JPH11117959A - Disc brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To keep the excellent slide characteristics of a disc brake operation of a brake and stably mount a caliper on a mounting member during non-brake. SOLUTION: Slide pins 11 and 17 fastened against the respective mounting parts 9 of a caliper 5 are slidably inserted in a fit-in state in respective pin holes 3 formed in the respective arm parts 2A of a mounting member 2. A pair of plane parts are formed in positions, situated facing each other in the rotation direction A of a disc 1, at the slide pin 11 on the outlet side in the rotation direction A of the disc 1, of the slide pins 11 and 17. This constitution provides a gap between the pin hole 3 and the slide pin 11 and being larger in a rotation direction A than the radial direction of the disc 1. Further, a pair of plane parts are formed in positions, situated opposite to each other in the radial direction of the disc 1, and at the slide pin 17 on the inlet side in the rotation direction of the disc 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc brake suitably used for applying a braking force to, for example, a vehicle or the like.

[0002]

2. Description of the Related Art Conventionally, a vehicle has a pair of arms spaced apart in a circumferential direction of a disk and straddling the disk in an axial direction, and a connecting portion connecting base ends of the arms to each other. And a caliper slidably provided on each arm of the mounting member and pressing a pair of friction pads against both surfaces of the disc. 2. Description of the Related Art Disc brakes are known in which a pair of sliding pins provided on a caliper are slidably inserted into respective provided pin holes.

In this type of disc brake, at the time of a brake operation, a piston provided on an inner leg portion of the caliper is slid toward the disc by supplying hydraulic pressure from the outside, and a friction pad on the inner side is pressed toward the disc. . Then, the entire caliper including the inner leg, the bridge and the outer leg is slidably displaced with respect to the mounting member via each sliding pin by the reaction force at this time, so that the piston and the outer leg of the caliper are displaced. During this time, each friction pad is pressed against both sides of the disc to apply a braking force to the disc.

[0004]

By the way, in the above-described conventional disk brake, the inner leg 7 'and the outer leg 8' are integrally formed as shown in FIG. Therefore, when the brake is operated, the inner leg 7 'and the outer leg 8' tend to be elastically deformed so as to expand, whereby the sliding pin 17 'provided on the caliper 5' moves along the axis of the disc 1 '. There is a tendency that the tip side is displaced so that the tip side is lower than the base end side in the direction.

[0005] Further, with respect to the mounting member, when the brake is operated, the torque from the disk via each friction pad is received by one of the arms of the mounting member. Also tends to rotate due to the torque from the disk, and is elastically deformed as described below.

In this case, as shown in FIG. 14, the arms 2Ai 'and 2Ao' of the mounting member 2 'for supporting the friction pad so as to be slidable in the axial direction of the disk 1' are connected at the base end thereof. It is attached to a non-rotating portion of the vehicle on the inner diameter side of the disk 1 'with respect to the arms 2Ai' and 2Ao 'by 2B'. The arms 2Ai 'and 2Ao' are connected to each other by a reinforcing beam 4 'at the distal end, but the rigidity of the reinforcing beam 4' is lower than that of the connecting portion 2B '.

For this reason, in the arm 2Ai 'on the inlet side in the rotation direction of the disk 1', the tip side (outer side) is raised with respect to the axial direction of the disk 1 'with respect to the base side (inner side). Tend to be elastically deformed in the direction of arrow F1,
In the arm 2Ao 'on the outlet side in the rotation direction of the disc 1',
There is a tendency for the tip side (outer side) to be elastically deformed in the direction of arrow F2 so that the tip side (outer side) is lower than the base side (inner side) with respect to the axial direction.

As a result, the sliding pin 17 'provided on the caliper 5' shown in FIG. 13 and the pin hole provided on the arm 2Ai 'of the mounting member 2' are located on the inlet side in the rotation direction of the disk 1 '. In this case, the disc 1 'is displaced in the opposite direction with respect to the radial direction and interferes with each other. If so,
The sliding pin 17 'and the pin hole strongly interfere with each other in the radial direction of the disk.

Further, with respect to the mounting member, a structure in which a torque from the disk via each friction pad during a brake operation is received by one of the arms of the mounting member on the outlet side in the rotation direction of the disk is used. On the other hand, the arm on the outlet side in the rotation direction of the disk tends to elastically deform in the rotation direction of the disk by receiving the torque from the disk via each friction pad. On the other hand, the arm on the entrance side in the rotational direction of the disk does not receive torque from the disk via each friction pad, and therefore does not elastically deform in the rotational direction of the disk. Therefore, with respect to the mounting member, when the brake is operated, the torque from the disk via each friction pad is received by the arm on the outlet side in the rotation direction of the disk among the arms of the mounting member. Regarding the rotation direction, there is a tendency that the space between the arms expands.

As a result, in any of the above cases, the sliding resistance between the pin hole and the sliding pin increases, the sliding characteristics of the caliper deteriorate, and brake noise and judder easily occur. is there.

Therefore, in order to solve such a problem, a relatively large clearance (clearance) is secured between the pin hole and the sliding pin over the entire sliding surface thereof, so that the pin hole during braking is provided. In the case where the pin is displaced with respect to the sliding pin, measures to alleviate the interference between the pin hole and the sliding pin can be considered.

However, if the gap between the pin hole and the sliding pin is made large over the entire sliding surface, the rattling between the two will increase, and the vehicle will bounce against the road surface during traveling. If so, the caliper may vibrate significantly with respect to the mounting member during non-braking.

