WO2015098782A1

WO2015098782A1 - Disc brake device

Info

Publication number: WO2015098782A1
Application number: PCT/JP2014/083807
Authority: WO
Inventors: 吉川　和宏
Original assignee: 曙ブレーキ工業株式会社
Priority date: 2013-12-25
Filing date: 2014-12-19
Publication date: 2015-07-02

Abstract

A disc brake device (10) is configured in such a manner that the axis of a camshaft (36) having a cam section (36c) is disposed outside the range of the width (W) of the back wall section of a caliper body (12), the cam section (36c) being adapted so that: the cam section (36c) pushes back a piston (26) by generating reaction force for releasing the pressing force of an operating spring (28), the pressing force acting on the piston (26), the reaction force being generated by the input of rotational force; and the cam section (36c) pushes back the piston (26) to an initial position when subjected to the pressing force when the input of the rotational force is released.

Description

Disc brake device

The present invention relates to a disc brake device.

In the conventional negative type disc brake device, a spring mechanism (actuating spring) is employed as a power source for generating a pressing force against the brake pad. In the negative type disc brake device having such a basic configuration, as a release mechanism for releasing the pressing force, a hydraulic mechanism for releasing the pressing force by a hydraulic force (see Patent Document 1), or a pressing force by an electromagnetic force. A release mechanism (see Patent Document 2) for releasing the battery has been employed. On the other hand, the applicant of the present application has considered using a mechanical force as the release mechanism, and tried to adopt a cam mechanism as disclosed in Patent Document 3 as a mechanism for releasing the pressing force. A disc brake device was devised. Note that the cam mechanism disclosed in Patent Document 3 is a mechanism for generating a braking force.

The disc brake device devised by the applicant of the present application is a device having a small floating caliper composed of a body main body, a claw portion, and a bridge portion connecting the two. In the disc brake device, a cam shaft for operating the cam mechanism protrudes from the body main body on the extension line of the bridge portion.

By the way, in the disc brake device having such a configuration, it is necessary to manually release the pressing force when an inspection or malfunction occurs. Patent Document 2 discloses that a lever with a plurality of link mechanisms is oscillated as means for manually releasing a pressing force. Thus, by adopting a configuration in which the pressing force is released by interposing a plurality of link mechanisms, it is possible to reduce the size of the release mechanism in addition to the configuration of only the lever using the lever.

Japanese Unexamined Patent Publication No. Sho 52-113187 Japanese Unexamined Patent Publication No. 2000-7290 Japanese Unexamined Patent Publication No. 2011-27132

Certainly, according to the release mechanism that releases the pressing force by the electromagnetic force having the configuration as disclosed in Patent Document 2, it is considered that the release mechanism can be made smaller than before. However, in the technique disclosed in Patent Document 2, a mechanism for electromagnetically and mechanically releasing the pressing force and a mechanism for manually releasing the pressing force are provided as separate bodies. Further, the mechanism for manually releasing the pressing force is too large to attach to the caliper body constituting the disc brake as it is even if a link mechanism is interposed.

In addition, the disc brake device in which the pressing force of the operating spring is released by the cam mechanism devised by the applicant of the present application has brought about various advantageous effects such as downsizing, simplification of incidental equipment, and improvement in maintainability.
However, in the disc brake device having such a configuration, a through-hole through which the camshaft protrudes is provided in the back meat portion positioned on the extension line of the bridge portion, so that the rigidity of the caliper body is reduced. A new problem has arisen.

Specifically, as shown in FIG. 7, the reaction force P <b> 2 of the claw portion 18 acts on the back meat portion 13, and thus when the rigidity of the portion decreases, a force is applied in the axial direction of the rotor. In addition, there is a possibility that an opening generated between the body main body 14 and the claw portion 18 becomes large.

