JP2006002855A - Floating caliper type disk brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To assure rigidity of a caliper 2a to realize low vibration and noise for easier assembling work, even if the caliper 2a is made from light weight material such as aluminum alloy, with no change in size of a wheel or rotor 1. <P>SOLUTION: The caliper 2a is supported with a support 3a for free displacement in the axial direction of the rotor 1. Engaging parts 8a on both entering side and leaving side constituting the support 3a are provided with guide holes penetrating in axial direction of the rotor 1. The intermediate parts of guide pins 5a and 5a whose both ends are supported/fixed by a cylinder part 12 and a claw part 13a of the caliper 2a are inserted for free sliding in the guide holes. An engagement part 20 formed at the portion protruding from the claw-side through hole formed at the claw part 13a to the outer side at the tips of the guide pins 5a and 5a engages with an engaging slot 26 formed at the claw part 13a, to prevent rotation of the guide pins 5a and 5a. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The floating caliper type disc brake according to the present invention is used for braking an automobile, and the present invention achieves light weight, low vibration and low noise without changing the size of the wheel and rotor, and the assembly work. It is intended to facilitate this.

  Conventionally, as a disc brake for braking an automobile, a floating caliper type in which a caliper is supported by a pair of guide pins so as to be displaceable with respect to a support has been widely used. Known and widely used in practice. 29 to 30 show a floating caliper type disc brake described in Patent Document 1 among such floating caliper type disc brakes. The floating caliper type disc brake displaces the caliper 2 with respect to the rotor 1 that rotates together with wheels (not shown) during braking. In the assembled state to the vehicle, the support 3 provided so as to be adjacent to one side of the rotor 1 is fixed to the vehicle body (not shown) through the mounting holes 4 and 4. Further, the caliper 2 is supported on the support 3 so that the axial displacement of the rotor 1 is possible.

  For this purpose, a pair of guide pins 5 and 5 are provided at both ends of the caliper 2 with respect to the rotational direction of the rotor 1, and a pair of guide holes 6 and 6 are provided at both ends of the support 3. It is provided parallel to the axis. Each of these guide holes 6, 6 has a bottomed shape with one end closed. The guide pins 5 and 5 are inserted into the guide holes 6 and 6 so as to be slidable in the axial direction.

  In addition, at both end portions of the support 3, both engaging and disengaging side engaging portions 8 and 9 are provided at positions separated in the circumferential direction of the rotor 1, respectively. Each of the engaging portions 8 and 9 has a U-shaped bent end so as to straddle the outer peripheral portion of the rotor 1 in the vertical direction of FIG. 29, and pads 10 a and 10 b are provided on both engaging portions 8 and 9. Both end portions of the pressure plates 11 and 11 constituting the rotor 1 are engaged with each other so that the rotor 1 can slide in the axial direction. The caliper 2 having a cylinder portion 12 and a claw portion 13 connected by a bridge portion 7 straddling the pads 10a and 10b is disposed. A pad 10a on the inner side (the lower side in FIG. 29 on the inner side in the width direction of the vehicle) is pressed against the rotor 1 in a cylinder hole 16 provided on the inner surface of the cylinder portion 12 so as to open toward the rotor 1. The piston 14 is fitted in a liquid-tight manner.

  When braking is performed, pressure oil is fed into the cylinder hole 16, and the lining 15 of the inner pad 10 a is pressed against the inner surface of the rotor 1 from the bottom of FIG. Then, as a reaction of this pressing force, the caliper 2 is displaced downward in FIG. 29 based on the sliding between the guide pins 5 and 5 and the guide holes 6 and 6, and the claw portion 13 is moved to the outer side. The lining 15 of the pad 10b on the side (the outer side in the width direction of the vehicle in FIG. 29) is pressed against the outer surface of the rotor 1. As a result, the rotor 1 is strongly clamped from both the inner and outer side surfaces, and braking is performed.

  In recent years, as one of means for reducing the weight of a disc brake, it has been considered that the caliper 2 is made of an aluminum alloy that is a lightweight material, and some of them are actually performed. However, when the caliper 2 is made of such a lightweight material with the conventional structure, the same dimensions as those of the caliper 2 of the conventional structure made by casting of an iron-based material are taken into consideration to ensure sufficient rigidity. It is difficult to make with. That is, in this case, it is necessary to ensure rigidity by increasing the thickness of the caliper 2 or the like. Further, in the case of the caliper 2 made of a light material, the rigidity reduction due to the temperature rise accompanying the friction between the rotor 1 and the pads 10a and 10b during braking is lower than in the case of the caliper 2 having a conventional structure made of iron-based material. Will also be remarkable. For this reason, when the caliper 2 is made of a light material as described above with a conventional structure, the diameter of the wheel constituting the wheel is increased or the diameter of the rotor 1 is decreased to increase the rigidity of the caliper 2. By ensuring this, problems due to reduced rigidity are prevented. However, when the diameter of the wheel is increased, the cost is increased. When the diameter of the rotor 1 is decreased, the heat capacity of the rotor 1 is decreased.

JP 55-123029 A JP-A-11-44331 Utility Model Registration No. 2596090

  In view of such circumstances, the floating caliper type disc brake of the present invention ensures sufficient caliper rigidity even when the caliper is made of a lightweight material without changing the size of the wheel or rotor. The invention was invented to realize low vibration and low noise and to facilitate the assembly work.

The floating caliper type disc brake of the present invention includes a support, a pair of pads, a caliper, a claw portion, and a piston, as in the above-described conventionally known floating caliper type disc brake.
The support is fixed to the vehicle body adjacent to the rotor that rotates with the wheels.
The pair of pads are supported by the support so as to be slidable in the axial direction on both sides of the rotor.
The caliper is supported so as to be displaceable in the axial direction of the rotor by a guide hole provided in the support and a guide pin fitted in the guide hole.
The claw portion of the claw portion and the piston is provided on one side of the bridge portion straddling the rotor of the caliper, and the piston is fitted on the other side of the bridge portion.
The base end portion of the guide pin is supported and fixed to the rotation direction end portion of the rotor of a cylinder portion provided on the piston side in a part of the caliper.
As the piston is pushed out, the pair of pads are pressed against both side surfaces of the rotor to perform braking.
In particular, in the floating caliper type disc brake of the present invention, the guide hole is formed as a through hole that opens on both the inner and outer sides, and an intermediate portion of the guide pin is slidably inserted into the guide hole. Yes. In addition, at the end of the claw portion in the rotation direction of the rotor, a portion closer to the tip of the guide pin is formed in a pair of claw portion side through holes formed in a portion protruding to one side in the rotation direction from the bridge portion. An anti-rotation means is provided between the leading end portion of the guide pin and the claw portion.

