KR100466133B1 - disk brake - Google Patents

Abstract

The present invention relates to a brake pad return structure of a disc brake, and slide grooves (15a) are formed on both inner surfaces of the caliper carrier (15), and slide projections on both sides of the back plate (16) to which the brake pads (17) are coupled. A wear sensor 61 having both ends protruding in the front-rear direction of the back plate 16 is coupled to the bottom of the slide protrusion 16a, and the slide protrusion 16a and the wear sensor 61 are formed. The disk is inserted into the slide groove (15a) is coupled to the linear movement, the guide pin 23 is inserted between the slide projection (16a) and the slide groove (15a) including the wear sensor 61 is coupled to the disk In the brake, one end of the wear sensor 61 protruding to the outside of the slide groove (15a) is formed in a plane and a coupling hole (61a) penetrating the upper and lower surfaces is formed in a predetermined portion spaced from the back plate (16) ; At both ends of the guide pin 23 toward the back plate 16, return springs 71 protruding toward the coupling holes 61a are formed, and at the ends of the return springs 71, the coupling The fitting portion 71a fitted into the hole 61a is formed while being bent at right angles to prevent uneven wear of the brake pad 17, thereby extending the life of the brake pad 17, and also By preventing thermal deformation of the disc 21 during braking, it is possible to reduce the braking noise and abnormal vibration as much as possible, and to prevent the phenomenon in which the braking force is reduced in advance, thereby improving the intermittent reliability.

Description

Brake pad return structure of disc brake

The present invention relates to a brake pad return structure of a disc brake, and in particular, the brake pad of the disc brake to smoothly return the brake pad during non-braking by the elastic restoring force of the return spring coupled to the wear sensor while being extended to the guide pin. It is about a return structure.

In general, a brake system is classified into a main brake mainly used for driving and a parking brake used for parking a car, and the main brake is configured to brake the hydraulic pressure generated by the operation of the brake pedal. Hydraulic brakes, heavy-duty brakes such as large vehicles, and air brakes for generating braking force by using compressed air pressure. There are disc brakes adapted to brake by hydraulic pressure on both sides of the rotating disk.

1 and 2, the disc brake is formed in a saddle shape of cast iron material and is attached to a caliper housing 11 attached to the knuckle spindle, and a cylinder mounted to the side of the caliper housing 11. (12), a piston (13) which is mounted on the inner peripheral surface of the cylinder (12) and moves in a straight line using hydraulic force, and a caliper coupled to the front surface of the caliper housing (11) via a guide rod (14). The carrier plate 15 and the back plate 16 coupled to the caliper carrier 15 by fitting the slide protrusions 16a formed on both sides into the slide grooves 15a formed on the caliper carrier 15 It is configured to include a brake pad 17 coupled to the front surface of the plate 16 to generate a braking force by the friction force while pressing both sides of the disk 21 when the piston 13 is operated using the hydraulic force do.

Here, the guide pins 23 are inserted into the slide grooves 15a formed in the caliper carrier 15, and the guide pins 23 have a structure that is fixed while being coupled with the caliper carrier 15.

The guide pin 23 blocks the direct contact between the slide protrusion 16a and the slide groove 15a in order to smoothly reciprocate the back plate 16.

Therefore, when the driver presses the brake pedal to generate the braking force, the pressure is applied to the master cylinder and the hydraulic pressure is pushed into the cylinder 12 to push the piston 13 out.

At this time, the piston 13 pushed toward the disk 21 is to linearly move the back plate 16 located in the support 18 of the caliper carrier 15, and thus the brake pad coupled to the back plate 16 17 is in close contact with one side of the disk 21.

In this way, the brake pad 17 which is stopped in contact with one side of the disk 21 is applied with a force in the direction of the cylinder 12 by the reaction, and the caliper carrier 15 and the guide rod 14 The caliper housing 11 connected through is pushed back as a whole, and the caliper housing 11 pushed back pushes the back plate 16 on the tightening jaw 19 toward the other side of the disk 21. The rest of the brake pads 17 coupled to the back plate 16 are brought into close contact with the other side of the disk 21, so that the rotating disk 21 is in contact with the brake pad 17. When the braking force is generated by friction, rotation stops.

