JP2008202637A - Disc brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a disc brake capable of preventing brake noise from being caused by an increase of slide resistance of a piston and the inclination of the piston in the pushing direction by restricting application of the brake torque applied to the pads to a cylinder part as much as possible. <P>SOLUTION: A carrier 5 holding the pad 4 and a caliper 7 comprising the piston 6 for pushing the pads 4 are formed as a separate block. The pads 4 are disposed on both sides of the brake disk 3, and held by the carrier 5 slidably in the axial direction. The caliper 7 and the carrier 5 are integrally coupled to each other by bolts 21 provided along the axial direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a disc brake used for vehicle wheel braking or the like.

A disc brake used for vehicle wheel braking has a brake disc integrally attached to the wheel side, and a cylinder portion is provided in a caliper attached to the vehicle body side, and a piston housed in a bore of the cylinder portion is a friction material. The brake disc is pressed through the pad.
As this type of disc brake, there is known an opposed piston type disc brake in which pads are arranged on both sides of the disc axis direction of the brake disc and both pads are pressed by a pair of opposed pistons. In this disc brake, a pair of pads are slidably supported by a caliper by pins along the disc axial direction, and a receiving portion for supporting both ends of the pad in the disc rotating direction is provided on the caliper. Thus, the braking torque acting on the pad is received. (For example, refer to Patent Document 1).
JP 2006-207655 A

  Although this conventional opposed piston type disc brake has good controllability of the pad clearance, the receiving part that receives the braking torque and the cylinder part that supports the piston are formed by an integral block. There is a concern that the braking torque acting on the cylinder acts as a large stress on the cylinder portion, thereby inhibiting the sliding of the piston and tilting the pressing direction of the piston. An increase in sliding resistance of the piston and an inclination in the pressing direction are likely to cause a brake squeal.

  Accordingly, the present invention can prevent the occurrence of brake squealing due to an increase in the sliding resistance of the piston or an inclination in the pressing direction by preventing the braking torque transmitted from the pad from acting on the cylinder portion as much as possible. Disc brakes are to be provided.

  The invention according to claim 1, which solves the above problem, includes a carrier that slidably supports a pair of pads arranged on both sides of the brake disc in the disc axial direction and receives the braking torque of the pads; The caliper is fixed to the carrier by fastening means and has a piston provided oppositely to press the pair of pads.

  According to a second aspect of the present invention, in the disc brake according to the first aspect, the caliper is fixed by a pair of fastening means spaced apart in the rotational direction of the disc on the side of the carrier mounting portion of the carrier. It is characterized by.

  According to a third aspect of the present invention, in the disc brake according to the first or second aspect, the caliper includes a pair of cylinder portions in which the piston is slidably disposed, and the pair of straddles across the brake disc. It is characterized by comprising a bridge part for connecting the cylinder part and a fixing part fastened by the fastening means, and the bridge part exists outside the pad in the disk radial direction.

  According to a fourth aspect of the present invention, in the disc brake according to any one of the first to third aspects, the fastening means fixes the carrier and the caliper in the disc axial direction.

  According to a fifth aspect of the present invention, in the disc brake according to any one of the first to third aspects, the fastening means is parallel to a line connecting the disc center and the center between the mounting portions of the carrier. The carrier and the caliper are fixed in a direction.

  The invention according to claim 6 is the disc brake according to any one of claims 1 to 5, wherein the fastening means is a bolt, and the carrier is provided with a screw hole into which the bolt is screwed. The screw hole has a bag shape.

  According to a seventh aspect of the present invention, in the disc brake according to any one of the first to sixth aspects, the caliper is provided with a pair of cylinder portions that house the piston, and both cylinder portions are formed by bridge portions. The cylinder portions and the bridge portion are connected and are integrally formed.

  The invention according to claim 8 is the disc brake according to any one of claims 1 to 7, wherein both sides of the pad in the disc rotation direction and the receiving portion for receiving the braking torque of the carrier are: The pad is concavo-convexly fitted so as to be movable in the disk axial direction, and movement of the pad to the outer side in the disk radial direction is restricted by the concavo-convex fitting.

  According to a ninth aspect of the present invention, in the disk brake according to any one of the first to eighth aspects, the caliper does not contact the pad in a disk rotation direction and a disk radial direction.

  According to a tenth aspect of the present invention, in the disc brake according to the ninth aspect, the caliper is such that only the piston abuts against the pad.

