JP3502248B2 - Disc brake - Google Patents

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art Conventionally, there has been a pair of arm portions which are spaced apart in the circumferential direction of the disc and straddle the disc in the axial direction, and a coupling portion which couples the base end sides of the respective arm portions, the coupling portion being a vehicle. Of the mounting member, and a caliper slidably provided on each arm of the mounting member for pressing a pair of friction pads against both sides of the disc. A disc brake is known in which a pair of slide pins provided on a caliper are slidably fitted in the provided pin holes.

In this type of disc brake, the piston provided on the inner leg of the caliper is slid toward the disc by the hydraulic pressure supplied from the outside when the brake is operated, and the inner friction pad is pressed toward the disc. . Then, by the reaction force at this time, the entire caliper including the inner leg portion, the bridge portion, and the outer leg portion is slidably displaced with respect to the mounting member via the respective sliding pins, so that the piston and the outer leg portion of the caliper are displaced. The friction pads are pressed against both sides of the disc between to apply a braking force to the disc.

[0004]

By the way, in the above-described conventional disc brake, as shown in FIG. 13, the inner leg portion 7'and the outer leg portion 8'are integrally formed. Therefore, when the brake is operated, the inner leg portion 7'and the outer leg portion 8 'tend to be elastically deformed so as to expand, whereby the sliding pin 17' provided on the caliper 5'will move to the axial line of the disc 1 '. There is a tendency for the distal end side to be displaced lower than the proximal end side with respect to the direction.

With regard to the mounting member, in the structure in which one of the arm portions of the mounting member receives the torque from the disk through each friction pad when the brake is operated, the friction pad itself. Also tries to rotate due to the torque from the disc, and thus elastically deforms as described below.

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

Therefore, in the arm portion 2Ai 'on the entrance side in the rotational direction of the disc 1', the tip side (outer side) rises with respect to the base end side (inner side) in the axial direction of the disc 1 '. Has a tendency to elastically deform in the direction of arrow F1,
In the arm portion 2Ao ′ on the outlet side in the rotation direction of the disc 1 ′,
The tip side (outer side) tends to be elastically deformed in the arrow F2 direction so that the tip side (outer side) is lower than the base end side (inner side) with respect to the axial direction.

As a result, on the inlet side of the disc 1'in the rotational direction, the sliding pin 17 'provided on the caliper 5'and the pin hole provided on the arm 2Ai' of the mounting member 2'shown in FIG. , The discs 1 ′ are displaced in the opposite radial directions and interfere with each other. Especially, the sliding pin 17 ′ on the inlet side of the disc 1 ′ in the rotational direction is a main pin having a small pin clearance with respect to the pin hole. If there is,
The sliding pin 17 'and the pin hole strongly interfere with each other in the radial direction of the disk.

Further, regarding the mounting member, in the structure in which the torque from the disc via each friction pad during brake operation is received by the arm of the mounting member on the outlet side in the rotational direction of the disc. The arm portion on the outlet side of the disc in the rotation direction tends to be elastically deformed in the rotation direction of the disc upon receiving the torque from the disc via each friction pad. On the other hand, the arm portion on the inlet side of the disc in the rotational direction does not receive the torque from the disc via each friction pad, and therefore is not elastically deformed in the rotational direction of the disc. Therefore, regarding the mounting member, when the torque from the disc via each friction pad during brake operation is received by the arm of the mounting member on the outlet side in the rotational direction of the disc, the disc Regarding the direction of rotation, there is a tendency for the arms to spread apart.

As a result, in any of the above cases, there is a problem that the sliding resistance between the pin hole and the sliding pin becomes large, the sliding characteristic of the caliper deteriorates, and brake squeal and judder easily occur. is there.

[0011] In order to solve such a problem, by ensuring a relatively large gap Te <br/> Tsu cotton on the sliding surface thereof throughout between the pin hole and the sliding pin (clearance) Even if the pin hole is displaced relative to the sliding pin during braking, it is possible to take measures to reduce the interference between the pin hole and the sliding pin.

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

With the vibration of the caliper, the friction pads integrated with the caliper partially come into repeated contact with the disc, resulting in uneven wear between the friction pad and the disc. There is a problem that judder occurs. Further, there is a problem that rattling between the pin hole and the sliding pin easily causes abnormal noise such as rattle noise.

The present invention has been made in view of the above-mentioned problems of the prior art. The present invention prevents the sliding pin and the pin hole from moving even when the torque from the disk largely acts on the arm portion of the mounting member during brake operation. They can slide smoothly against each other, prevent the occurrence of judder, etc., can stabilize the mounting posture of the caliper when not braking, and cause uneven wear between the sliding surfaces of the disc and the friction pad. It is an object of the present invention to provide a disc brake that can prevent the occurrence of noise and reduce the generation of abnormal noise such as rattle noise.

[0015]

In order to solve the above-mentioned problems, a mounting which has a pair of arm portions which are spaced apart in the circumferential direction of the disc and straddle the disc in the axial direction and which is mounted on a non-rotating portion of a vehicle. A member and a caliper slidably provided on each arm of the mounting member for pressing a pair of friction pads against both surfaces of the disc, and one member of the arm and the caliper of the mounting member is provided. It is applied to a disc brake in which a sliding pin provided on the other member is slidably fitted in a provided pin hole.