[0013] With the vibration of the caliper, each friction pad integrated with the caliper comes into partial contact with the disk repeatedly, causing uneven wear between the friction pad and the disk. And there is a problem that judder occurs. In addition, there is a problem that abnormal noise such as rattle noise is easily generated due to play between the pin hole and the sliding pin.

The present invention has been made in view of the above-mentioned problems of the prior art, and the present invention provides a method of forming a sliding pin and a pin hole even when a torque from a disk greatly acts on an arm of a mounting member during a brake operation. They can slide smoothly with each other, preventing the occurrence of judder, etc., stabilizing the mounting position of the caliper when braking is not performed, and causing uneven wear etc. between the sliding surface of the disc and the friction pad An object of the present invention is to provide a disc brake capable of preventing the occurrence of abnormal noise such as rattling noise.

[0015]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, there is provided a pair of arms spaced apart in a circumferential direction of a disk and straddling the disk in an axial direction, and attached to a non-rotating portion of a vehicle. A member and a caliper slidably provided on each arm of the mounting member, and a caliper for pressing a pair of friction pads against both surfaces of the disc, wherein one of the arm and the caliper of the mounting member is provided. The present invention is applied to a disk brake in which a sliding pin provided on the other member is slidably inserted into a provided pin hole.

A feature of the structure adopted by the first aspect of the present invention is that, between the sliding pin and the pin hole located on the inlet side in the rotational direction of the disk, the radial direction is larger than the rotational direction of the disk. This is because a large gap is formed.

According to the above construction, when the brake is operated, the sliding pin provided on the caliper is displaced such that the distal end side is lower than the base end side with respect to the axial direction of the disk, and the arm of the mounting member on the inlet side in the disk rotation direction is provided. Even if the outer part rises in the disk axis direction with respect to the inner side and the arm on the outlet side in the disk rotation direction is elastically deformed so that the outer side lowers in the disk axis direction with respect to the inner side, the entrance in the disk rotation direction Since the gap between the pin hole provided on the side arm and the sliding pin is increased in the radial direction of the disc, the radial displacement of the pin hole and the sliding pin in the disc can be tolerated. Interference with each other can be prevented.

Further, in the invention according to claim 2, the sliding pin and the arm located on the inlet side in the rotation direction of the disk include:
A gap is formed between the sliding pin and the pin hole, which is larger in the radial direction than the rotating direction of the disk, and the sliding pin and the arm located on the outlet side in the rotating direction of the disk have the sliding. The object is to form a gap between the pin and the pin hole that is larger in the rotational direction than the radial direction of the disk.

Thus, in the disc brake having a configuration in which the torque from the disc through each friction pad during the brake operation is received by the arm on the outlet side in the rotation direction of the disc among the arms of the mounting member, Even when the arms are widened in the rotating direction of the disk, the gap between the pin hole provided on the arm on the outlet side in the rotating direction of the disk and the sliding pin is increased in the rotating direction of the disk. The displacement of the pin and the pin hole in the rotational direction of the disk can be allowed, and the two can be prevented from interfering with each other.

Further, according to the third aspect of the present invention, the disk is attached to the non-rotating portion at least at a position closer to the front of the vehicle than the center of rotation of the disk. The arm is disposed at least above the arm on the outlet side, and the braking force of the friction pad is received by the arm on the outlet side in the rotation direction of the disk.

Thus, the whole caliper can be stably supported by the sliding pin and the pin hole located on the inlet side in the rotation direction of the disc while being suspended from the arm on the inlet side of the mounting member.

Further, in the invention according to claim 4, the mounting member is mounted on the non-rotating portion at least at a position closer to the rear side of the vehicle than the center of rotation of the disk, and the disk of the arms of the mounting member is provided. The arm on the outlet side in the rotation direction is arranged at least above the arm on the inlet side, and the braking force of the friction pad is received by the arm on the inlet side in the rotation direction of the disc.

Thus, the entire caliper can be stably supported on the arm on the inlet side of the mounting member by the sliding pin and the pin hole located on the outlet side in the rotation direction of the disk.

Further, in the invention of claim 5, one of the sliding pin and the pin hole is formed in a circular cross section, and the other is formed in a non-circular cross section.

Thus, the gap between the pin hole and the sliding pin can be easily formed in different sizes in the radial direction and the rotational direction of the disk.

Further, in the invention according to claim 6, the pin hole is formed in a circular cross section, and the slide pin is formed to have a smaller diameter than the pin hole and has a substantially long cross section having a flat portion on the outer peripheral surface. It is composed of circular pins.

Thus, a relatively large gap can be easily secured between the pin hole and the flat portion of the sliding pin. In addition, a flat portion can be easily formed on the outer peripheral surface of the sliding pin by press-molding the entire sliding pin using header processing or the like.

In addition, in the invention according to claim 7, the pin hole has a circular cross section, and the sliding pin has a cylindrical bush on an outer peripheral surface formed to have a smaller diameter than the pin hole. The bush is fitted and inserted into the pin hole, and a gap extending in the axial direction is opposed to the bush with a cylindrical hole interposed therebetween.

As a result, the sliding pin and the pin hole can be kept in a circular cross section which is easy to process.

[0030]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIGS. 1 to 7 show a case where the disc brake according to the first embodiment of the present invention is applied to an automobile.

