JP2011220402A - Opposed piston type disk brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a structure for easily performing assembling work, by effectively preventing looseness of both inner-outer pads 5a to a caliper 2a in non-braking, without using an anti-rattle spring having large resiliency.SOLUTION: Two positions separated in the peripheral direction of both pads 5a are respectively axially displaceably supported to the caliper 2a by engagement between a pair of guide pins 7a and 7b and respective guide holes 17a and 17b formed in a pressure plate 13a for constituting both pads 5a. One support part supports both pads 5a to the caliper 2a in a state of preventing displacement in the radial direction, and the other support part similarly supports both pads in a state of allowing the displacement in the radial direction. By applying resiliency of directing the radial direction to both pads 5a by the other support part by an elastic member, the resiliency in the direction of rocking around one support part, is applied to both the pads 5a.

Description

  The present invention relates to an improvement of an opposed piston type disc brake in which pistons are provided on both sides of a rotor in a state of facing each other among disc brakes used for braking an automobile. Specifically, it is intended to realize a structure that can effectively prevent the outer and inner pads from rattling against the caliper during non-braking without using an anti-rattle spring having a large elasticity.

  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 have been known. However, the opposed piston type disc brake, which is provided with pistons on both sides of the rotor so as to face each other, can obtain a stable braking force. In recent years, use cases have increased. Conventionally, for example, a structure described in Patent Document 1 is known as such an opposed piston type disc brake. Based on the description of Patent Document 1 among these, the basic structure of the opposed piston type disc brake which is the subject of the present invention will be briefly described.

  As shown in FIGS. 21 to 22, the opposed piston type disc brake 1 described in Patent Document 1 includes a caliper 2, a plurality of cylinders 3 and 3 (see FIG. 3 showing the embodiment of the present invention), and , A plurality of pistons 4, 4 (also see FIG. 3), a pair of pads 5, 5, a plurality of guide holes 6, 6, and a pair of guide pins 7, 7.

  Of these, the caliper 2 includes outer and inner body parts 8 and 9 and a pair of connecting parts 10 and 10. Of these, both the outer and inner body portions 8 and 9 are configured so that a part of the rotor 11 that rotates together with the wheels is axially (in the present specification and claims, “axial direction”, “radial direction”, “circumferential direction”). "Direction" refers to the direction of the rotor unless otherwise specified. In addition, the rotation side and the rotation side of the rotor refer to the state when moving forward unless otherwise specified.) It is provided in the state. Further, the both connecting portions 10 and 10 connect both end portions of the body portions 8 and 9 at positions radially outward from the outer peripheral edge of the rotor 11. In the illustrated example, these two body parts 8 and 9 made separately from each other are combined and fixed by a plurality of bolts 12 and 12, but an integrated caliper made by casting is also, for example, It has been conventionally known, for example, as described in Patent Document 2.

  Regardless of the structure, the cylinders 3 and 3 are provided in the body portions 8 and 9 so as to face each other. The pistons 4 and 4 are fitted into the cylinders 3 and 3 in a liquid-tight manner and capable of displacement in the axial direction. Each of the pads 5 and 5 includes a pressure plate 13 and a lining 14 attached and fixed to a surface of the pressure plate 13 facing the rotor 11. The two pads 5 and 5 each having such a configuration are held in holding recesses 15 and 15 provided on the opposing surfaces of the body parts 8 and 9 so as to be axially displaceable. . Each of the cylinders 3 and 3 is opened in the back surface of the both holding recesses 15 and 15. Each of the guide holes 6, 6 is a radially outer portion of the pressure plates 13, 13 constituting both the pads 5, 5 than the outer peripheral edge of the rotor 11, and is spaced apart in the circumferential direction. Two positions are provided for each of the pressure plates 13 and 13 of the pads 5 and 5. Further, both the guide pins 7 and 7 are provided in a state of being passed between the body portions 8 and 9 in a state of being inserted through the guide holes 6 and 6 in the axial direction.

  When braking is performed by the disc brake 1 as described above, hydraulic pressure is introduced into the cylinders 3 and 3 (pressurized brake oil is fed), and the pistons 4 and 4 are supplied from the cylinders 3 and 3. Extrude The pistons 4, 4 press the linings 14, 14 of the pads 5, 5 against both axial sides of the rotor 11, and braking is performed by friction between the linings 14, 14 and the rotor 11.

  In the disc brake 1 configured and operated as described above, both the pads 5 and 5 need to be displaced in the axial direction in accordance with braking and release thereof. It is necessary to interpose a gap between the holding recess 15 and the inner surface of the holding recess 15. Therefore, both the pads 5 and 5 can be displaced with respect to the caliper 2 by the gap. Therefore, if no countermeasures are taken, both pads 5 and 5 rattle in the holding recess 15 in a state where they are not pressed by the pistons 4 and 4 when not braked. And vibration. For this reason, conventionally, both the pads 5 and 5 are held down by a leaf spring called an anti-rattle spring. In the case of the conventional structure shown in FIGS. 21 to 22, an anti-rattle spring 16 is provided between the guide pins 7 and 7 and the pads 5 and 5, and the pads 5 and 5 are arranged in the radial direction. It is elastically pressed inward.

  In the case of such a conventional structure, the gap between the edge of the pressure plate 13 and the inner surface of the holding recess 15 remains as it is. Therefore, in order to prevent the two pads 5 and 5 from rattling against the caliper 2 even when a large vibration is applied, such as when traveling on a rough road, the elasticity of the anti-rattle spring 16 is considerably increased. There is a need to. For this reason, the side of the pads 5 and 5 that is pressed by the anti-rattle spring 16 is less likely to displace in the direction away from the rotor 11 when the brake is released. As a result, since both the pads 5 and 5 are in contact with the both side surfaces in the axial direction of the rotor 11, the rotational torque (the drag torque) increases, and the both sides in the axial direction of the rotor 11 partially Wear occurs, causing judder during braking and a reduction in fuel consumption. Further, the work of assembling the anti-rattle spring 16 at a predetermined position becomes troublesome, which causes an increase in the assembly cost of the disc brake 1.

  In view of the above circumstances, the present invention can effectively prevent the outer and inner pads from rattling against the caliper during non-braking without using an anti-rattle spring having a large elasticity. The invention was invented in order to realize a structure of an opposed piston type disc brake that can be easily assembled, and at the same time to minimize the inclination of the pad with respect to the rotor.

The opposed piston type disc brake of the present invention is similar to the conventionally known opposed piston type disc brake described in the above-mentioned Patent Document 1, etc., and includes a caliper, a plurality of cylinders, a plurality of pistons, Pad, a plurality of guide holes, and a pair of guide pins.
Of these, the caliper is formed between the outer and inner body portions provided across the rotor that rotates together with the wheels, and the outer circumferential edges of the rotors at both ends in the circumferential direction. It consists of a pair of connecting parts to be connected.
The cylinders are provided opposite to each other on the body parts.
The pistons are fitted in the cylinders in a liquid-tight manner and capable of displacement in the axial direction.
Each of the pads includes a pressure plate and a lining fixedly attached to a surface of the pressure plate facing the rotor. And it is hold | maintained at the holding | maintenance recessed part provided in the mutually opposing surface of both the said body parts so that the displacement of an axial direction is possible.
Each of the guide holes is provided in each of the pressure plates at a position radially outward from the outer peripheral edge of the rotor and spaced apart in the circumferential direction among the pressure plates constituting the pads. Two places are provided.
Further, the both guide pins are provided in such a state that these guide holes are inserted through the guide holes in the axial direction and are spanned between the body parts.

