JP6803953B2 - Disc brake device - Google Patents

Description

The present invention relates to a disc brake device, and more particularly to a type of disc brake device called a negative type that generates a braking force when not operating.

When a disc brake device is used to hold a rotating body in an industrial machine, etc., a negative type disc brake device that directly uses the load of a disc spring as a braking force generally uses a hydraulic force to release the braking force. Known for However, as a system for the entire negative type disc brake device, it is desired to eliminate the space and piping for adopting the hydraulic mechanism and to reduce the size and simplification.

Here, in a disc brake device, as a method of applying a force to a piston by means other than hydraulic pressure, a technique using a cam as disclosed in Patent Document 2 and Patent Document 3 is known. In the disc brake device disclosed in Patent Document 2, an eccentric camshaft is arranged in a through hole provided on the side surface of the piston, and the eccentric camshaft is rotated to apply a pressing force to the piston. Has been done. Further, in the disc brake device disclosed in Patent Document 3, a cam lever is arranged at the rear end of the piston, and the piston is pushed out and a pressing force is applied by rotating the cam lever.

Jikkai Sho 52-11187 Japanese Unexamined Patent Publication No. 2011-27132 Special Table No. 10-507811

An object of the present invention is to provide a disc brake device capable of slimming down the disc brake device and improving the degree of freedom in the installation position of the disc brake device in a negative type disc brake device.

The disc brake device of the present invention for achieving the above object is a disc brake device in which a piston arranged in a cylinder formed in a caliper body presses a brake pad by receiving a pressing force from an operating spring. The piston is provided with a cam portion that releases the pressing force of the piston by inputting a rotational force, the piston is provided with an adjust pin for adjusting the position of the brake pad, and the operating spring in the caliper body is arranged. The claw portion connected to the body body via the bridge portion is provided with an actuator for inputting rotational power to the cam portion.

Further, in the disc brake device having the above characteristics, the operating spring is a laminated disc spring, and the through hole provided in the center of the disc spring slides in the axial direction of the rotor with respect to the caliper body. It is preferable that the holding shafts supported at both ends are arranged so as to be movable.

With such a feature, there is no possibility that the disc springs arranged in a laminated manner are displaced, and the position of the piston or the like can be adjusted by the holding shaft.

Further, in the disc brake device having the above-mentioned characteristics, it is preferable that the power input portion of the cam portion and the actuator are connected by a connecting member through which the hole portion provided in the caliper body is inserted.

By having such a feature, the movable portion is not exposed to the outside. Therefore, there is no risk of malfunction due to adhesion of dust or the like.

Further, in the disc brake device having the above-mentioned characteristics, the actuator can be an air chamber that operates the connecting member by the force of air.
With such a feature, it is possible to simplify the configuration of the actuator that operates the rotational power input unit of the cam unit. Further, since the connecting member is operated by the operation of the air chamber, the responsiveness is good.

Further, in the disc brake device having the above-mentioned characteristics, the actuator may be a motor gear unit that applies an operating force in a direction of releasing the pressing force to the rotational power input unit via the connecting member.

With such a feature, it is possible to eliminate the piping around the actuator. In addition, tanks and compressors that store fluids for operating actuators can be eliminated.

Further, in the disc brake device having the above characteristics, the motor gear unit is provided with a ball screw that rotates by the operation of the motor gear unit and a ball nut that moves along the ball screw, and the ball nut is used to the ball nut. The connecting member can be extruded.

By having such a feature, it is possible to release the pressing force of the operating spring even when the generated torque of the motor gear unit is small.

Further, in a disc brake device having the above-mentioned characteristics, the holding shaft has a screwed portion between the holding shaft and the piston, and one of the end portions of the holding shaft has the caliper via the piston. It is preferable that the structure is such that the gap between the brake pad and the brake pad can be adjusted through the screwed portion while sliding on the body.