[0016] The feature of the configuration invention of claim 1 is employed, between the slide pin and the pin hole positioned in the rotational direction the inlet side of the disc, and the sliding pin and the pin hole
Are displaced in opposite directions in the radial direction of the disc
In order to allow the above, a gap that is larger in the radial direction than the rotational direction of the disk is formed.

With the above configuration, when the brake is operated, the key is
The sliding pin provided on the caliper is
Displace so that the tip side is lower than the base side, and the mounting member
The arm on the inlet side of the disc rotation direction is in the disc axis direction.
The outer side rises with respect to the inner side, and the disc rotation direction
The outer arm of the
Even when elastically deformed so that
The pin hole and sliding pin provided on the arm on the inlet side in the rotation direction
The gap between them in the radial direction of the disc., The abovePin hole
And sliding pinButDisk radial directionIn opposite directionsposition
GapDoTo allowSince there is a gap, the pin hole
And sliding pinCan interfere with each other, Pin hole
It is possible to prevent the sliding resistance between the sliding pin and the sliding pin from increasing.
It

[0018] In the present invention of claim 2, between the rotational direction entrance you positioned side front Kisurido pin and the pin hole of the disc, radially above the sliding pin and the pin hole of the disk
Between the sliding pin and the pin hole, a gap that is larger in the radial direction than the rotational direction of the disc is formed in order to allow positional displacement in opposite directions . Between the sliding pin and pin hole
In order to allow the disc to be displaced in the rotational direction, a gap that is larger in the rotational direction than in the radial direction of the disk is formed.

[0019] Thus, in the disc brake configured to receive the torque from the disc via each friction pad at the time of braking operation, the arm portion on the outlet side of the disc in the rotation direction of the arm portion of the mounting member further receives: Even when the arms expand in the disk rotation direction, the gap between the pin hole and the sliding pin provided on the arm on the exit side in the disk rotation direction is increased in the disk rotation direction to allow the sliding movement. A gap that allows misalignment of the pin and pin hole in the disc's rotational direction.
Since the space is provided, it is possible to prevent the sliding pin and the pin hole from interfering with each other , and the sliding resistance between the pin hole and the sliding pin can be prevented.
Ru it is possible to prevent the increase.

Further, according to the invention of claim 3, the mounting
The member is attached to the non-rotating portion at a position closer to the front side of the vehicle than at least the center of rotation of the disc, and the arm portion on the inlet side of the disc in the rotational direction of the arm portions of the attaching member is more than the arm portion on the outlet side. Is also disposed at least on the upper side, and the braking force of the friction pad is received by the arm portion on the outlet side in the rotational direction of the disc.

As a result, the entire caliper can be stably supported by the sliding pin and the pin hole located on the inlet side in the rotational direction of the disk in a state of being suspended from the arm portion on the inlet side of the mounting member.

Further, in the invention of claim 4, the mounting member is mounted on the non-rotating portion at a position at least near the rear side of the vehicle with respect to the center of rotation of the disc, and the disc among the arm portions of the mounting member is attached. The arm portion on the outlet side in the rotation direction is arranged at least above the arm portion on the inlet side, and the braking force of the friction pad is received by the arm portion on the inlet side in the rotation direction of the disc.

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

Furthermore, in the invention of claim 5, one of the sliding pin and the pin hole has a circular cross-sectional shape, and the other has a non-circular cross-sectional shape.

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

Further, in the invention of claim 6, the cross section of the pin hole is formed in a circular shape, and the sliding pin is formed to have a diameter smaller than that of the pin hole and has a flat surface on the outer peripheral surface. It is composed of circular pins.

As a result, a relatively large gap can be easily secured between the pin hole and the flat portion of the sliding pin. Further, by pressing the entire sliding pin using header processing or the like, a flat surface portion can be easily formed on the outer peripheral surface of the sliding pin.

In addition, in the invention of claim 7, the pin hole is formed in a circular sectional shape, and the sliding pin has a cylindrical bush on the outer peripheral surface formed to have a smaller diameter than the pin hole. The bushing 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 therebetween.

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

[0030]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

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

In the figure, 1 is a disk which rotates in the direction of the arrow A in FIG. 1 together with the wheels of an automobile, 2 is a mounting member provided on the inner side of the disk 1, and the mounting member 2 is shown in FIG.
As shown in FIG. 3, a pair of arm portions 2A, 2A that are separated in the rotational direction of the disc 1 and extend in the axial direction so as to straddle the outer periphery of the disc 1 and a coupling portion that couples the proximal end sides of the respective arm portions 2A. It is integrally formed with 2B and the like. And the mounting member 2
Is integrally attached to a knuckle portion (not shown), which is 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.
It is arranged at a position at least near the front side of the vehicle with respect to the rotation center O of the disk 1 (the axle of the vehicle). This allows
Of the arms 2A, the arm 2 on the entrance side of the disc 1 in the rotation direction
A is disposed above the arm portion 2A on the outlet side in the rotation direction.

