JPS5921293Y2 - Pin slide type disc brake - Google Patents

Description

[Detailed description of the invention] The present invention relates to an improvement of a pin slide type disc brake, and in particular, it is capable of absorbing pitch errors between a pair of slide pins and their guide holes without hindering the easy movement of the caliper. It's about what you get.

One type of disc brake is called a pin slide type disc brake.

This is because, among a pair of pads placed on both sides of a rotating disc rotor, one pad is pressed against one side of the disc rotor by the action of a piston that is slidably fitted to a caliper, and the other pad is pressed against one side of the disc rotor by the action of a piston that is slidably fitted to a caliper. And the caliper
A pair of slide pins provided upright on either the arm portion of the caliper or a torque member attached to a fixed position are fitted with their guide holes to move while being guided, and the caliper is provided opposite to the piston. It is of a type that is pressed against the other side of the disc rotor by a claw portion.

In this type of disc brake, the pair of slide pins and their fitting holes are erected and drilled using the end surfaces of the caliper arm and the torque member as reference planes, but the pitch between the slide pins A mismatch in pitch between the guide types is likely to occur, which increases sliding resistance between the guide holes and the caliper, which may impede smooth movement of the caliper.

In order to avoid such a situation, it has been conventional practice to insert a rubber bushing between one slide pin and its guide hole.

In this way, the above-mentioned pitch discrepancy is absorbed by the elastic deformation of the rubber bushing, but on the other hand, since the metal and rubber are brought into direct contact, the coefficient of friction is lower than that between metals. It got bigger,
The reality is that it cannot be said that the sliding resistance when moving the caliper has been sufficiently reduced.

For this reason, in Utility Model Application No. 51-65188, it was proposed that the bushing should have a double structure of a rubber bushing and a rigid bushing, and the discrepancy between the slide pin and the guide hole would be absorbed by the rubber bushing, and the sliding would be performed on the surface of the rigid bushing. has been done.

However, if the bushing is made of a double structure, it is inevitable that the bushing will become thicker, so the guide hole has to be made larger, and the area around the guide hole becomes larger.

If the rubber bushing is made thinner to avoid this, the elastic deformability of the rubber bushing will be reduced, the contact pressure between the rigid bushing and the slide pin will increase, and the frictional force between them will eventually increase.

With this background in mind, the present invention was made with the purpose of providing a pin slide type disc brake that can absorb the pitch discrepancy between the slide pin and the guide hole, and can sufficiently reduce the sliding resistance when moving the caliper. The gist is that the sliding surface side is made of a metal or synthetic resin cylinder, and the non-sliding surface side is made of an elastic material between at least one of the pair of slide pins and its guide hole. A double cylindrical member consisting of a cylindrical body, in which a plurality of axial protrusions are interposed on at least one of the inner circumferential surface and the outer circumferential surface of the cylindrical body made of an elastic material. be.

In this way, the cylindrical body of the elastic material can be easily elastically deformed in the radial direction by the compressive deformation of the protrusions, so a relatively thin one is sufficient. It is possible to avoid the increase in size.

Moreover, since the sliding surface side is covered with a cylinder made of metal or synthetic resin, even if a protrusion is provided on the elastic material, the contact surface pressure only at the portion where the protrusion is provided will not particularly increase. Local progress of wear on the double cylindrical member can be avoided, and the frictional force can also be suppressed to a small level.

Incidentally, if only to increase the elastic deformation ability of the cylindrical body made of elastic material, protrusions may be provided in the circumferential direction, but in the present invention, the manufacturing and assembly of a double cylindrical member In order to facilitate this process, the protrusions are shaped in the axial direction.

In other words, when manufacturing a cylinder made of elastic material, the elastic material is manufactured singly and then assembled into a metal or synthetic resin cylinder, or the former is fixed to the latter by molding, but in either case. However, it is easier to manufacture the protrusions if they are formed in the axial direction.