  In the case of the floating caliper type disc brake of the present invention configured as described above, since the guide pin can be supported and fixed to the claw portion and the cylinder portion in a both-end supported state, the rigidity of the caliper including the claw portion and the cylinder portion is increased. improves. That is, the guide pin serves as a reinforcing member for the caliper, and even when the caliper tends to be deformed due to an increase in hydraulic pressure of the pressure oil introduced into the cylinder hole, the caliper can be hardly deformed. For example, at the time of braking, this increase in hydraulic pressure tends to cause the claw portion and the cylinder portion to be deformed so as to open, but according to the present invention, this deformation can be reduced. Therefore, even when a caliper is made of a light material such as an aluminum alloy without changing the size of the wheel or rotor, the caliper can have sufficient rigidity and vibration and noise can be kept low. Further, in order to ensure the rigidity of the caliper, it is not necessary to cast another reinforcing member made of a high-strength material integrally with the caliper. In particular, when the caliper is made of an aluminum alloy, the caliper is easily deformed due to a temperature rise, and thus the effect of improving the caliper rigidity by adopting the configuration of the present invention becomes remarkable. Further, it is possible to suppress uneven wear of each pad.

  Further, since the guide pin cannot be rotated by the rotation preventing means provided between the distal end portion of the guide pin and the claw portion, the base end portion of the guide pin is coupled and fixed to the cylinder portion with a nut or the like. Work can be done easily. Further, it is not necessary to perform this operation while using a tool for preventing the rotation of the guide pin for preventing the rotation of the guide pin. Further, when a locking portion that protrudes only in one radial direction from the flange portion provided at the intermediate portion is provided at the distal end portion of the guide pin, and the rotation preventing means is configured by this locking portion, the tip portion Compared with the case where the head portion of the bolt having a hexagonal cross section is provided, the portion constituting the detent means can be made smaller. For this reason, it can suppress that the part which comprises this rotation prevention means protrudes outside from the outer surface of the main-body part of the said nail | claw part. Further, simply providing the head of the bolt is incomplete as a detent for fastening a nut or the like to the base end, and a tool for preventing the rotation may be required. On the other hand, when the anti-rotation means is constituted by the locking portion, it is effective because such inconvenience can be prevented. Furthermore, when the portion constituting the rotation preventing means is made by upsetting a part of the guide pin, the upsetting ratio can be reduced and the yield can be improved. Further, since the rotation of the guide pin can be prevented, the degree of freedom in setting a clearance (pin clearance) between the outer peripheral surface of the intermediate portion of the guide pin and the inner peripheral surface of the guide hole can be improved.

  In the case of the present invention, the guide hole is a through hole that opens on both the inner and outer sides, and an intermediate portion of the guide pin is inserted into the guide hole. For this reason, even when the lining constituting the pad is worn, the fitting length between the guide hole and the guide pin does not change. Therefore, the caliper posture can be hardly changed regardless of the wear of the lining. In addition, when the gap in the radial direction of the rotor between the outer peripheral surface of the intermediate portion of the guide pin and the outer peripheral surface of the guide hole is increased, a virtual plane perpendicular to the rotational center of the rotor due to temperature rise during braking, etc. When it deform | transforms so that it may incline, it can make it easy to maintain the freedom degree in the intermediate part of the said guide pin. For this reason, the inner side surface of the claw portion and the tip end surface of the piston can be easily made parallel to both side surfaces of the rotor. As a result, the lining of the pair of pads is pressed almost uniformly from the inner peripheral edge to the outer peripheral edge with respect to both side surfaces of the rotor. It is possible to prevent uneven wear in the radial direction of the rotor. Also, in this case, the outer peripheral surface of the guide pin that is bent and deformed in an arc shape inside the guide hole can be brought into contact with the inner peripheral surface of the guide hole. Unlike the case of the conventional structure in which the front end edge easily comes into contact with the inner peripheral surface of the guide hole, the twisting at the contact portion can be suppressed, and the guide pin can be easily slid easily in the guide hole.

  Further, since the guide hole is a through hole, it is easy to perform a machining operation for finishing the inner peripheral surface of the guide hole with high accuracy. Moreover, it becomes easy to discharge | emit the chip generated at the time of processing of this guide hole, and the improvement of work efficiency can be aimed at.

  When carrying out the present invention, preferably, as described in claim 2, the rotation preventing means is configured such that the distal end portion of the guide pin is parallel to each other provided in the opening on the side opposite to the rotor of the claw portion side through hole. It shall be comprised by engaging with at least any one side wall surface of a pair of side wall surfaces.

More preferably, as described in claim 3, the guide pin is arranged in order of the claw part side through hole, the guide hole provided in the support, and the cylinder side through hole provided in the other side of the bridge part. It is assumed that a fastening means is coupled to a base end portion that is inserted through and protrudes from the cylinder side through hole to the other outer side.
According to this preferable configuration, the base end portion of the guide pin can be prevented from coming out of the cylinder side through hole with an inexpensive structure, and the guide pin can be prevented from rattling, and the caliper rigidity can be sufficiently increased even when the temperature rises. It can be secured.

More preferably, as described in claim 4, the gap between the outer peripheral surface of the portion inserted through the guide hole at the intermediate portion of the guide pin and the inner peripheral surface of the guide hole is The dimension in the radial direction is made different between a direction related to one direction parallel to both side surfaces of the rotor and a direction related to a direction parallel to both side surfaces of the rotor and perpendicular to the one direction.
According to this more preferable configuration, the size of the gap between the guide pin and the guide hole can be arbitrarily set by the designer in two directions orthogonal to each other.

  More preferably, as described in claim 5, the dimension of the gap between the outer peripheral surface of the portion inserted into the guide hole at the intermediate portion of the guide pin and the inner peripheral surface of the guide hole is determined by the rotor. The rotation direction of the rotor and the radial direction of the rotor are different from each other.

Further, in this case, as in the configuration described in claim 6, the dimension of the gap between the outer peripheral surface of the portion inserted through the guide hole at the intermediate portion of the guide pin and the inner peripheral surface of the guide hole. Of these, the dimension in the radial direction of the rotor is made larger than the dimension in the rotational direction of the rotor.
In this way, even when the rotor falls in the axial direction due to a temperature rise accompanying braking, etc., the inner surface of the claw portion and the tip surface of the piston can easily follow the both side surfaces of the rotor. In addition, since the size of the clearance between the outer peripheral surface of the intermediate portion of the guide pin and the inner peripheral surface of the guide hole can be reduced, the guide pin moves in the rotational direction inside the guide hole. The caliper shakiness can be suppressed, and the generation of vibration and noise can be suppressed low.