In the drawing, reference numeral 1 denotes a disk which rotates in the direction of arrow A in FIG. 1 together with the wheels of the automobile, 2 denotes a mounting member provided on the inner side of the disk 1, and the mounting member 2
As shown in FIG. 3, a pair of arms 2A, 2A extending in the axial direction so as to extend over the outer periphery of the disk 1 at a distance in the rotation direction of the disk 1 and a connecting portion connecting the base ends of the arms 2A. 2B and the like. And the mounting member 2
Is integrally attached to a knuckle portion (not shown) serving as a non-rotating portion of the vehicle through a pair of screw holes 2B1 provided in the connecting portion 2B.

Here, the mounting member 2 is, as shown in FIG.
The disk 1 is disposed at least at a position closer to the front side of the vehicle than the rotation center O (the axle of the vehicle). This allows
Arm 2 of each arm 2A on the entrance side in the rotation direction of disk 1
A is arranged above the arm 2A on the outlet side in the rotation direction.

Each arm 2A is provided with pin holes 3, 3 for sliding pins 11, 17, which will be described later.
Is formed as a circular hole with a bottom having a substantially circular cross section and extending in the axial direction of the disk 1. Further, on the base end side (inner side) and distal end side (outer side) of the arm 2A, there are pad guides 2A1 having a substantially U-shape and torques protruding inward in the rotation direction of the disk 1. Receiving part 2A2
(Only the outer side is shown).

Each arm 2A of the mounting member 2 is slidably engaged with a back guide 23A of each friction pad 23, which will be described later, with each pad guide 2A1. It is slidably guided and receives torque from the disk 1 via each friction pad 23 at each torque receiving portion 2A2. As shown in FIG. 1, a reinforcing beam 4 is formed in each of the arms 2A so as to extend in an arcuate manner between the two, and integrally connect the distal ends of the arms 2A.

Numeral 5 denotes a caliper slidably supported on the mounting member 2. The caliper 5 is located between the arms 2A of the mounting member 2 on the outer peripheral side of the disc 1 as shown in FIGS. , An inner leg 7 integrally formed on one side of the bridge 6 on the inner side of the disc 1, and an outer leg integrally formed on the other side of the bridge 6. 8, a cylinder bore 7 </ b> A is formed on the inner peripheral side of the inner leg 7.

A pair of mounting portions 9, 9 are provided on the inner leg portion 7 at the left and right sides in FIG. 2 in the direction of rotation of the disk 1. Each pin bolt hole 9A is formed in each protruding end side. Further, sliding pins 11 and 17 are provided in the respective pin bolt holes 9A via pin bolts 16 and 21 which will be described later, so that the caliper 5 is attached to each arm 2A of the mounting member 2 by the shaft of the disc 1. It is slidably mounted in the direction.

As shown in FIGS. 1 and 2, the center line O1-O1 passing through the center of the cylinder bore 7A is the center line O2-O between the pin holes 3 of the mounting member 2.
2, it is eccentrically arranged by the dimension δ near the outlet side in the rotation direction of the disk 1. The outer leg 8 is formed of a pair of forked claws 8A and 8B.
B, the claw portion 8B is formed to have a larger thickness in the rotation direction of the disc 1 than the claw portion 8A, thereby increasing the rigidity of the claw portion 8B as a whole.

Further, as shown in FIG. 2, each of the mounting portions 9 has engaging projections 10 and 10 extending radially of the disc 1 at portions of the mounting member 2 on the side of the arms 2A. The engagement projections 10 are engaged with engagement surfaces 15, 20 of sliding pins 11, 17, respectively.

Reference numeral 11 denotes a sliding pin provided at the mounting portion 9 of the caliper 5 at the outlet side in the rotation direction of the disk 1. The sliding pin 11 is formed by press-forming a columnar material by header processing or the like. , FIG. 2 and FIG.

The sliding pin 11 is formed integrally with one end of the shaft 11A, which extends in the axial direction of the disk 1 and is slidably inserted into the pin hole 3. The shaft 11A is formed to have a slightly smaller diameter than the pin hole 3. Also, the shaft 11A
Is a small-diameter portion 11C having a small diameter extending from the middle position in the length direction to the distal end side of the small-diameter portion 11C, and a cylindrical rubber bush 12 is fitted on the outer peripheral side of the small-diameter portion 11C. As a result, rattling between the shaft portion 11A and the pin hole 3 is minimized.

Here, the shaft portion 11A is formed in a substantially elliptical cross section as a whole, and a portion extending parallel to the outer peripheral side along the axial direction becomes a pair of flat portions 13, 13, and each of the flat portions 13 13 is curved in an arc shape to form each arc surface portion 14
It has become. As a result, the sliding pin 11 is
A relatively large gap is formed between the circular arc surface portion 3 and the pin hole 3, and a relatively small gap is formed between each arc surface portion 14 and the pin hole 3.

The head 11B is integrally formed with an abutment plate portion 11D which abuts against the outer edge side surface of the pin bolt hole 9A of the mounting portion 9. A pair of engagement surfaces is provided on the outer surface of the abutment plate portion 11D. 15 and 15 are formed so as to be parallel to each other. When one of the engagement surfaces 15 is engaged with the engagement protrusion 10 of the caliper 5, the sliding pin 11 is attached to the mounting portion 9 via a pin bolt 16 or the like.
It is fastened to.