  In particular, in the opposed piston type disc brake of the present invention, two positions separated in the circumferential direction of the two pads by the engagement between the two guide pins and the respective guide holes are axially arranged with respect to the caliper. Of the first and second support parts that support displacement, the first support part near one end in the circumferential direction supports the pads with respect to the body parts in a state where radial displacement is prevented. Yes. Similarly, the second support portion near the other end in the circumferential direction supports the pads with respect to the body portions in a state in which radial displacement is allowed. Then, by applying an elastic force in the radial direction to the second support portion by the elastic member, an elastic force in a swinging direction about the first support portion is applied to the two pads.

In order to implement the opposed piston type disc brake of the present invention as described above, specifically, one of the two guide pins constituting the first support portion as in the invention described in claim 2. And the other guide pin constituting the second support portion with respect to the two body portions in the radial direction. Support in an acceptable state.
Then, by applying elastic force directed in the radial direction to the other guide pin by the elastic member, elastic force in a direction of swinging around the one guide pin is applied to the two pads.

In carrying out the invention described in claim 2 as described above, the relationship between the installation position of the pair of guide pins and the direction in which the other guide pin is pressed depends on the rotation direction of the rotor. It is preferable to regulate by relationship.
For example, as in the invention described in claim 3, when the one guide pin is positioned on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the return side. Gives the other guide pin a radially inwardly directed elasticity.
Further, as in the invention described in claim 4, the one guide pin is positioned on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the return side. There may be a structure in which the other guide pin is given a radially outwardly directed elasticity.
On the other hand, as in the invention described in claim 5, the one guide pin is positioned on the turning-in side of the rotor in the forward movement state of the vehicle, and the other guide pin is also positioned on the outlet side When doing so, an elastic force directed radially inward is applied to the other guide pin.
Further, as in the invention described in claim 6, when the one guide pin is positioned on the turning-in side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the outlet side. The other guide pin may be structured to give a radially outwardly directed elasticity.

Further, when the invention described in claims 2 to 6 as described above is carried out, the elastic member is preferably a leaf spring arranged in the circumferential direction as in the invention described in claim 12. Then, the positions of the two intermediate portions of the leaf spring are set such that the radially inner side surface of the axially intermediate portion of one of the guide pins at the position of both guide pins and the radially outer surface of the axially intermediate portion of another guide pin And elastically contact with each other.
Further, when the invention described in claim 12 as described above is carried out, preferably, as in the invention described in claim 13, the pressure plate that constitutes both end faces in the circumferential direction of the holding recess and the pads. A pair of pad clips that are sandwiched between both end surfaces in the circumferential direction are provided in a state of being spanned between the outer and inner body portions. The leaf springs are displaced in the axial direction by engaging the circumferential ends of the leaf springs with the engagement portions formed at the axially intermediate portions of the radial outer edges of the pad clips. To prevent.

  Alternatively, in order to implement the opposed piston type disc brake of the present invention as described above, specifically, as in the invention described in claim 7, the both guide pins are arranged in the radial direction with respect to the both body portions. It supports in the state which blocked the displacement. And while inserting one guide pin in the said guide hole which comprises said 1st support part in the state which prevented the displacement of radial direction, the other guide pin is inserted in the said guide hole which comprises said 2nd support part. In the state allowing the displacement in the radial direction, it is inserted. Further, by applying an elastic force in the radial direction to a portion near the other end in the circumferential direction of both pads by the elastic member, an elastic force in a swinging direction about the one guide pin is applied to both the pads.

In carrying out the invention described in claim 7 as described above, the relationship between the installation position of the pair of guide pins and the direction of pressing the other end portion in the circumferential direction of both pads is the rotation of the rotor. It is preferable to regulate in relation to the direction.
For example, as in the invention described in claim 8, the one guide pin is positioned on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the return side. In some cases, an elastic force directed radially inward is applied to a portion closer to the other circumferential end of both pads.
Further, as in the ninth aspect of the invention, the one guide pin is positioned on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the return side. In addition, it is also possible to adopt a structure in which the elastic force directed radially outward is applied to the portion near the other circumferential end of both pads.
On the other hand, as in the invention described in claim 10, the one guide pin is positioned on the turning-in side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the outlet side. In the case where it is to be applied, the elastic force directed inward in the radial direction is applied to the portion near the other circumferential end of both the pads.
Further, as in the invention described in claim 11, the one guide pin is positioned on the turning-in side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also positioned on the outlet side. In some cases, it is also possible to adopt a structure in which a resilient force directed radially outward is applied to a portion closer to the other circumferential end of both pads.

Furthermore, when implementing the opposed piston type disc brake of the present invention, preferably, as in the invention described in claim 14, at both ends in the radial direction of the circumferential end edges of the pressure plates constituting the both pads, Anchor protrusions that engage with stepped surfaces provided at both ends in the circumferential direction of the both holding recesses are provided.
Alternatively, as in the invention described in claim 15, a return spring is provided between the pads for pressing the pads in a direction to separate them from each other.

  In the case of the opposed piston type disc brake of the present invention configured as described above, the portion corresponding to the second support portion of the pair of pads during non-braking is caused by the elastic member in the radial direction, directly or via the other guide pin. The two pads are oscillated and displaced in a predetermined direction around the portion corresponding to the first support portion. And the circumferential direction edge of the pressure plate which comprises these both pads, and the inner surface of the holding | maintenance recessed part of a caliper mutually contact | abut at two positions which exist in the diagonal direction of this pressure plate. In this state, the circumferential edge of the pressure plate and the inner surface of the holding recess are frictionally engaged, and the pressure plate does not rattle against the caliper even if the two pads are not strongly pressed toward the caliper. Disappears. As a result, it is possible to effectively prevent the outer and inner pads from rattling against the caliper during non-braking without using an anti-rattle spring having a large elasticity, thereby facilitating assembly work.

  During braking, the lining and the rotor constituting both pads rub against each other, and when a large frictional force (brake torque) accompanying braking is applied to these two pads, both these pads resist the elasticity of the elastic member, With one guide pin as the center, it swings and displaces in the direction opposite to the predetermined direction. Of the two circumferential edges of the pressure plate constituting the two pads, the delivery-side edge of the rotor is in contact with the delivery-side inner surface of the holding recess to support the brake torque. In this state, the delivery-side edge and the delivery-side inner surface are in contact with each other over a sufficiently large area, so that excessive contact pressure does not act on the contact portion, and the delivery-side edge and the rotation-side edge are not affected. It is possible to prevent the occurrence of significant wear on the outlet inner surface. In particular, if the configuration described in claim 14 is adopted, the postures of the two pads at the time of braking can be stabilized, and the vibration of both the pads at the time of braking can be suppressed.

  In the case of the present invention, since the edge of the pressure plate and the inner surface of the holding recess are frictionally engaged even during non-braking based on the elasticity of the elastic member, There is a possibility that the side surfaces of the rotor are difficult to be separated from each other, and the respective surfaces remain rubbed with each other. On the other hand, if a return spring is provided as in the invention described in claim 15, such rubbing can be prevented.