The configuration of the caliper body 12 is a configuration in which a plurality of bridge portions 16 are provided (in the patent document 3, two locations on the turning-in side and the feeding-out side of the rotor) as in the disc brake device disclosed in Patent Document 3. In this case, it is considered that the rigidity of the caliper body 12 can be maintained even when the through hole 17 is provided in the back portion 13. In this case, however, the caliper body 12 may be increased in size.

Therefore, in the present invention, even when a cam mechanism is employed as a mechanism for releasing the pressing force generated by the operating spring, the caliper body is made small, and the rigidity to the force in the axial direction of the rotor is not reduced. It is a first object to provide a disc brake device.
It is a second object of the present invention to provide a disc brake device that can reduce the size of the entire disc brake device while providing means that can manually release the pressing force of the operating spring.

The first object of the present invention is achieved by a disc brake device having the following configurations (1) and (2).
(1) A disc brake device that presses a brake pad via one end face by a piston disposed in a cylinder formed in a caliper body receiving a pressing force from an operating spring, and is an input of rotational force To generate a reaction force for releasing the pressing force against the piston and push the piston back, and when the input of the rotational force is released, the cam receives the pressing force and pushes the piston back to the initial position. A disc brake device in which an axis of a camshaft having a portion is arranged so as to avoid a range of a width of a back portion of the caliper body.

(2) The disc brake device having the configuration of (1) above, wherein the shaft center includes at least a part of the camshaft passing through a center of the cylinder, and an arrangement surface of the back meat portion and the brake pad. The disc brake device is arranged so as to be parallel to both of the arrangement surfaces.

According to the disc brake device configured as described in (1) and (2) above, there is almost no influence on the reaction force from the claw portion. Moreover, the weight balance on the inflow side and the outflow side of the rotor can be kept good.

The second object is achieved by a disc brake device having the following configurations (3) to (6).
(3) The brake pad is pressed by the pressing force from the operating spring, a cam mechanism for releasing the pressing force is provided in the caliper body, and a camshaft for operating the cam mechanism protrudes outside the caliper body. A disc brake device, wherein a manual mechanism for rotating the camshaft is attached to a force transmission path from an actuator for inputting a force for rotating the camshaft.

(4) above a disc brake apparatus having the configuration of (3), the said force transmission path, the distance to the point from the center of rotation of the cam shaft when the l _2, emphasis from the center of rotation the distance to the l _1, and the cam lever is provided with a relation of l _1> l _2, the manual mechanism, the emphasis disc brake device that is attached to the side of the cam lever.
According to the disc brake device configured as in the above (3) and (4), it is possible to release the pressing force from the operating spring with a small force.

(5) The disc brake device having the configuration of (4), wherein the manual mechanism rotates the camshaft by tightening a connecting member provided on the power point side of the cam lever by screwing. A disc brake device that is a bolt that moves in the direction to be moved.
According to the disc brake device having the configuration as described in (5) above, the released state can be maintained without applying a force after the pressing force from the operating spring is released.

(6) In the disc brake device having the configuration of (4), a linear motion rod for operating the cam lever is provided between the actuator and the cam lever, and a male screw is provided on a side surface of the linear motion rod. And the manual mechanism is a nut that is screwed into the linear motion rod to move the linear motion rod in a direction in which the cam lever operates.
Even in the disc brake device configured as described in (6) above, the pressing force from the operating spring can be manually released.

According to the disc brake device having the configuration as described in the above (1), even when the cam mechanism is employed as a mechanism for releasing the pressing force generated by the operating spring, the caliper body is provided with the bridge portion as one place. It is possible to suppress a reduction in rigidity to a force in the axial direction of the rotor while downsizing.
Further, according to the disc brake device having the configuration as described in the above (3), the entire disc brake device can be reduced in size while being provided with means capable of manually releasing the pressing force by the operating spring.