In addition, when the braking of the vehicle is terminated and the driver releases the pedaling force applied to the brake pedal, the piston 13 is returned to its original position while the hydraulic pressure pushed into the cylinder 12 is released. At the same time, the brake pad 17 is also separated from the disk 21 and returned to its original position, thereby releasing the braking action.

However, in the structure of the general disc brake as described above, as the driving distance increases (as the wear of the brake pad increases), the return operation of the brake pad 17 gradually becomes poor, and thus, the brake pad during non-braking. It is often the case that a part of the (17) is in continuous contact without falling off the disk 21. As described above, when the brake pad 17 is in continuous contact without falling off the disk 21, the braking force is maintained. When it occurs, not only shortens the service life by causing the abrasion of the brake pad 17, but also accelerates the heat deformation of the disk 21, there is a problem that severe noise is generated and abnormal vibration phenomenon occurs.

Accordingly, in order to solve the above problem, as shown in FIG. 3, the coupling protrusion 16a is formed on the back plate 16, and the return spring 31 is mounted using the coupling protrusion 16b to prevent braking. One embodiment has been devised that facilitates the return operation of the brake pad 17.

However, one embodiment as described above has the advantage that the brake pad 17 is easily separated from the disk 21 by the elastic restoring force of the return spring 31 during non-braking to facilitate the return operation of the brake pad 17. However, the problem of poor workability still remains due to the difficulty of installation of workers.

In addition, in the structure of one embodiment, as the wear of the brake pad 17 increases, the tensile force of the return spring 31 also increases, so that the hydraulic force for operating the piston 13 is set at an initial set pressure (brake pad). To maintain the initial braking performance only when the hydraulic pressure that actuates the piston when it is not worn is reduced. In reality, the hydraulic force that actuates the piston 13 by the tension of the return spring 31 increases. However, the problem remains that the deterioration of the deterrent during the deterioration of the braking force is caused by the deterioration of the braking force.

On the other hand, Figure 4 and Figure 5 is another embodiment to facilitate the return operation of the brake pad 17 when the non-braking by using the ball bearing 42 installed on the brake pad 17.

That is, a plurality of mounting grooves 17a are formed on the surface of the brake pad 17 facing the disk 21, and the ball bearings 42 are respectively formed through the elastic member 41 in the mounting grooves 17a. Press-fit installation, and the structure to seal the lubrication member 43 to the installation groove (17a), the ball bearing 42 is a state in which a part of its outer peripheral surface slightly protrudes to the front of the brake pad 17 to be.

In another embodiment as described above, the tip of the ball bearing 42 facing the surface of the disk 21 is always in contact with the surface of the disk 21 by the restoring force of the elastic member 41, so that the brake pad 17 when not braking. ) Is easily spaced apart from the disk 21 to facilitate the return operation of the brake pad 17, but the dust of friction material generated by the wear of the brake pad 17 is reduced to the brake pad 17 and the ball bearing 42. There is a new problem that the ball bearing 42 is fixed to the surface of the disk 21 when the braking force is generated by fusion between them.

In addition, in another embodiment described above, the lubrication member 43 enclosed in the installation groove 17a partially applies the surface of the disk 21 through the ball bearing 42. Thus, the surface of the disk 21 When the lubrication member 43 is applied, the frictional force between the brake pad 17 and the disc 21 is reduced when the braking force is generated, which in turn causes a decrease in the braking force, thereby reducing the deterrent during the period.

Accordingly, the present invention has been made to solve all the above problems, by integrally forming a return spring on one side of the guide pin and the end of the return spring coupled with the wear sensor mounted on the back plate, When the brake pads gradually wear out due to the increase, the return operation of the brake pads starts to be poor. By using the restoring force of the return spring when the brakes are not braking, the brake pads can be smoothly returned. To provide the brake pad return structure of the disc brake, which can reduce the noise and abnormal vibration phenomenon generated at the time as well as prevent the reduction of the braking force in advance, thereby increasing the quality of the brake. There is this.