The perspective view which shows the 1st example of embodiment of this invention in the state seen from the radial direction outer side and inner side of the caliper. Similarly, the orthographic view seen from the radial direction outer side. II sectional drawing of FIG. FIG. 4A and 4B show support holes formed in the caliper to support both ends of the pair of guide pins, (A) is on the entrance side in the forward state, and (B) is also on the exit side in the same direction as FIG. The partial orthographic view seen from. FIG. 3 is a cross-sectional view of FIG. The pad clip clamped at the abutting portion between the circumferential edge of the pressure plate of the pair of pads and the inner surface of the holding recess is cut in a stepped manner in the state (A) viewed from the circumferential direction and in the center of (A). The orthographic projection shown by the state (B) seen from the axial direction. The figure similar to FIG. 4 which shows the 2nd example of embodiment of this invention. The figure similar to FIG. 2 which shows the 3rd example. FIG. 10 is a knee cross-sectional view of FIG. 9. FIG. 6 is a cross-sectional view of the hoeho of FIG. 2 showing a fourth example of the embodiment of the present invention. The fragmentary sectional view which took out the pad and a pair of guide pin and which looked at the 5th example of embodiment of this invention from the same direction as FIG. A first example of a representative structure belonging to the technical scope of the present invention includes a non-braking to light braking state (A), a forward braking state (B), and a reverse braking state (C). FIG. The schematic diagram which shows the 2nd example. The schematic diagram which shows the 3rd example. The schematic diagram which shows the 4th example. The schematic diagram which shows the 5th example. The schematic diagram which shows the 6th example. The schematic diagram which shows the 7th example. The schematic diagram which shows the 8th example. The orthographic projection figure which shows one example of the conventional structure in the state seen from radial direction outer side. FIG. 22 is a cross-sectional view of FIG.

[First example of embodiment]
FIGS. 1-7 has shown the 1st example of embodiment of this invention corresponding to Claims 1-3, 12, 13, 14, and 15. FIG. The opposed piston type disc brake of this example includes a caliper 2a, a plurality of cylinders 3, 3, a plurality of pistons 4, 4, a pair of pads 5a, 5a, a plurality of guide holes 6a, 6a, and a pair of guides. Pins 7a and 7b, a leaf spring 18, and a pair of return springs 20 and 20a are provided. The feature of the opposed piston type disc brake of this example is that, when not braking, both circumferential edges of the pads 5a and 5a are inclined with respect to the receiving surface which is the inner surface of the holding recesses 21 and 21 provided in the caliper 2a. The point is that the delivery-side edges of the pads 5a and 5a are brought into uniform contact with the receiving surface during braking. For this reason, in the case of this example, the guide pin 7b on the delivery side (the right side in FIGS. 1, 2 and 4) of both the guide pins 7a and 7b is supported so as to be able to swing and displace, The leaf spring 18 presses the guide pin 7a on the turn-in side (left side in FIGS. 1, 2, and 4) radially inward. Hereinafter, the structure of this example having such characteristics will be described.

  The caliper 2a is integrally formed by casting an aluminum alloy, and includes an outer and inner body portions 8a and 9a and a pair of connecting portions 10a and 10a. Outer and inner body portions 8a and 9a are provided with a rotor 11a that rotates together with the wheels sandwiched from both sides in the axial direction. In the case of this example, this rotor 11a rotates clockwise in FIG. Moreover, both the said connection parts 10a and 10a have connected the circumferential direction both ends of both said body parts 8a and 9a in the radial direction outer position rather than the outer periphery of this rotor 11a. In addition, holding concave portions 21 and 21 are provided in portions between the connecting portions 10a and 10a, respectively, on the surfaces of the outer and inner body portions 8a and 9a facing each other. In addition, each of the pads 5a and 5a is configured to hold the displacement in the axial direction. The inner surfaces of both holding recesses 21 and 21 in the circumferential direction and the surfaces of the connecting portions 10a and 10a facing each other are on the same plane. In other words, the inner surfaces of both end portions in the circumferential direction of the holding recesses 21 and 21 and the surfaces of the connecting portions 10a and 10a facing each other are smoothly continuous without a stepped portion or the like. Each of the cylinders 3 and 3 is open to the mutually opposing surfaces of the outer and inner body portions 8a and 9a at the bottom portions of the holding recesses 21 and 21. The pistons 4 and 4 are fitted in the cylinders 3 and 3 in such a manner as to be fluid-tight and displaceable in the axial direction.

  Each of the pads 5a and 5a is composed of a pressure plate 13a and linings 14a and 14a fixedly attached to a surface of the pressure plate 13a facing the rotor 11a. Of these, the pressure plate 13a is held in the holding recesses 21 and 21 via pad clips 22 and 22 so as to be capable of axial displacement. In the case of this example, the pad clips 22 and 22 are subjected to a large surface pressure based on the brake torque on the inner surfaces of the end portions of the holding recesses 21 and 21 provided in the caliper 2a made of aluminum alloy. In this case, it is provided to prevent damage such as indentation on the inner surface of the end portion. On the other hand, when a caliper made of cast iron is used, a similar pad clip is required to prevent the sliding contact portion between the caliper and the pad backing plate from rusting.

  In any case, both the pad clips 22, 22 are made of a thin metal plate having corrosion resistance and compression resistance, such as a stainless steel plate, and have a gate-shaped substrate portion 23 as shown in FIG. . In addition, a plurality of side bent portions 24, 24, one inner diameter side bent portion 25, and a pair of outer diameter side bent portions 26, 26 are formed on the edge portion of the substrate portion 23. Of these, the side bent portions 24, 24 are substantially perpendicular to the same direction from the substrate portion 23 from a plurality of locations on both ends of the substrate portion 23 in the axial direction (two locations in the illustrated example, a total of four locations). It is formed in a bent state. Further, the inner diameter side bent portion 25 is formed on the inner peripheral surface of the both connecting portions 10a and 10a in the direction opposite to the side bent portions 24 and 24 from the inner radial end of the central portion of the substrate portion 23. It is formed in a state of being bent according to the inclination. Further, the both outer-diameter side bent portions 26, 26 are 180 at the intermediate portion of the portion extending radially outward from the portion slightly deviated from the central portion of the outer-diameter side edge of the substrate portion 23 toward both ends. It is formed in a state in which it is slightly folded back and its tip is bent in the opposite direction to the side bent portions 24, 24.

  As shown in FIGS. 1, 2, and 4, the two pad clips 22 and 22, each having the shape as described above, are attached to portions near both ends of the caliper 2 a in the circumferential direction. That is, the base plate part 23 constituting both the pad clips 22 and 22 is brought into contact with the inner surfaces of both the holding recesses 21 and 21 in the circumferential direction and the opposing surfaces of the connecting parts 10a and 10a. In this state, the side bent parts 24, 24 are brought into contact with the mutually opposing surfaces of the outer and inner body parts 8a, 9a at both circumferential ends of the holding recesses 21, 21. Also, the inner diameter side bent portion 25 is brought into contact with the inner peripheral surfaces of both the connecting portions 10a and 10a, and the both outer diameter side bent portions 26 and 26 are brought into contact with the outer peripheral surfaces of the both connecting portions 10a and 10a.

  The pressure plates 13a and 13a constituting the pads 5a and 5a are respectively connected to the substrate portions 23 and 23 of the pad clips 22 and 22 attached to the circumferentially opposite ends of the caliper 2a as described above. Wear between. The distance between the two substrate portions 23 and 23 (in a state where the two substrate portions 23 and 23 and the inner surfaces of both holding recesses 21 and 21 are in contact with each other with no gap) is set between the pressure plates. 13a and 13a are slightly larger than the length in the circumferential direction. Accordingly, both the pressure plates 13a and 13a can be displaced in the axial direction in the holding recesses 21 and 21, and in addition to the virtual center axis O in the front and back direction in FIG. A slight oscillating displacement centered on the center) is held possible.