FIG. 1 is a view showing a side configuration of a disc brake device according to a first embodiment of the present invention. FIG. 2 is a view showing a II-II cross section in FIG. FIG. 3 is a view showing a III-III cross section in FIG. FIG. 4 is an enlarged partial cross-sectional view for explaining the relationship between the camshaft and the connecting rod. FIG. 5 is a schematic view of a caliper body showing a VV cross section in FIG. FIG. 6 is a schematic diagram for explaining the relationship between forces applied to the caliper body. FIG. 7 is a schematic diagram for explaining that when a through hole is provided in the back portion, the rigidity of the back portion is affected when a force in the axial direction of the rotor is applied. FIG. 8 is a view showing a side configuration of the disc brake device according to the second embodiment of the present invention. FIG. 9 is a view showing a section IX-IX in FIG. FIG. 10 is a view showing an XX section in FIG. FIG. 11 is an enlarged partial cross-sectional view for explaining the relationship between the camshaft and the connecting rod. FIG. 12 is an external perspective view of the disc brake device before screwing the manual release bolt. FIG. 13 is an external perspective view of the disc brake device with the manual release bolt screwed therein. FIG. 14 is an external perspective view of the disc brake device in a state where the pressing force of the operating spring is released by tightening the manual release bolt. FIG. 15 is a diagram showing a configuration example when a rack and pinion type mechanism is adopted as the manual mechanism.

Hereinafter, embodiments of the disc brake device according to the present invention will be described in detail with reference to the drawings.
FIG. 1 is a side view of the disc brake device according to the first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along the line II-II in FIG. FIG. 3 is a view showing a III-III cross section in FIG. FIG. 4 is an enlarged partial cross-sectional view for explaining the relationship between the camshaft and the connecting rod.

The disc brake device 10 according to the first embodiment is basically configured to include a caliper body 12, an inner pad 60, an outer pad 62, and an air chamber 50, and is supported by a fixing portion (not shown) via a support 66. The

The caliper body 12 basically has a body main body 14, a claw portion 18, and a bridge portion 16. The body main body 14 includes a cylinder 20, a bore 22, and a bearing hole 24 inside. A piston 26 is disposed in the cylinder 20, and an operating spring 28 and a guide 30 are disposed in the bore 22.

The piston 26 slides in the cylinder 20 and plays a role of pressing an inner pad 60 disposed between the claw portion 18 described later by one end face. The piston 26 according to the first embodiment has a through hole 26a in a direction orthogonal to the pressing direction. Further, an axial hole 26b penetrating the side wall of the through hole 26a is formed on the other end face of the piston 26.

The actuating spring 28 is an element that generates a pressing force P1 that presses the piston 26 in the arrangement direction (pressing direction) of the inner pad 60. A specific configuration of the operating spring 28 can be a disc spring. This is because the disc spring is suitable as a pressing force generating means for generating a braking force because a large load can be applied with a small deflection. In addition, when employ | adopting a disc spring, it is good to set it as the structure arrange | positioned so that a plurality of disc springs may be piled up alternately.

The end of the bore 22 on the opposite side to the connecting end with the cylinder 20 is a release end, and a plug 32 as a spacer for adjusting the thickness of the operating spring 28 and the pressing force P1 is disposed here. By adopting such a configuration, it is possible to change the bending and thickness of the actuating spring 28 (when a disc spring is employed, the number of the springs) and the like, and the pressing force P1 can be adjusted. In the first embodiment, the plug 32 has a male screw portion that can be screwed into a female screw portion formed at the open end of the bore 22, and is positioned by tightening the male screw portion. . The plug 32 is sealed by a fastening plate 34 that is a cover that covers the open end of the bore 22. The plug 32 according to the first embodiment is formed with a through hole 32a at the center so that the slider 31a of the adjuster 31 in the guide 30, which will be described in detail later, is slidable.

The guide 30 is a transmission element that transmits a pressing force P1 by the operating spring 28 to the piston 26 and receives a reaction force by a camshaft 36, which will be described in detail later. The guide 30 according to the first embodiment has a convex portion 30a and a flange portion 30b in appearance. The convex portion 30a has an outer shape that is slightly smaller than the diameter of the central hole formed in the disc spring when the disc spring is employed as the operating spring 28. Further, the flange portion 30b is formed at one end of the convex portion 30a so as to protrude to the outer peripheral side with respect to the outer shape of the convex portion 30a, and serves as an element for receiving the pressing force P1 by the operating spring 28. Moreover, the recessed part 30c which formed the bottom face in the hemispherical shape is provided in one edge part of the guide 30, ie, the flange part 30b formation side edge part.