According to these characteristics, even if the brake pads are worn and the gap between the rotor and the pads becomes large, it is possible to adjust the sliding range of the piston so that it is in the proper position. it can.

According to the disc brake device having the above characteristics, the disc brake device can be slimmed down. Therefore, the degree of freedom in the installation position of the disc brake device can be improved.

It is a figure which shows the front structure of the disc brake device which concerns on 1st Embodiment. It is a figure which shows the structure of the right side surface of the disc brake device which concerns on 1st Embodiment. It is a partial cross-sectional view which shows the arrow view of AA in FIG. It is a partial cross-sectional view which shows the BB arrow view in FIG. It is a partially enlarged view for demonstrating the cam mechanism. It is an exploded perspective view which shows the structure of the disc brake device which concerns on 1st Embodiment. It is a partial cross-sectional view which shows the structure of the disc brake device which concerns on 2nd Embodiment. It is a partially disassembled perspective view which shows the structure of the disc brake device which concerns on 2nd Embodiment. It is a perspective view which shows the structure of the disc brake device which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the ABCD cross section in FIG. 9 is a cross-sectional view showing a state in which the brake is operating in the configuration of the EFGH cross section in FIG. 9. 9 is a cross-sectional view showing a state in which the brake is released in the configuration of the EFGH cross section in FIG. 9 is a cross-sectional view showing a state in which only the ball nut and the nut holder are pulled back in the configuration of the EFGH cross section in FIG.

Hereinafter, embodiments of the disc brake device of the present invention will be described in detail with reference to the drawings. In the drawings, FIG. 1 is a diagram showing a front configuration of the disc brake device according to the first embodiment. Further, FIG. 2 is a diagram showing the configuration of the right side surface in FIG. 1. FIG. 3 is a partial cross-sectional view showing the arrow AA in FIG. FIG. 4 is a partial cross-sectional view showing the arrow BB in FIG. Further, FIG. 5 is a partially enlarged view for explaining the cam mechanism. Further, FIG. 6 is an exploded perspective view showing the configuration of the disc brake device according to the first embodiment.

The disc brake device 10 according to the first embodiment is configured and supported on the basis of having a caliper body 12, two brake pads (piston side pad 50, claw side pad 56), and an air chamber 62 in appearance. It is supported by a fixing portion (not shown) via 66.

The caliper body 12 basically has a body body 14, a claw portion 18, and a bridge portion 16. The body body 14 is provided with a cylinder 20 and a support portion 22, and a case 24 is provided on a side surface located on the side opposite to the surface facing the rotor 70 to form a bore 26 as an internal space. A sliding portion 30 of a piston 28, which will be described in detail later, is arranged on the cylinder 20. Further, an actuating spring 36, a cam mechanism 42, and the like are arranged in the bore 26.

The piston 28 according to the embodiment is composed of a sliding portion 30 and an interlocking portion 32, and a reaction force receiving 34 is provided on the outer periphery of the interlocking portion 32. The reaction force receiving 34 is a portion to which a reaction force for releasing the pressing force by the operating spring 36 is applied, and is arranged at a position facing the support portion 22 provided on the body main body 14. With such an arrangement configuration, the pressing force by the operating spring 36 can be released by pressing the reaction force receiver 34 with the support portion 22 as the base point. Further, a flat surface 32a formed along the projecting direction is provided on the side portion of the interlocking portion 32 (see FIG. 6). When the cam portion 44b, which will be described in detail later, comes into contact with the flat surface 32a, the cam portion 44b, which is supported by the support portion 22, serves as a detent for the piston 28.

A through hole 30a provided with a female screw is formed on the inner peripheral side of the sliding portion 30, and an adjusting pin 38 is screwed into the female screw of the through hole 30a. The adjust pin 38 adjusts the gap when the piston side pad 50 and the claw side pad 56, which are brake pads, are worn, and adjusts the piston 28 so that it is located in an appropriate operating range. It also serves as a holding shaft for laminating and holding the disc spring as the spring 36. One end of the adjusting pin 38 is in contact with the piston-side pad 50, and the other end is configured to have a length protruding outward of the case 24. Therefore, the adjustment pin 38 is arranged so as to penetrate both the sliding portion 30 and the interlocking portion 32 of the piston 28 in the axial direction of the piston 28. Therefore, the adjusting pin 38 is slidably supported at both ends with respect to the caliper body 12 in the axial direction of the rotor 70 via the piston 28.