The peripheral portions of the pressure plates 13a and 13a constituting the pads 5a and 5a protrude from the peripheral portions of the linings 14a and 14a, respectively. In particular, the radially outer end portion and the circumferential end portion are sufficiently protruded in the respective directions from the peripheral portions of both the linings 14a and 14a.
First, with respect to the radially outer end portions of the pressure plates 14a, 14a, projecting portions 27, 27 projecting radially outward are provided at portions near both ends in the circumferential direction. The guide holes 6a and 6a are formed respectively. The guide pins 7a and 7b are inserted through the guide holes 6a and 6a. The inner dimension of each of the guide holes 6a, 6a (the distance between the inner surfaces facing each other) is slightly smaller than the outer diameter of the guide pins 7a, 7b with respect to the radial direction (although relative displacement in the axial direction is allowed, It is large enough to substantially prevent the relative displacement in the radial direction) and slightly larger than the outer diameter in the circumferential direction (to the extent that the relative displacement in the circumferential direction can be allowed to some extent).

  Both the guide pins 7a and 7b are spanned between the outer body portion 8a and the inner body portion 9a constituting the caliper 2a in a state of being arranged in the axial direction. However, the support states of the guide pins 7a and 7b with respect to the body parts 8a and 9a are different from each other. In the case of this example, the guide pin 7a on the entry side is supported by the body portions 8a and 9a so as to be able to be slightly displaced in the radial direction, and the guide pin 7b on the delivery side is supported by both the body portions. 8a and 9a are supported in a state where displacement in each direction is prevented. Therefore, in the case of this example, in order to support both end portions of the both guide pins 7a and 7b, the radially outer ends of the body portions 8a and 9a are respectively located at two positions separated in the circumferential direction. The shapes of the formed support holes 28a and 28b are different from each other.

  That is, the support holes 28a for supporting both ends of the guide pin 7a on the entrance side are long in the radial direction as shown in FIG. 5A (preferably, support on the delivery side described below). The hole 28b is a long hole having a partial arc shape centered on the center. The width dimension of the support hole 28a on the turn-in side is slightly larger than the outer diameter of the guide pin 7a on the turn-in side, and the length dimension is also larger than the diameter of the guide pin 7a on the turn-in side. Is slightly larger (so that the guide pin 7a can be slightly displaced radially in the support hole 28a). On the other hand, the support holes 28b for supporting both ends of the guide pin 7b on the delivery side are simple circular holes as shown in FIG. The guide pin 7b on the delivery side is inserted through the support hole 28b with almost no gap. In the case of this example, the engaging portion between the guide pin 7b on the delivery side and the support hole 28b on the delivery side of the pressure plates 13a and 13a is the first support portion described in the claims, Similarly, the engaging portion between the guide pin 7a on the turn-in side and the support hole 28a on the turn-in side is the second support portion.

  In the case of this example, the two pads 5a, 5a (both the pressure plates 13a, 13a) are placed in the holding recesses 21, 21 of the caliper 2a by the above-described configuration. The guide pin 7b (first support portion) is supported so as to be able to slightly swing. Further, the leaf spring 18 provided between the caliper 2a and the guide pin 7a on the turn-in side imparts an elastic force directed radially inward to the guide pin 7a on the turn-in side. The leaf spring 18 is formed by bending a belt-like metal plate having elasticity, such as a stainless spring steel plate, and the distance between the two coupling portions 10a and 10a constituting both ends in the circumferential direction of the caliper 2a. Have a greater length dimension. In addition, elastic pressing portions 29a and 29b each having a partial arc shape are provided at two positions in the middle portion in the longitudinal direction of the leaf spring 18. The bending directions of these elastic pressing portions 29a and 29b are opposite to each other, the elastic pressing portion 29a on the entry side has a radially outer surface, the elastic pressing portion 29b on the delivery side has a radially inner surface, and a convex surface. It is curved in the direction.

  The leaf spring 18 having such a shape elastically abuts both end portions in the length direction (circumferential direction) against the radially outer surfaces of the connecting portions 10a and 10a, and the elastic pressing portion on the entry side. 29a on the radially outer side of the axially intermediate portion of the guide pin 7a on the delivery side, and the elastic pressing portion 29b on the delivery side on the radially inner surface of the intermediate portion of the guide pin 7b on the delivery side. , Each hit elastically. In this state, elasticity is applied to the guide pin 7a on the turn-in side, which is directed radially inward, and to the guide pin 7b on the feed-out side, which is directed outward in the radial direction. Further, both end portions of the leaf spring 18 are positioned between the outer diameter side bent portions 26, 26, which are respectively provided in pairs on the radially outer end edges of the pad clips 22, 22. Therefore, the leaf spring 18 does not move in the axial direction from the installation position shown in FIGS.

  The plate spring 18 is provided to press the guide pin 7a on the turn-in side inward in the radial direction, as will be described below. Accordingly, among the leaf springs 18, both the elastic pressing portions 29a and 29b are elastically brought into contact with the predetermined positions of the both guide pins 7a and 7b as described above, and either one end thereof is It is necessary to make it contact | abut to the radial direction outer surface of any one of the connection parts 10a and 10a provided in the circumferential direction both ends of the caliper 2a. On the other hand, the other end portion of the leaf spring 18 may be lifted from the radially outer surface of the other connecting portion 10a (see, for example, the right end portion in FIG. 8 described later). However, in order to prevent the displacement of the installation position, it is not preferable to lift more than the radial height of each of the outer diameter side bent portions 26, 26 (the degree of lifting should be stopped at the right end portion of FIG. 8 described later). Is).

  As described above, the guide pin 7b on the delivery side is supported so as not to be displaced with respect to the caliper 2a, whereas the guide pin 7a on the entry side is displaced in the radial direction with respect to the caliper 2a. Is supported by possible. For this reason, when the external force is not applied to the pads 5a and 5a (during non-braking) and when the external force is small (during light braking), the turning-in side guide pin 7a is The pads 5a and 5a are displaced inward in the radial direction, and are oscillated and displaced counterclockwise in FIG. 4 around the guide pin 7b on the delivery side. As a result of the swing displacement, as shown in the figure, among the circumferential ends of the pressure plates 13a and 13a constituting the pads 5a and 5a, , The radially inner end of the outlet side edge (the diagonal position portions of the pressure plates 13a and 13a) are the inner surfaces of the holding recesses 21 and 21, respectively, 22).

  On the other hand, at the time of braking (at the time of braking in which a large brake torque is applied to the extent that the leaf spring 18 is elastically deformed, the same applies hereinafter), the linings 14a and 14a constituting the pads 5a and 5a and the rotor 11a. 4, a moment in the clockwise direction in FIG. 4 is applied to both the pads 5a and 5a. That is, the brake torque is applied in a tangential direction from the friction center O between the linings 14a and 14a and the rotor 11a as shown by an arrow α in FIG. In this way, the brake torque, as shown by the arrow α, during the non-braking period or during the light braking period, is provided at the feeding-side edges of the pressure plates 13a, 13a and the feeding-side edges of the holding recesses 21, 21. It acts on the outer portion in the radial direction from the abutting portion (non-braking anchor side abutting portion) with the inner surface. For this reason, the pressure plates 13a, 13a elastically deform the leaf spring 18 and displace the anchor side guide pin 7a radially outward, while centering the respective non-braking anchor side contact portions. As shown in FIG. And the delivery side edge of both said pressure plates 13a and 13a and the delivery side edge inner surface of both said holding | maintenance recessed parts 21 and 21 contact | abut not only in a radial direction inner end part but in a radial direction outer end part. As a result, the brake torque can be transmitted from the pressure plates 13a and 13a to the caliper 2a over a wide area during braking in which a large brake torque acts.

