaged with the two concave grooves 26, and the two flat surfaces 29 are connected to the torques. It is made to oppose with respect to the flat surface 27 for support. Thus, by engaging both the protrusions 28 in the both concave grooves 26, in the case of this example, the positioning of the pads 10a and 11a in the radial direction on the delivery side is achieved. Further, by providing the both recessed portions 31, excessive stress is prevented from concentrating on the continuous portion between the both projecting portions 28 and the two flat surfaces 29. Further, in the case of this example, the contact portion between the inner diameter side surface of the tip end portion of both protrusions 28 and the inner diameter side surface of both concave grooves 26 is the rotation center of the pads 10a and 11a (FIG. 2). The center of rotation C is located radially inward from the friction surface center of these pads 10a and 11a (the point O in FIG. 2 and the center of the linings 18a and 18a). To position. Therefore, in the case of this example, a counterclockwise moment (couple) in FIG. 2 is applied to both the pads 10a and 11a due to the friction between the rotor 2 and the both linings 18a and 18a during braking. .

  In particular, in the case of this example, a pad spring 14a is provided between the caliper 5a and the two pads 10a and 11a. In the case of this example, the pad spring 14a is integrally formed in a shape as shown in FIG. 3 by bending a single wire having elasticity such as stainless spring steel. That is, the pad spring 14a is provided with an engaging portion 32 at the axial center portion and a pair of urging portions 33, 33 substantially parallel to the engaging portion 32 on both axial sides of the engaging portion 32, respectively. The engaging portion 32 and the urging portions 33 and 33 are connected by connecting portions 34 and 34 having substantially square shapes, respectively. Further, the folded portions 35, 35 are formed by folding the tip portions of the urging portions 33, 33 180 degrees in a direction approaching each other (towards the center of the pad spring 14a), thereby forming both folded portions 35. , 35 are bent to the opposite side of the engaging portion 32 to form elastic arm portions 36, 36. Both the elastic arm portions 36 and 36 have elasticity in a direction in which the distance between the tip portions expands in the free state, as indicated by the chain line in FIG. 3A. That is, the width in the free state between the tip portions of the elastic arm portions 36, 36 is wider than the distance between the inner surfaces of the pair of pressure plates 13a, 13a constituting the pads 10a, 11a. Further, the tip portions of the elastic arm portions 36 and 36 are bent in the direction away from each other (the axial direction of the rotor 2) to form the lock portions 37 and 37, respectively. Are bent at substantially right angles to form retaining portions 38, 38.

  As shown in FIG. 2, the pad spring 14a as described above is assembled between the caliper 5a and the two pads 10a and 11a. That is, the engagement portion 32 constituting the pad spring 14a is engaged with an engagement recess 39 formed on the inner peripheral surface of the cover portion 21 provided in the caliper 5a. Further, the urging portions 33, 33 are formed on an outer peripheral edge portion of the turn-around portion of the pressure plates 13a, 13a on the turn-in side surface 41 of the substantially triangular prism-like urged protrusion 40, Each elastically abuts. The elastic arms 36 and 36 are elastically bent from the position indicated by the chain line in FIGS. 2 to 3 to the position indicated by the solid line (clockwise in FIG. 2), and the distance between the tip ends is elastically changed. The both locking portions 37, 37 are respectively locked in locking holes 42 formed on the outlet side of the guide holes 23 at the portions close to the rotation of the pressure plates 13a, 13a. In the case of this example, both the locking holes 42 are long holes in the rotation direction of the rotor 2, and the both locking portions 36 are formed at the intermediate portions in the length direction of the locking holes 42. Engage.

As described above, the pad spring 14a is assembled between the caliper 5a and the two pads 10a and 11a, so that the engaging portion 32 and the engaging recess 39 are rotated around the pad spring 14a. A clockwise moment is applied with the contact portion (point A in FIGS. 2, 4, and 5) with the entry side surface 43 as a fulcrum. As a result, as shown by the arrows f ₁ in FIGS. A force f ₁ is applied in a direction perpendicular to 41. In particular, in the case of this example, by restricting the inclination angle of the turn-in side surface 41, the direction of the line of action of the force f ₁ is set so that the torque receiving portion 30 faces the torque receiving surface 24. The direction of pressing and the center of rotation of the pads 10a and 11a (the point C in FIGS. 2 and 5), the contact between the inner diameter side surface of the tip 28 and the inner diameter side surface of the groove 26 Part) in a direction that deviates outward in the radial direction of the rotor 2 (in the example shown, it deviates by L). Therefore, in the case of this example, the counterclockwise moment of FIG. 2 acts on both the pads 10a and 11a by the force f _{1 applied} from both the urging portions 33 and 33.