Here, each flat portion 13 and each engagement surface 15 of the sliding pin 11 are disposed so as to be substantially parallel to each other as shown in FIG. Therefore, by engaging the engaging surface 15 with the engaging protrusion 10 extending in the radial direction of the disk 1, the sliding pin 11 allows each flat portion 13 to rotate in the rotational direction of the disk 1 (the direction indicated by the arrow A in FIG. 6). ) Is positioned in the pin hole 3 so as to face each other.

As a result, a relatively large gap is formed between the sliding pin 11 and the pin hole 3 in the rotation direction A of the disk 1 located between each flat portion 13 and the pin hole 3. At the same time, a relatively small gap is formed between each arc surface portion 14 and the pin hole 3 in the radial direction of the disk 1.

Reference numeral 17 denotes a sliding pin provided on the mounting portion 9 of the caliper 5 at the entrance side in the rotation direction of the disk 1, and the sliding pin 17 has a shaft portion 17A as shown in FIGS. , The head 17B and the abutment plate 17C are formed substantially in the same manner as the sliding pin 11. Also, the shaft portion 17A
Has each plane part 18 and each arc surface part 19,
The abutment plate portion 17C has each engagement surface 20. And
With one of the engagement surfaces 20 being engaged with the engagement protrusion 10 of the caliper 5, the sliding pin 1
Reference numeral 7 is fastened to the mounting portion 9 via a pin bolt 21 or the like.

However, the sliding pin 17 differs from the sliding pin 11 in that, as shown in FIG. 5, each flat portion 18 and each engaging surface 20 are arranged in directions substantially orthogonal to each other. I have. Accordingly, when the engaging surface 20 is engaged with the engaging projection 10, the sliding pin 17 is positioned in the pin hole 3 with the flat portions 18 facing each other in the radial direction of the disk 1.

As a result, a relatively large gap is formed between the sliding pin 17 and the pin hole 3 in the radial direction of the disc 1 located between each flat portion 18 and the pin hole 3. ,
The disk 1 is located between each arcuate surface portion 19 and the pin hole 3.
A relatively small gap is formed in the rotation direction A of the above.

Reference numeral 22 denotes a piston slidably inserted into the cylinder bore 7A of the caliper 5;
The brake fluid pressure supplied from the outside into the cylinder bore 7A causes the cylinder bore 7A to be slid and displaced in the axial direction, and the friction pads 23 are moved between the claws 8A and 8B of the outer leg 8 on both sides of the disk 1. Pressing.

23, 23 are discs 1 by a caliper 5
Each of the friction pads 23 is formed in a flat plate shape as shown in FIGS. 1 and 3, and back metal members 23A, 23A are fixed on the back surface side thereof so as to overlap each other. . Each of the friction pads 23 has its back metal 23A slidably supported by the pad guide portion 2A1 of the mounting member 2, and applies a braking force to the disk 1.
The disc 1 is pressed against both sides of the disc 1 by the caliper 5.

The disc brake according to this embodiment is
Having the above-described configuration, its operation will be described below.

First, at the time of the brake operation of the vehicle, when the piston 22 slides toward the disk 1 due to the brake fluid pressure supplied from the outside into each cylinder bore 7A of the caliper 5, when the piston 22 slides toward the inner side, the inner friction pad is moved by the piston 22. 23 is pressed against the disc 1. Then, at this time, the caliper 5 receives the reaction force from the disk 1, and the sliding pins 11,
17 and is displaced toward the inner side with respect to the mounting member 2, and the outer side friction pad 23 is pressed against the disc 1 via the claw portions 8 </ b> A and 8 </ b> B of the outer leg portion 8. Thereby, the braking force is applied to the disk 1 from both sides by the friction pads 23.

At this time, the braking torque transmitted from the disc 1 to the caliper 5 via the friction pads 23 causes the outer side of the caliper 5 to be displaced in a direction indicated by an arrow A (hereinafter referred to as a rotation direction A). Since it acts as a moment, on the inner leg 7 side, the surface pressure of the friction pad 23 against the disk 1 becomes smaller on the outlet side than on the inlet side in the rotation direction A, and on the outer leg 8 side, the surface pressure of the friction pad 23 Tend to be larger on the outlet side than on the inlet side.

On the other hand, the inner leg 7 is disposed eccentrically near the outlet side in the rotation direction A, and the claw 8B on the inlet side of the outer leg 8 is formed larger than the claw 8A on the outlet side. Therefore, the surface pressure of each friction pad 23 is
Are adjusted so as to be uniform with respect to the rotation direction A on both sides.

Further, at the time of the brake operation, as described above with reference to FIG. 13, the caliper 5 is moved by the torque from the disc 1 through the friction pads 23 through the bridge 6 arranged on the outer peripheral side of the disc 1. Inner legs 7
And the outer leg portion 8 are integrally formed, there is a tendency that the inner leg portion 7 and the outer leg portion 8 are elastically deformed so as to expand, thereby providing the caliper 5. The sliding pin 17 tends to be displaced such that the distal end side is lower than the base end side with respect to the axial direction of the disk 1.

Further, as described above with reference to FIG. 14, each of the friction pads 23 is supposed to rotate by the torque from the disk 1, so that each of the friction pads 23 can be displaced. Each of the arms 2A of the mounting member 2 to be supported has its base end closer to the disk 1 than the arms 2A by a screw hole 2B1 provided in the connecting portion 2B.
Is fixed to the non-rotating portion of the vehicle on the inner diameter side of the vehicle, so that the arm 2A on the entrance side in the rotation direction of the disk 1 is elastically deformed so that the outer side rises with respect to the inner side with respect to the axial direction of the disk 1. The arm 2A on the outlet side in the rotation direction of the disk 1 tends to be elastically deformed so that the outer side is lower than the inner side with respect to the axial direction.