Further, each arm portion 2A is provided with pin holes 3 and 3 for sliding pins 11 and 17, which will be described later.
Is formed as a bottomed circular hole having a substantially circular cross section and extending in the axial direction of the disc 1. Further, on the base end side (inner side) and the tip end side (outer side) of the arm portion 2A, the substantially U-shaped pad guide portions 2A1 and the torques protruding inward in the rotational direction of the disc 1 are provided. Receiver 2A2
(Both are shown only on the outer side).

Each arm portion 2A of the mounting member 2 is slidably engaged with each pad guide portion 2A1 by a back metal 23A of each friction pad 23, which will be described later, to move each friction pad 23 in the axial direction of the disc 1. In addition to slidably guiding, the torque from the disk 1 via each friction pad 23 is received by each torque receiving portion 2A2. In addition, a reinforcing beam 4 is formed on each arm 2A as shown in FIG. 1 so as to extend in a slender shape between them and integrally connect the tip ends of the arms 2A.

Reference numeral 5 denotes a caliper slidably supported with respect to the mounting member 2. The caliper 5 is, as shown in FIGS. 2 and 3, between the arms 2A of the mounting member 2 on the outer peripheral side of the disc 1. A bridge portion 6 extending so as to straddle the inner side of the disk 1, an inner leg portion 7 integrally formed on one side of the bridge portion 6 on the inner side, and an outer leg portion integrally formed on the other side of the bridge portion 6. 8 and a cylinder bore 7A is formed on the inner peripheral side of the inner leg portion 7.

On the inner leg 7, a pair of mounting portions 9, 9 located on both the left and right sides in FIG. 2 are provided so as to project in the rotation direction of the disc 1, and each mounting portion 9 has a protrusion. Each pin bolt hole 9A is bored on each projecting end side. The caliper 5 is attached to the respective pin bolt holes 9A through the pin bolts 16 and 21 described below, so that the caliper 5 can move the shaft of the disc 1 relative to each arm 2A of the mounting member 2. Mounted so that it can slide in any direction.

Here, as shown in FIGS. 1 and 2, the cylinder bore 7A has a center line O1 -O1 passing through the center thereof which is a center position between the pin holes 3 of the mounting member 2 and a center line O2 -O.
The disk 1 is disposed closer to the outlet side of the disk 1 in the rotational direction than the disk 2 with a size δ. The outer leg portion 8 is composed of a pair of bifurcated claw portions 8A and 8B.
The claw portion 8B of B is formed such that the wall thickness in the rotation direction of the disk 1 is larger than that of the claw portion 8A, and the rigidity of the claw portion 8B is increased as a whole.

Further, as shown in FIG. 2, in each of the mounting portions 9, engaging projections 10 and 10 extending in the radial direction of the disk 1 are formed at portions of the mounting member 2 on the side of the respective arm portions 2A. The engaging surfaces 15 and 20 of the sliding pins 11 and 17 are engaged with the engaging protrusions 10.

Reference numeral 11 denotes a slide pin provided on the mounting portion 9 of the caliper 5 positioned on the outlet side of the disc 1 in the rotation direction. The slide pin 11 is formed by press-molding a columnar material by header processing or the like. , As shown in FIGS. 2 and 4.

The sliding pin 11 is integrally formed with a shaft portion 11A which extends in the axial direction of the disk 1 and is slidably fitted in the pin hole 3 and one end side of the shaft portion 11A. The head portion 11B and the shaft portion 11A are formed to have a diameter slightly smaller than that of the pin hole 3. Further, the shaft portion 11A
Is a small-diameter portion 11C having a columnar shape in the middle part of which the diameter is reduced from the middle position in the length direction to the tip side, 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 generally oval cross-section as a whole, and a portion of the outer peripheral side extending in parallel along the axial direction forms a pair of flat surface portions 13 and 13, and the respective flat surface portions. A curved portion between 13 is an arc surface portion 14
Has become. As a result, the sliding pin 11 is moved to each flat surface portion 1
A relatively large gap is formed between the pin 3 and the pin hole 3, and a relatively small gap is formed between each arcuate surface portion 14 and the pin hole 3.

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

Here, each flat surface portion 13 of the sliding pin 11 and each engagement surface 15 are arranged so as to be substantially parallel to each other as shown in FIG. Therefore, by engaging the engagement surface 15 with the engagement protrusion 10 extending in the radial direction of the disc 1, the respective flat portions 13 of the sliding pin 11 cause the plane portions 13 to rotate in the rotation direction of the disc 1 (the direction of arrow A in FIG. 6). ), They are positioned in the pin hole 3 while facing each other.

As a result, between the sliding pin 11 and the pin hole 3, there is a relatively large gap in the rotation direction A of the disc 1, which is located between each flat surface portion 13 and the pin hole 3 , that is, sliding. pin
11 and the pin hole 3 are displaced in the rotation direction A of the disc 1.
A gap is formed to allow the movement, and a relatively small gap is formed in the radial direction of the disc 1 between each circular arc surface portion 14 and the pin hole 3.