  According to the present invention, the carrier that receives the braking torque through the pad and the caliper that holds the piston are fixed by the fastening means, and the braking torque transmitted from the pad is less likely to act as stress around the piston. It is possible to prevent the occurrence of brake squealing due to an increase in sliding resistance and inclination in the pressing direction.

Embodiments of the present invention will be described below with reference to the drawings.
First, the first embodiment shown in FIGS. 1 to 11 will be described.
1 to 7 show an entire block of a disc brake 1 according to the present invention. The disc brake 1 is coupled to a knuckle (not shown) for supporting an axle of a vehicle by fastening bolts in the fastening holes 2 and 2 at the lower edge. The block of the disc brake 1 is attached to the knuckle so as to cover a part of the outer peripheral edge of the brake disc 3 (see FIG. 4) that rotates integrally with the wheel. A braking force is generated by pressing. In the following, the description will be given with the vehicle mounted state, the radial direction of the brake disk 3 in this mounted state will be referred to as the disk radial direction, the axial direction of the brake disk 3 will be referred to as the disk axial direction, and the brake disk 3 The circumferential direction is referred to as the disk circumferential direction.

  The block of the disc brake 1 is directly coupled to the knuckle by a bolt, and a caliper 7 having a carrier 5 that mainly holds the pads 4 and 4 pressed against the brake disc 3 and a piston 6 that presses the pads 4 and 4. It is constituted by. The disc brake 1 has substantially arc-shaped disc passage recesses 8A and 8B (see FIG. 7) that allow passage of the outer peripheral edge of the brake disc 3 across the carrier 5 and the caliper 7, and the disc radius of the carrier 5 A caliper 7 is arranged on the outer side in the direction of polymerization.

  The disc brake 1 is an opposed piston type brake, and pads 4 and 4 held by the carrier 5 are disposed on both sides in the disc axial direction of the brake disc 3 and the piston 6 held by the caliper 7. Are arranged on both sides of the brake disc 3 so as to press the back of each pad 4. In the case of this embodiment, two pistons 6 and 6 are arranged side by side in the disk rotation direction on one side of the brake disk 3, and the two pistons 6 and 6 arranged in parallel are arranged on the pad 4 that is horizontally long in the disk circumferential direction. The back is pressed.

  First, the caliper 7 will be described. The caliper 7 includes an inner side cylinder portion 9 and an outer side cylinder portion 10 on the inner side and the outer side in the vehicle width direction with the brake disc 3 interposed therebetween, and each of the cylinder portions 9 and 10 includes a piston. A bore 11 that slidably accommodates 6 is formed along the disk axial direction. The inner and outer cylinder portions 9 and 10 are connected to each other by a bridge portion 12 straddling the radially outer side of the brake disk 3 and surrounded by the bridge portion 12 and the cylinder portions 9 and 10 on both sides. The area is a disk passage recess 8B on the caliper 7 side. The bores 11 in the caliper 7 are connected to each other by a supply / discharge passage (not shown) in the caliper 7, and brake fluid is supplied / discharged through a supply / discharge plug 13 formed in the inner cylinder portion 9 of the caliper 7. It has become so.

  In the case of this embodiment, the remaining part including the outer side cylinder part 10 and part of the bridge part 12 and the inner side cylinder part 9 are formed as separate caliper blocks C1 and C2, and both caliper blocks C1 and C2 are formed. Later, they are connected to each other by a plurality of bolts 14a, 14b, 14c along the caliper axial direction.

  4 and 5, the caliper 7 as a whole is formed in a substantially arc shape when viewed from the disk axial direction, but at both ends of the inner cylinder portion 9 in the disk circumferential direction. In order to fix the caliper 7 to the carrier 5, a connecting tongue piece 15 (fixing portion) is extended. Furthermore, a pair of long hole-shaped confirmation windows 30 penetrating in the radial direction of the disk as shown in FIGS. 1 to 3 are formed in the bridge section 12 connecting both the cylinder sections 9 and 10, and The degree of reduction of the pad 4 can be confirmed through the confirmation window 30 from the outside in the radial direction. As described above, since the bridge portion 12 is located on the outer side in the disk radial direction of the pad 4 except for the confirmation window 30, the caliper 7 can exhibit high rigidity, and both cylinder portions 9 can be used during braking. , 10 can be restrained from being deformed in the direction away from each other, giving a feeling of rigidity as a brake feeling.