The actuating spring 36 is a pressing means for pressing the piston 28. In the present embodiment, a plurality of disc springs through which the other end of the adjusting pin 38 screwed into the piston 28 is inserted are stacked and arranged. The actuating spring 36 is arranged between the sliding portion 30 of the piston 28 and the inner peripheral surface of the case 24 constituting the bore 26. The pressing force of the operating spring 36 is adjusted by the adjusting bolt 40 screwed to the end of the case 24 after fixing the case 24 to the body body 14. The tip of the adjusting bolt 40 is projected inside the case 24, and by tightening the bolt head, the operating spring 36 is pressed to amplify the repulsive force (pad pressing pressure) of the operating spring 36.

The cam mechanism 42 is an element that pushes back the reaction force receiver 34 from the support portion 22 as a base point between the support portion 22 in the body body 14 of the caliper body 12 and the reaction force receiver 34 in the interlocking portion 32 of the piston 28. Is. The cam mechanism 42 of the present embodiment is basically composed of a cam portion 44 and a lever portion 46. The cam portion 44 is provided so as to correspond to each of the two reaction force receivers 34 provided in pairs via the piston 28.

The cam portion 44 according to the embodiment includes a cam outer peripheral portion 44b which is a center of rotation and a cylindrical pin 44a arranged on the inner peripheral side of the cam outer peripheral portion 44b. The pin 44a has a length that matches the width of the outer peripheral portion 44b of the cam. Further, the cam outer peripheral portion 44b includes an arc surface centered on the pin 44a as a sliding surface with the indicator portion 22. Since the thickness of the outer peripheral portion 44b of the cam is made different along the arc surface, the distance from the pin center to the arc surface is continuously changing. R1 to r3, which indicate the distance from the center point O shown in FIG. 5, have a relationship of r1 <r2 <r3.

With such a configuration, the distance between the support portion 22 and the reaction force receiver 34 can be changed by moving the cam outer peripheral portion 44b located between the support portion 22 and the reaction force receiver 34 so as to change the thickness. That is, when a portion on the r1 side where the thickness of the outer peripheral portion 44b of the cam is thin is arranged between the support portion 22 and the reaction force receiver 34, the operating spring 36 is attached to the piston side pad 50, which will be described in detail later. The pressing force will work. On the other hand, when a thick r3 side portion of the cam outer peripheral portion 44b is arranged between the support portion 22 and the reaction force receiver 34, the pressing by the operating spring 36 acting on the piston side pad 50 The pressure will be released. In the assembled state, the cam portion 44 according to the embodiment reduces the thickness of the portion located on the radial outer peripheral side of the rotor 70, and increases the thickness of the portion located on the radial inner peripheral side of the rotor 70. As described above, the thickness is continuously different.

In the present embodiment, the width d between the contact point P1 with the support portion 22 and the contact point P2 with the reaction force receiver 34 in the cam portion 44 is configured to be smaller than the diameter of the pin 44a. ing. This is to efficiently transmit force.

A lever portion 46 that connects the two cam outer peripheral portions 44b across the piston 28 is connected to a portion of the cam outer peripheral portion 44b that is thin (a portion located on the outer peripheral side in the radial direction of the rotor 70). The lever portion 46 serves as a rotational power input portion for rotating the eccentric member 44b by tilting the rotor 70 in the axial direction. In the present embodiment, by tilting the lever portion 46 in the direction away from the rotor 70, the cam outer peripheral portion 44b can be rotated in the direction in which the pressing force by the operating spring 36 is released.