On the other hand, the locking portions 37 and 37 locked in the locking holes 42 are urged radially outward based on the elastic restoring force of the elastic arm portions 36 and 36. A force f ₂ directed outward in the radial direction of the rotor 2 is applied to both the locking holes 42. Therefore, in the case of this example, also, the two pads 10a, to 11a, counterclockwise moment in FIG. 2 is applied by the force f ₂ is applied from the both locking portions 37. Further, the distal end portions of the elastic arm portions 36 and 36 are stretched between the pressure plates 13a and 13a, whereby a force in a direction in which the pads 10a and 11a are separated from each other is applied to the inwardly moving portions of the pads 10a and 11a. Is done.

According to the disc brake of this example as described above, the postures of the two pads 10a and 11a with respect to the caliper 5a can be stabilized regardless of whether the brake is applied or not. For this reason, it is possible to prevent abnormal noise and vibration from occurring in both the pads 10a and 11a not only during non-braking but also during braking.
That is, in the case of this example, the direction of the moment (coupled rotation direction) applied along with the friction between the side surface of the rotor 2 and the linings 18a and 18a during braking, and both urging forces constituting the pad spring 14a. The directions of the moments acting on the pads 10a and 11a by the forces (f ₁ and f ₂ ) applied from the portions 33 and 33 and the locking portions 37 and 37 are the same. For this reason, it is possible to keep (restrain) the postures of both the pads 10a and 11a when not braking in the same state as the posture during braking. Therefore, the postures of both the pads 10a and 11a during braking can be stabilized. Thus, even when braking is started, the torque receiving part 30 and the torque receiving surface 24 or a part of the guide hole 23 and the outer peripheral surface of the pad pin 12a can be prevented from colliding with each other. It can prevent the generation of a strong cronk sound.

Further, in the case of this example, as shown in FIG. 4, the both flat surfaces 29 are formed on the basis of the circumferential component force f _1x of the force f _{1 applied} by the both biasing portions 33, 33. It can be pressed toward the flat surface 27 for both torque bearings. For this reason, it is possible to prevent rattling of the pads 10a and 11a in the circumferential direction. Further, based on the force f ₁ of the radial component force f _1y, an inner diameter side surface of said both projections 28 can be pressed toward the inner diameter side surface of each groove 26. Furthermore, the force f ₂ is given by the both locking portions 37 and 37, a portion of the inner peripheral surface of the guide hole 23 can be pressed against the outer peripheral surface of the radially inner side of the pad pin 12a. For this reason, it is possible to prevent the radial shaking of both the pads 10a and 11a. Accordingly, in the case of this example, the postures of both the pads 10a and 11a during non-braking can be sufficiently stabilized, and rattling and abnormal noise (rattle sound) at the both pads 10a and 11a portions. Can be effectively prevented.
As a result, in the case of this example, the posture of both the pads 10a and 11a with respect to the caliper 5a can be stabilized regardless of whether the brake is applied or not applied. It is possible to prevent abnormal noise and vibration from occurring in the pads 10a and 11a.

  Further, in the case of this example, the distance between the reentrant portions of the two pads 10a, 11a is increased during non-braking based on the elasticity of the two elastic arm portions 36, 36. Therefore, both the pads 10a, 11a It is possible to prevent the linings 18a, 18a from rubbing against both side surfaces of the rotor 2. For this reason, the rotational resistance of the wheel to which the rotor 2 is fixed can be kept low, and the running performance of the automobile including acceleration performance and fuel consumption performance can be improved.

Further, in the case of this example, both the urging portions 33 and 33 are brought into contact with the leading end side or the intermediate side side surface 41 of the both urged projections 40 so that both the urging portions are brought into contact with each other. A gap 55 is provided between 33 and 33 and a portion of the outer peripheral edge portions of the pressure plates 13a and 13a adjacent to the turn-in side of the two biased protrusions 40. Therefore, the radial component force f _1y force f ₁ which imparted by the both urging portion 33, 33, can be prevented that the unnecessarily large, the two pads 10a, to 11a, applied to the non-braking, the It is possible to effectively prevent the moment in the direction opposite to the counterclockwise moment in FIG. 2 centering on point C (the moment applied in the clockwise direction in FIG. 2 around point C). Therefore, the postures of both the pads 10a and 11a can be sufficiently stabilized, and it is possible to effectively prevent the generation of abnormal noise and vibration at both the pads 10a and 11a.