  8 to 11 show the carrier 5 of the disc brake 1 of this embodiment. The carrier 5 has an inner wall 16 and an outer wall 17 disposed inside and outside in the vehicle width direction with the brake disc 3 interposed therebetween, as shown in FIG. Are formed so as to be continuous with the arc of the outer shape of the caliper 7, and arc portions of both edges extend in the disk axial direction, and the inner wall 16 and the outer wall 17 are connected to each other. As shown in FIG. 8, the carrier 5 has a substantially rectangular opening 18 when viewed from the outside in the radial direction of the disk, and the opening 18 is continuous with the disk passage recess 8B on the caliper 7 side. ing.

  An extending portion 19 is provided at the inner end of the inner wall 16 in the disk radial direction, and the aforementioned fastening for bolting the carrier 5 to the knuckle at two positions spaced apart in the disk circumferential direction of the extending portion 19 is provided. A hole 2 is provided. Also, screw holes 20 are formed in the vicinity of both ends of the inner wall 16 in the disk circumferential direction along the disk axial direction. Each screw hole 20 is a screw hole into which a bolt 21 (fastening means) attached to the tongue piece 15 of the caliper 7 is screwed, and the caliper 7 can be fixed to the carrier 5 by screwing the bolt 21. ing. In the case of this embodiment, the bottom of the screw hole 20 has a sealed bag structure, and does not penetrate the passage recess 8A side.

  In addition, a substantially rectangular pad receiving groove 23 in which the pad 4 and the back metal 22 that supports the pad 4 are arranged is formed at the outer edges of the inner wall 16 and the outer wall 17 in the disk radial direction. Each of the pad receiving grooves 23 opens to the outer side in the disk radial direction so that the substantially lower half of the pad 4 and the back metal 22 is received. In other words, the upper half of the pad 4 and the back metal 22 protrudes outward from the carrier 5 in the disk radial direction. Further, substantially rectangular guide grooves 24 are continuously formed on the side edges of the inner wall 16 and the outer wall 17 of each pad receiving groove 23 on both sides in the disk circumferential direction.

In each guide groove 24, a substantially rectangular protrusion 25 protruding from both edges of the back metal 22 is guided so as to be slidable along the disk axial direction. Further, between the bottom of the pad receiving groove 23 and the vicinity of the protrusion 25 of the back metal 22, a leaf spring 26 for biasing the back metal 22 together with the pad 4 outward in the disk radial direction is interposed. That is, the pad 4 is unevenly fitted into the guide grooves 24 on both sides via the protrusions 25 of the back metal 22, and the displacement in the disk circumferential direction and the disk radial direction outside is allowed while the guide groove 24 allows displacement in the disk axial direction. Being regulated. In the case of this embodiment, the edge portions 24 a of the guide grooves 24 of the inner wall 16 and the outer wall 17 serve as receiving portions that receive the braking torque of the pad 4.
The leaf spring 26 does not have a guide piece that is conventionally provided for engaging the protrusion 25 of the back metal 22 with the guide groove 24. This is because the guide piece protrudes from the carrier 5 in the disc axial direction so that the caliper 7 is not hindered.

  The caliper 7 is integrated with the carrier 5 in a state where the pad 4 is set on the carrier 5 together with the back metal 22 and the leaf spring 26. At this time, the corresponding pistons 6 of the caliper 5 are set on the backs of the inner and outer backing plates 22, and in this state, the tongue pieces 15 and 15 on both edges of the inner cinder portion 9 of the caliper 7 are set. Superposed on the side surface of the inner wall 16 of the carrier 5, both tongue pieces 15, 15 are fastened and fixed to the carrier 5 by bolts 21.

  The carrier 5 and the caliper 7 can be formed of cast iron or aluminum. However, when the materials of the carrier 5 and the caliper 7 are different, for example, the carrier 5 is formed of cast iron and the caliper 7 is formed of aluminum. In such a case, it is desirable to interpose an insulating spacer between them in order to prevent electrolytic corrosion.

  In the disc brake 1 configured as described above, when brake fluid is supplied to the bores 11 of the cylinder portions 9 and 10 during braking, the pistons 6 in the bores 11 are moved forward by receiving fluid pressure, 6 advances the corresponding pad 4 through the back metal 22. As a result, the pads 4 on both sides of the brake disc 3 are similarly pressed against both sides of the disc 3, thereby applying a braking force.