  In addition, recessed portions 30 and 30 are formed in the radial intermediate portions of both the inlet and outlet edges of the pressure plates 13a and 13a, respectively. In other words, both end portions in the radial direction of the circumferential edge portions of the pressure plates 13a, 13a are protruded in the circumferential direction from the intermediate portion in the radial direction, and these portions are respectively opposed to the circumferential ends of the holding recesses 21, 21 respectively. Anchor protrusions 31a and 31b that engage (abut) the stepped surface provided in the portion. During non-braking and light braking described above, out of these anchor convex portions 31a and 31b, the convex portion 31a on the outer diameter side on the inward side and the convex portion 31b on the inner diameter side on the outlet side are The holding recesses 21 and 21 are brought into contact with the radially outer end and the radially inner end of the stepped surfaces at both ends in the circumferential direction. On the other hand, at the time of braking described above, of the respective anchor protrusions 31a, 31b, the protrusions 31a, 31b at both ends in the radial direction on the output side are stepped on the output side end portions of the holding recesses 21. It is made to contact | abut to the radial direction both ends, respectively.

  Further, in the case of this example, the return springs 20 and 20a that press the pads 5a and 5a in the direction of separating them from each other are provided using the recessed portions 30 and 30. Of these, as shown in FIGS. 1 and 6, the return spring 20 has a bottom portion of each of the recessed portions 30, 30 and a circumference of the linings 14 a, 14 a among both circumferential ends of the pressure plates 13 a, 13 a. It is installed by using stepped portions 32 and 32 that exist in a state of facing each other at the portion between both ends in the direction. For this purpose, V-shaped locking receiving portions 33 and 33 are provided in a part of each of the step portions 32 and 32, respectively, and a portion of the rotor 11a is straddled over each of the locking receiving portions 33 and 33. Locking portions 34 and 34 provided at both ends of the return spring 20 having a shape are locked.

  The return spring 20 is a plate spring formed by bending a metal plate having elasticity and corrosion resistance, such as stainless spring steel and galvanized steel plate, and includes an elastic deformation portion 35, a pair of arm portions 36, 36, A pair of bent portions 37 and 37 are provided. Among these, the elastic deformation portion 35 is provided at a central portion of the return spring 20 as a whole and in a portion straddling the rotor 11a. In the case of this example, the elastic deformation portion 35 has a corrugated shape, ensures an elastic deformation amount, and keeps the spring constant related to bringing the two bent portions 37 and 37 close to each other. The arms 36 and 36 are bent radially inward from both axial ends of the elastic deformation portion 35. Further, the bent portions 37 and 37 are bent from the radially inner ends of the arms 36 and 36 in a direction approaching each other in the axial direction. Further, with respect to the circumferential direction (front and back direction in FIG. 6), the width of the bent portions 37 and 37 is larger than the width of the elastically deformable portion 35 and the arms 36 and 36. And about the circumferential direction, the one half part (back side half part of FIG. 6) of the said both bending parts 37 and 37 is extended in the same direction rather than the radial direction inner end part of both said arm parts 36 and 36. FIG. . And this extended part is engaged with each said latching receiving part 33,33 as the said both latching | locking parts 34,34.

The return spring 20 as described above has both ends in the circumferential direction of the pressure plates 13a and 13a in a state where the distance between the tips of the arms 36 and 36 is reduced while the elastic deformation portion 35 is elastically deformed. Assemble between the parts. That is, the elastically deforming portion 35 is positioned radially outward from the outer peripheral edge of the rotor 11a, and the both locking portions are disposed in a state where the both arm portions 36 and 36 are disposed on both axial sides of the rotor 11a. The leading edges of the portions 34 and 34 are abutted against the bottom portions (the deepest portions of the V-shaped grooves) of the both locking receiving portions 33 and 33. In this manner, in the state where the return spring 20 is assembled between the circumferential ends of the pressure plates 13a, 13a, the circumferential ends of the pads 5a, 5a are separated from each other. The elasticity of the direction to be given is given. For this reason, when the force pressing the two pads 5a and 5a against the side surface of the rotor 11a is released along with the release of braking, the two return springs 20 cause the both pads 5a and 5a to move to the side surface of the rotor 11a. Evacuate from. For this reason, it is possible to eliminate friction (dragging) between the side surface of the rotor 11a and the linings 14a and 14a during non-braking. Further, in the assembled state, as shown in FIG. 6, the central spring portion of the corrugated shape of the elastic deformation portion 35 of the return spring 20 is in contact with the leaf spring 18. For this reason, this leaf | plate spring 18 plays the role of an anchor, and can give the elasticity of the direction which mutually separates with respect to the said pads 5a and 5a stably.
Note that the return spring 20a is folded back of an elastically deformable portion 35a provided at the center as compared with the return spring 20, as shown in FIG. 11 for explaining the structure of a fourth example of the embodiment described later. By increasing the number of portions (waveforms), the spring constant of the return spring 20a is kept low. Except this structure, it is the same as the return spring 20 described above.

  As described above, in the case of the opposed piston type disc brake of this example, during non-braking or light braking, the anchors provided at both circumferential ends of the pressure plates 13a and 13a as shown in FIG. Among the convex portions 31a and 31b, the convex portion 31a on the outer diameter side on the inlet side and the convex portion 31b on the inner diameter side on the outlet side (for each of the pressure plates 13a and 13a, two convex positions on the diagonal line). Portions 31a, 31b) abut on the radially outer end and the radially inner end of the stepped surfaces at both circumferential ends of the holding recesses 21, 21 respectively. In this state, the tip edges of the convex portions 31a and 31b at the two positions and the circumferentially opposite side portions of the inner surfaces of the holding concave portions 21 and 21 are frictionally engaged via the pad clips 22 and 22, respectively. . As a result, both the pressure plates 13a and 13a can be connected to the caliper 2a (the holding recesses 21 and 21) without particularly pressing both the pads 5a and 5a toward the caliper 2a (the holding recesses 21 and 21). No more rattling against. As a result, it is possible to effectively prevent the two pads 5a and 5a from rattling against the caliper 2a during non-braking without using an anti-rattle spring having a large elasticity, thereby facilitating assembly work. Further, since it is not necessary to use an anti-rattle spring having a large elasticity (the elasticity of about 1/2 to 1/3 of the conventional one is sufficient), the edges of the pressure plates 13a and 13a and the edges are frictioned. The contact pressure with the engaged part can be kept low. As a result, the force required to displace both the pads 5a and 5a in the axial direction along with braking and releasing thereof can be kept low.

  On the other hand, at the time of braking during forward movement, as described above, the pads 5a and 5a are oscillated and displaced in the clockwise direction in FIG. 4 around the guide pin 7b on the delivery side due to the braking torque accompanying the braking. Become a trend. When the brake torque is increased, the pads 5a and 5a are swung clockwise while the guide pin 7a on the turning-in side is displaced radially outward against the elasticity of the leaf spring 18. The anchor protrusions 31a and 31b that are dynamically displaced and provided at both ends in the radial direction of the output side edges of the pressure plates 13a and 13a are the inner surfaces of the output side of the holding recesses 21 and 21, respectively. And the brake torque is supported. In this state, the direction in which the brake torque is applied passes between the contact portions of the anchor protrusions 31a, 31b and the inner surfaces of the holding recesses 21, 21, so that the brake torque Acts in a direction to stabilize the posture of the pads 5a, 5a. Therefore, it is possible to suppress the vibration of both the pads 5a and 5a during braking. Each of the anchor protrusions 31a, 31b is a flat surface parallel to the inner surfaces of both holding recesses 21, 21 in the circumferential direction. It abuts on the inner surface (via a pad clip 22 installed on the outlet side). For this reason, it is possible to secure a sufficient area of the contact portion for transmitting the brake torque from the both pads 5a, 5a to the caliper 2a, and an excessive surface pressure does not act on the contact portion. As a result, it is possible to prevent significant wear from occurring on the distal end surfaces of the anchor protrusions 31a and 31b and the delivery-side inner surfaces of the holding recesses 21 and 21.