More preferably, as described in claim 7, of the pair of pads provided on both sides of the rotor, the width of the lining constituting the outer side pad in the rotational direction of the rotor is set to the inner side pad. It is made larger than the width | variety regarding this rotation direction of lining which comprises.
According to this more preferable structure, the claw which opposes the both ends of the said outer side pressure plate by making the width | variety of the said rotation direction of the pad of an outer side larger than the width | variety of this rotation direction of the inner side pad. It is possible to suppress the bending deformation of both ends of the claw portion toward the inner side even when the hydraulic pressure of the pressure oil introduced into the cylinder hole during braking increases. As a result, the caliper rigidity is further improved, and the bending deformation of each guide pin in which the respective tip portions are supported and fixed at both end portions of the claw portion can be suppressed to be small.

  Furthermore, since the contact area between the lining constituting the outer pad and the rotor is increased, the contact pressure at the contact portion can be reduced, and uneven wear of the lining can be prevented. Moreover, the lining constituting the inner side pad cannot be made much larger than the portion facing the front end surface of the piston from the surface that makes the contact surface pressure non-uniformity with the rotor less likely to occur. The pad has few such restrictions. For this reason, if a configuration in which the width of the lining constituting the outer side pad is made larger than the width of the lining constituting the inner side pad, the contact surface pressure between the rotor and each pad is improved. In addition, the rigidity of the claw portion can be improved.

More preferably, as described in claim 8, in the configuration described in claim 7, the thickness of the lining constituting the outer side pad is set to the thickness of the lining constituting the inner side pad. By making it smaller than the thickness, the lining volumes of the outer side pad and the inner side pad are made the same.
According to this more preferable configuration, the outer side and inner side pads have substantially the same life until replacement (replacement life), and the outer side pad thickness is reduced while ensuring a sufficient braking force. It is possible to easily reduce the caliper dimensions in the axial direction of the rotor. Further, by reducing the thickness of the lining constituting the outer side pad, the distance between the inner surfaces of the claw portion and the cylinder portion (milling width) can be reduced, and the caliper rigidity can be further increased. I can do things.

  FIGS. 1-14 has shown Example 1 of this invention corresponding to Claims 1-3. The floating caliper disc brake of the present embodiment includes a support 3a, a pair of pads 10a and 10b, a caliper 2a, a claw portion 13a, and a piston 14. The support 3a is fixed to the vehicle body adjacent to the rotor 1 that rotates with the wheels. The two pads 10a and 10b are disposed on both sides of the rotor 1 while being supported by the support 3a. A portion for supporting the support 3a on the vehicle body, a portion for supporting the pads 10a and 10b on the support 3a, and the claw portion 13a and the piston 14 connect the pads 10a and 10b to the rotor 1. The structure and operation of the portion that presses on both side surfaces are the same as those of the disk brakes that have been widely known in the past, including the structure shown in FIGS. Further, the same parts as those in the conventional structure shown in FIGS. 28 to 29 described above are denoted by the same reference numerals, and redundant description is omitted or simplified.

  The caliper 2a is made by casting an aluminum alloy. The axial direction of the rotor 1 with respect to the support 3a (the left-right direction in FIGS. 1-4, the up-down direction in FIG. 5, the front-back direction in FIGS. 6, 7). It supports the displacement of. For this purpose, guide holes opened on both sides of the inner and outer sides inside the turn-in side engaging portion 8a and the turn-out side engaging portion 9a provided at both ends in the circumferential direction of the rotor 1 of the support 3a. 6a and 6a are formed so as to penetrate the rotor 1 in the axial direction. In the case of the illustrated example, the rotor 1 rotates in the direction indicated by the arrow A in FIG.

  Further, at the tip of a pair of inner side arm portions 17, 17 formed in a state where the cylinder portion 12 provided at a part (inner side end portion) of the caliper 2 a protrudes to both ends in the circumferential direction of the rotor 1. The base ends of the guide pins 5a and 5a are supported and fixed, respectively. Further, the claw portion 13a of a part (outer side end portion) of the caliper 2a is formed in a state protruding from both ends of the rotor 1 in the circumferential direction. The tip portions of the guide pins 5a and 5a are supported and fixed. For this purpose, the guide pins 5a and 5a are configured as shown in detail in FIGS.

  That is, each of these guide pins 5a includes a flange portion 19 and a locking portion 20 that is integrally fixed to the tip of the flange portion 19 (the left end in FIGS. 10 to 11). The front half portion (the lower half portion of FIGS. 10 to 12) of the locking portion 20 protrudes on one side in the radial direction of the flange portion 19. Moreover, this latching | locking part 20 makes the shape seen in the axial direction of this collar part 19 the ellipse as shown in FIG. That is, a pair of plane portions 21 and 21 parallel to each other are provided at two positions on the outer circumferential surface of the locking portion 20 on the opposite side in the circumferential direction. And the outer peripheral surface of this latching | locking part 20 is comprised by connecting one end edge (lower end edge of FIGS. 10-12) of these pair of plane parts 21 and 21 by the curved-surface part 22 of cross-sectional arc shape. Yes. In addition, one half portion (the upper half portion in FIGS. 10 to 12) of the front end surface (the left end surface in FIGS. 10 and 11 and the front end surface in FIG. 12) of the locking portion 20 is a curved surface portion 23 having an arcuate cross section. Similarly, the other half (the lower half of FIGS. 10 to 12) is a flat surface. Moreover, the external thread part 24 is formed in the outer peripheral surface of the base end part (right end part of FIGS. 10-11) of the said collar part 19. As shown in FIG.

  On the other hand, a claw portion side through hole 25 is formed in each outer side arm portion 18, 18 so as to penetrate in the axial direction of the rotor 1, and the outer side surface of each outer side arm portion 18, 18 (FIGS. 4 is formed on the peripheral edge of the opening of each claw portion side through hole 25 on the left side surface of the claw portion 25, and the locking grooves 26 and 26 for locking the locking portions 20 and 20 of the guide pins 5a and 5a are formed. . That is, each of the locking grooves 26 and 26 is formed in a direction substantially coincident with the radial direction of the rotor 1 in the present embodiment. As shown in detail in FIGS. A bottom surface portion 27 extending longer to the inner diameter side of the rotor 1 (FIG. 1) than each claw portion side through hole 25 and a pair of side wall surfaces 28 and 28 parallel to each other are provided. Of these, the bottom surface portion 27 is located on a virtual plane orthogonal to the rotation center of the rotor 1. Further, the interval between the both side wall surfaces 28, 28 is slightly larger than the interval between the pair of flat surface portions 21, 21 constituting the outer peripheral surface of the locking portion 20 of each guide pin 5a. The inner side surface (the right side surface in FIG. 10) of the locking portion 20 is allowed to abut on the bottom surface portion 27 of the locking groove 26.