In the present embodiment, however, the gap between the sliding pin 17 on the inlet side and the pin hole 3 is formed to be large in the radial direction, and the torque of the disk 1 is received via each friction pad 23. Since the gap between the sliding pin 11 on the outlet side and the pin hole 3 is formed to be smaller in the radial direction of the disc 1 than the inlet side, the disc 1 in the rotational direction of the disc 1 at the time of braking operation. Even if the sliding pin 17 on the inlet side of the disk 1 and the pin hole 3 of the arm 2A are displaced in opposite directions in the radial direction of the disc 1, the diameter secured between the sliding pin 17 and the pin hole 3 The relative displacement between the two can be tolerated by the gap in the direction and it is possible to prevent the two from strongly interfering with each other in the radial direction of the disk 1, so that the sliding resistance between the two can be reduced. At this time, disk 1
A small gap is formed between the sliding pin 11 on the outlet side of the disc 1 and the pin hole 3 of the arm 2A, which is displaced in the same direction with respect to the radial direction of the disc 1, so that the caliper 5 The rattling in the direction can be suppressed firmly.

Further, as in the present embodiment, the torque from the disc 1 via the friction pads 23 during the brake operation is applied to the arm 2A of the mounting member 2 on the exit side of the disc 1 in the rotation direction. When the torque is received by the torque receiving portion 2A2 of the portion 2A, the arm 2A on the outlet side receives the torque from the disk 1 via each friction pad 23,
6, there is a tendency that the disk 1 is slightly elastically deformed in the rotation direction A of the disk 1, while the arm 2A on the inlet side receives the torque from the disk 1 through each friction pad 23. Therefore, there is a tendency that the disk 1 hardly elastically deforms in the rotation direction.

However, in the present embodiment, the gap between the sliding pin 11 on the outlet side and the pin hole 3 is formed so as to increase in the rotation direction of the disk 1, and the sliding pin 17 on the inlet side and the pin hole 3 are formed. 3 is formed so as to be smaller with respect to the outlet side in the rotation direction of the disc 1, the torque of the disc 1 causes the arms 2 </ b> A to expand due to the torque of the disc 1 when the brake is operated, and the pin hole 3 on the outlet side is formed. Even when the disc is displaced in the rotation direction of the disc 1, the pin hole 3 on the outlet side is fixed to the sliding pin 11 by a gap in the rotation direction of the disc 1 secured between the pin pin 3 and the slide pin 11.
1 can be allowed, the pin hole 3 and the sliding pin 11 can be prevented from strongly interfering with each other, and the sliding resistance between the two can be reduced. Further, at this time, since the sliding hole 17 on the inlet side which is hardly elastically deformed with respect to the rotation direction of the disk 1 and the pin hole 3 form a small gap, the caliper 5 moves relative to the mounting member 2 in the rotation direction of the disk 1. The rattling can be suppressed firmly.

In addition, even when the brake is not operated and the brake is not applied, the rattling of the caliper 5 in the radial direction of the disc 1 can be restricted between the arcuate surface portions 14 of the sliding pins 11 and the pin holes 3 and the caliper 5 5 is the rotation direction A of the disk 1
The rattling can be restricted between each arcuate surface portion 19 of the sliding pin 17 and the pin hole 3.

Further, when the mounting member 2 and the caliper 5 are disposed closer to the front of the vehicle than the center of rotation of the disc 1 (the axle of the vehicle) as in the present embodiment, the rotation direction A of each arm 2A is used. The arm 2A on the entrance side is the arm 2A on the exit side
Since the caliper 5 is entirely disposed above the arm 2A on the entrance side via the pin hole 3 and the sliding pin 17,
Can be firmly supported in a suspended state,
The mounting posture of the caliper 5 can be stabilized.

Therefore, according to the present embodiment, when the brake is operated, the pin hole 3 on the entrance side in the rotation direction of the disc 1 and the sliding pin 11 are displaced in the radial direction of the disc 1,
The arm 2A on the exit side in the rotation direction of the disc 1 is
Even if the pin hole 3 is displaced in the rotation direction of the disk 1 with respect to the sliding pin 11 under the influence of the torque from the sliding pin 3, the sliding pins 11 and 17 are smoothly slid in the respective pin holes 3. Can be moved. As a result, the operational feeling at the time of the brake operation can be improved, and even when the brake operation is released, each friction pad 23 can be reliably separated from the disc 1, and the friction pads 23 can be prevented from being dragged, and judder Not only can be suppressed, but also the ability to follow the rotor surface runout of the disk 1 and the thermal deformation of the rotor sliding surface can be improved.