Further, in the present embodiment, the sliding member 48 is arranged between the support portion 22, the outer peripheral portion of the cam 44b, and the eccentric member 44b and the pin 44a, respectively, in order to reduce the resistance during sliding. The sliding member 48 may be a bearing with rollers or an OILES bearing, and is not particularly limited.

The piston side pad 50 is arranged on the surface of the body body 14 facing the rotor 70. The piston side pad 50 is basically composed of a lining 52 which is a friction member and a pressure plate 54 made of a steel plate, and the adjustment pin 38 is in contact with the pressure plate 54.

The claw portion 18 is arranged to face the body main body 14, receives the pressing force via the piston 28, and plays a role of sandwiching the rotor 70 between the piston side pad 50 and the claw side pad 56. Therefore, the claw side pad 56 is arranged on the surface of the claw portion 18 facing the rotor 70. The claw side pad 56 is basically composed of the lining 58 and the pressure plate 60, like the piston side pad 50 described above, and the pressure plate 60 is fastened to the claw portion 18.

Further, in the disc brake device 10 according to the present embodiment, the operating force is input to the lever portion 46 of the cam mechanism 42 on the outer peripheral side of the claw portion 18, that is, the side surface located on the side opposite to the side surface on which the rotor 70 is arranged. An air chamber 62 as an actuator for the purpose is arranged. By providing the air chamber 62 on the outer peripheral portion on the claw portion 18 side, the body body 14 and the bridge portion 16 can be slimmed down. By connecting the rod 64 to the lever portion 46 of the cam mechanism 42, the air chamber 62 can operate the cam mechanism 42 according to the expansion and contraction of the rod 64.

The bridge portion 16 plays a role of connecting the body body 14 and the claw portion 18 across the rotor 70. The bridge portion 16 in the present embodiment is provided with a through hole 16a along the axial direction of the rotor 70. The through hole 16a communicates the outer circumference of the claw portion 18 with the bore 26 formed in the body body 14, and allows the rod 64 in the air chamber 62 to be inserted therethrough.

With such a configuration, the cam mechanism 42 and the rod 64, which are movable parts, are not exposed to the outside. Therefore, there is no possibility that dust adheres to the movable portion and the sliding portion, which hinders the operation.

In the disc brake device 10 having the above configuration, a pressing force is applied to the piston 28 by the action of the operating spring 36 in the non-operating state. Therefore, the adjusting pin 38 screwed into the piston 28 presses the pressure plate 54 of the piston side pad 50, and the lining 58 of the piston side pad 50 is pressed against the sliding surface of the rotor 70.

When the lining 58 of the piston side pad 50 is pressed against the sliding surface of the rotor 70, the body body 14 of the caliper body 12 slides in a direction away from the rotor 70 due to the reaction force against the pressing. At this time, since the claw portion 18 is connected to the body main body 14 by the bridge portion 16 straddling the rotor 70, the claw portion 18 slides in a direction close to the rotor 70.

Therefore, the lining 58 of the claw side pad 56 arranged on the surface of the claw portion 18 facing the rotor 70 is pressed against the sliding surface of the rotor 70. By such an action, the rotor 70 is in a state of being sandwiched between the piston side pad 50 and the claw side pad 56, and the state in which the braking force is applied is maintained.

Next, when the air chamber 62, which is an actuator, is operated, the rod 64 projects toward the body body 14. As the rod 64 protrudes, the lever portion 46 of the cam mechanism 42 tilts in the direction of arrow a (see FIG. 3). When the lever portion 46 is tilted, the eccentric member rotates in the direction of arrow b (see FIG. 3) with the center O of the pin 44a as a base point, and the reaction force receiver 34 is rotated by arrow c (see FIG. 3) due to the change in thickness thereof. Push back in the direction of. By pushing back the reaction force receiver 34, the piston 28 slides in the direction of releasing the pressing force of the operating spring 36. As a result, the pressing of the piston side pad 50 pressed by the adjustment pin 38 and the pressing of the claw side pad 56 are released.