  And the intermediate part of the collar part 19 which comprises each said guide pin 5a, 5a is slidably inserted in each guide hole 6a formed in the said support 3a, and the front-end | tip part of these each collar part 19 is said each said The claw portion side through hole 25 is inserted. Further, the respective locking portions 20, 20 are made to enter inside the respective locking grooves 26, 26, and the inner side surfaces of the respective locking portions 20, 20 are set to the bottom surface portions 27 of the respective locking grooves 26, 26. It has hit against. Of the flat portions 21, 21 constituting the outer peripheral surface of each locking portion 20, one flat surface portion 21 is replaced with one of the side wall surfaces 28, 28 of each locking groove 26, 26. 28 is engaged. In FIG. 8, the plane portions 21 and 21 and the side wall surfaces 28 and 28 are shown as being separated from each other. However, in the actual assembled state, the plane portions 21 and 21 and the side wall surfaces are separated. At least one of the opposing surfaces of 28 and 28 is engaged (contacted). Further, in this state, each of the locking portions 20 does not protrude from the outer surface of the main body portion of the outer side arm portion 18 constituting the claw portion 13a (the end surfaces of the locking portions 20 and 20 are the outer surfaces). It is made to substantially follow the outer surface of the main body of the side arms 18 and 18). In the case of the present embodiment, the locking portions 20 and 20 and the locking grooves 26 and 26 constitute rotation preventing means for preventing the rotation of the guide pins 5a and 5a.

On the other hand, cylinder-side through holes 29 are formed in the distal end portions of the inner-side arm portions 17 and 17 so as to penetrate in the axial direction of the rotor 1. The male screw portions 24 formed at the base end portions of the guide pins 5a and 5a are inserted into the cylinder side through holes 29, and the male screw portions 24 protrude from the cylinder side through holes 29. The nut 30 is screwed and further tightened. With this configuration, the guide pins 5a and 5a are supported and fixed at the both end portions of the inner side arm portions 17 and 17 and the outer side arm portions 18 and 18, respectively. In this embodiment, the cylinder hole 16 and the central axis o _{2 of the} piston 14 (see FIG. 2) are arranged on a virtual plane including both the central axes o ₁ (FIGS. 2 and 6) of the guide pins 5a and 5a. 3, 6, 7). Also, the vertical positions of these central axes o ₁ and o ₂ when viewed in the same direction as those in FIGS. ₂ , ₃ , 6, and 7 are made to coincide.

  The guide pins 5a and 5a are supported and fixed to the inner side and outer side arm portions 17 and 18 as follows. First, the guide pins 5a and 5a are inserted through the claw portion side through holes 25, the guide holes 6a, and the cylinder side through holes 29 in this order from the base end side where the male screw portion 24 is formed. Let Next, a nut 30 is screwed into a portion protruding from each cylinder-side through hole 29 with the male screw portion 24 formed at the base end portion, and further tightened. As a result, the inner side surface of each locking portion 20 that has entered each locking groove 26 is strongly pressed against the bottom surface portion 27 of each locking groove 26, and the inner end surface of the nut 30 is the inner side arm. It is strongly pressed against the side surfaces of the parts 17 and 17. Further, the planar portions 21 of the respective locking portions 20 and the side wall surfaces 28 of the respective locking grooves 26 engage with each other, so that the rotation of the respective guide pins 5a and 5a within the respective guide holes 6a is prevented. The In this state, the outer peripheral surfaces of the intermediate portions of the guide pins 5a and 5a and the inner peripheral surfaces of the guide holes 6a are slidably engaged in the axial direction.

  In this embodiment, since the guide pins 5a and 5a are inserted into the guide holes 6a in this way, the caliper 2a is inserted into the support 3a in the axial direction of the rotor 1 (FIGS. 4 in the left-right direction).

  In the case of the floating caliper type disc brake of the present invention configured as described above, since the pair of guide pins 5a and 5a can be supported and fixed to the claw portion 13a and the cylinder portion 12 in a state where both ends are supported, the vibration resistance of the caliper 2a. Since the nut 30 is fastened, the rigidity of the caliper 2a including the claw portion 13a and the cylinder portion 12 is improved. That is, these guide pins 5a and 5a serve as a reinforcing member for the caliper 2a, and even when the caliper 2a tends to be deformed due to an increase in hydraulic pressure of the pressure oil introduced into the cylinder hole 16, The caliper 2a can be hardly deformed. For example, at the time of braking, the increase in hydraulic pressure tends to cause the claw portion 13a and the cylinder portion 12 to be deformed so that the deformation can be reduced according to the present invention. For this reason, even when the caliper 2a is made of a light material such as an aluminum alloy without changing the size of the wheel or the rotor 1, the caliper 2a can have sufficient rigidity, and vibration and noise can be kept low. it can. Further, in order to ensure the rigidity of the caliper 2a, it is not necessary to cast another reinforcing member made of a high strength material integrally with the caliper 2a. In particular, when the caliper 2a is made of an aluminum alloy as in the present embodiment, the caliper 2a is easily deformed due to a temperature rise, so that the effect of improving the rigidity of the caliper 2a by adopting the configuration of the present invention is obtained. Become prominent. Further, it is possible to suppress uneven wear of the pads 10a and 10b. In order to obtain such an effect, the locking portions 20 and 20 provided at the distal ends of the guide pins 5a and 5a have a strength that can sufficiently withstand the axial force applied as the hydraulic pressure increases. And

  Further, in the case of the present invention, the detent formed by the engaging portion 20 projecting outward from the claw portion 13a at the tip portion of each of the guide pins 5a and 5a and the locking groove 26 provided in the claw portion 13a. Since the guide pins 5a and 5a cannot be rotated by the means, the base end portions of the guide pins 5a and 5a can be easily fixed to the cylinder portion 12 by the nut 30. Further, it is not necessary to perform this operation while using a follow-up prevention tool for preventing the rotation of the guide pins 5a and 5a. Furthermore, in the case of the present embodiment, a locking portion 20 protruding only on one side in the circumferential direction from the coupling portion with the flange portion 19 is provided at the tip of each guide pin 5a, 5a. Since the anti-rotation means is constituted by 20, the portion constituting the anti-rotation means can be made smaller by providing a head of a hexagonal cross-section bolt at the tip portion as compared with the case of constituting the anti-rotation means. . For this reason, it can suppress that the part which comprises this rotation prevention means protrudes outside from the outer surface of the main-body part of the outer side arm parts 18 and 18 which comprise the said nail | claw part 13a. Further, simply providing the head of the bolt is incomplete as a detent for fastening a nut or the like to the base end, and a tool for preventing the rotation may be required. On the other hand, in the case of the present embodiment in which the anti-rotation means is constituted by the locking portion 20, such an inconvenience can be prevented, which is effective. Further, when the portion constituting the rotation preventing means is manufactured by upsetting a part of each of the guide pins 5a and 5a, the upsetting ratio can be reduced and the yield can be improved. Further, since the rotation of the guide pins 5a and 5a can be prevented, the clearance (pin clearance) between the outer peripheral surface of the intermediate portion of the guide pins 5a and 5a and the inner peripheral surface of the guide holes 6a can be freely set. The degree of improvement can be achieved.