  Further, in the case of this example, as shown in FIG. 6, the diameter of the turn-in side surface 41 of both the biased protrusions 40 (for example, at the center in the circumferential direction of the pads 10 a and 11 a). The inclination angle α with respect to the direction is larger than the inclination angle β with respect to the same direction of the turn-in side surface 43 of the engagement recess 39 (α> β). For this reason, it is possible to prevent the pad spring 14a from falling off radially inward from the state in which the pad spring 14a is assembled. That is, in the case of this example, the engagement portion 32 is displaced radially inward along the turn-in side surface 43 in accordance with the pressing between the engagement portion 32 and the turn-in side surface 43. It tends to (drop off). On the other hand, the two urging protrusions 33, 33 are diametrically moved along the both entrant side surfaces 41 in accordance with the pressing of the urging protrusions 33, 33 and the both entry side surfaces 41. It tends to shift outward. In the case of the structure of this example, since the magnitude relationship between the two inclination angles α and β is α> β as described above, the force that tends to shift outward in the radial direction is greater in the radial direction. It becomes larger than the force that tries to shift toward. For this reason, it is possible to make it difficult to drop the engaging portion 32 radially inward from the engaging concave portion 39 by making the engaging portion 32 tend to be pushed into the engaging concave portion 39. Therefore, it is possible to effectively prevent the pad spring 14a from falling off. As a result, it is possible to prevent the inconvenience that the pad spring 14a falls off when traveling on a rough road, and the quality of the disc brake can be ensured. The difference between the inclination angle α and the inclination angle β is that the friction coefficient μ between the pad spring 14a (engagement portion 32) and the caliper 5a (engagement recess 39) and the pad spring 14a ( It can be determined by the difference between the friction coefficient μ ′ between the urging portion 33) and the pressure plates 13a, 13a (the urged protrusions 40). In this example, the inclination angle α And the difference (α−β) between the tilt angle β and the tilt angle β is about 30 °.

  In this example, the pad spring 14a can be easily assembled between the caliper 5a and the pads 10a and 11a. For this reason, the assembly process of the disc brake can be simplified and the working efficiency can be improved. Furthermore, from the aspect of using only one pad pin 12a, the assembly process can be simplified and the working efficiency can be improved.

[Second Example of Embodiment]
FIGS. 7-12 has shown the 2nd example of embodiment of this invention corresponding to Claims 1-5. The feature of this example is that a pad clip 44 is provided between a part of the caliper 5b (anchor part at the time of reverse travel) and the turn-in side edges of the pressure plates 13b and 13b. Since the configuration, operation, and effects of the other parts are almost the same as in the case of the first example of the above-described embodiment, the overlapping description will be omitted or simplified. Explained.

  In the case of this example, the pad clip 44 has a shape as shown in FIGS. 11 and 12 by punching and bending a metal plate having elasticity and corrosion resistance, such as a stainless steel plate, into a predetermined shape. That is, the pad clip 44 includes a substrate portion 45, a locking plate portion 46 formed in a state of being bent at a substantially right angle from an edge on the outer diameter side of the substrate portion 45, and the axial direction of the substrate portion 45 {FIG. (A) up and down direction, (C) left and right direction} In a state where the respective base end portions are continued to the inner diameter side edge portion of the intermediate portion, the entire intermediate portion is folded into a substantially letter shape. A pair of bending portions 47 and 47 and an urging plate portion 48 provided in a state where the tip portions of both the bending portions 47 and 47 are connected to each other are provided. In addition, depending on the both axial ends of the substrate portion 45, there are provided hanging plate portions 49, 49 that hang inward in the radial direction as compared with the intermediate portion in the axial direction. Further, the urging plate portion 48 has a substantially arc-shaped cross section and is located on the outlet side with respect to the substrate portion 45.