According to the present invention for achieving the above object, both sides of the inner surface of the caliper carrier is formed with slide grooves, both sides of the back plate to which the brake pads are coupled are formed with slide projections, both ends of the slide projection on the bottom surface of the back plate The wear sensor protruding in the front and rear direction of the is coupled, the slide protrusion and the wear sensor is coupled to the slide groove so as to move in a straight line, between the slide projection and the slide groove including the wear sensor is coupled to the guide pin is fitted. In the disc brake, one end of the wear sensor protruding to the outside of the slide groove is formed in a flat surface and a coupling hole penetrating the upper and lower surfaces is formed in a predetermined portion spaced from the back plate; Both ends of the guide pin toward the back plate toward the return spring is formed to protrude toward the coupling hole, the end of the return spring is characterized in that the fitting portion inserted into the coupling hole is formed while bending in a right angle. It is done.

1 and 2 are a perspective view and a longitudinal sectional view for explaining a disc brake generally used;

3 is a longitudinal sectional view for explaining a return structure of a brake pad according to a conventional embodiment;

4 and 5 are a front view and a longitudinal sectional view for explaining a return structure of a brake pad according to another embodiment of the prior art,

6 is a schematic exploded perspective view for explaining a return structure of a brake pad according to the present invention;

7 is a left side view of FIG. 6;

8 is a plan view of the coupled state of FIG.

9 to 11 are schematic side views for explaining a return operation process of the brake pad according to the present invention.

<Description of Symbols for Main Parts of Drawings>

15-Caliper Carrier 15a-Slide Groove

16-Backplate 16a-Slide Projector

17-Brake Pads 23-Guide Pins

61-wear sensor 61a-mating hole

71-return spring 71a-fitting

71b-bend

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Figure 6 is a schematic exploded perspective view for explaining the return structure of the brake pad according to the present invention, will be described with the same reference numerals to the same parts as the conventional structure.

The return structure of the brake pad 17 according to the present invention combines the wear sensor 61 mounted on the back plate 16 and the return spring 71 extending to the guide pin 23, thereby increasing the mileage. When the brake pad 17 gradually wears out and the return operation of the brake pad 17 starts to become poor during non-braking, the brake pad 17 is smoothly returned by using the elastic restoring force of the return spring 71. Its characteristics are that it has a structure to make.

That is, the general disc brake, as described above with reference to FIG. 1, is formed in a saddle shape of cast iron material and is attached to the caliper housing 11 and the cylinder 12 mounted on the side of the caliper housing 11. And a piston 13 which is mounted on the inner circumferential surface of the cylinder 12 and moves in a straight line using hydraulic force, and a caliper carrier coupled to the front surface of the caliper housing 11 by a guide rod 14. 15, a back plate 16 coupled to the caliper carrier 15 by fitting the slide projections 16a formed on both sides into the slide groove 15a formed on the caliper carrier 15, and the back plate 16 It is configured to include a brake pad 17 coupled to the front surface of the piston 13 to generate a braking force by the frictional force while pressing both sides of the disk 21 when the piston 13 is operated using the hydraulic force.

In addition, as shown in FIGS. 6 to 8, a wear sensor 61 (wearsensor) having both ends protruding in the front-rear direction of the back plate 16 is attached to the bottom of the slide protrusion 16a by welding. The wear sensor 61 is manufactured as steel, and when the brake pad 17 is worn over a certain amount, when the braking force is generated, the tip contacts the surface of the disk 21 to generate noise to generate a brake pad. It informs the driver of the replacement time of (17).

In addition, the guide pin 23 is coupled between the slide protrusion 16a including the wear sensor 61 and the slide groove 15a, and the guide pin 23 is fixed while being coupled with the caliper carrier 15. In addition, the guide pin 23 is a smooth straight line of the back plate 16 by blocking the slide protrusion (16a) and the wear sensor 61 in direct contact with the slide groove (15a) in the middle It plays a role in helping the round trip.

Meanwhile, as described above, the wear sensor 61 is coupled to the bottom of the slide protrusion 16a while overlapping, and both ends thereof protrude toward the front and rear directions of the back plate 16. The front end of the back plate 16, that is, one end projecting toward the brake pad 17, of the both ends of the 61 is located inside the slide groove 15a, and the other end is the rear side of the back plate 16, It protrudes outward of the slide groove 15a.