Reference numeral 17 denotes a sliding pin provided on the mounting portion 9 of the caliper 5 located on the inlet side of the disc 1 in the rotational direction, and the sliding pin 17 has a shaft portion 17A as shown in FIGS. The head 17B and the abutment plate 17C are formed in substantially the same manner as the sliding pin 11. Also, the shaft portion 17A
Has each flat surface portion 18 and each circular arc surface portion 19, and further,
The abutment plate portion 17C has each engagement surface 20. And
With one of the engagement surfaces 20 engaged with the engagement protrusion 10 of the caliper 5, the sliding pin 1
7 is fastened to the mounting portion 9 via pin bolts 21 and the like.

However, the sliding pin 17 differs from the sliding pin 11 in that, as shown in FIG. 5, the respective flat portions 18 and the respective engaging surfaces 20 are arranged in directions substantially orthogonal to each other. There is. Therefore, when the engagement surface 20 is engaged with the engagement protrusion 10, the slide 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, between the sliding pin 17 and the pin hole 3, there is a relatively large gap in the radial direction of the disc 1, which is located between each flat surface portion 18 and the pin hole 3 , that is, the sliding pin. 17
And the pin hole 3 are arranged in opposite directions in the radial direction of the disc 1.
A gap that allows displacement is formed, and a relatively small gap is formed between each arc surface portion 19 and the pin hole 3 in the rotation direction A of the disc 1.

Reference numeral 22 is a piston slidably fitted in the cylinder bore 7A of the caliper 5, and the piston 22 is
The brake fluid pressure supplied from the outside into the cylinder bore 7A causes the cylinder bore 7A to be slidably displaced in the axial direction, and the friction pads 23 between the claw portions 8A and 8B of the outer leg portion 8 on both sides of the disc 1. It is to press.

Reference numerals 23 and 23 denote discs 1 by the caliper 5.
As shown in FIGS. 1 and 3, each friction pad 23 is a pair of friction pads that are pressed against both surfaces of the plate, and the backing plates 23A and 23A are fixed to the back surface of the friction pads 23 so as to overlap each other. . Then, in each friction pad 23, each back metal 23A is slidably supported by the pad guide portion 2A1 of the mounting member 2 so as to apply a braking force to the disc 1.
The caliper 5 presses both surfaces of the disk 1.

The disc brake according to the present embodiment is
It has the above-mentioned configuration, and its operation will be described below.

First, when the vehicle is braked, when the piston 22 slides and displaces toward the disc 1 by the brake fluid pressure supplied from the outside into each cylinder bore 7A of the caliper 5, the piston 22 causes the friction pad on the inner side to move. 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 pin 11,
It is displaced to the inner side with respect to the mounting member 2 via 17, and the outer side friction pad 23 is pressed against the disc 1 via the claw portions 8A and 8B of the outer leg portion 8. As a result, the braking force is applied to the disc 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 each friction pad 23 is bent so as to displace the outer side of the caliper 5 in the arrow A direction (hereinafter referred to as the rotational direction A). Since it acts as a moment, the surface pressure of the friction pad 23 against the disc 1 on the inner leg 7 side is smaller on the outlet side than the inlet side in the rotation direction A, and on the outer leg 8 side, the surface pressure of the friction pad 23 is smaller. Tends to be larger on the outlet side than on the inlet side.

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

When the brake is operated, as described above with reference to FIG. 13, the caliper 5 passes through the bridge portion 6 arranged on the outer peripheral side of the disc 1 by the torque from the disc 1 via each friction pad 23. Inner leg 7
Since the outer leg portion 8 and the outer leg portion 8 are integrally formed, the inner leg portion 7 and the outer leg portion 8 tend to elastically deform so as to expand, and thus the caliper 5 is provided. The sliding pin 17 tends to be displaced such that the tip end side is lower than the base end side with respect to the axial direction of the disc 1.

Further, as to the mounting member 2, since each friction pad 23 itself also tries to rotate by the torque from the disk 1 as described above with reference to FIG. 14, each friction pad 23 can be slidably displaced. Each arm 2A of the mounting member 2 to be supported has a disk 1 rather than each arm 2A by a screw hole 2B1 provided in the connecting portion 2B at the base end side thereof.
Since it is attached and fixed to the non-rotating portion of the vehicle on the inner diameter side of the vehicle, the arm portion 2A on the inlet side in the rotational direction of the disc 1 is elastically deformed so that the outer side rises with respect to the inner side in the axial direction of the disc 1. The arm portion 2A on the outlet side in the rotation direction of the disk 1 tends to elastically deform so that the outer side is lower than the inner side in the axial direction.