  As shown in FIG. 10, the pad clip 44 having the above-described configuration constitutes the outer side and inner pads 10a, 11a, and the outer side and inner pads 10a, 11a of the connecting portion 20a on the side of the incoming side that constitutes the caliper 5b. The pressure plates 13b and 13b are assembled with the outer diameter portion of the turn-in side edge. That is, the locking plate portion 46 constituting the pad clip 44 is locked to the flat surface 50 formed on the outer peripheral surface of the connecting portion 20a, and the substrate portion 45 is fixed to the delivery side surface of the connecting portion 20a. The pad clip 44 is attached to the caliper 5b in advance by abutting. When the pads 10a and 11a are assembled to the caliper 5b, the inner diameter side surface of the overhanging portion 51 provided near the outer diameter of the turn-in side edge of the pressure plates 13b and 13b is used. Then, both end portions of the urging plate portion 48 are pressed inward in the radial direction. As a result, the pad pin 12a is inserted into the guide hole 23 in a state where both the bent portions 47, 47 are elastically deformed (the opening angle of the bent portion 47 is larger than the opening angle in the free state). As a result, the pad clip 44 is assembled between the turn-out side surface of the connection portion 20a on the turn-in side and a portion near the outer diameter of the turn-in side edge portions of the pressure plates 13b and 13b.

In the state where the pad clip 44 is assembled as described above, on the basis of the elasticity of the two bent portions 47, 47, the urging plate portion 48 and the overhanging portion 51 are radially outward of the rotor 2. A force directed to the direction is given. For this reason, a part of the inner peripheral surface of the guide hole 23 can be pressed against the outer peripheral surface of the inner diameter side portion of the guide pin 12a. Therefore, in the case of this example, the force applied to both the pads 10a and 11a by the pad spring 14b is suppressed as compared with the case of the first example of the above-described embodiment. That is, when the postures of the two pads 10a and 11a during light braking are stabilized only by the force applied from the pad spring 14b, the force f applied from the urging portions 33a and 33a constituting the pad spring 14b. ₁ in the circumferential direction component force f _1x (see FIG. 4) it becomes excessive. As a result, the delivery side edge portions of the pressure plates 13b and 13b are pressed too strongly toward the caliper 5b, and the sliding performance (easiness of displacement) of the pads 10a and 11a in the axial direction. May lead to inconveniences such as lowering.

  On the other hand, in the case of this example, the pad clip 44 presses a part of the inner peripheral surface of the guide hole 23 toward the outer peripheral surface of the inner diameter side portion of the guide pin 12a. Even when the force applied from the spring 14b is kept small, the postures of the pads 10a and 11a can be sufficiently stabilized during light braking. Further, as the force applied by the pad spring 14b can be kept small, it is possible to effectively prevent the sliding performance of both the pads 10a and 11a from decreasing in the axial direction. Thus, in the case of this example, by using the pad clip 44 having a relatively simple shape, the connection portion 20a on the turn-in side and the turn-in side edge portions of the pressure plates 13b and 13b As compared with the case where only the pad spring 14b is used, the stability of the posture of the pads 10a and 11a during light braking and the sliding of the pads 10a and 11a are effectively compared. This makes it easy to achieve both dynamic performance and safety.

  In the case of this example, the configuration of the torque receiving portion 30a provided on the delivery side of both the pads 10a and 11a is different from that of the first example of the above-described embodiment. That is, in the case of this example, the inclined surface portion 52 and the convex curved surface 53 are provided on the inner diameter side portion of the projection 28 provided at the radial intermediate portion of the delivery side edge portion of the pressure plates 13b and 13b. Are provided in a state of being smoothly and continuously connected to each other. The inner diameter side surface of the protrusion 28, the inclined surface portion 52, and the convex curved surface 53 serve as the torque receiving portion 30a.

  Further, the inclined surface portion 52 is inclined in a direction toward the delivery side as it goes inward in the radial direction. The convex curved surface 53 is a partial cylindrical surface in which the central axis of curvature is disposed in the axial direction in a state where the pads 10a and 11a are disposed at predetermined positions of the caliper 5b. In the case of this example, the center of curvature of the convex curved surface 53 is the rotation center (point C ′ in FIG. 10) of the pads 10a and 11a. In the case of this example, the protrusion 28 and the inclined surface portion 52 are smoothly and continuously connected to each other by the recessed portion 31 that is curved to the entrance side. Then, with the two pads 10a and 11a arranged at predetermined positions on the caliper 5b, the protrusion 28 is placed in a pair of concave grooves 26 formed on the wall 25 of the inner and outer body portions 3a and 4a. The slanted surface portion 52 and the convex curved surface 53 are opposed to the torque bearing flat surface 27 provided on the inner diameter side portions of the both concave grooves 26, respectively.