  In the case of the present invention, each guide hole 6a is a through-hole that opens on both the inner and outer sides, and intermediate portions of the guide pins 5a and 5a are inserted into the guide holes 6a. For this reason, even when the linings 15 and 15 constituting the pads 10a and 10b are worn, the fitting length between the guide holes 6a and the guide pins 5a and 5a does not change. Therefore, regardless of the wear of the linings 15 and 15, the posture of the caliper 2a can be hardly changed.

Further, when the gap in the radial direction of the rotor 1 between the outer peripheral surface of the intermediate portion of each guide pin 5a, 5a and the outer peripheral surface of each guide hole 6a is increased, the rotor 1 is As shown in FIG. 13, when it is deformed so as to be inclined with respect to a virtual plane perpendicular to the rotation center of the rotor 1, it is possible to easily maintain the degree of freedom at the intermediate portion of each guide pin 5a, 5a. . For this reason, the inner surface of the claw portion 13 a and the tip surface of the piston 14 can be easily made parallel to the both side surfaces of the rotor 1. For example, with the inclination of both side surfaces, the central axis of the piston 14 can be inclined with respect to the rotation center from the position indicated by o ₂ to the position indicated by o ₂ ′ in FIG. As a result, the linings 15 and 15 of the pair of pads 10a and 10b are pressed almost uniformly from the inner peripheral edge to the outer peripheral edge with respect to both side surfaces of the rotor 1, and this is caused by the displacement of the rotor 1 itself in the inclination direction. Thus, the pads 10a and 10b and the rotor 1 can be prevented from being unevenly worn in the radial direction of the rotor 1. In this case, as shown in FIG. 14, the outer peripheral surface of the intermediate portion of each guide pin 5a bent and deformed in an arc shape inside each guide hole 6a is used as the inner peripheral surface of the guide hole 6a. Since the contact can be made, the twisting at the contact portion can be suppressed. On the other hand, in the case of the conventional structure shown in FIGS. 28 to 29, the guide pins 5 are inserted into the bottomed cylindrical guide holes 6, so that the rotor 1 is inclined as described above. When the caliper 2 is inclined with respect to a virtual plane orthogonal to the rotation center of the rotor 1, the tip edge of the guide pin 5 is likely to come into contact with the inner peripheral surface of the guide hole 6 as shown in FIG. . In the case of such a conventional structure, it becomes easy to produce a twist between this front-end edge and this internal peripheral surface. In the case of the present invention, in order to eliminate such inconvenience, the guide pins 5a and 5a can be easily slid well in the guide holes 6a.

  Further, since each guide hole 6a is a through hole, it is easy to perform a machining operation to finish the inner peripheral surface of each guide hole 6a with high accuracy. Further, it becomes easy to discharge chips generated during the processing of the guide holes 6a, and the work efficiency can be improved.

In this embodiment, the cylinder hole 16 and the central axis o _{2 of the} piston 14 (see FIG. 2) are arranged on a virtual plane including both the central axes o ₁ (FIGS. 2 and 6) of the guide pins 5a and 5a. 3, 6, 7). Therefore, the guide pins 5a and 5a can be positioned on the outer diameter side with respect to the radial direction of the rotor 1, and the length of the outer side arm portions 18 and 18 reinforced by the guide pins 5a and 5a can be increased. Can be shorter. For this reason, it is possible to easily increase the rigidity of the caliper 2a.

  Further, in the case of the present embodiment, the guide pins 5a and 5a are inserted through the claw portion side through hole 25, the guide hole 6a provided in the support 3a, and the cylinder side through hole 29 in this order. It is assumed that a nut 30 is coupled to a base end portion protruding from the side through hole 29 to the outside of the cylinder portion 12. For this reason, it is possible to prevent the base end portions of the guide pins 5a and 5a from coming out of the cylinder side through holes 29 and to prevent the guide pins 5a and 5a from rattling with an inexpensive structure. In addition, this invention is not limited to the structure which couple | bonds the nut 30 with the base end part of each guide pin 5a, 5a in this way. However, even when a member other than the nut 30 is used and the base end portion is supported and fixed to the cylinder portion 12, the shape has a strength that can sufficiently withstand the axial force applied to the guide pins 5a and 5a. And a structure.

Next, FIG. 16 shows Embodiment 2 of the present invention corresponding to claims 1 to 4. In the case of the present embodiment, the cross-sectional shape of the outer peripheral surface of the portion inserted into each guide hole 6a at the intermediate portion of the flange portion 19a constituting each guide pin 5a is an ellipse. On the other hand, the inner peripheral surface of each guide hole 6a is a simple cylindrical surface. Then, both end portions of each guide pin 5a are supported and fixed to the claw portion 13a and the cylinder portion 12 (see FIG. 1 and the like) constituting the caliper 2a in a state where the rotation of each guide pin 5a is prevented. . Also, in this state, the minor axis direction of the ellipse on the outer peripheral surface is set to one direction parallel to both side surfaces of the rotor 1 (see FIG. 1 and the like) at the intermediate part of the flange part 19a of each guide pin 5a. The direction is parallel to both side surfaces of the rotor 1 and is orthogonal to this one direction. More specifically, in the case of the present embodiment, the one direction (the minor axis direction of the ellipse of the outer peripheral surface of the flange portion 19a) is orthogonal to the virtual plane including both the central axes of the pair of guide pins 5a. Direction. For this reason, the major axis direction of the ellipse on the outer peripheral surface of the flange portion 19a is a direction orthogonal to both directions of these central axes. With this configuration, the radial direction of each guide pin 5a in the gap between the outer peripheral surface of the portion inserted into each guide hole 6a at the intermediate portion of each guide pin 5a and the inner peripheral surface of each guide hole 6a. The dimension D ₁ (= d ₁ + d ₂ ) in one direction parallel to both side surfaces of the rotor 1 is the dimension D ₂ (in the direction perpendicular to the one direction parallel to both side surfaces of the rotor 1. = D ₃ + d ₄ ) (D ₁ > D ₂ ). In the case of this embodiment configured as described above, the size of the gap between the guide pin 5a and the guide hole 6a can be arbitrarily set by the designer in two directions orthogonal to each other.
Since other configurations and operations are the same as those in the first embodiment described above, the same parts are denoted by the same reference numerals, and overlapping illustrations and descriptions are omitted.