Here, one end of the wear sensor 61 protruding to the outside of the slide groove (15a) is formed in a plane as shown in Figs. 6 to 8 and also penetrates the upper and lower surfaces to predetermined portions spaced apart from the back plate (16). Rectangular engaging holes 61a are formed.

And, the guide pin 23 is inserted into the slide groove (15a) is coupled to the caliper carrier 15 so that both ends thereof toward the back plate 16, bar at both ends of the guide pin (23) As shown in FIG. 8, a return spring 71 protruding toward the coupling hole 61a of the wear sensor 61 extends, and the coupling hole 61a is formed at the end of the return spring 71. The fitting portion 71a fitted into the bend is formed while being bent in a right angle direction.

Here, the return spring 71 is produced as steel (steel) having its own elastic force.

In addition, when the fitting portion 71a of the return spring 71 is fitted into the coupling hole 61a, the coupling hole 61a is preferably located at the middle height of the fitting portion 71a. Between the sections extending from the pin 23 to the fitting portion 71a, the bent portion 71b is bent in a predetermined shape, and the curved portion 71b is formed while being directly connected to the fitting portion 71a. Most preferred.

On the other hand, the length L ₁ of the straight section from the interface with the back plate 16 to the coupling hole 61a among the entire length of the wear sensor 61 is the guide pin (of the entire length of the return spring 71). The structure is formed in the same dimension as the length L ₂ of the straight section extending from the boundary surface 23 to the fitting portion 71a.

In addition, the overall length L ₃ of the coupling hole 61a toward the end of the wear sensor 61 is linearly connected to the return spring 71 among the straight sections of the coupling hole 61a formed in the wear sensor 61. The thickness t and the predetermined length L ₄ of the formed fitting portion 71a are formed as a dimension.

That is, the total length L ₃ of the coupling hole 61a is t + 3mm, where t is the thickness of the fitting portion 71a and 3mm is the total length L ₃ of the coupling hole 61a. It is the predetermined length L ₄ remaining except the thickness t of the fitting part 71a.

Hereinafter, the return operation of the brake pad 17 according to the present invention will be described in detail with reference to FIGS. 9 to 11.

First, when the brake pad 17 is replaced with a new one, as shown in FIG. 9, the gap C between the brake pad 17 and the disc 21 at this time is a coupling hole formed in the wear sensor 61. a total length (L ₃₎ of smaller dimensions than the insertion portion (71a) a predetermined length (L ₄₎ with the exception of the thickness (t) of 61a) is to be formed.

In this state, when the driver presses the brake pedal to generate the braking force, the back plate 16 and the brake pad 17 which receive the force of the piston 13 (shown in FIG. 1) by hydraulic pressure are shown in FIG. 9. As shown in the dotted line, it is protruded while moving straight toward the disk 21. Accordingly, the brake pad 17 is in contact with the disk 21 to generate a braking force due to frictional force, thereby rotating the disk 21. This stops and the vehicle is braked.

On the other hand, as the mileage increases and decreases, the brake pad 17 gradually wears out, so that the distance C between the brake pad 17 and the disc 21 becomes the total length of the coupling hole 61a as shown in FIG. 10. When formed as a dimension larger than the predetermined length L ₄ other than the thickness t of the fitting portion 71a of the L ₃ , the brake pad 17 that has been moved toward the disc 21 during braking is released when the braking force is released. It does not return smoothly to its original position, and at this time, it is forcibly returned by the elastic restoring force of the return spring 71 according to the present invention.

That is, as shown in FIG. 10, the gap C between the brake pad 17 and the disc 21 is fitted between the total length L ₃ of the coupling hole 61a formed in the wear sensor 61. When it is formed as a dimension larger than the predetermined length (L ₄ ) other than the thickness t of), the driver presses the brake pedal at this time, before the brake pad 17 contacts the surface of the disk 21. The rear end of the coupling hole 61a formed in the wear sensor 61 comes into contact with the rear surface of the fitting portion 71a of the return spring 71, and the brake pad 17 finally comes into contact with the surface of the disk 21. When contacted, the fitting portion 71a of the return spring 71 maintains a state in which the return spring 71 is elastically curved toward the disc 21 as shown in FIG. 11 by the movement force of the wear sensor 61.