Furthermore, in the case of this example, a second pad clip 54 made of a metal plate having corrosion resistance, such as a stainless steel plate, is provided between the torque receiving portion 30a as described above and the torque receiving surface 24. . For this reason, at the time of braking, the inner diameter side surface of the protrusion 28 and the inner diameter side surface of the concave groove 26, a part of the inclined surface portion 52 and the convex curved surface 53, the flat surfaces 27 for torque support, However, it abuts via the second pad clip 54, and supports the torque acting on the pads 10a and 11a by friction with both side surfaces of the rotor 2. Thus, by providing the second pad clip 54, in the case of this example, it is possible to prevent the sliding portions between the pressure plates 13b, 13b and the wall portions 25 from being rusted. The wear generated in the sliding portion can be reduced.
About another structure and an effect, it is the same as that of the case of the 1st example of embodiment mentioned above.

[Third example of embodiment]
13 to 20 show a third example of an embodiment of the present invention corresponding to claims 6 and 7. The feature of this example is that a plate spring 14c provided between the caliper 5c and the outer pad 10a and the inner pad 11a applies a moment in the same direction as the moment applied during braking to both the pads 10a and 11a. The pad 10a and 11a are kept in the same posture during non-braking and during braking. The configuration, operation, and effects of the other parts are almost the same as those in the first example of the above-described embodiment and the second example of the above-described embodiment. Therefore, the overlapping description is omitted or simplified. Hereinafter, the characteristic part of this example will be mainly described.

  Also in this example, both the pads 10a and 11a are suspended by one pad pin 12a. This pad pin 12a is arranged in a state of being partly stretched in the axial direction of the rotor 2 at a part radially outside the outer peripheral edge of the rotor 2 (see FIGS. 21 to 22) in a part of the caliper 5c. That is, the outer and inner body portions 3a and 4a constituting the caliper 5c are closer to the center of the outer portion and the inner body portions 3a and 4a, and the portion is slightly closer to the center than the connecting portion 20a on the side of connecting the body portions 3a and 4a. Further, the pad pin 12a is arranged. Then, relative displacement in the axial direction can be freely made in the guide holes 23 and 23 provided in the portions near the both ends of the pressure plates 13c and 13c constituting the pads 10a and 11a. Is loosely inserted.

  In the case of this example, the biased protrusions 40a, 40a are provided at the outer peripheral edge of the revolving part of the pressure plates 13c, 13c on the radially outer portions of the guide holes 23, 23. Each is provided. The turn-in side surfaces 41a and 41a of both the biased protrusions 40a and 40a are inclined in the direction toward the turn-in side as they go radially outward.

  Further, in the case of this example, as in the case of the second example of the above-described embodiment, the protrusions 28 provided at the radial intermediate portions of the delivery side side edges of the pressure plates 13c, 13c are provided. An inclined surface portion 52 and a convex curved surface 53 are provided on the inner diameter side portion so as to be smoothly continuous with each other. The inner diameter side surface of the protrusion 28, the inclined surface portion 52, and the convex curved surface 53 are used as the torque receiving portion 30a. In the case of this example, the center of curvature of the convex curved surface 53 is the rotation center (point C ′ in FIG. 17) of the two pads 10a and 11a, and the rotation center C ′ is the both pads 10a. , 11a is located radially inward from the center of the friction surface (point O in FIG. 17). Accordingly, also in this example, the counterclockwise moment (couple) of FIG. 17 is applied to both the pads 10a and 11a due to the friction between the side surface of the rotor 2 and the linings 18a and 18a during braking. Join.