In the gap between the sliding pins 11 and 17 and the pin hole 3, the gap between each of the arc-shaped surface portions 14 and 19 and the pin hole 3 is small. 17
Although a relatively large gap is formed between each of the flat portions 13 and 18 and the pin hole 3 for allowing a positional shift during a brake operation, rattling of the caliper can be sufficiently suppressed. . This prevents the caliper 5 from vibrating largely with respect to the mounting member 2 due to the impact transmitted to the vehicle body during traveling, even when the brake is not applied, by using the pin holes 3 and the sliding pins 11, 1.
7, the friction pads 23 integrated with the caliper 5 can be kept always separated from the disk 1. Thereby, the cause of drag of each friction pad 23 can be further eliminated, uneven wear and the like can be prevented from occurring in the disk 1 and each friction pad 23, the life thereof can be extended, and fuel consumption can be improved. be able to. In addition, it is possible to suppress the generation of the abnormal noise such as the rattle noise together with the generation of the above-mentioned shudder, and it is possible to perform comfortable traveling.

Further, each of the pin holes 3 and the sliding pins 11 and 17
The gap between the pin hole 3 and the sliding pin 1 is reduced by a portion necessary for suppressing the rattling of the caliper 5.
The gap between the calipers 1 and 17 is formed to be large to allow a displacement during the operation of the brake. Therefore, the weight of the caliper 5 is reduced as compared with the related art by the size of the gap to allow the displacement. Therefore, the material cost can be reduced, and the riding comfort can be improved by reducing the fuel consumption and the unsprung load.

Further, since the entire sliding pins 11 and 17 including the flat portions 13 and 18 are formed by using a header process or the like, a special process for forming the flat portions 13 and 18 is performed. Also becomes unnecessary.

Next, FIGS. 8 to 11 show a second embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals. The description is omitted. However, the feature of this embodiment is that
The cross-sectional shape of each pin hole 31, 32 provided in each arm 2 </ b> A of the mounting member 2 is formed in a non-circular shape, and the shaft 33 of each sliding pin 33, 34 provided integrally with the caliper 5.
By forming the cross-sectional shape of A and 34A into a circular shape,
The gap between the pin hole 31 on the outlet side and the sliding pin 33 is formed larger in the rotation direction A than the radial direction of the disk 1, and the gap between the pin hole 32 on the inlet side and the sliding pin 34 is That is, it is formed to be larger in the radial direction than the rotation direction A of No. 1.

Here, the pin hole 31 is formed as a circular hole with a bottom extending the arm 2A of the mounting member 2 in the longitudinal direction, similarly to the pin holes 3 described in the first embodiment. Is formed. However, as shown in FIGS. 8 and 10, the pin hole 31 has an oval cross section (elliptical shape).
On its inner peripheral side, a portion curved in a semi-arc shape is an arc-shaped portion 31.
A, 31A, and portions extending substantially linearly between the arc holes 31A are linear portions 31B, 31B.
Further, the pin hole 32 is formed substantially in the same manner as the pin hole 31, and has each arc-shaped portion 32A and each linear portion 32B.

Here, the pin hole 31 on the outlet side of the pin holes 31 and 32 is oriented such that the arc-shaped portions 31A are oriented in the rotation direction A of the disk 1 and the pin hole 32 on the inlet side.
Each of the arc-shaped portions 32A is oriented in the radial direction of the disk 1.

The sliding pins 33 and 34 are formed substantially in the same manner as the sliding pins 11 and 17 described in the first embodiment, and include shaft portions 33A and 34A and head portions 33B and 34B.
And abutment plate portions 33C and 34C. Each of the engagement projections 1 of the caliper 5 is provided on the abutment plate portions 33C, 34C.
The respective engagement surfaces 35 and 36 that engage with 0 are formed respectively.

However, the shaft 3 of the sliding pins 33, 34
3A and 34A are substantially circular in cross section as a whole, and are formed as cylindrical bodies extending straight in the pin holes 31 and 32 in the axial direction, and are different from those of the first embodiment. Is different.

As a result, the sliding pin 33 on the outlet side of the sliding pins 33, 34 is connected to the respective arc-shaped portions 31A of the pin hole 31.
A relatively large gap is formed in the rotation direction A of the disc 1, and a relatively small gap is formed in the radial direction of the disc 1 between each linear portion 31 </ b> B.

On the other hand, the sliding pin 34 on the entrance side is
A relatively large gap is formed in the radial direction of the disk 1 between each of the two arc-shaped portions 32A, and a relatively small gap is formed in the rotational direction A of the disk 1 between each of the linear portions 32B.

Thus, also in the present embodiment having such a configuration, it is possible to obtain substantially the same operation and effect as in the first embodiment.

FIG. 12 shows the first and second embodiments described above.
As in the first embodiment, the cross section of one of the shaft portion and the pin hole of the sliding pin is formed in a substantially elliptical shape, and a gap in the disk radial direction or the rotating direction is provided between the sliding pin and the pin hole. Instead of providing a sliding pin and a pin hole, a variation is provided in which a disk radial direction or rotational direction gap is provided between the sliding pin and the pin hole while keeping the cross-sectional shape of each of the sliding pin and the pin hole circular. It is a thing.

In the figure, a shaft 43A of a sliding pin 43 is inserted into a pin hole 41 formed in an arm 2A of the mounting member 2 by fitting a cylindrical rubber bush 44 into the pin hole 41. It is fitted. Two gap portions 45 are formed inside the rubber bush 44 so as to extend in the axial direction so as to be opposed to each other with the cylindrical hole 44A interposed therebetween so as to match the radial direction or the rotating direction of the disk 1. .

As a result, a gap is formed between the pin hole 41 and the sliding pin 43 in the radial direction or the rotating direction of the disk 1. Thus, also in this modification, the first and second embodiments described above are performed. Almost the same effects as those of the embodiment can be obtained.