In addition, when the protrusions are provided in the circumferential direction, it is difficult to assemble the elastic material cylinder and the metal or synthetic resin cylinder, or the elastic material cylinder and the guide hole or slide pin. In this case, the protrusion feels like it gets caught, making it difficult to assemble, and the protrusion is difficult to deform when subjected to force along the longitudinal direction, but easily deforms when subjected to force in the width direction. Therefore, when the protrusions are provided in the circumferential direction, the protrusions are elastically deformed in the width direction during assembly, and the elastically deformed protrusions return to their original shape at the final stage of assembly. By returning to the original position, a phenomenon occurs in which the elastic cylinder, once fitted to a sufficient depth, is slightly pulled out of the mating member, which also makes assembly difficult.

On the other hand, if the protrusions are shaped in the axial direction, such elastic deformation will be extremely small, and such assembly difficulties will not arise.

Hereinafter, one embodiment of the present invention will be described in detail based on the drawings.

In this embodiment, a slide pin is erected on the caliper arm,
The present invention is applied to a pin slide type disc brake in which a guide hole is bored in the torque member.

In FIGS. 1 to 3, 1 is a disc rotor that rotates together with a rotating body to be braked, and 2 is a torque member attached to a non-rotating member.

A pair of guide holes 15L and 15R are bored in this torque member 2 in a direction perpendicular to the plate surface of the rotor 1.

3 in the figure is a caliper disposed so as to straddle the disc rotor 1, and has a cylinder part 5 equipped with a piston 4 on one side, and the action of the piston 4 causes the pad 7 to move between the disc rotor 1 and the disc rotor 1. While pressing against one side, the caliper 3 moves to the left in FIGS. 1 and 3 while being guided by the engagement of the pair of slide pins 10L and IOR with the guide holes 15L and 15R due to the reaction, A claw portion 6 provided opposite to the piston 4
This presses the pad 8 against the other side of the disc rotor 1.

The slide pins IOL and IOR are erected perpendicularly to the end surfaces of the caliper arms 11L and 11R by screwing one end into the caliper arms 11L and 11R, respectively. Although both are similar, they differ in their functions and are therefore designed to suit each function.

That is, in FIG. 1, the upper slide pin 10L acts as the main slide pin, and therefore has a large diameter and only a slight clearance is provided between it and the guide hole 15L. do not have.

On the other hand, in the same figure, the lower slide pin IOR
has a small diameter and a relatively large clearance is provided between it and the guide hole 15R, and the bushing 20 is fitted into the approximately cylindrical space formed between the two.

As is clear from the figure, this fish 20 has a double structure consisting of two layers, the inner and outer layers, and the inner layer 21 and the outer layer 25 are
At the right end (in FIG. 1) of each inner layer 21
They are coupled to each other by engagement between an annular groove 23 formed on the outer peripheral surface of the outer layer 25 and an annular protrusion 27 formed on the inner peripheral surface of the outer layer 25.

Further, as shown in FIG. 4, a plurality of protrusions 26 are formed on the inner circumferential surface of the outer layer 25 in the axial direction.
1 is intended to be easily inserted and to increase its elastic deformability.

Further, the outer layer 25 of the bushing 20 has a large diameter portion 28 formed on the outer peripheral surface of the right end portion engaged with the large diameter portion 14 formed in the guide hole 15R, and the entire outer peripheral surface of the outer layer 25 is formed in the guide hole 15R. It is fixed to the guide hole 15R by being brought into close contact with the inner peripheral surface of the guide hole 15R.

That is, in this embodiment, the inner layer 21, which is on the sliding surface side when the caliper moves, is made of metal, and the outer layer 25, which is on the non-sliding surface side, is made of rubber.

In addition, 16L and 16R in the figure. 17 is boots, 18
is the piston seal.

Since the slide pin 10R of this embodiment is configured as described above, there are certain pitch errors between the slide pins 10L, 10R and the guide holes 15L, 15R, the pitch error between the slide pins 10L, the IORs, and the guide holes 15L, Slide pin 10L based on parallelism between 15R,
All the discrepancies between IOR and guide holes 15L and 15R are
This is absorbed by the elastic deformation of the outer layer 25 of the bushing 20.

Furthermore, when the caliper 3 moves, sliding occurs between the inner layer 21 of the bushing 20 and the slide pin IOR, but this is metal-to-metal contact, and the sliding resistance is different from that of the conventional slide pin. Caliper 3 is much smaller than when it slides in contact with rubber.
moves extremely easily.