  Further, the pad spring 14c used in this example is an integrated leaf spring formed by bending an elastic metal plate having elasticity and corrosion resistance, such as stainless steel, and has a shape as shown in FIG. That is, the pad spring 14c is bent substantially perpendicularly inwardly in the radial direction from the locking plate portion 56 and the output side edge of the locking plate portion 56, and its intermediate portion is folded back by 180 degrees to substantially U. A pair of urging plate portions projecting in directions away from each other in the axial direction (outer and inner sides) in a state in which the base end portions are connected to the distal end portions of the bent portions 57 and the bent portions 57 in the shape of a letter. 58, 58. Further, at the delivery-side end portions of these urging plate portions 58, 58, there are formed pressing surfaces 59, 59 that are partially cylindrical and are formed by bending the respective intermediate portions over the entire length in the axial direction into a substantially U shape. Provided. Of the pad spring 14c having such a configuration, the locking plate portion 56 is a portion locked to the outer peripheral surface of the caliper 5c, and the biasing plate portions 58 and 58 (of the pressing surfaces). 59, 59) are portions for urging the above-described urged protrusions 40a, 40a. The bending portion 57 is located between the urging plate portions 58 and 58 and the locking plate portion 56 and can be bent and deformed.

  In the case of this example, as shown in FIG. 19C and FIG. 20, the two pressing surfaces 59, 59 are separated from each other in the axial direction {the left-right direction of FIG. 19C, FIG. It is inclined in the direction toward the turn-in side {upper side of Fig. 19C, right side of Fig. 20} as it goes in the vertical direction. Specifically, as shown in FIG. 20, both the pressing surfaces 59, 59 have an inclination of an angle θ with respect to an imaginary line I parallel to the central axis of the rotor 2.

  The pad spring 14c as described above is assembled between the caliper 5c and the pads 10a and 11a as shown in FIG. That is, the locking plate portion 56 constituting the pad spring 14c is locked to the outer peripheral surface of the connection portion 20a on the turn-in side constituting the caliper 5c, and the side surface on the turn-in side of the bending portion 57 is fixed. The pad spring 14c is attached in advance to the caliper 5c in contact with the delivery side surface of the connecting portion 20a. When the pads 10a and 11a are assembled to the caliper 5c, the biasing plate portions 58 and 58 are pressed by the turn-in side surfaces 41a and 41a of the biased protrusions 40a and 40a. The surfaces 59 and 59 are pressed toward the entrance side. Thereby, in the state where the bending portion 57 is elastically bent from the state shown by the chain line in FIG. 18 to the position shown by the solid line (the opening angle of the bending portion 57 is made smaller than the opening angle in the free state), The pad pin 12a is inserted into the guide holes 23, 23.

In the state where the pad spring 14c is assembled as described above, the two biased protrusions 40a from the pressing surfaces 59, 59 of the biasing plate portions 58, 58 based on the elastic restoring force of the flexible portion 57. , 40a times entrance side surface 41a, with respect to 41a, as shown by arrow f ₃ in FIG. 17 and 18, both of these times the entry side side surfaces 41a, the force f ₃ is applied in a direction perpendicular to 41a. Particularly, in the case of this example, both of these times the entry side side surfaces 41a, by regulating the inclination angle of 41a (the inclination angle with respect to the radial direction), the direction of the line of action of the force f _3, the run-out side and the The rotor 2 is restricted in a direction facing radially outward. Therefore, the force f ₃ applied from the both the urging plate portions 58 and 58, the two pads 10a, to 11a, the counterclockwise moment in FIG. 17 acts.

  Further, in the case of this example, as described above, the two pressing surfaces 59, 59 constituting the two urging plate portions 58, 58 are directed toward the turn-in side as they move away from each other in the axial direction. Therefore, a force is applied to both the pads 10a and 11a in a direction that widens the distance between the close-in portions of the pads 10a and 11a.

According to the disc brake of this example as described above, the postures of the pads 10a and 11a with respect to the caliper 5c can be stabilized regardless of whether the brake is applied or not. For this reason, it is possible to prevent abnormal noise and vibration from occurring in both the pads 10a and 11a not only during non-braking but also during braking.
That is, also in the case of this example, the direction of the moment (couple rotation direction) applied along with the friction between the side surface of the rotor 2 and the linings 18a and 18a at the time of braking, and the both biases constituting the pad spring 14c The direction of the moment acting on both the pads 10a and 11a by the force (f ₃ ) applied from the pressing surfaces 59 and 59 of the plate portions 58 and 58 is the same. For this reason, it is possible to keep (restrain) the postures of both the pads 10a and 11a when not braking in the same state as the posture during braking. Therefore, the postures of both the pads 10a and 11a during braking can be stabilized. Thereby, even when braking is started, the torque receiving portion 30a and the torque receiving surface 24, or a part of the both guide holes 23 and 23 and the outer peripheral surface of the pad pin 12a can be prevented from colliding with each other. Therefore, generation of an unpleasant cron sound can be prevented.