In each of the above embodiments, each pin hole 3
(31, 32) is formed on each arm 2A of the mounting member 2 and the sliding pins 11, 17 (33, 34) are mounted on the mounting portions 9 of the caliper 5; For example, each pin hole 3 (31, 32) may be formed in each mounting part 9 of the caliper 5, and each sliding pin 11, 17 (33, 34) may be mounted on each arm 2A of the mounting member 2.

In each of the above embodiments, the disk 1
Although the torque receiving portion 2A2 of the arm portion 2A on the exit side in the rotation direction receives the torque from each friction pad 23, for example, the side surface of the back metal 23A on the entrance side in the rotation direction of the disc 1 of each friction pad 23 is formed. A hook-shaped projection is formed on the arm 2A of the mounting member 2 on the entrance side.
3 is applied to a pin hole and a sliding pin of a disc brake of a type that receives the torque of the disc 1 at the arm 2A on the inlet side in the rotation direction of the disc 1 such that a groove in which the hook portion of the projection is engaged is formed. The disc brake of this type may be arranged at a position at least closer to the vehicle rear side than the rotation center O (axle of the vehicle) of the disc 1.

[0079]

As described in detail above, according to the first aspect of the present invention, the disk is provided between the sliding pin and the pin hole at the sliding pin and the arm located on the inlet side in the rotation direction of the disk. Since the gap that is larger in the radial direction than the rotation direction of the brake is formed, the mounting member is deformed under the influence of the torque from the pad during the braking operation, and the caliper is deformed by the braking of the piston. Therefore, even if the sliding pin and the pin hole are relatively displaced in the radial direction of the disk due to this, the gap between the sliding hole and the pin hole on the inlet side in the rotating direction of the disk in the radial direction of the disk. Since the size is increased, the displacement between the pin hole and the sliding pin can be allowed, and the two can be prevented from interfering with each other. Therefore, the sliding pin can be smoothly slid in the pin hole. In addition, when the brake is not applied, rattling of the caliper in the rotational direction and the radial direction of the disk can be suppressed between each pin hole and each sliding pin, and the caliper can be stably mounted on the mounting member.

Therefore, the life of the disc and each friction pad can be extended, the fuel consumption can be improved, the fuel consumption can be improved, and the judder, rattle noise and the like can be eliminated by eliminating the cause of torque fluctuation during braking and dragging of the friction pad during braking. It is possible to perform comfortable running by suppressing abnormal noise of the vehicle.

According to the second aspect of the present invention, the sliding pin and the arm located on the inlet side in the rotational direction of the disk are provided with:
A gap is formed between the sliding pin and the pin hole, which is larger in the radial direction than the rotating direction of the disk, and the sliding pin and the arm located on the outlet side in the rotating direction of the disk have the sliding. Since a gap that is larger in the rotational direction than the radial direction of the disc is formed between the pin and the pin hole, the torque from the disc through each friction pad during the braking operation is
In the disc brake of the configuration in which the arm on the exit side in the rotation direction of the disc among the arms of the mounting member is received, furthermore, the exit in the disc rotation direction is provided even if the space between the arms expands in the disc rotation direction. The gap between the pin hole provided in the side arm and the sliding pin is increased in the rotating direction of the disk, so that the displacement of the sliding pin and the pin hole in the rotating direction of the disk can be tolerated. Interference with each other can be prevented.

Therefore, the life of the disc and each friction pad can be extended, the fuel efficiency can be improved, and the judder, rattle noise, etc. can be extended by eliminating the cause of torque fluctuation during braking and dragging of the friction pad during non-braking. It is possible to perform comfortable running by suppressing abnormal noise of the vehicle.

Further, according to the third aspect of the present invention, at least a position closer to the front side of the vehicle than the center of rotation of the disk is attached to the non-rotating portion of the vehicle, and the arm of the mounting member on the inlet side in the rotation direction of the disk is provided. Is arranged at least above the arm on the exit side, and the braking force of the friction pad is received by the arm on the exit side in the rotation direction of the disc. Therefore, the entire caliper is located on the entrance side in the rotation direction of the disc. By the moving pin and the pin hole, the mounting member can be stably supported by being suspended from the arm on the entrance side of the mounting member.

According to the fourth aspect of the present invention, the mounting member is mounted on the non-rotating portion of the vehicle at least at a position closer to the rear side of the vehicle than the center of rotation of the disk. Since the arm on the outlet side in the rotating direction is arranged at least above the arm on the inlet side, and the braking force of the friction pad is received by the arm on the inlet side in the rotating direction of the disc, the entire caliper rotates the disc. The sliding pin and the pin hole located on the exit side in the direction allow the attachment member to be stably supported while being suspended from the arm on the entrance side of the mounting member.

Further, according to the fifth aspect of the present invention, one of the cross-sectional shape of the sliding pin and the pin hole is formed in a circular shape, and the other is formed in a non-circular shape. The gap between the moving pin and the moving pin can be easily formed in different sizes in the radial direction and the rotating direction of the disk, and the gap can be easily designed.

Further, according to the invention of claim 6, the pin hole is formed in a circular cross section, and the sliding pin is formed in a smaller diameter than the pin hole and has a substantially elliptical cross section having a flat portion on the outer peripheral surface. By forming the entire sliding pin including the flat part by press forming using header processing etc.
Special processing for forming the flat portion is not required, and workability in manufacturing the sliding pin can be improved.