Further, a concave portion in which a female screw is formed is provided at the other end portion of the guide 30, and the adjuster 31 can be screwed into the concave portion. The adjuster 31 plays a role of adjusting the thickness of the operating spring 28 and the height of the guide 30, and a slider 31 a protrudes from an end surface facing the plug 32. The slider 31a is an element slidable in a through hole 32a formed in the plug 32, and bears the positioning action of the guide 30 in the axial direction.

In the first embodiment, the guide 30 having such a configuration is arranged such that the convex portion 30a penetrates the center hole of the disc spring (actuating spring 28) arranged in a stacked manner. By adopting such an arrangement form, it is possible to prevent the disc springs arranged in a stacked manner from shifting in the radial direction.

The camshaft 36 is disposed in the bearing hole 24. The camshaft 36 is configured based on a rotating shaft 36a and a large diameter portion 36b. In the camshaft 36 according to the first embodiment, a rotation shaft 36a is provided so as to penetrate the large diameter portion 36b. Further, the large-diameter portion 36b of the camshaft 36 according to the first embodiment is configured such that the connecting rod 42 is in sliding contact with a concave cam portion 36c having an arcuate bottom as shown in FIG. Yes. In the cam mechanism having such a configuration, it is possible to generate a force in a direction orthogonal to the rotation shaft 36a due to the rotation of the rotation shaft 36a by changing the thickness of the arc-shaped bottom portion.

The bearing hole 24 is a hole arranged in a direction orthogonal to the forming direction of the cylinder 20 in the body main body 14. Further, the bearing hole 24 in the disc brake device 10 according to the first embodiment is arranged so as to avoid the range of the width (W) of the back portion 13 in the caliper body 12. Here, the back portion 13 is a portion that transmits a force acting in the axial direction of the rotor 70 in the bridge portion 16 and the body main body 14. Specifically, the back portion 13 is a portion to which the reaction force from the claw portion 18 is transmitted, and is positioned on the bridge portion 16 and an extension line of the width of the bridge portion 16 as illustrated by a broken line in FIG. This is a part of the body main body 14 to be operated. When the bearing hole 24 is provided within the range of the width (W) of the back portion 13, the rigidity of the portion of the caliper body 12 to which the force acting in the axial direction is transmitted is reduced. For this reason, when the reaction force P2 in the axial direction is applied during braking, the caliper body 12 is greatly bent, and the caliper body 12 is enlarged if the bending is to be suppressed.

For this reason, the bearing hole 24 is formed so that the center (S) of the camshaft 36 is located in the range of (A) shown in FIG. Is done. By setting the formation range of the bearing hole 24 in such a range, it is possible to make it less susceptible to the reaction force P2 from the claw portion 18 as shown in FIG. In the first embodiment, at least a part of the camshaft 36 passes through the center of the cylinder 20, and the axis (S) extends to the arrangement surface of the back portion 13 (perpendicular to the paper surface of FIG. 6 and to the left and right). The bearing hole 24 is formed so as to be parallel to both the surface) and the surface on which the inner pad 60 is disposed (a surface extending vertically and vertically with respect to the paper surface of FIG. 6). This is because the bearing hole 24 is in such an arrangement form, so that it can be hardly affected by the reaction force P2.

The camshaft 36 disposed in the bearing hole 24 is disposed such that the rotating shaft 36a passes through the through hole 26a formed in the piston 26. By adopting such an arrangement, the camshaft 36 also serves as a rotation stop for the piston 26. The inner pad 60 pressed by the piston 26 is caused to rotate by a couple generated during braking. For this reason, a rotational force is also applied to the piston 26 that is in contact with the inner pad 60 during braking. When the piston 26 rotates, an unspecified force acts on a boot, a seal, or an operating spring 28 disposed between the cylinder 20 and the piston 26. Therefore, by inhibiting the rotation of the piston 26, breakage or malfunction of these elements can be prevented.