[0057] However in this embodiment, the clearance between the sliding pin 17 and the pin holes 3 of the inlet side, the slide pin 17 and the pin
A gap that allows the radial displacement of the disc 1 from the hole 3
The disk 1 is formed so that the space becomes large in the radial direction.
The torque of the clearance between the sliding pin 11 and the pin holes 3 on the outlet side for receiving via the friction pads 23, since formed to be smaller relative to the inlet side in the radial direction of the disk 1,
Even when the sliding pin 17 on the inlet side of the disc 1 and the pin hole 3 of the arm 2A are displaced in the radial direction of the disc 1 with respect to the inlet side in the rotational direction of the disc 1 during brake operation, even if the displacement occurs. only radial gap component secured between the rotating pin 17 and the pin holes 3 can allow relative displacement therebetween, both can be prevented from being so interfere strongly in the radial direction of the disk 1, which As a result , the sliding resistance between them can be reduced. At this time, the sliding pin 1 on the outlet side of the disc 1 is displaced in the same direction in the radial direction of the disc 1.
Since there is a small gap between 1 and the pin hole 3 of the arm portion 2A, it is possible to firmly prevent the caliper 5 from rattling with respect to the mounting member 2 in the radial direction of the disc 1.

Further, as in the present embodiment, the torque from the disc 1 via each friction pad 23 at the time of braking is applied to the arm on the outlet side of the disc 1 in the rotation direction of the arm 2A of the mounting member 2. In the case where the torque receiving portion 2A2 of the portion 2A receives the torque, the arm portion 2A on the outlet side receives the torque from the disc 1 via each friction pad 23, and as shown in FIG.
6 has a tendency to be slightly elastically deformed in the rotation direction A of the disk 1 as indicated by a chain double-dashed line, whereas the arm portion 2A on the inlet side receives torque from the disk 1 via each friction pad 23. Since it is not received, it tends to be hardly elastically deformed in the rotation direction of the disk 1.

[0059] However in this embodiment, the clearance between the sliding pin 11 and the pin holes 3 on the outlet side, the slide pin 11 and the pin
Allows misalignment of the disc 1 in the rotation direction with the hole 3
Since the gap is formed to be large in the rotation direction of the disc 1, and the gap between the sliding pin 17 on the inlet side and the pin hole 3 is formed to be small in the rotation direction of the disc 1 to the outlet side. Even when the arm portions 2A are expanded due to the torque of the disc 1 during brake operation and the pin hole 3 on the outlet side is displaced in the rotational direction of the disc 1, the pin hole 3 on the outlet side becomes the sliding pin 11. The relative displacement with respect to the sliding pin 11 can be allowed by the amount of the gap in the rotational direction of the disk 1 secured between the two . This can prevent the pin hole 3 and the sliding pin 11 from strongly interfering with each other and reduce the sliding resistance between them. Further, at this time, the sliding pin 1 on the inlet side, which is hardly elastically deformed in the rotation direction of the disk 1,
Since a small gap 7 and the pin hole 3, from rattling <br/> a rotational direction of the disk 1 caliper 5 to the mounting member 2 can be suppressed securely.

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

Further, when the mounting member 2 and the caliper 5 are arranged closer to the front side of the vehicle than the rotation center of the disk 1 (the axle of the vehicle) as in the present embodiment, the rotation direction A of each arm 2A is changed. 2A on the inlet side of the
Since it is arranged on the upper side, the entire caliper 5 is inserted through the pin hole 3 and the sliding pin 17 into the arm portion 2A on the inlet side.
It can be firmly supported in the state of being hung,
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 inlet side of the disc 1 in the rotational direction and the sliding pin 17 are displaced in the radial direction of the disc 1, or the disc 1 is rotated. and directions outlet side of the arm portion 2A affected torque from the friction pad 23, the pin hole 3 is displaced in the direction of rotation of the Shi pair slide pin 11 disk 1
Even interest can be smoothly slide the slide pins 11, 17 within each pin hole 3. As a result, it is possible to improve the feeling of operation during brake operation, and it is possible to reliably separate the friction pads 23 from the disc 1 even when the brake operation is released, so that it is possible to prevent the friction pads 23 from being dragged and to prevent the judder. It is possible to suppress the occurrence of such as the above, and also to improve the followability to the rotor surface runout of the disk 1 and the thermal deformation of the rotor sliding surface.

In addition, among the gaps between the sliding pins 11 and 17 and the pin hole 3, since there are small gaps between the arcuate surface portions 14 and 19 and the pin hole 3, the sliding pins 11 and 17 are small. 17
Although there is a relatively large gap between the respective flat surface portions 13 and 18 and the pin hole 3 for allowing the positional displacement during brake operation, the rattling of the caliper can be sufficiently suppressed. . As a result, the caliper 5 vibrates greatly with respect to the mounting member 2 due to the impact transmitted to the vehicle body during traveling even when the brakes are not applied.
7 and the friction pads 23 integrated with the caliper 5 can be held in a state where they are always separated from the disc 1. As a result, the cause of dragging of each friction pad 23 can be further eliminated, uneven wear or 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. Then, it is possible to suppress the generation of abnormal noise such as rattle noise as well as the generation of the shudder described above, and it is possible to perform comfortable traveling.

Furthermore, each pin hole 3 and sliding pins 11, 17
The gap between the caliper 5 and the sliding pin 1 is reduced by reducing the clearance required for suppressing the rattling of the caliper 5.
Since the gap between 1 and 17 is formed to be large to allow the positional deviation during brake operation, the weight of the caliper 5 is reduced as compared with the conventional case by the amount of the larger gap for allowing the positional deviation. It is possible to reduce the material cost and improve the riding comfort by reducing fuel consumption and unsprung load.