  On the other hand, the braking torque acting on the pad 4 at this time is received by the edge 24 a of each guide groove 24 of the carrier 5. Although this braking torque acts as a stress on the carrier 5, the carrier 5 and the caliper 7 are formed separately from each other and are connected to each other by the bolts 21 along the axial direction. 7 does not act directly. That is, in this disc brake 1, the edge 24 a of the guide groove 24 of the carrier 5 regulates the displacement of the pad 4 and the back metal 22 in the disc circumferential direction and the disc radial direction outside, and the caliper 7 side has only the piston 6 and the pad 4. Therefore, the caliper 7 is not directly subjected to the stress caused by the braking torque.

  For this reason, in the disc brake 1, the cylinder portions 9 and 10 of the caliper 7 do not bend and deform due to the stress caused by the braking torque, and the piston 11 is prevented from sliding due to the deformation or inclination of the bore 11. The problem that the pressing direction of the piston 6 is inclined does not occur. In particular, in the case of this embodiment, the two positions at both ends of the caliper 7 in the circumferential direction of the caliper 7 separated from the bores 11 of the cylinder portions 9 and 10 are coupled to the carrier 5 by bolts 21 along the axial direction. It is possible to effectively prevent the influence on the piston 6. Therefore, in this disc brake 1, a stable operation of the piston 6 can always be obtained, and the occurrence of brake squeal can be prevented in advance.

  Further, in the disc brake 1 of this embodiment, the inner and outer cylinder portions 9 and 10 of the caliper 7 almost completely cover the radially outer side of the brake disc 3 and do not have large openings such as pad replacement holes. Since they are coupled by 12, the rigidity of the caliper 7 is effectively increased. Therefore, the occurrence of brake squeal can also be prevented from this point.

  Further, in the disc brake 1, when replacing parts such as the pad 4 and the piston 6, the bolts 21 at both ends in the disc circumferential direction of the caliper 7 are loosened to remove the entire caliper 7. When the entire caliper 7 is removed in this way, the pad 4 and the piston 6 can be replaced in a space with a margin.

  Further, in manufacturing, the processing of the bore 11 that accommodates the piston 6 and the processing of the portion that guides the pad 4 are performed on different blocks, respectively, so that the manufacturing becomes easy and the manufacturing cost can be reduced. become.

  In the case of this embodiment, the bolt 21 is used as a fastening means for connecting the caliper 7 and the carrier 5 and the bottom of the screw hole 20 formed on the carrier 5 side has a bag structure. Can be prevented from occurring. Therefore, in this disc brake 1, the maintenance performance can be maintained satisfactorily.

  Subsequently, second and third embodiments of the present invention will be sequentially described below. In each embodiment described below, the same parts as those in the first embodiment are denoted by the same reference numerals, and description of overlapping parts is omitted.

  12 to 15 show a disc brake 101 according to a second embodiment of the present invention. The basic structure of the disc brake 101 is substantially the same as that of the first embodiment. However, the entire block of the caliper 107, that is, the inner and outer cylinder portions 9 and 10 and the two cylinder portions 9 and 10 are combined. The bridge portion 12 to be connected is cast as an integral block, and is not provided with a bolt for connecting the caliper 107 blocks together.

  Therefore, the disc brake 101 can basically obtain the same operations and effects as those of the first embodiment, but the caliper 107 is formed by a single block, so that the cost can be reduced by reducing the number of parts. And the rigidity can be improved. Further, since the caliper 107 is not coupled by bolts, the caliper 107 has a higher rigidity than that of the first embodiment. In particular, in the disc brake 101, since the caliper 107 and the carrier 5 are formed as separate parts, even if the entire caliper 107 is a single block, the processing inside the bores 11 that are arranged to face each other can be spared in space. Can be easily done.

  FIGS. 16-19 shows embodiment of the disc brake 201 of 3rd Embodiment of this invention. The disc brake 201 is basically the same in the basic configuration as in the first embodiment, but the bolt fastening direction between the caliper 207 and the carrier 205 is such that the center O of the brake disc 3 and the mounting portion 2 of the carrier 205 are the same. The direction is parallel to the line P connecting the centers of the two, that is, the disk radial direction (vertical direction in FIGS. 17 to 19). Specifically, the tongue pieces 215 extending at both ends of the caliper 207 in the disk circumferential direction are formed with a wide width in the disk axial direction, and the tongue pieces 215 are formed at both ends of the carrier 205 in the disk circumferential direction. The flat surfaces 40 are superposed on each other, and are joined by bolts 21 extending substantially along the disk radial direction. In the case of this embodiment, the caliper 207 has a structure in which two caliper blocks C1 and C2 are bolted as in the first embodiment.