  Further, at the time of braking in the reverse state, the pads 5a and 5a tend to swing and displace in the clockwise direction in FIG. When the brake torque is increased, the pads 5a and 5a are moved to the timepiece while the guide pin 7a, which becomes the return side when retreating, is displaced radially outward against the elasticity of the leaf spring 18. The anchor protrusions 31a and 31b provided at both ends of the pressure plates 13a and 13a in the radial direction of the edge that is on the return side when retreating are provided in the holding recesses. 21, 21 abuts against the inner surface of the delivery side and supports the brake torque. In this state, the direction in which the brake torque is applied passes between the contact portions of the anchor protrusions 31a, 31b and the inner surfaces of the holding recesses 21, 21, so that the brake torque Acts in a direction to stabilize the posture of the pads 5a, 5a. Therefore, it is possible to suppress the vibration of both the pads 5a and 5a during braking.

  In the case of the structure of this example as described above, the edges of the pressure plates 13a, 13a of the pads 5a, 5a and the inner surfaces of the holding recesses 21, 21 based on the elasticity of the leaf spring 18, Since frictional engagement is performed even during non-braking, the front surfaces of the linings 14a and 14a of the pads 5a and 5a are not easily separated from the side surfaces of the rotor 11a when braking is released, and these surfaces remain rubbed together. there is a possibility. On the other hand, in the structure of this example, since both the return springs 20 and 20a are provided between the circumferential ends of both the pads 5a and 5a, both the pads 5a are released when the brake is released. 5a can be sufficiently separated (larger than the rotor 11a). For this reason, it is possible to prevent rubbing after the braking is released as described above.

When the rotation direction of the rotor 11a is opposite to that in the first example of the embodiment described above, that is, when the vehicle moves forward, the rotor 11a rotates counterclockwise in FIG. In the case where the right side in FIG. 4 is the turn-in side, and the left side is also the turn-out side), it is possible to impart radially outward elasticity to the left guide pin 7a in FIG. good). Applying the elastic force outward in the radial direction can be easily performed by reversing the assembling direction of the leaf spring 18 with respect to FIG. When such a configuration is adopted, during non-braking and light braking, the anchor projections 31a, 31b formed at both circumferential ends of the pressure plates 13a, 13a are arranged on the inner diameter side on the outlet side. The anchor convex portion 31b and the anchor convex portion 31a on the outer diameter side on the entrance side come into contact with the inner surfaces of both holding concave portions 21, 21 in the circumferential direction. At the time of braking, the pressure plates 13a and 13a are oscillated and displaced counterclockwise in FIG. As a result, as in the case of the first example of the above-described embodiment, the anchor convex portions 31a and 31b at the outlet side edge contact the inner surfaces of the outlet end portions of the holding concave portions 21 and 21. . In this process, the anchor protrusion 31b on the inner diameter side and the pad clip 22 on the delivery side slightly slide in the radial direction on the delivery side, so that the movement of both the pads 5a and 5a during braking is performed. This is heavier than the first example of the above-described embodiment (the force required for the rocking displacement is increased). In other words, in the first example of the above-described embodiment, the movement of both the pads 5a and 5a can be lightened during braking, and a desired braking force can be obtained more stably.
In the case of this example, hollow guides are used as the guide pins 7a and 7b to reduce the size and reduce the material cost. It is safe to use solid ones.

[Second Example of Embodiment]
FIG. 8 shows a second example of an embodiment of the present invention corresponding to claims 1 to 3, 12, 13, and 14. In the case of this example, the shape of the elastic pressing portion 29c on the delivery side constituting the leaf spring 18a is close to a semi-cylindrical shape as compared with the first example of the embodiment described above. And this elastic press part 29c is made to contact | abut so that this guide pin 7b may be held to the lower half part of the axial direction middle of the guide pin 7b on the delivery side. Since the configuration and operation of the other parts are the same as in the first example of the embodiment described above, overlapping illustrations and descriptions are omitted.

[Third example of embodiment]
9 to 10 also show a third example of the embodiment of the present invention corresponding to claims 1 to 3, 12, 13, and 14. FIG. In the case of this example, the length dimension of the leaf spring 18b is made shorter than in the case of the first example and the second example described above. Of the leaf springs 18b, only the outlet side end portion is formed at the radially outer end edge portion of the pad clip 22 and is disposed between the pair of outer radius side bent portions 26, 26, so Positioning in the axial direction of the output side end is achieved. On the other hand, positioning in the axial direction of the turn-in side end and the intermediate portion of the leaf spring 18b exists at both ends of the small diameter portions 38 and 38 formed on the outer peripheral surface of the intermediate portion of the pair of guide pins 7c and 7d. This is achieved by engaging with the stepped portion. Since the configuration and operation of other parts are the same as those in the first example of the above-described embodiment, overlapping illustrations and descriptions are omitted.

[Fourth Example of Embodiment]
FIG. 11 shows a fourth example of the embodiment corresponding to the fifteenth aspect. The 4th example of embodiment of this invention is shown. In the case of this example, the number of folded portions (waveforms) of the elastic deformation portion 35a provided at the center portion of the return spring 20a is increased to keep the spring constant of the return spring 20a low, and the pair of pads 5a, 5a. As the wear of the linings 14a and 14a progresses, the change in elasticity acting in the direction of separating the two pads 5a and 5a can be suppressed to a lower level. Since the configuration and operation of other parts are the same as those in the first example of the above-described embodiment, overlapping illustrations and descriptions are omitted.

[Fifth Example of Embodiment]
An embodiment of the invention corresponding to claims 7 to 11 will be described with reference to FIG. In carrying out the inventions according to the seventh to eleventh aspects, the outer and inner body portions 8a and 9a (see, for example, FIG. 1) constituting the caliper 2a are connected to both ends of the pair of guide pins 7 and 7. On the other hand, it supports in the state which prevented the displacement of radial direction (and circumferential direction). Then, one guide pin 7 (on the right in FIG. 12) is inserted into the guide hole 17a constituting the first support portion in a state in which the radial displacement is prevented, and the guide hole constituting the second support portion. The other guide pin 7 (left side in FIG. 12) is inserted into 17b in a state allowing radial displacement. Further, by applying elastic force directed in the radial direction to the portion closer to the second support portion of the pair of pads 5b by an elastic member such as a leaf spring, the one guide pin 7 is centered on both the pads 5b. As a result, elasticity in the swinging direction is applied.