Next, FIG. 17 shows Embodiment 3 of the present invention corresponding to claims 1 to 6. In the case of the present embodiment, in the structure of the second embodiment shown in FIG. 16 described above, the rotor 1 (FIG. 1 etc.) Similarly, the minor axis direction coincides with the rotational direction of the rotor 1 (the direction indicated by the arrow B in FIG. 17), and the radial direction of the rotor 1 (the direction indicated by the arrow B in FIG. 17). With this configuration, the diameter of each guide pin 5a in the gap between the outer peripheral surface of the portion inserted into each guide hole 6a at the intermediate portion of each guide pin 5a and the inner peripheral surface of each guide hole 6a. Of the dimensions in the direction, the dimension D ₃ (= d ₅ + d ₆ ) related to the radial direction of the rotor 1 is larger than the dimension D ₄ (= d ₇ + d ₈ ) related to the rotational direction of the rotor 1 (D ₃ > D ₄ ).

  In the case of the present embodiment configured as described above, even when the rotor 1 falls down in the axial direction due to a temperature rise accompanying braking, etc., the inner surface of the claw portion 13a and the piston 14 (see FIG. 3 etc.) The front end surface can easily follow both side surfaces of the rotor 1. In addition, the size of the gap in the rotational direction of the rotor 1 between the outer peripheral surface of the intermediate portion of each guide pin 5a and the inner peripheral surface of each guide hole 6a can be reduced. For this reason, rattling of the caliper 2a due to the movement of each guide pin 5a in the rotation direction inside each guide hole 6a can be suppressed, and the generation of vibration and noise can be suppressed low.

Next, FIG. 18 shows Embodiment 4 of the present invention, which also corresponds to claims 1-6. In the case of the present embodiment, a pair of planes parallel to each other at two positions on the radially outer side of the outer peripheral surface of the portion inserted into each guide hole 6a at the intermediate portion of the flange portion 19b constituting each guide pin 5a. Portions 31 and 31 are provided. And by this structure, the dimension regarding the radial direction (direction shown by arrow B in FIG. 18) of the rotor 1 among the dimension of the clearance gap between the outer peripheral surface of each said guide pin 5a, and the inner peripheral surface of each guide hole 6a. D ₃ ′ (= d ₅ ′ + d ₆ ′) is made larger than the dimension D ₄ ′ (= d ₇ ′ + d ₈ ′) with respect to the rotation direction of the rotor 1 (the direction indicated by the arrow A in FIG. 18). _{(D 3 '> D 4'} ).
Since other configurations and operations are the same as those of the third embodiment shown in FIG. 17 described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.

  Next, FIGS. 19 to 23 show a fifth embodiment of the present invention corresponding to claims 1 to 3, 7 and 8. In the case of this embodiment, the thickness of the pair of outer side arm portions 18a provided at both ends of the claw portion 13b in the rotational direction is increased on the inner side (upper side in FIG. 19), and the outer portion of the bridge portion 7 (see FIG. 19 is connected to both sides of the rotation direction of the rotor 1 (the left-right direction in FIG. 19) at the lower end portion of the outer side arm portion 18a. And the front-end | tip part of the guide pins 5a and 5a is inserted in the nail | claw part side through-hole 25 formed in these each outer side arm part 18a, and these each front end part is supported and fixed to these each outer side arm part 18a. With this configuration, the rigidity of the claw portion 13b can be further increased.

In the case of this embodiment, of the pair of pads 10 a and 10 b provided on both sides of the rotor 1, the width W ₁ of the lining 15 b constituting the outer pad 10 b in the rotational direction of the rotor 1 is set as the inner width. lining 15a constituting the side pads 10a, it is larger than the width W ₂ on this direction of rotation (W _1> W _2). Further, by making the thickness T ₁ of the lining 15b constituting the outer side pad 10b smaller than the thickness T ₂ of the lining 15a constituting the inner side pad 10a (T ₁ <T ₂ ), The volumes of the linings 15b and 15a of the outer side and inner side pads 10b and 10a are the same.

In the case of the present embodiment configured as described above, the width W ₁ of the lining 15b constituting the outer side pad 10b with respect to the rotational direction of the rotor 1 is set to the rotational direction of the lining 15a constituting the inner side pad 10a. Is larger than the width W ₂ (W ₁ > W ₂ ). For this reason, the rigidity of the claw portion 13b facing both ends of the pressure plate 11b constituting the outer side pad 10b is increased, and each outer side arm is also increased by the increase in the hydraulic pressure of the pressure oil introduced into the cylinder hole 16 during braking. It is possible to suppress the bending of the portion 18a toward the inner side to a small extent.

In other words, in the case of the present invention, as the hydraulic pressure of the pressure oil increases during braking, the claw portion 13b and the cylinder portion 12 tend to be deformed so as to open around the bridge portion 7. And the base end part of each guide pin 5a, 5a is pulled to the inner side by each inner side arm part 17, 17 of the cylinder part 12, and each outer side arm part 18a is inner via these each guide pin 5a, 5a. It tends to deform to the side. In this case, the fulcrum for bending deformation of each of the outer side arm portions 18a is in the vicinity of both end edges of the outer side pad 10b in the rotational direction of the rotor 1, as shown in FIG. For this reason, if the distance L ₁ from the both edges in the rotational direction of the pad 10b to the edge in the width direction of each outer arm portion 18a is short, the inner side (the lower side in FIG. 23) of each outer arm portion 18a. The amount of deformation can be reduced. Accordingly, as exaggeratedly shown in the figure, the angle θ ₁ at which each guide pin 5a having the distal end portion fixed to each outer side arm portion 18a is inclined at the intermediate portion can be kept small. Conversely, as shown in FIG. 24, the distance L ₂ from the rotational direction opposite edges of the pad 10b until the widthwise end edges of the respective outer side arm portion 18a is long, the inner of the outer side arm portion 18a The amount of deformation to the side (the lower side in FIG. 24) increases. For this reason, as exaggeratedly shown in the figure, the angle θ ₂ at which each guide pin 5a is inclined at the intermediate portion with the respective distal end portions fixed to the respective outer arm portions 18a is increased. On the other hand, in the case of the present embodiment, since the width W ₁ is larger than the width W _2, each outer side arm portion 18a is bent and deformed to the inner side even when the hydraulic oil pressure increases. Can be kept small. As a result, the caliper 2a can be further improved in rigidity, and the bending deformation of the guide pins 5a and 5a in which the respective distal end portions are supported and fixed to the outer side arm portion 18a can be suppressed to be small.