Further, in the case of this example, as shown in FIGS. 17 and 18, the torque receiving is performed based on the circumferential force component f _3x of the force f _{3 applied} by the biasing plate portions 58 and 58. The inclined surface portion 52 to the convex curved surface 53 constituting the portion 30 a can be pressed toward the torque bearing flat surface 27 constituting the torque receiving surface 24. For this reason, it is possible to prevent rattling of the pads 10a and 11a in the circumferential direction. Further, based on the radial component force f _3y of the force f ₃ , a part of the inner peripheral surface of the guide holes 23 and 23 can be pressed against the outer peripheral surface on the radially inner side of the pad pin 12a. For this reason, it is possible to prevent the radial shaking of both the pads 10a and 11a. Accordingly, in the case of this example, the postures of both the pads 10a and 11a during non-braking can be sufficiently stabilized, and rattling and abnormal noise (rattle sound) at the both pads 10a and 11a portions. Can be effectively prevented.
As a result, in the case of this example, the posture of both the pads 10a and 11a with respect to the caliper 5c can be stabilized regardless of whether the brake is applied or not applied. It is possible to prevent abnormal noise and vibration from occurring in the pads 10a and 11a.

Furthermore, in the case of this example, the two urging plate portions 58, 58 increase the spacing between the close-in portions of the pads 10a, 11a during non-braking, and therefore the lining 18a of the pads 10a, 11a. , 18a and both sides of the rotor 2 can be prevented from rubbing. For this reason, the rotational resistance of the wheel to which the rotor 2 is fixed can be kept low, and the running performance of the automobile including acceleration performance and fuel consumption performance can be improved. Further, the pad spring 14c used in this example is excellent in assembling performance as compared with the pad springs 14a and 14b made of wire as in the first and second examples of the above-described embodiment. For this reason, the assembly process of the disc brake can be simplified and the work efficiency can be further improved. Furthermore, the pad spring 14c of this example locks the locking plate portion 56 to the outer peripheral surface of the connecting portion 20a in the assembled state, and the side surface of the bending portion 57 on the turn-in side of the connecting portion 20a. The pad spring 14c can be effectively prevented from falling off even when traveling on a rough road because it can be elastically pressed against the side surface of the delivery side.
About another structure and an effect, it is the same as that of the case of the 1st example of embodiment mentioned above and the 2nd example of embodiment mentioned above.

  The shapes of the pad spring and the pad clip used when implementing the present invention are not limited to the illustrated shapes, and various shapes can be adopted as long as the pressure plate constituting the pad can be pressed in the direction described above.

DESCRIPTION OF SYMBOLS 1 Disc brake 2 Rotor 3, 3a Outer body part 4, 4a Inner body part 5, 5a, 5b, 5c Caliper 6 Outer cylinder 7 Inner cylinder 8 Outer piston 9 Inner piston 10, 10a Outer pad 11, 11a Inner pad 12, 12a Pad pin 13 , 13a, 13b, 13c Pressure plate 14, 14a, 14b, 14c Pad spring 15a, 15b Metal plate 16 Bending portion 17 Elastic engagement portion 18, 18a Lining 19 Pad 20a, 20b Connection portion 21 Cover portion 22a, 22b Mounting seat 23 Guide hole 24 Torque receiving surface 25 Wall portion 26 Concave groove 27 Torque support flat surface 28 Projection portion 29 Flat surface 30, 30a Torque receiving portion 31 Recessed portion 32 Engaging portion 33, 33a Energizing portion 34 Connecting portion 35 Folding portion 36 elastic arm portion 37 locking portion 38 retaining portion 39 engaging concave portion 40, 40a biased protrusion 41, 41a side surface on the entrance side 42 engaging hole 43 side surface on the entrance side 43 pad clip 45 substrate portion 46 locking plate Part 47 Bending part 48 Energizing plate part 49 Suspended plate part 50 Flat surface 51 Overhanging part 52 Inclined surface part 53 Convex surface 54 Second pad clip 55 Gap 56 Locking plate part 57 Bending part 58 Energizing plate part 59 Pressing surface

Claims (7)