The relationship between the installation positions of the both guide pins 7 and 7 and the direction in which the other end in the circumferential direction of the pads 5b is pressed is restricted by the relationship with the rotational direction of the rotor.
For example, the one guide pin 7 is positioned on the return side of the rotor when the vehicle is moving forward (the rotor rotates clockwise in FIG. 12), and the other guide pin 7 is also positioned on the return side. In the case where it is to be applied, the elastic force directed radially inward or radially outward is applied to the turn-in side portions of the pads 5b. Such a radially inward elasticity can be easily imparted by pressing the outer diameter side edge of the pressure plate 13b constituting both the pads 5b radially inward. In addition, the radially outward elasticity is provided, for example, by providing a stepped portion facing radially outward at the inner diameter side and the turn-in side end portion of the holding recess provided in the caliper. A compression spring such as a leaf spring is provided between the inner peripheral edge portion of the end of the pressure plate 13b.
On the other hand, the one guide pin 7 is positioned on the rotational entry side of the rotor when the vehicle is moving forward (the rotor rotates counterclockwise in FIG. 12), and the other guide pin 7 is rotated in the same manner. In the case where it is located on the exit side, a resilience directed radially outward or radially inward is applied to the delivery side portions of both pads 5b. In order to provide such a radially outward elasticity, for example, a step portion directed radially outward is provided on the inner diameter side and the outlet side end portion of the holding recess provided in the caliper, and this step portion and A compression spring such as a leaf spring is provided between the inner peripheral edge portion of the outlet side end portion of the pressure plate 13b constituting both the pads 5b. Further, the radially inward elasticity can be easily applied by pressing the outer diameter side end edge of the pressure plate 13b constituting both the pads 5b radially inward.

  Such a structure is somewhat smaller than the case of the first to fourth examples of the above-described embodiment from the aspect of suppressing the force that displaces both the pads 5b in the axial direction with the start and release of braking. It will be disadvantageous. However, as in the case of the first to fourth examples of these embodiments, the two pads 5b can be effectively rattled against the caliper during non-braking without using an anti-rattle spring having a large elasticity. This can prevent the assembly work. Further, during braking, the lining 14a constituting both the pads 5b and the rotor rub against each other, and the discharge side end edges of the pressure plates 13b constituting both the pads 5b and the holding recesses provided in the caliper It is possible to prevent the wear-out side edge and the feed-out side inner surface from being significantly worn by contacting the feed-out side inner surface with a sufficiently large area. In other words, in the case of the first to fourth examples of the above-described embodiment, the pair of pads 5a and 5a (see, for example, FIG. 1) are swung through the guide pins supported so as to be displaceable in the radial direction. Since the structure for displacing is employed, the force for displacing both the pads 5a and 5a in the axial direction along with the start and release of braking can be kept small. The reason for this is that, unlike the case of this example, a portion that rubs in the axial displacement can be suppressed to a small extent (the leaf spring 18 and the pressure plates 13a and 13a do not need to be relatively displaced).

  The present invention can be modified in various ways within the technical scope defined by the claims. Of these, a pair of guide pins is fixed to the caliper, the other guide pin is supported so as to be radially displaceable with respect to the caliper, and the other guide pin is pressed in the radial direction by an elastic member. The four examples will be briefly described with reference to FIGS. 13 to 16 including the embodiment described above.

  First, the first example shown in FIG. 13 corresponds to the first to third examples of the embodiment shown in FIGS. 1 to 10, and fixes the guide pin 7b on the delivery side during advance. At the same time, the guide pin 7a on the turn-in side is supported so as to be able to be displaced in the radial direction, and elastic force directed radially inward is applied to the guide pin 7a on the turn-in side. With this structure, the posture of the pad 5a is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and (C) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are as described above.

  Next, the second example shown in FIG. 14 fixes the guide pin 7b on the delivery side at the time of forward movement, and also supports the guide pin 7a on the delivery side so that it can be displaced in the radial direction. Elasticity directed outward in the radial direction is applied to the guide pin 7a on the turn-in side. With this structure, the posture of the pad 5a is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and (C) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are substantially the same as in the first example described above.

  Next, the third example shown in FIG. 15 fixes the guide pin 7a on the entrance side during forward movement, and also supports the guide pin 7b on the delivery side so that it can be displaced in the radial direction. Elasticity directed radially inward is applied to the guide pin 7b on the delivery side. With this structure, the posture of the pad 5a is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and (C) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are substantially the same as in the first example described above.

  Next, the fourth example shown in FIG. 16 fixes the guide pin 7a on the entrance side during forward movement, and also supports the guide pin 7b on the delivery side so that it can be displaced in the radial direction. Elasticity directed radially outward is applied to the guide pin 7b on the delivery side. With this structure, the posture of the pad 5a is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and (C) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are substantially the same as in the first example described above.

  A similar combination can be implemented even in a structure in which the pair of pins 7 and 7 are fixed and the pressure plate 13a can be displaced relative to the pins 7 and 7 as shown in FIG. is there. Such a structure can be obtained by making a long guide hole drawn in a broken line in FIGS. 13 to 16 and a guide hole overlapping in the axial direction into a large guide hole 17b as shown on the left side of FIG. Long long holes are omitted). Four representative examples of such a structure will be briefly described with reference to FIGS. 17 to 20 including the embodiment described above.

First, the fifth example shown in FIG. 17 corresponds to the fifth example of the embodiment shown in FIG. 12 described above, and both ends of the pair of guide pins 7 and 7 are connected to the outer constituting the caliper 2a. The inner body portions 8a and 9a (see, for example, FIG. 1) are supported in a state in which radial (and circumferential) displacement is prevented. Then, the guide pin 7 (the right side in FIG. 17) at the time of advancement is inserted into the guide hole 17a constituting the first support portion while preventing radial displacement, and the second support portion. The guide pin 7 (the left side in FIG. 17) on the turn-in side at the time of forward movement is inserted into the guide hole 17b that constitutes the above in a state that allows radial displacement. Further, the elastic member imparts the elastic force directed radially inward to the portion of the pair of pads 5b closer to the second support portion.
With this structure, the posture of the pad 5b is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and as shown in (B) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are as described above.

Next, in the sixth example shown in FIG. 18, both ends of the pair of guide pins 7 and 7 are arranged in the radial direction with respect to the outer and inner body parts 8a and 9a (see, for example, FIG. 1) constituting the caliper 2a. It supports in the state which prevented the displacement of (and circumferential direction). Then, the guide pin 7 (the right side in FIG. 18) at the time of advancement is inserted into the guide hole 17a constituting the first support portion while preventing radial displacement, and the second support portion. The guide pin 7 (the left side in FIG. 18) on the turn-in side at the time of forward movement is inserted into the guide hole 17b that constitutes the above in a state that allows radial displacement. Further, an elastic member imparts a radially outward force to the portion of the pair of pads 5b closer to the second support portion.
With this structure, the posture of the pad 5b is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and as shown in (B) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are as described above.

Next, in the seventh example shown in FIG. 19, both ends of the pair of guide pins 7 and 7 are arranged in the radial direction with respect to the outer and inner body parts 8a and 9a (see FIG. 1 for example) constituting the caliper 2a. It supports in the state which prevented the displacement of (and circumferential direction). Then, the guide pin 17 (the left side in FIG. 19) on the turning-in side at the time of advancement is inserted into the guide hole 17a constituting the first support part in a state in which the radial displacement is prevented, and the second support part. The guide pin 7 (the right side in FIG. 19) on the delivery side at the time of forward movement is inserted through the guide hole 17b constituting the above in a state that allows radial displacement. Further, the elastic member imparts the elastic force directed radially inward to the portion of the pair of pads 5b closer to the second support portion.
With this structure, the posture of the pad 5b is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and as shown in (B) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are as described above.