Furthermore, since the entire sliding pins 11 and 17 including the flat surface portions 13 and 18 are formed by using header processing or the like, special processing for forming the flat surface portions 13 and 18 is performed. 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 designated by the same reference numerals, and The description will be omitted. However, the feature of this embodiment is that
The cross-sectional shape of each pin hole 31, 32 provided in each arm 2A of the mounting member 2 is formed in a non-circular shape, and the shaft portion 33 of each sliding pin 33, 34 integrally provided in the caliper 5 is formed.
By forming the cross-sectional shape of A and 34A into a circular shape,
A gap between the pin hole 31 on the outlet side and the sliding pin 33 is formed larger in the rotational direction A than the radial direction of the disc 1, and a gap between the pin hole 32 on the inlet side and the sliding pin 34 is formed on the disc. It is formed to be larger in the radial direction than the rotation direction A of 1.

Here, the pin hole 31 is a bottomed circular hole extending in the lengthwise direction of the arm portion 2A of the mounting member 2 as in the case of each pin hole 3 described in the first embodiment. Has been formed. However, the pin hole 31 has an oval cross section (elliptical shape) as shown in FIGS.
On the inner peripheral side, a portion curved in a semi-circular shape is the circular arc portion 31.
A, 31A, and the portions extending substantially linearly between the arcuate hole portions 31A are the linear portions 31B, 31B.
The pin hole 32 is also formed in substantially the same manner as the pin hole 31, and has each arcuate portion 32A and each linear portion 32B.

Of the pin holes 31 and 32, the pin hole 31 on the outlet side is oriented so that the arcuate portion 31A side is oriented in the rotational direction A of the disc 1 and the pin hole 32 on the inlet side is formed.
Is oriented in the radial direction of the disk 1 on the side of each arcuate portion 32A.

The sliding pins 33 and 34 are formed in substantially the same manner as the sliding pins 11 and 17 described in the first embodiment, and the shaft portions 33A and 34A and the head portions 33B and 34B are formed.
And has abutting plate portions 33C and 34C. Further, the engaging projections 1 of the caliper 5 are attached to the abutting plate portions 33C and 34C.
Engaging surfaces 35 and 36 that engage with 0 are respectively formed.

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

As a result, of the sliding pins 33, 34, the sliding pin 33 on the outlet side has the arcuate portion 31 of the pin hole 31.
A relatively large gap in the direction of rotation A of the disc 1 between A and A, that is, the rotation of the disc 1 between the sliding pin 33 and the pin hole 31.
A gap that allows positional deviation in the rolling direction is formed, and a relatively small gap is formed between each linear portion 31B in the radial direction of the disc 1.

On the other hand, the sliding pin 34 on the inlet side has a relatively large gap in the radial direction of the disc 1 between each arcuate portion 32 A of the pin hole 32, that is, between the sliding pin 34 and the pin hole 32.
A gap that allows the disc 1 to be displaced in the rotational direction is formed, and the disc 1 is rotated in the rotational direction A between the linear portions 32B.
A relatively small gap is formed at

Thus, in this embodiment having such a structure, it is possible to obtain substantially the same operational effects as those of the first embodiment.

Furthermore, FIG. 12 shows the above-mentioned first and second.
As in the above embodiment, one of the shaft portion and the pin hole of the sliding pin is formed to have a substantially oval cross-sectional shape, and the gap between the sliding pin and the pin hole in the disk radial direction or the rotation direction is formed. Instead of providing the above, a modification in which a gap in the disk radial direction or the rotational direction is provided between the sliding pin and the pin hole while the cross-sectional shape of both the sliding pin and the pin hole is circular is shown. It is a thing.

In the figure, the shaft portion 43A of the sliding pin 43 is fitted into the pin hole 41 formed in the arm portion 2A of the mounting member 2 by inserting a cylindrical rubber bush 44 into the pin hole 41. It is fitted. Then, inside the rubber bush 44, two gap portions 45 are formed so as to be opposed to each other with the cylindrical hole 44A interposed therebetween so as to extend in the axial direction in conformity with the radial direction or the rotation 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 rotation direction of the disk 1. Thus, in the present modification as well, the above-described first and second portions are formed. It is possible to obtain substantially the same operational effects as the embodiment.

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

In each of the above embodiments, the disk 1
The torque receiving portion 2A2 of the arm portion 2A on the outlet side in the rotation direction receives torque from each friction pad 23. For example, the side surface of the backing plate 23A on the inlet side in the rotation direction of the disc 1 of each friction pad 23 A hook-like protrusion is formed on the upper part of the friction member, and each friction pad 2 is attached to the arm 2A of the mounting member 2 on the inlet 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 portion 2A on the inlet side of the disc 1 in the rotation direction, such as a groove formed by engaging the hook portion of the protrusion. However, a disc brake of this type may be arranged at least at a position closer to the vehicle rear side than the rotation center O of the disc 1 (the axle of the vehicle).