In addition, one end (the upper end in FIG. 2) of the rotating shaft 36 a is exposed to the outside of the body main body 14 from the opening of the bearing hole 24, and a rotation operation can be imparted from the outside of the body main body 14. The The large-diameter portion 36 b constituting the camshaft 36 is arranged and formed so as to be positioned inside the through hole 26 a of the piston 26 in the arrangement state in the bearing hole 24. A gap is provided between the through hole 26a and the large diameter portion 36b so that the large diameter portion 36b and the inner wall surface of the through hole 26a do not contact when the piston 26 moves in the axial direction. .

In addition, the hole diameter of the bearing hole 24 is formed to be sufficiently larger than the rotating shaft 36a because it is necessary to insert the large-diameter portion 36b therein. For this reason, by interposing the shaft holder 38 between the inner wall of the bearing hole 24 and the rotary shaft 36a, it is possible to exert both effects of preventing the camshaft 36 from coming off and preventing rattling.

Between the cam part 36c of the large diameter part 36b in the cam shaft 36 disposed in the through hole 26a of the piston 26 and the concave part 30c of the guide 30 that receives the pressing force P1 of the operating spring 28, an axial hole 26b is interposed. The connecting rod 42 is arranged. With such an arrangement, the contact portion between the cam portion 36c and the connecting rod 42 changes as the large-diameter portion 36b rotates as the rotating shaft 36a rotates. With this action, a part of the connecting rod 42 is pushed out from the axial hole 26b to generate a reaction force that pushes back the guide 30. Thereby, the pressing force P1 of the operating spring 28 is released, and the urging force of the inner pad 60 against the rotor 70 is also released. At this time, the pressing force P1 of the actuating spring 28 is received by the inner peripheral wall of the bearing hole 24, that is, the body body 14 via the rotating shaft 36a of the camshaft 36, so that a reaction force can be generated.

Here, the piston 26 according to the first embodiment is connected to the guide 30 via a connecting pin 44 as shown in FIG. For this reason, when the guide 30 is pushed back to the arrangement side of the operating spring 28 by the connecting rod 42, the piston 26 is also pulled back. Thereby, drag of the inner pad 60 pressed against the rotor 70 by the piston 26 can also be prevented.

The camshaft 36 is arranged and configured such that the rotation center O1 of the rotary shaft 36a is deviated from the extended line of the straight line L passing through the axis of the connecting rod 42. For this reason, when the rotational force with respect to the camshaft 36 is released, the connecting rod 42 transmits the pressing force P1 of the operating spring 28 to the cam portion 36c, and the cam portion 36c is formed at a predetermined initial position (formed in a concave shape). The cam portion 36c is pushed back to the position where the thickness of the bottom surface is reduced.

In order to realize the operation as described above, it is necessary that the rotating shaft 36a of the camshaft 36 be configured to be able to apply a rotational force. For this reason, one end of the cam lever 46 is attached to an exposed portion of the rotating shaft 36a of the camshaft 36 from the bearing hole 24. Here, the booster mechanism constituted by the cam mechanism including the camshaft 36 and the connecting rod 42 and the cam lever 46 is a distance from the rotation center O1 of the rotation shaft 36a as a fulcrum to the center O3 of the pin 47 as a power point. Based on the ratio between l ₁ (see FIG. 1) and the distance l ₂ from the rotation center O1 of the rotation shaft 36a as the fulcrum to the arc center O2 of the connecting rod 42 as the action point, the lever ratio (l ₁ / l ₂ ) is determined. For this reason, by making the effective length l ₁ of the cam lever 46 longer than l ₂ , a large force can be obtained with a small operating force. Therefore, it is possible to generate a reaction force that pushes back the guide 30 in opposition to the pressing force P1 of the operating spring 28 that generates a large load.