Next, in the eighth example shown in FIG. 20, both ends of the pair of guide pins 7 and 7 are arranged in the radial direction with respect to the outer and inner body parts 8a and 9a (for example, see FIG. 1) constituting the caliper 2a. It supports in the state which prevented the displacement of (and circumferential direction). Then, the guide pin 17 (the left side in FIG. 20) at the time of advancement is inserted into the guide hole 17a constituting the first support portion while preventing radial displacement, and the second support portion. The guide pin 7 (the right side in FIG. 20) at the time of advancement is inserted into the guide hole 17b that constitutes the above in a state that allows radial displacement. Further, an elastic member imparts a radially outward force to the portion of the pair of pads 5b closer to the second support portion.
With this structure, the posture of the pad 5b is as shown in (A) in the non-braking to light braking state, as shown in (B) in the braking state during forward movement, and as shown in (B) in the braking state during backward movement. As shown in Fig. The actions and effects in each state are as described above.

  It is also conceivable that the guide pins 7a and 7b are supported on the caliper 2a so that they can be displaced in any radial direction, and the guide pins 7a and 7b are pressed in opposite directions with respect to the radial direction. . However, such a structure is not preferable because the radial positions of the pads 5a and 5a become unstable and cause stepped wear on the rotor 11a.

DESCRIPTION OF SYMBOLS 1 Disc brake 2, 2a Caliper 3 Cylinder 4 Piston 5, 5a, 5b Pad 6, 6a Guide hole 7, 7a, 7b, 7c, 7d Guide pin 8, 8a Outer body part 9, 9a Inner body part 10, 10a Connecting part 11 , 11a Rotor 12 Bolt 13, 13a, 13b Pressure plate 14, 14a Lining 15 Holding recess 16 Anti-rattle spring 17, 17a, 17b Guide hole 18, 18a, 18b Leaf spring 20, 20a Return spring 21 Holding recess 22 Pad clip 23 Substrate Part 24 Side bent part 25 Inner diameter side bent part 26 Outer diameter side bent part 27 Projection part 28a, 28b Support hole 29a, 29b, 29c Elastic pressing part 30 Recessed part 31a, 31b Anchor convex part 32 Step part 33 Locking receiving part 34 Locking part 35, 35a Elastic deformation part 36 Arm part 37 Bending part 38 Small diameter part

JP 2008-208970 A JP 2009-68593 A JP 2002-174280 A JP 2003-148525 A

Claims (15)

  Outer and inner body parts provided across a rotor that rotates together with the wheels, and a pair of connections that connect both circumferential ends of both body parts at positions radially outward from the outer peripheral edge of the rotor. Calipers composed of parts, a plurality of cylinders provided opposite to each other on both body parts, and a plurality of pistons fitted in each of the cylinders in a liquid-tight manner and capable of displacement in the axial direction, Is composed of a pressure plate and a lining that is attached and fixed to a surface of the pressure plate that faces the rotor, and is held in a holding recess provided on the surfaces of the two body portions facing each other so as to be capable of axial displacement. Of the pressure plates constituting the pair of pads and the pressure plates, the outer circumferential portion of the rotor is radially outward and the circumferential direction A pair of guide holes provided at two positions for each of the pressure plates, and a pair of the guide holes provided in a state of passing through the guide holes in the axial direction and spanning between the body parts. In an opposed piston type disc brake having a plurality of guide pins, two positions separated in the circumferential direction of the two pads by engagement between the two guide pins and the respective guide holes are axially arranged with respect to the caliper. Of the first and second support portions that are supported to allow displacement, the first support portion near one end in the circumferential direction supports the pads with respect to the body portions in a state where radial displacement is prevented. Similarly, the second support portion near the other end in the circumferential direction supports the two pads in a state in which radial displacement is allowed with respect to the two body portions, and is supported on the second support portion by an elastic member. Diameter Wherein the both pads, opposed piston type disc brake, characterized in that have granted the direction of resilient swings about the first support portion by imparting elasticity facing to.   Of the two guide pins, one of the guide pins constituting the first support portion is supported with respect to the two body portions in a state where radial displacement is prevented, and the other constitutes the second support portion. The guide pins are supported with respect to the two body portions in a state in which displacement in the radial direction is allowed, and by applying elastic force directed in the radial direction to the other guide pins by an elastic member, The opposed piston type disc brake according to claim 1, wherein an elastic force is applied in a swinging direction about the one guide pin.   The one guide pin is located on the return side of the rotor in the forward movement state of the vehicle, and the other guide pin is also located on the turn-in side. The other guide pin is radially inward. The opposing piston-side disc brake according to claim 2, wherein a facing elasticity is applied.   The one guide pin is located on the return side of the rotor in a forwardly moving state of the vehicle, and the other guide pin is also located on the return side, and the other guide pin is radially outward. The opposing piston-side disc brake according to claim 2, wherein a facing elasticity is applied.   The one guide pin is positioned on the rotor entrance side in the forward traveling state of the vehicle, and the other guide pin is also located on the exit side, and the other guide pin is radially inward. The opposing piston-side disc brake according to claim 2, wherein a facing elasticity is applied.   The one guide pin is located on the rotor entrance side in the forward traveling state of the vehicle, and the other guide pin is also located on the exit side, and the other guide pin is radially outward. The opposing piston-side disc brake according to claim 2, wherein a facing elasticity is applied.   The two guide pins are supported with respect to the two body portions in a state in which radial displacement is prevented, and one guide pin is prevented from being displaced in the radial direction in the guide hole constituting the first support portion. And the other guide pin is inserted into the guide hole constituting the second support portion in a state allowing a radial displacement, and the elastic member is provided near the other end in the circumferential direction of the two pads. 2. The opposed piston type disc brake according to claim 1, wherein a resilient force in a swinging direction about the one guide pin is imparted to the two pads by imparting a resilient force directed in a radial direction to the two pads.   The one guide pin is located on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also located on the turn-in side. The opposed piston-side disc brake according to claim 7, wherein a resilient force directed radially inward is applied.   The one guide pin is located on the return side of the rotor in the forward traveling state of the vehicle, and the other guide pin is also located on the turn-in side. The opposed piston-side disc brake according to claim 7, wherein a resilient force directed radially outward is applied.   The one guide pin is located on the turning-in side of the rotor when the vehicle is moving forward, and the other guide pin is also located on the turning-out side. The opposed piston-side disc brake according to claim 7, wherein a resilient force directed radially inward is applied.   The one guide pin is located on the turning-in side of the rotor when the vehicle is moving forward, and the other guide pin is also located on the turning-out side. The opposed piston-side disc brake according to claim 7, wherein a resilient force directed radially outward is applied.   The elastic member is a leaf spring arranged in the circumferential direction, and the positions of two intermediate portions of the leaf spring are different from the radially inner side surface of the axially intermediate portion of any one of the guide pins. The opposed piston type disc brake according to any one of claims 2 to 6, which elastically abuts against a radially outer surface of an axially intermediate portion of the guide pin.   A state in which a pair of pad clips sandwiched between both circumferential end surfaces of the holding recess and both circumferential end surfaces of the pressure plate constituting the both pads is spanned between the outer and inner body portions. The leaf springs are axially secured by engaging both circumferential ends of the leaf springs with the engagement portions formed at the axially intermediate portions of the radial outer edges of the two pad clips. The opposed-piston disc brake according to claim 12, which prevents shifting.   The anchor convex part which engages with the level difference surface provided in the circumferential direction both ends of the both holding crevice respectively was provided in the diameter direction both ends of the circumferential direction both ends of the pressure plate which constitutes the both pads. The opposing piston type disc brake described in any one of 1 to 13.   The opposed piston type disc brake according to any one of claims 1 to 14, wherein a return spring is provided between the pads for pressing the pads in a direction to separate the pads from each other.

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