[0079]

As detailed above, according to the present invention, According to the present invention, a sliding pin you position in the rotational direction the inlet side of the disc
Between the pin hole, and the sliding pin and the pin hole of the disk
Since a gap that is larger in the radial direction than the rotational direction of the disc is formed to allow displacement in the opposite directions in the radial direction, it is affected by the torque from the pad during brake operation. mounting member is deformed Te, by or key Yaripa is deformed, the slide pin and the pin hole receiving this effect even caused the relative positional deviation in the radial direction of the disk, the rotational direction of the disk the gap between the pin hole and the sliding pin of the inlet side can tolerate misalignment between the pin hole and the sliding pin, thereby, it is possible to prevent the both interfere with each other, the sliding pin It can be slid smoothly in the pin hole. Moreover, during non-braking, the caliper can be prevented from rattling in the disk rotation direction and the radial direction between each pin hole and each sliding pin, and the caliper can be stably attached to the attachment member.

Therefore, it is possible to extend the service life of the disc and each friction pad by eliminating the causes of torque fluctuation during braking and dragging of the friction pad during non-braking, as well as improving fuel consumption, and judder, rattle noise, etc. It is possible to suppress abnormal noise and drive comfortably.

Further, in the invention of claim 2, the brake operation is
The torque from the disc through each friction pad at the time of production,
Of the arms of the mounting member, the arm on the exit side in the disc rotation direction
In the disc brake arrangement for nest in parts, with the sliding pin and the pin hole you position in the rotational direction the inlet side of the disc
Between, the slide pin and the pin hole and the radial direction of the disk
Between the sliding pin and the pin hole that is located on the outlet side in the rotational direction of the disc, forming a gap that is larger in the radial direction than the rotational direction of the disc in order to allow the displacement in opposite directions. the, di with the sliding pin and the pin hole
From <br/> forming the gap becomes larger in the rotation direction than the radial direction of the disk to permit the displacement of the rotational direction of the disk, the rotation between the arms of the mounting member is a disk at the time of braking operation Even if it is expanded in the direction of the disc, it is not possible to use the gap between the pin hole and the sliding pin provided in the arm on the outlet side in the disc rotation direction .
Thus , the positional deviation of the sliding pin and the pin hole in the rotation direction of the disc can be allowed, and it is possible to prevent the both from interfering with each other.

Therefore, it is possible to extend the service life of the disc and each friction pad by eliminating the causes of torque fluctuation during braking and dragging of the friction pad during non-braking, and also improve fuel consumption, such as judder and rattle noise. It is possible to suppress abnormal noise and drive comfortably.

Further, according to the invention of claim 3, the mounting
The member is attached to the non-rotating portion of the vehicle at a position at least near the front side of the vehicle with respect to the center of rotation of the disc, and among the arm portions of the attaching member, the arm portion on the inlet side of the disc in the rotational direction of the arm member is more than the arm portion on the outlet side. Since it is arranged at least on the upper side, and the braking force of the friction pad is received by the arm portion on the outlet side of the disc in the rotational direction, the entire caliper is attached by the sliding pin and pin hole located on the inlet side of the disc in the rotational direction. stabilized at a state of suspended arm of the inlet side can it to supported.

Further, in the invention of claim 4, the mounting member is mounted on a non-rotating portion of the vehicle at a position at least near the rear side of the vehicle with respect to the center of rotation of the disc, and the arm of the mounting member is mounted on the disc. Since the arm portion on the outlet side in the rotational direction is arranged at least above the arm portion on the inlet side and the braking force of the friction pad is received by the arm portion on the inlet side in the rotational direction of the disc, the entire caliper is rotated by the disc. the sliding pin and the pin hole is positioned in a direction outlet side, stabilized so can you to supported in a state of suspended arms of the outlet <br/> side of the mounting member.

Further, according to the invention of claim 5, one of the sliding pin and the pin hole has a circular cross-sectional shape and the other has a non-circular cross-sectional shape. The gap between the moving pin and the disc can be easily formed to have different sizes in the radial direction and the rotation direction of the disk, and the design of the gap can be easily performed.

Further, in the invention of claim 6, the pin hole is formed to have a circular cross section, and the sliding pin is formed to have a diameter smaller than that of the pin hole and has a substantially oval cross section having a flat surface portion on the outer peripheral surface. Since it is composed of pins, the entire sliding pin including the flat part is press-molded using header processing,
No special processing is required to form the flat portion, and workability at the time of manufacturing the sliding pin can be improved.

In addition, in the invention of claim 7, the pin hole is formed to have a circular cross-sectional shape, and the sliding pin has a cylindrical bush on the outer peripheral surface formed to have a smaller diameter than the pin hole. Since the sliding pin and the pin hole are fitted and inserted into the pin hole, and the bush has a gap extending in the axial direction facing each other with a cylindrical hole in between, the sliding pin and the pin hole can be easily machined in a circular cross section. You can keep the shape.

[Brief description of drawings]

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

2 is a plan view showing a disc brake in FIG. 1. FIG.

FIG. 3 is an enlarged sectional view taken along the line III-III in FIG.