Accordingly, the brake pad 17 is smoothly braked because the brake pad 17 is in contact with the disc 21 to generate a braking force due to frictional force.

When the braking of the vehicle is ended and the driver releases the pedaling force applied to the brake pedal, the piston 13 is returned to its original position while the hydraulic pressure pushed into the cylinder 12 is released. At the same time, the fitting portion 71a of the return spring 71, which is elastically bent toward the disk 21, has the force to elastically restore to its original shape with the release of the hydraulic pressure that has applied the piston 13. As a result, the wear sensor 71 moved toward the disc 21 moves backward by the elastic restoring force of the fitting portion 71a.

As such, when the wear sensor 71 moves backward by the elastic restoring force of the fitting portion 71a, the back plate 16 coupled to the wear sensor 71 also moves backward and eventually the brake pad ( 17 is also returned from the disk 21 to its original position.

Therefore, the return operation of the brake pad 17 according to the present invention is formed in the coupling hole 61a of the wear sensor 61 mounted on the back plate 16 and the guide pin 23, and the coupling hole ( 61a) is made by the fitting portion (71a) of the return spring 71 is coupled to be fitted, according to the present invention can prevent the uneven wear of the brake pad 17 to extend the life of the brake pad 17 In addition, it is possible to prevent the thermal deformation of the disk 21 during braking of the vehicle, thereby reducing the braking noise and abnormal vibration phenomenon.

In addition, the return structure of the present invention has the advantage that the operator's convenience is greatly improved in configuring the return structure of the brake pad 17 as compared with the conventional embodiment described above with reference to FIGS. As a result, it is possible to prevent the phenomenon that the braking force is reduced in advance, thereby improving the qualitative quality.

As described above, according to the present invention, the return operation of the brake pad is performed by a wear sensor mounted on the back plate and a return spring extending to the guide pin, thereby preventing uneven wear of the brake pad, thereby providing a life of the brake pad. It is possible to extend the, and also to prevent the thermal deformation of the disk during braking of the vehicle can be reduced to the maximum noise and abnormal vibration phenomena, and to prevent the phenomenon of the braking force is reduced in advance to increase the stability during the It will work.

Claims (5)

Slide grooves 15a are formed on both inner surfaces of the caliper carrier 15, and slide projections 16a are formed on both sides of the back plate 16 to which the brake pads 17 are coupled. The bottom surface is coupled to the wear sensor 61, both ends protruding in the front and rear direction of the back plate 16, the slide projection (16a) and the wear sensor 61 is inserted into the slide groove (15a) can be moved linearly. In the disc brake is coupled so that the guide pin 23 is inserted between the slide projection (16a) including the wear sensor 61 and the slide groove (15a), One end of the wear sensor 61 protruding to the outside of the slide groove 15a is formed in a flat shape, and a coupling hole 61a penetrating the upper and lower surfaces is formed in a predetermined portion spaced from the back plate 16; At both ends of the guide pin 23 toward the back plate 16, return springs 71 protruding toward the coupling holes 61a are formed, and at the ends of the return springs 71, the coupling A brake pad return structure for a disc brake, characterized in that the fitting portion (71a) fitted into the hole (61a) is bent in a right angle. The return spring (71) according to claim 1, wherein the return spring (71) extends from the guide pin (23) to the fitting portion (71a) so that the coupling hole (61a) is located at the intermediate height of the fitting portion (71a). Brake pad return structure of the disc brake, characterized in that the bent portion (71b) formed between. The length L ₁ of the straight section extending from the interface with the back plate 16 to the coupling hole 61a of the overall length of the wear sensor 61 and the total length of the return spring 71. A brake pad return structure of a disc brake, characterized in that the length (L ₂ ) of the straight section from the interface with the guide pin (23) to the fitting portion (71a) is formed in the same dimension. The total length L ₃ of the coupling hole 61a facing the end of the wear sensor 61 is a sum of the thickness t of the fitting portion 71a and the predetermined length L ₄ . Brake pad return structure of the disc brake, characterized in that formed in the dimensions. 5. The brake pad return structure of claim 4, wherein the predetermined length (L ₄ ) is 3 mm.