At least one of the pair of slide pins that guide the movement of the caliper 3 has flexibility that can absorb mismatch between the slide pin and its guide hole, and low friction that does not impair sliding properties. It is necessary to satisfy two mutually contradictory properties, and for this purpose, it was conventionally thought that it was unavoidable to give priority to flexibility and sacrifice low friction to some extent, but as shown here, According to this embodiment, both of the above two contradictory requirements are suitably satisfied.

Another embodiment of the invention is shown in FIG.

In this embodiment, the inner layer 31 of the bushing 30 is rubber and the outer layer 35 is rubber.
This embodiment differs from the above embodiment in that the bush 30 itself is made of metal and moves integrally with the slide pin IOR.

In this case, slide pin 10L, IOR and guide hole 1
5L and 15R (see Figure 1) is absorbed by the inner layer 31 made of rubber, and the contact with the torque member 2 is made by the outer layer 35 made of metal.
Similar to the above embodiments, the object of the present invention is well achieved.

Yet another embodiment of the invention is shown in FIG.

This embodiment differs from the above embodiments in that a slide pin 10R is erected in the torque member 2 and a guide hole 15R is bored in the caliper arm 11R, and the inner layer 41 is metal and the outer layer 45 is rubber. Boots 40, which was considered to be 17.1
It is attached by being clamped from both sides by 8.

The aforementioned drawbacks of pin slide type disc brakes are also common to this type of disc brake, and according to the present invention, the drawbacks of this type of disc brake can be similarly eliminated.

In addition, in each of the above examples, the bushing is 20.30°40
The sliding surface side of each of these was made of metal, but as mentioned above, the sliding surface side only needs to be made of a material with a low coefficient of friction, and the metal in each example was replaced with synthetic resin. You can also.

Furthermore, each of the above embodiments includes a pair of slide pins 10.
In this case, the bushing 20.30.40 was interposed between one of the slide pins IOR and its guide hole 15R among the slide pins 10L and 10R, but both slide pins 10L,
A bushing 20. is installed between the IOR and the guide holes 15R and 15L.
It is also possible to interpose 30 and 40, which has the advantage of widening the range in which discrepancies between the two can be accommodated.

[Brief explanation of the drawing]

FIG. 1 is a plan view (partially cut away) showing an embodiment of the present invention;
Figure 2 is the same front view, Figure 3 is ■II in Figure 1.
-III sectional view, FIG. 4 is a IV-IV sectional view in FIG. 1, and FIG. 5 is a sectional view of main parts showing another embodiment of the present invention,
FIG. 6 is a plan view illustrating a main part of still another embodiment of the present invention in cross section. 1... Disc rotor, 2... Torque member, 3... Caliper 4... Piston, 5... Cylinder part, 6... ...claw part,
7, 8...Pad, IOL, IOR...
・Slide pin, 11 L, 11 R... Caliper arm, 15 L, 15 R... Guide hole,
20.30.4tJ・・・Butush, 2L 31
．． 41...Inner layer, 25.35.45...
・Outer layer, 26... Protrusion ridge, 23... Annular groove, 2
7... Annular projection, 14.28... Merchant's diameter.

Claims (1)

[Claims for Utility Model Registration] One of the pads disposed on both sides of the disc rotor is pressed against one side of the disc rotor by the action of a piston that is slidably fitted to the cylinder part of the caliper, and due to the reaction, The caliper moves while being guided by the engagement of a pair of slide pins and their guide holes.
In a pin slide type disc brake in which the other pad is pressed against the other side of the disc rotor by the claws of the caliper, there is a space between at least one of the pair of slide pins and its guide hole, the sliding surface of which is made of metal or synthetic material. It is a double cylindrical member consisting of a cylinder made of resin and a cylinder made of an elastic material on the non-sliding surface side, and a plurality of tubes are formed on at least one of the inner peripheral surface and the outer peripheral surface of the cylinder made of the elastic material. A disc brake characterized by having an interposed protrusion in the axial direction.