FIG. 4 is a perspective view showing a single sliding pin in FIG.

FIG. 5 is a perspective view showing another sliding pin in FIG. 1 as a single body.

6 is an enlarged view of an essential part on the outlet side in the rotation direction of the disk, showing the pin hole and the sliding pin in FIG.

7 is an enlarged view of an essential part on the inlet side in the rotation direction of the disk, showing the pin hole and the sliding pin in FIG.

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

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

10 is an enlarged view of an essential part on the outlet side in the rotation direction of the disk, showing the pin hole and the sliding pin in FIG.

11 is an enlarged view of a main part on the inlet side in the rotation direction of the disk, showing the pin hole and the sliding pin in FIG.

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

FIG. 13 is an explanatory diagram showing a state in which a caliper of a disc brake according to a conventional technique is deformed when a brake is operated.

FIG. 14 is an explanatory view showing a state in which a mounting member of a disc brake according to a conventional technique is deformed when a brake is operated.

[Explanation of symbols]

1 disc 2 Mounting member 2A arm 3, 31, 32, 41 pin holes 5 calipers 11, 17, 33, 34, 43 Sliding pins 13,18 Plane 23 Friction pad 44 Rubber Bush (Bush)

─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Hideaki Ishii 1000 Yoshida, Kushigata-cho, Nakakoma-gun, Yamanashi Tokiko Co., Ltd. Yamanashi Plant (56) Bibliography 1-73530 (JP, U) -28367 (JP, U) Actual development 56-47920 (JP, U) Actual development 55-122542 (JP, U) Actual development 54-165682 (JP, U) (58) Fields investigated (Int.Cl . ⁷ , DB name) F16D 55/224 110 F16D 65/02

Claims (7)

(57) [Claims] 1. A mounting member which has a pair of arm portions which are spaced apart from each other in the circumferential direction of the disk and straddle the disk in the axial direction, and which is mounted on a non-rotating portion of a vehicle, and slides on each arm portion of the mounting member. And a caliper that presses a pair of friction pads against both sides of the disc, and a slide provided on the other member in a pin hole provided on one of the arm part and the caliper of the mounting member. in disk brake formed by inserting a rotating pin slidably, between the slide pin and the pin hole positioned in the rotational direction the inlet side of the disc, and the sliding pin and the pin hole the di
Allows displacement in opposite directions in the radial direction of the disk
Disc brake, characterized in that the formation of the gap to be larger in the radial direction than the rotational direction of because the disk. 2. A mounting member having a pair of arm portions which are spaced apart in the circumferential direction of the disc and straddle the disc in the axial direction, the mounting member being mounted on a non-rotating portion of a vehicle, and sliding on each arm portion of the mounting member. And a caliper that presses a pair of friction pads against both sides of the disc, and a slide provided on the other member in a pin hole provided on one of the arm part and the caliper of the mounting member. In a disc brake in which a dynamic pin is slidably inserted and the braking force of the friction pad is received by an arm portion on the outlet side in the rotational direction of the disc, the sliding pin and the pin located on the inlet side in the rotational direction of the disc Between the hole and the sliding pin and the pin hole,
Allows displacement in opposite directions in the radial direction of the disk
Forming a gap to be larger in the radial direction than the rotational direction of the order the disk, between the slide pin and the pin hole positioned in the rotational direction the outlet side of the disk, the sliding pin and the pin
A disc brake, characterized in that a gap larger in the rotational direction than in the radial direction of the disc is formed in order to allow the disc to be displaced from the hole in the rotational direction . 3. The mounting member is mounted on the non-rotating portion at a position at least near the front side of the vehicle with respect to the center of rotation of the disc, and among the arm portions of the mounting member, the arm portion on the inlet side of the disc in the rotational direction. 3. The disc brake according to claim 1, wherein the disc brake is arranged at least above the arm portion on the outlet side, and the braking force of the friction pad is received by the arm portion on the outlet side in the rotational direction of the disc. 4. The mounting member is mounted on the non-rotating portion at a position at least near the rear side of the vehicle with respect to the center of rotation of the disk, and among the arm portions of the mounting member, the arm on the outlet side in the rotational direction of the disk. The disc brake according to claim 1, wherein the portion is disposed at least above the arm portion on the inlet side, and the braking force of the friction pad is received by the arm portion on the inlet side in the rotational direction of the disc. 5. The method according to claim 1, 2, 3 or 4, wherein one of the sliding pin and the pin hole has a circular cross-sectional shape and the other has a non-circular cross-sectional shape. Disc brakes. 6. The pin hole is formed in a circular cross section, and the sliding pin is formed of a pin having a smaller diameter than that of the pin hole and having a flat surface on the outer peripheral surface and having a substantially oval cross section. The disc brake according to claim 1, 2, 3, or 4. 7. The pin hole is formed to have a circular cross section, and the sliding pin is fitted in a cylindrical bush on an outer peripheral surface formed to have a smaller diameter than the pin hole. The disc brake according to claim 1, 2, 3, or 4, wherein the disc brake is inserted and fitted, and a gap extending in the axial direction is opposed to the bush with a cylindrical hole therebetween.