The other end of the cam lever 46 is connected to a linear rod 48 that is operated by the air chamber 50. The linear motion rod 48 that moves linearly by the operation of the air chamber 50 is connected to the other end of the cam lever 46, so that the linear motion generated by the operation of the air chamber rotates the rotating shaft 36a of the camshaft 36. It is converted into rotating motion. When the cam lever 46 is rotated, even if the rotation angle is small, the trajectory is slightly arcuate. For this reason, since the connection between the cam lever 46 and the linearly acting rod 48 is a pin connection via the clevis 52, it is possible to absorb the distortion due to the difference in the movement locus.

The claw portion 18 is a reaction force receiver that faces the body main body 14, and is configured such that the outer pad 62 can be disposed at a position facing the inner pad 60. In the claw portion 18 in the first embodiment, a through hole 18a is provided from the outer surface of the claw portion 18 toward the inner surface on which the outer pad 62 is disposed (see FIG. 2). The through-hole 18a is subjected to female threading at least on the outer surface side. An adjuster bolt 64 can be disposed in the through hole 18a, and the axis of the rotor 70 of the outer pad 62 (actually supported by a support 66 described in detail later) assembled to the inner surface of the claw portion 18 is provided. The direction position can be adjusted.

Since the pressing force P1 of the disc brake device 10 according to the first embodiment is generated by the displacement of the operating spring 28, the sliding amount (protruding amount) of the piston 26 is small. For this reason, the clearance for the pad wear can be adjusted by tightening the adjuster bolt 64. The bridge portion 16 is a connecting portion that connects the body main body 14 and the claw portion 18.

The caliper body 12 configured as described above is assembled to the support 66 via guide pins 68 arranged in parallel with the axial direction of the rotor 70. With such a configuration, the caliper body 12 can slide in the axial direction of the rotor 70 with the support 66 as a base point. The inner pad 60 and the outer pad 62 are supported by the torque receiving portion of the support 66 so that the rotor 70 can slide in the axial direction.

In the disc brake device 10 configured as described above, the bearing hole 24 for disposing the camshaft 36 constituting the cam mechanism is disposed so as to avoid the range of the width (W) of the back portion of the caliper body 12. It is configured. Therefore, it is possible to configure the disc brake device 10 that does not have insufficient rigidity against the reaction force P2 from the claw portion 18 while making the caliper body 12 small.

Next, the operation of the disc brake device 10 configured as described above will be described.
First, when the air chamber 50 is not in operation, the guide 30 and the piston 26 are pressed by the pressing force P1 of the operating spring 28, and the piston 26 is pushed out to the rotor side. In this state, the inner pad 60 is pushed out to the rotor side by receiving the pressing force P <b> 1 from the piston 26 and is urged to the rotor 70. When the inner pad 60 is urged against the rotor 70, the caliper body 12 is pushed back through the guide pin 68 by the reaction force P2. By this action, the outer pad 62 disposed on the claw portion 18 is pushed out to the rotor side, the rotor 70 is sandwiched between the inner pad 60 and the outer pad 62, and a braking force is generated.

Next, when the air chamber 50 is operated, the linear motion rod 48 moves in a direction protruding from the air chamber 50, and the cam lever 46 is rotated (swinged) in the direction of arrow B (see FIG. 1). Thereby, the rotating shaft 36a rotates and the large diameter part 36b rotates. When the large-diameter portion 36b rotates, the connecting rod 42 that is in sliding contact with the cam portion 36c is pushed out toward the operating spring 28, and a reaction force that pushes back the guide 30 is generated.

When the guide 30 is pushed back by the generation of the reaction force, the pressing force P1 to the piston 26 connected to the guide 30 by the connecting pin 44 is also released. As a result, the braking of the rotor 70 caused by being sandwiched between the inner pad 60 and the outer pad 62 is released.