According to the disc brake device 10 according to the present embodiment, the pressing force of the operating spring 36 can be released by the action of the cam mechanism 42 without using the hydraulic pressure. Further, the cam mechanism 42 receives the pressing force of the operating spring 36 in the thickness direction of the eccentric member 44b. Therefore, the durability of the cam mechanism 42 can be improved as compared with the case where a pressing force is applied to the side surface of the rotating shaft as in the cam mechanism disclosed in the prior art.

Next, a second embodiment according to the disc brake device of the present invention will be described with reference to FIGS. 7 and 8. Most of the configurations of the disc brake device 10A according to the present embodiment are the same as those of the disc brake device 10 according to the first embodiment described above. Therefore, the parts having the same configuration are designated by the same reference numerals in the drawings, and detailed description thereof will be omitted.

In the disc brake device 10A according to the present embodiment, the arrangement form of the cam mechanism 42 is different from that of the first embodiment. Specifically, in the disc brake device 10 according to the first embodiment, the arc of the eccentric member 44b is arranged toward the body main body 14, and the pin 44a is brought into contact with the reaction force receiver 34. On the other hand, in the disc brake device 10A according to the present embodiment, the arc of the eccentric member 44b is arranged toward the reaction force receiving 34 side, and the pin 44a is brought into contact with the support portion 22.

When the cam mechanism 42 is arranged in this way, the action of the rotation of the cam portion 44 when the lever portion 46 is tilted is reversed. Therefore, the cam portion 44 of the present embodiment is configured to increase the thickness of the portion located on the outer peripheral side in the radial direction of the rotor 70 and decrease the thickness of the portion located on the inner peripheral side in the radial direction of the rotor 70. ing. The lever portion 46 is connected to the thick portion.

Further, due to the difference in the arrangement form of the eccentric member 44b and the pin 44a, the form of the contact surface between the support portion 22 and the reaction force receiving 34 is also different. This is to stabilize the arrangement state of the cam outer peripheral portion 44b and the pin 44a. Further, in the present embodiment, the support portion 22 is configured to be separate from the body main body 14. The support portion 22 arranged on the body main body 14 is configured to abut on the side portion of the interlocking portion 32 of the piston 28 with respect to the flat surface 32a formed along the projecting direction. Therefore, the support portion 22 serves as a detent for the piston 28.

Even when the cam mechanism 42 is configured in this way, the same effect as that of the disc brake device 10 according to the first embodiment can be obtained. The other constituent actions and effects are the same as those of the disc brake device 10 according to the first embodiment described above.

Next, a third embodiment according to the disc brake device of the present invention will be described with reference to FIGS. 9 to 13. 9 is a perspective view showing the configuration of the disc brake device according to the embodiment, and FIG. 10 is a diagram showing the configuration of the ABCD cross section in FIG. 9. 11 to 13 are views showing the configuration of the EFGH cross section in FIG. 10.

Most of the configurations of the disc brake device 10B according to the present embodiment are the same as those of the disc brake devices 10 and 10A according to the first and second embodiments described above. Therefore, the parts having the same configuration are designated by the same reference numerals in the drawings, and detailed description thereof will be omitted.

In the disc brake device 10B according to the present embodiment, the actuator configuration is different from the disc brake devices 10 and 10A according to the first and second embodiments described above. Specifically, in the disc brake device 10B according to the present embodiment, the actuator is a motor gear unit 80, and the ball screw unit 90 is attached to the motor gear unit 80 to form a lever portion 46 constituting the cam mechanism 42. The rod 64, which is a connecting member of the above, is pushed and pulled.

The motor gear unit 80 includes a motor 82 and a gear unit 84 for transmitting the rotational force of the motor 82 to a ball screw 92, which will be described later. The gear unit 84 is composed of a plurality of gears arranged in the casing 86, and generates torque for rotating the ball screw 92 by changing the gear ratio.