A pair of pads provided with a rotor that rotates together with the wheels, a caliper that supports these pads so as to be movable in the axial direction of the rotor, and a piston that presses against both sides of the rotor, and a caliper of the caliper A torque receiving surface that is arranged on the delivery side and supports the torque acting on both pads during braking, and a part of the caliper is hung in the axially outer portion of the outer periphery of the rotor in the axial direction of the rotor. The pad pins are arranged in a handed state and are inserted between the guide holes provided in the pressure plates constituting the two pads, and between the two pads and the caliper. In disc brakes with pad springs to prevent,
A cover portion is provided on the outlet side portion of the outer peripheral portion of the caliper so as to cover the radially outer sides of the outlet side portions of the two pads. Similarly, a biased protrusion is provided on the outer peripheral edge of the outlet side portion, the pad pin is provided only on the inlet side portion, and the pad spring has elasticity. The wire is formed by bending a single wire, and includes an engaging portion, a pair of urging portions disposed substantially parallel to the engaging portion, and both ends of the wire in the axial direction of the rotor. A pair of engaging portions formed by bending the engaging portions into engagement recesses formed on the inner peripheral surface of the cover portion, and In a state where it is elastically brought into contact with the turn-in side surface of the biased projection, By engaging in both the locking holes, the direction of the line of action of the two biasing portions from the two biasing portions to the turn-in side surfaces of the two biased projections is the edge on the outlet side of the pressure plates. A direction in which the torque receiving portion provided in the portion is pressed toward the torque receiving surface, and a force in a direction deviating radially outward of the rotor from the rotation center of the two pads is applied. The direction of the moment applied to the two pads at the time of braking, the two urging portions, and the both latches are applied from both the latching portions to the both latching holes with a force directed radially outward of the rotor. A disc brake characterized by preventing the rattling of both pads by making the direction of the moment acting on each of these pads the same by the force applied from the part.   The disc brake according to claim 1, wherein the pair of locking portions have elasticity in a direction in which they are separated from each other in a state in which a pad spring is assembled between the pair of pads.   The biasing portion is in contact with the tip side or intermediate side surface of the biased protrusion, and of the biasing portion and the outer peripheral edge of the pressure plate, the biasing protrusion is on the winding side. The disc brake according to any one of claims 1 and 2, wherein a gap is provided between a portion adjacent to the disc brake.   The inclination angle with respect to the radial direction of the turn-in side surface of the energized protrusion is larger than the inclination angle with respect to the radial direction of the turn-in side surface of the engaging recess. Disc brake.   A pad clip formed by bending a metal plate is provided between a part of the caliper and the turn-in edge of both pressure plates, and this pad clip is connected to the turn-in edge of both pressure plates. The disc brake according to any one of claims 1 to 4, wherein a force directed outward in the radial direction of the rotor is applied to the portion. A pair of pads provided with a rotor that rotates together with the wheels, a caliper that supports these pads so as to be movable in the axial direction of the rotor, and a piston that presses against both sides of the rotor, and a caliper of the caliper A torque receiving surface that is arranged on the delivery side and supports the torque acting on both pads during braking, and a part of the caliper is hung in the axially outer portion of the outer periphery of the rotor in the axial direction of the rotor. The pad pins are arranged in a handed state and are inserted between the guide holes provided in the pressure plates constituting the two pads, and between the two pads and the caliper. In disc brakes with pad springs to prevent,
A biased protrusion is provided at the outer peripheral edge of the turn-in side portion of both pressure plates, the pad pin is provided only at the turn-in side portion, and the pad spring is an elastic metal plate And a pair of urging plate portions for urging both of the urging projections, and both of these urging plate portions. A bending portion provided between the urging plate portion and the locking plate portion, and locking the locking plate portion to an outer peripheral surface of the caliper side portion of the caliper, and the bending The two urging plate portions are bent from the two urging plate portions by elastically abutting the two urging plate portions with the turn-in side surfaces of the two urged projection portions. The force of the direction of the action line is applied to the outlet side and radially outward of the rotor with respect to the inlet side surface of the part. The direction of the moment applied to the two pads during braking and the direction of the moment acting on the two pads by the force applied from the two urging plate portions are made the same to prevent rattling of both the pads. Disc brake characterized by things.   Of the pair of urging plate portions, the portions that are in contact with the turn-in side surfaces of both urged protrusions are inclined in the direction toward the turn-in side as they move away from each other with respect to the axial direction of the rotor, The disc brake according to claim 6, wherein a force is applied to the two pads in a direction to widen the distance between the close-in portions of the pads in a state in which a pad spring is assembled between the pair of pads. .

Images