Further, since the contact area between the lining 15b constituting the outer side pad 10b and the rotor 1 is increased, the contact pressure at the contact portion can be reduced, and uneven wear of the lining 15b can be hardly caused. Moreover, the lining 15b that constitutes the inner pad 10a cannot be made much larger than the portion facing the tip end surface of the piston 14 from the surface that makes it difficult to cause nonuniform contact surface pressure with the rotor 1. The outer side pad 10b has few such restrictions. Therefore, according to this embodiment, the width W ₁ of the lining 15b constituting the outer side pad 10b is larger than the width W _{2 of the} lining 15a constituting the inner side pad 10a. The rigidity of the claw portion 13b can be improved while improving the contact surface pressure with 10a and 10b.

In the case of this embodiment, the thickness T ₁ of the lining 15b constituting the outer side pad 10b is made smaller than the thickness T ₂ of the lining 15a constituting the inner side pad 10a. The volumes of the linings 15b and 15a of the side and inner pads 10b and 10a are the same. For this reason, the life until replacement (replacement life) between both the outer side pad 10a and the inner side pad 10a can be made substantially the same, and the thickness T ₁ of the outer side pad 10b can be reduced while ensuring a sufficient braking force. The size of the caliper 2a in the axial direction of the rotor 1 can be easily reduced. Also, by reducing the thickness T ₁ of the lining 10b constituting the outer side of the pad 10b, can be reduced spacing (milling width) of the inner surfaces of the claw portion 13b and the cylinder portion 12, the caliper The rigidity of 2a can be further increased.
Since other configurations and operations are the same as those in the first embodiment shown in FIGS. 1 to 14 described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.

  In the case of adopting a so-called 1-POT structure in which one piston 14 is provided in the inner cylinder portion 12 as in the above-described embodiments, the linings 15 and 15a of the inner pad 10a are used. The width of the linings 15 and 15a in the rotation direction of the rotor 1 cannot be increased so much that the contact pressure between the rotor and the rotor 1 is less likely to be uneven. On the other hand, when a structure such as 2-POT, for example, in which two or more pistons 14 are provided in the cylinder portion 12, a contact surface acting between the linings 15 and 15a and the rotor 1 is used. It is possible to increase the width of the inner side linings 15 and 15a while improving the pressure. In this case, unlike the case of the present embodiment, it is easy to increase the width of both the linings 15a and 15b while keeping the widths of the linings 15a and 15b constituting the pads 10a and 10b on both sides of the inner and outer sides the same. it can. In any case, by bringing the contact pressure between the linings 15a and 15b constituting the pads 10a and 10b and the rotor 1 closer to each other more uniformly, it is possible to provide a disc brake that can obtain excellent effects in terms of vibration and noise.

Next, FIGS. 25 to 28 show a sixth embodiment of the present invention corresponding to claims 1 to 3. In the case of each of the above-described embodiments, the pair of flat portions 21 (see FIGS. 8 and 10 to 12) extending over the entire length in the axial direction provided on the locking portion 20 (see FIG. 1 and the like) of each guide pin 5 a, The rotation prevention means for preventing the rotation of each guide pin 5a in each guide hole 6a (see FIG. 2 etc.) is configured. On the other hand, in the case of the present embodiment, only the part in the axial direction of the locking portion 32 of each guide pin 5b constitutes the above-mentioned rotation preventing means. That is, in the case of the present embodiment, the locking portion 32 of each guide pin 5b has a disk shape as a whole, and the outer peripheral surface of the base end portion (the right end portion in FIG. 25, the upper end portion in FIG. 28). A pair of plane portions 33, 33 parallel to each other are provided at two positions opposite to each other in the radial direction. The distance d 33 between the flat portions 33 and ₃₃ is substantially the same as the diameter D _{19 of the} flange portion 19.

On the other hand, in the outer side arm portions 18 provided at both end portions of the claw portion 13a, the locking groove 26a formed in the outer peripheral opening peripheral portion of each claw portion side through hole 25 is outside the rotor 1 (see FIG. 1 and the like). A first notch 34 having a U-shaped cross section that opens to the radial side and a second notch 35 having a width W ₃₅ that is larger than the width W _{34 of} the first notch 34 are passed through each claw portion. The holes 25 are provided in order from the back side. Constituting the first notch 34 of this, the interval W ₃₄ parallel pair of side wall surfaces 36 and 36 between each other, than the distance d ₃₃ of each plane 33, 33 that constitute the locking portion 32 Is slightly larger (W ₃₄ > d ₃₃ ). In addition, the first half of the locking portion 32 can enter the inside of the second cutout 35.

And in the state which inserted the front-end | tip part of each said guide pin 5b in each said nail | claw part side through-hole 25, the part which has a pair of plane parts 33 and 33 in an outer peripheral surface in the base end part of the said latching | locking part 32 is provided. In the first cutout 34, the base half of the locking portion 32 is inserted into the second cutout 35 without rattling. With this configuration, the base end portion of the locking portion 32 is engaged with the inner surface of the first notch 34, and the guide pins 5b are rotated in the guide holes 6a (see FIG. 2 and the like). Be blocked. Therefore, in the case of the present embodiment, the base end portion of the locking portion 32 and the first cutout 34 constitute the detent means.
Other configurations and operations are the same as those of the first embodiment shown in FIGS. 1 to 14 described above, and therefore, redundant description and illustration are omitted.
In addition, the shape of the latching | locking parts 20 and 32 provided in the front-end | tip part of each guide pin 5a, 5b for comprising a detent means is not limited to the shape shown in each Example mentioned above, Various Of course, the shape can be adopted.

In each of the embodiments described above, when the nut 30 is coupled to the guide pins 5a and 5b, the inner side arm portion 17 and the outer side arm portions 18 and 18a are arranged in the axial direction of the guide pins 5a and 5b. It is also possible to employ an appropriate configuration for preventing the two arm portions 17 and 18 from being deformed so much by the acting axial force. For example, as shown in FIGS. 10, 11, and 31, a stepped portion 37 is provided in a part of the flange portion 19 of the guide pin 5a so that the inner side arm portion 17 and the outer side arm portion 18 approach as described above. When the inner side arm portion 17 tends to be deformed, the inner side surface (the left side surface in FIG. 31) of the inner side arm portion 17 abuts against the stepped portion 37 to prevent further deformation. In this case, the axial dimension L ₁ (FIGS. 11 and 31) from the stepped surface 37 to the inner side surface (the right side surface in FIG. 31) of the flange portion 19 is the inner arm portion. The length L ₂ from the inner side surface of 17 to the portion where the inner side surface of the locking portion 20 of the guide pin 5a abuts on the outer side surface (left side surface in FIG. 31) of the outer side arm portion 18 (FIGS. 19 and 31) It is set to be slightly smaller than (L ₁ <L ₂ ).