The ball screw unit 90 is basically composed of a ball screw 92, a ball nut 94, an electromagnet 96, an electromagnet plate 98, and a casing 100. The ball screw 92 is a rotating shaft in which the rotational force of the motor 82 is transmitted from the motor gear unit 80 described above. The ball nut 94 is a slider that moves on the ball screw 92 along the axial direction of the ball screw 92 by rotating the ball screw 92. By adopting such a mechanism, it is possible to rotate the ball screw 92 and release the pressing force of the operating spring 36 even if the torque generated by the motor 82 and the gear unit 84 is small. Become.

A nut holder 94a is attached to the ball nut 94 according to the embodiment. The nut holder 94a moves with the operation of the ball nut 94, presses the electromagnet plate 98, and receives the pressing force of the preset spring 94b arranged between the casing 100 and the nut holder 94a. When the ball nut 94 is moved to the side where the motor gear unit 80 is arranged, the preset spring 94b pushes back the nut holder 94a when the power supply to the motor 82 is cut off, and puts the ball nut 94 in the initial position. It plays a role of returning.

The electromagnet 96 is provided on the side of the ball screw unit 90 where the caliper body 12 is arranged, and plays a role of attracting the electromagnet plate 98. The electromagnet plate 98 may be a flat plate made of a magnetic material that is attracted by the operation of the electromagnet 96. Further, the electromagnet plate 98 is a plate to which the rod 64 is fastened, and when the electromagnet plate 98 moves in the axial direction of the ball screw 92, the rod 64 is pushed out or pulled back. A guide stud 100a is arranged between the electromagnet 96 and the casing 100 so as to penetrate the nut holder 94a and the electromagnet plate 98. When the preset spring 94b described above is arranged between the nut holder 94a and the casing 100, it is preferable to arrange the preset spring 94b so as to surround the guide stud 100a.

The casing 100 is an outer shell that houses the above-mentioned ball screw 92, ball nut 94, nut holder 94a, electromagnet 96, electromagnet plate 98, preset spring 94b, and guide stud 100a.

In the disc brake device 10B having such a configuration, when the nut holder 94a and the electromagnet plate 98 are both located at the initial positions (on the side where the motor gear unit 80 is arranged) as shown in FIG. 11, the operating spring 36 is pressed. The state where pressure is applied, that is, the state where the brake is operating. From such a state, by driving the motor 82 to operate the motor gear unit 80, the ball screw 92 in the ball screw unit 90 is rotated in the forward rotation direction (for example, clockwise rotation). As a result, the ball nut 94 moves in the direction of arrangement of the electromagnet 96 along the axial direction of the ball screw 92. At this time, the nut holder 94a attached to the ball nut 94 presses the electromagnet plate 98. As a result, the rod 64 is pushed out, the cam mechanism 42 operates, the pressing force of the operating spring 36 is released, and the brake is released.

As shown in FIG. 12, when the electromagnet plate 98 is pressed to the electromagnet 96 and power is supplied to the electromagnet 96, the electromagnet plate 98 is attracted to the electromagnet 96. As a result, even if the power supply to the motor 82 is cut off, the brake release state is maintained.

Here, the ball nut 94 moves to the holding braking force acting position (initial position) determined by the load between the preset spring 94b and the spring 101 by shutting off the motor power supply.

After the electromagnet plate 98 is attracted to the electromagnet 96, electric power of opposite phase is supplied to the motor 82. As a result, the motor 82 is driven in the reverse rotation, and the ball screw 92, which is rotated via the gear unit 84, also rotates in the reverse direction (for example, counterclockwise rotation). Due to the reversal of the ball screw 92, the ball nut 94 moves together with the nut holder 94a in a direction away from the electromagnet 96. After moving the ball nut 94, the power supply to the motor 82 is cut off to receive the force of the preset spring 94b. The ball nut 94 is pushed back to the initial position via the nut holder 94a.