  The disc brake 201 can basically obtain the same operations and effects as those of the first embodiment. However, since the caliper 207 and the carrier 205 can be bolted from the outside in the disc radial direction, There is a further advantage that desorption workability is improved.

  In addition, this invention is not limited to said embodiment, A various design change is possible in the range which does not deviate from the summary.

The perspective view of the whole block of the disc brake of 1st Embodiment of this invention. The perspective view seen from another angle of the whole block of the disc brake of the embodiment. The top view of the whole block of the disc brake of the embodiment. FIG. 4 is a view of the disc brake of the same embodiment as viewed in the direction of arrow D in FIG. The E arrow line view of FIG. 3 of the disc brake of the embodiment. The F arrow directional view of FIG. 3 of the disc brake of the embodiment. The G arrow directional view of FIG. 4 of the disc brake of the embodiment. The top view of the carrier of the disc brake of the embodiment. FIG. 9 is an A arrow view of the carrier of the disc brake of the same embodiment in FIG. 8. The arrow B figure of FIG. 8 of the carrier of the disc brake of the embodiment. The arrow C figure of FIG. 8 of the carrier of the disc brake of the embodiment. The top view of the whole block of the disc brake of 2nd Embodiment of this invention. The H arrow directional view of FIG. 12 of the disc brake of the embodiment. The arrow I view of FIG. 12 of the disc brake of the embodiment. FIG. 13 is a view of the disc brake of the same embodiment as viewed in the direction of arrow J in FIG. 12. The top view of the whole block of the disc brake of 3rd Embodiment of this invention. FIG. 17 is a view as viewed in the direction of arrow K in FIG. 16 of the disc brake of the same embodiment. The L arrow directional view of FIG. 16 of the disc brake of the embodiment. The M arrow directional view of Drawing 16 of the disc brake of the embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,101,201 ... Disc brake 3 ... Brake disc 4 ... Pad 5,205 ... Carrier 6 ... Piston 7, 107, 207 ... Caliper 9 ... Inner side cylinder part (cylinder part)
10 ... Outer cylinder part (cylinder part)
12 ... Bridge part 15 ... Tongue piece (fixing part)
20 ... Screw hole 21 ... Bolt (fastening means)
24a ... Edge (receiving part)

Claims (10)

  A pair of pads disposed on both sides of the brake disc are slidably supported in the disc axial direction and receive the braking torque of the pads, and the pair of pads fixed to the carrier by fastening means are pressed respectively. A disc brake characterized by comprising a caliper having a piston provided so as to face each other.   2. The disc brake according to claim 1, wherein the caliper is fixed by a pair of fastening means spaced apart in the rotation direction of the disc on the side of the carrier mounting portion of the carrier.   The caliper includes a pair of cylinder portions in which the piston is slidably arranged, a bridge portion connecting the pair of cylinder portions across the brake disc, and a fixing portion fastened by the fastening means. 3. The disc brake according to claim 1, wherein the bridge portion exists outside the pad in the disc radial direction.   The disc brake according to any one of claims 1 to 3, wherein the fastening means fixes the carrier and the caliper in the disc axial direction.   The said fastening means fixes the said carrier and a caliper in the direction parallel to the line | wire which connects the said disk center and the center between the said attaching parts of the said carrier, The any one of Claims 1-3 characterized by the above-mentioned. Disc brake as described in.   The fastening means is a bolt, and the carrier is provided with a screw hole into which the bolt is screwed, and the screw hole has a bag shape. The disc brake according to claim 1.   2. The caliper is provided with a pair of cylinder parts for accommodating the pistons, the cylinder parts are connected by a bridge part, and the cylinder part and the bridge part are integrally formed. The disc brake of any one of -6.   The both sides of the pad in the disk rotation direction and the receiving part for receiving the braking torque of the carrier are ruggedly fitted so that the pad is movable in the disk axis direction, and the pad is radially outer by the rugged fitting. The disc brake according to any one of claims 1 to 7, wherein the movement to is restricted.   The disc brake according to claim 1, wherein the caliper does not contact the pad in the disc rotation direction and the disc radial direction.   The disc brake according to claim 9, wherein only the piston contacts the caliper with respect to the pad.

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