1 is a schematic perspective view showing Example 1 of the present invention. The arrow A figure of FIG. 1 which abbreviate | omits and shows a part. BB sectional drawing of FIG. The schematic perspective view which takes out and shows only a caliper and a guide pin. The figure which looked at the back half part of FIG. 2 from upper direction. The figure seen from the lower part of FIG. The same view from above. The figure which shows the C section of FIG. 6 in the state which expanded and made the radial direction of the rotor correspond to an up-down direction. DD sectional drawing of FIG. 8 shown in the state which abbreviate | omitted the guide pin. The perspective view which takes out and shows only a guide pin. Similarly front view. The figure seen from the left of FIG. FIG. 4 is a view similar to FIG. 3, showing a state in which the caliper is inclined with respect to a virtual plane perpendicular to the rotation center of the rotor as the rotor is deformed due to a temperature rise or the like during braking. The figure for demonstrating the state in which a guide pin carries out a bending deformation. The figure similar to FIG. 14 in a conventional structure. The fragmentary sectional view which shows the relationship between the guide hole and guide pin in Example 2 of this invention. The fragmentary sectional view which shows the relationship between a guide hole and a guide pin in the Example 3. FIG. The fragmentary sectional view which shows the relationship between the guide hole and guide pin in Example 4 of the present invention. The figure which looked at Example 5 from the diameter direction outside of a rotor in the state where a part was cut. EE sectional drawing of FIG. The figure which shows the FF cross section of FIG. 19 in the right half part, and what looked at the left half part from the upper part of the figure. The figure which looked at the right half part from the downward direction of FIG. 19, and the GG cross section of the figure in the left half part, respectively. FIG. 6A is a schematic diagram illustrating a state in which the outer arm portion is deformed when the width of the pressure plate constituting the outer pad is long, (A) before deformation and (B) after deformation. FIG. 6A is a schematic diagram illustrating a state in which the outer side arm portion is deformed when the width of the pressure plate constituting the outer side pad is short, (A) before deformation and (B) after deformation. The figure which shows the part near the front-end | tip of the guide pin used for Example 6 of this invention. HH sectional drawing of FIG. The figure in Example 6 similar to FIG. The figure which looked at FIG. 27 from upper direction. The figure which looked at one example of the conventional structure from the radial direction outer side of the rotor in the state which cut a part. FIG. 30 is a cross-sectional view taken along the line II of FIG. The fragmentary sectional view which shows the structure for suppressing a deformation | transformation of the inner side and outer side both arm part.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotor 2, 2a Caliper 3, 3a Support 4 Mounting hole 5, 5a, 5b Guide pin 6, 6a Guide hole 7 Bridge part 8, 8a Entry side engagement part 9, 9a Entry side engagement part 10a, 10b Pad 11, 11a, 11b Pressure plate 12 Cylinder part 13, 13a, 13b Claw part 14 Piston 15, 15a, 15b Lining 16 Cylinder hole 17 Inner side arm part 18, 18a Outer side arm part 19, 19a, 19b Hook part 20 Locking Part 21 Flat part 22 Curved part 23 Curved part 24 Male thread part 25 Claw part side through hole 26, 26a Locking groove 27 Bottom face part 28 Side wall surface 29 Cylinder side through hole 30 Nut 31 Flat part 32 Locking part 33 Flat part 34 First One cutout 35 Second cutout 36 Side wall surface 37 Stepped portion

Claims (8)

  A support fixed to the vehicle body adjacent to the rotor rotating with the wheel, a pair of pads supported by the support on both sides of the rotor so as to be slidable in the axial direction, and a guide hole provided in the support; A caliper supported so as to be displaceable in the axial direction of the rotor by a guide pin that fits in the guide hole, a claw portion provided on one of the bridge portions straddling the rotor of the caliper, and the other of the bridge portions. And a base end portion of the guide pin is supported and fixed to a rotation direction end portion of the rotor of a cylinder portion provided on the piston side by a part of the caliper. Accordingly, in the floating caliper type disc brake that performs braking by pressing the pair of pads against both side surfaces of the rotor, The guide pin is slidably inserted in the guide hole through the guide hole. At the end of the claw portion in the rotational direction of the rotor, the intermediate portion of the guide pin is more than the bridge portion. The claw part side through hole formed in the part projecting to one side in the rotational direction is inserted through a portion near the tip of each guide pin, and a rotation prevention means is provided between the tip of the guide pin and the claw part. Floating caliper type disc brake featuring   In the rotation preventing means, the distal end portion of the guide pin is engaged with at least one of the pair of parallel side wall surfaces provided in the opposite rotor side opening of the claw portion side through hole. The floating caliper type disc brake according to claim 1, which is configured by a thing.   The guide pin sequentially inserts the claw part side through hole, the guide hole provided in the support, and the cylinder side through hole provided on the other side of the bridge part, and protrudes from the cylinder side through hole to the outside of the other side. The floating caliper type disc brake according to claim 1 or 2, wherein a fastening means is coupled to the base end portion.   The radial dimension of the guide pin in the gap between the outer peripheral surface of the guide pin inserted through the guide hole at the intermediate portion of the guide pin and the inner peripheral surface of the guide hole is set in one direction parallel to both side surfaces of the rotor. The floating caliper type disc brake according to any one of claims 1 to 3, wherein the disc brake is different from the one related to the direction parallel to both sides of the rotor and perpendicular to the one direction.   The size of the gap between the outer peripheral surface of the portion inserted into the guide hole at the intermediate portion of the guide pin and the inner peripheral surface of the guide hole is made different between the rotational direction of the rotor and the radial direction of the rotor. The floating caliper type disc brake according to claim 4.   Of the dimensions of the gap between the outer peripheral surface of the guide pin inserted into the guide hole at the middle portion of the guide pin and the inner peripheral surface of the guide hole, the dimension in the radial direction of the rotor is the dimension in the rotational direction of the rotor. The floating caliper type disc brake according to claim 5, which is larger than the above.   Of the pair of pads provided on both sides of the rotor, the width of the lining constituting the outer side pad in the rotational direction of the rotor is made larger than the width of the lining constituting the inner side pad in the rotational direction. The floating caliper type disc brake according to any one of claims 1 to 6.   The lining volume of both the outer side pad and the inner side pad is made equal to each other by making the thickness of the lining constituting the outer side pad smaller than the thickness of the lining constituting the inner side pad. Floating caliper type disc brake described in 1.

Images