In addition, in the invention of claim 7, the pin hole has a circular cross section, and the sliding pin has a cylindrical bush on an outer peripheral surface formed to have a smaller diameter than the pin hole. The sliding pin and the pin hole are formed in an easy-to-process cross-sectional circle because the bush is configured to be fitted and inserted into the pin hole, and the bush is formed with a gap extending in the axial direction opposed to the cylindrical hole. The shape can be left as it is.

[Brief description of the drawings]

FIG. 1 is a partially broken front view showing a disc brake according to a first embodiment of the present invention.

FIG. 2 is a plan view showing the disc brake in FIG.

FIG. 3 is an enlarged cross-sectional view taken along a line III-III in FIG. 2;

FIG. 4 is a perspective view showing the sliding pin in FIG. 1 alone;

FIG. 5 is a perspective view showing another sliding pin in FIG. 1 alone;

FIG. 6 is an enlarged view of a main part on the outlet side in the rotation direction of the disk, showing the pin holes and the sliding pins in FIG. 1;

FIG. 7 is an enlarged view of a main part on the rotation direction entrance side of the disk, showing the pin holes and the sliding pins in FIG. 1;

FIG. 8 is a partially broken front view showing a disc brake according to a second embodiment of the present invention.

FIG. 9 is a plan view showing the disc brake in FIG. 8;

FIG. 10 is an enlarged view of a main part on the exit side in the rotation direction of the disc, showing the pin holes and the sliding pins in FIG. 8;

FIG. 11 is an enlarged view of a main part on the inlet side in the rotation direction of the disc, showing the pin holes and the sliding pins in FIG. 8;

FIG. 12 is a sectional view showing a pin hole, a sliding pin, and a bush of a disc brake according to a modification of the present invention.

FIG. 13 is an explanatory diagram showing a state in which a caliper of a conventional disc brake is deformed during a brake operation.

FIG. 14 is an explanatory view showing a state in which a mounting member of a conventional disc brake is deformed during a brake operation.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Disc 2 Mounting member 2A Arm part 3,31,32,41 Pin hole 5 Caliper 11,17,33,34,43 Sliding pin 13,18 Flat part 23 Friction pad 44 Rubber bush (bush)

Continued on the front page (72) Inventor Hideaki Ishii 1000 Yoshida, Kushigata-cho, Nakakoma-gun, Yamanashi Pref.

Claims (7)

[Claims] 1. A mounting member having a pair of arms spaced in a circumferential direction of a disk and straddling the disk in an axial direction, and a mounting member mounted on a non-rotating portion of a vehicle, and sliding on each arm of the mounting member. A caliper for pressing the pair of friction pads against both surfaces of the disc, and a slide provided on the other member in a pin hole provided on one of the arm and the caliper of the mounting member. In a disk brake in which a moving pin is slidably inserted, a gap between the sliding pin and the pin hole located on the rotation direction entrance side of the disk is larger in a radial direction than the rotation direction of the disk. A disc brake characterized by having a gap formed therein. 2. A mounting member attached to a non-rotating portion of a vehicle, comprising a pair of arms spaced apart in a circumferential direction of the disk and straddling the disk in an axial direction, and sliding on each arm of the mounting member. A caliper for pressing the pair of friction pads against both surfaces of the disc, and a slide provided on the other member in a pin hole provided on one of the arm and the caliper of the mounting member. In a disk brake in which a moving pin is slidably inserted and a braking force of the friction pad is received by an arm on a rotation direction exit side of the disk, the sliding pin and the pin located on the rotation direction entrance side of the disk A gap that is larger in the radial direction than the rotation direction of the disk is formed between the sliding pin and the pin hole, and the gap between the sliding pin and the pin hole located on the outlet side in the rotation direction of the disk is formed between the hole and the hole. Rotation rather than radial direction In disc brake, characterized in that the formation of the gap becomes larger. 3. The mounting member is mounted on the non-rotating portion at least at a position closer to the front side of the vehicle than the center of rotation of the disk, and the arm of the mounting member on the disk rotation direction entrance side is included in each of the arms of the mounting member. 3. The disc brake according to claim 1, wherein the disc brake is arranged at least above the arm on the exit side, and the braking force of the friction pad is received by the arm on the exit side in the rotation direction of the disc. 4. The mounting member is mounted on the non-rotating portion at least at a position closer to the rear side of the vehicle than the center of rotation of the disk, and the arm of the mounting member on the side of the disk rotating direction exit side is provided. 2. The disc brake according to claim 1, wherein the portion is disposed at least above the arm on the inlet side, and the braking force of the friction pad is received by the arm on the inlet side in the rotation direction of the disc. 5. The sliding pin and the pin hole, wherein one of the cross-sectional shapes is formed in a circular shape, and the other cross-sectional shape is formed in a non-circular shape. Disc brake. 6. The pin hole is formed in a circular cross section, and the slide pin is formed of a pin having a smaller diameter than the pin hole and having a substantially elliptical cross section having a flat portion on an outer peripheral surface. The disc brake according to claim 1, 2, 3, or 4, wherein 7. The pin hole is formed in a circular cross section, and the sliding pin is formed by fitting a cylindrical bush to an outer peripheral surface formed to have a smaller diameter than the pin hole so as to fit in the pin hole. 5. The disc brake according to claim 1, wherein the bush is inserted and fitted with an axially extending gap opposed to the bush with a cylindrical hole interposed therebetween.