When the supply of electric power to the electromagnet 96 is cut off in such a state, the cam mechanism 42 is pushed back by the force of the operating spring 36. Along with this, the rod 64 is also pushed back, and the electromagnet plate 98 to which the end of the rod 64 is fastened comes into contact with the nut holder 94a. In this way, by attracting and holding the electromagnet plate 98 by the electromagnet 96 and then pulling the ball nut 94 back to the initial position, the motor gear unit 80 becomes the operating resistance when the pressing force of the operating spring 36 is applied. There is no such thing as. Therefore, it is possible to maintain good responsiveness when the brake is operated.

Even with the disc brake device 10B having such a structure of the actuator, the same effect as the disc brake devices 10 and 10A according to the first and second embodiments can be obtained.

10, 10A, 10B ......... Disc brake device, 12 ......... Caliper body, 14 ......... Body body, 16 ......... Bridge part, 16a ......... Through hole, 18 ......... Claw part, 20 ... … Cylinder, 22 ……… Support, 24 ……… Case, 26 ……… Bore, 28 ……… Piston, 30 ……… Sliding part, 30a ……… Through hole, 32 ……… Interlocking part, 32a ………… Flat surface, 34 ………… Reaction force receiver, 36 ………… Actuating spring, 38 ………… Adjust pin, 40 ………… Adjustment bolt, 42 ………… Cam mechanism, 44 ………… Cam part, 44a ……… Pin, 44b ……… Cam outer circumference, 46 ……… Lever part, 48 ……… Sliding member, 50 ……… Piston side pad, 52 ……… Lining, 54 ……… Pressure plate, 56 ……… Claw side pad, 58 ……… Lining, 60 ……… Pressure plate, 62 ……… Air chamber, 64 ……… Rod, 66 ……… Support, 70 ……… Rotor, 80 ……… Motor gear unit, 82 ……… Motor, 84 ……… Gear unit, 86 ……… Casing, 90 ……… Ball screw unit, 92 ……… Ball screw, 94 ……… Ball nut, 94a ……… Nut Holder, 94b ……… Preset spring, 96 ……… Electromagnet, 98 ……… Electromagnet plate, 100 ……… Casing, 100a ……… Guide stud, 101 ……… Spring.

Claims (7)

A disc brake device in which a piston arranged in a cylinder formed in a caliper body presses a brake pad by receiving a pressing force from an operating spring.
It is equipped with a cam unit that releases the pressing force of the piston by inputting rotational power.
The piston is provided with an adjusting pin for adjusting the position of the brake pad.
A disc brake device characterized in that an actuator for inputting rotational power to the cam portion is provided in a claw portion of the caliper body which is connected to a body body in which the actuating spring is arranged via a bridge portion. The operating spring is a laminated disc spring.
A claim characterized in that a holding shaft supported at both ends is arranged in a through hole provided at the center of the disc spring so as to be slidable in the axial direction of the rotor with respect to the caliper body. Item 1. The disc brake device according to item 1. The disc brake device according to claim 1 or 2, wherein the rotational power input portion of the cam portion and the actuator are connected by a connecting member that inserts a hole portion provided in the caliper body. The disc brake device according to claim 3, wherein the actuator is an air chamber that operates the connecting member by the force of air. The disc brake device according to claim 3, wherein the actuator is a motor gear unit that applies an operating force in a direction of releasing the pressing force to the rotational power input unit via the connecting member. The motor gear unit is provided with a ball screw that rotates by the operation of the motor gear unit and a ball nut that moves along the ball screw.
The disc brake device according to claim 5, wherein the connecting member is extruded by the ball nut. The holding shaft has a threaded portion between the holding shaft and the piston.
One of the ends of the holding shaft slides on the caliper body via the piston, and the gap between the holding shaft and the brake pad can be adjusted via the screwed portion. The disc brake device according to claim 2, or any one of claims 3 to 6, which cites claim 2.

Images