On the other hand, when the operation of the air chamber 50 is released, the reaction force via the connecting rod 42 is released. As a result, the connecting rod 42 and the piston 26 are pushed back together with the guide 30 by the pressing force P <b> 1 by the operating spring 28, and the pressing force P <b> 1 against the inner pad 60 is generated. At this time, the large diameter portion 36 b is pushed back to the initial position via the connecting rod 42.

In the first embodiment, the air chamber 50 is taken as an example of the actuator, but a motor or the like may be employed (not shown). When a motor is used as an actuator, a crank lever (not shown) or the like is interposed between the linear motion rod 48 and the motor rotation shaft in order to convert the rotational force into a linear force. You can make it.

Next, a disc brake device according to a second embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 8 is a side view of the disc brake device according to the second embodiment, and FIG. 9 is a view showing a IX-IX cross section in FIG. FIG. 10 is a diagram showing a cross section taken along line XX in FIG. Furthermore, FIG. 11 is a partial cross-sectional enlarged view for explaining the relationship between the camshaft and the connecting rod.

The disc brake device 110 according to the second embodiment is basically configured to include a caliper body 12, an inner pad 60, an outer pad 62, and an air chamber 50, and is supported by a fixing portion (not shown) via a support 66. The

The piston 26 slides in the cylinder 20 and plays a role of pressing an inner pad 60 disposed between the claw portion 18 described later by one end face. The piston 26 according to the second embodiment has a through hole 26a in a direction orthogonal to the pressing direction. Further, an axial hole 26b penetrating the side wall of the through hole 26a is formed on the other end face of the piston 26.

The actuating spring 28 is an element that generates a pressing force that presses the piston 26 in the arrangement direction (pressing direction) of the inner pad 60. A specific configuration of the operating spring 28 can be a disc spring. This is because the disc spring is suitable as a pressing force generating means for generating a braking force because a large load can be applied with a small deflection. In addition, when employ | adopting a disc spring, it is good to set it as the structure arrange | positioned so that a plurality of disc springs may be piled up alternately.

The end of the bore 22 opposite to the end connected to the cylinder 20 is a release end, and a plug 32 as a spacer for adjusting the thickness and pressing force of the operating spring 28 is disposed here. By adopting such a configuration, it is possible to change the deflection and thickness of the actuating spring 28 (if a disc spring is employed, the number of the springs), and the like, and the pressing force can be adjusted. In the first embodiment, the plug 32 has a male screw portion that can be screwed into a female screw portion formed at the open end of the bore 22, and is positioned by tightening the male screw portion. . The plug 32 is sealed by a fastening plate 34 that is a cover that covers the open end of the bore 22. Note that the plug 32 according to the second embodiment has a through hole 32a at the center, and the slider 31a of the adjuster 31 in the guide 30, which will be described in detail later, is slidable.

The guide 30 is a transmission element that transmits a pressing force by the operating spring 28 to the piston 26 and receives a reaction force by a camshaft 36 to be described in detail later. The guide 30 according to the second embodiment has a convex portion 30a and a flange portion 30b in appearance. The convex portion 30a has an outer shape that is slightly smaller than the diameter of the central hole formed in the disc spring when the disc spring is employed as the operating spring 28. Further, the flange portion 30b is formed at one end of the convex portion 30a so as to protrude to the outer peripheral side from the outer shape of the convex portion 30a, and serves as an element that receives the pressing force by the operating spring 28. Moreover, the recessed part 30c which formed the bottom face in the hemispherical shape is provided in one edge part of the guide 30, ie, the flange part 30b formation side edge part.

In the second embodiment, the guide 30 having such a configuration is arranged such that the convex portion 30a penetrates the central hole of the disc spring (actuating spring 28) arranged in a stacked manner. By adopting such an arrangement form, it is possible to prevent the disc springs arranged in a stacked manner from shifting in the radial direction.

The camshaft 36 is disposed in the bearing hole 24. The camshaft 36 is configured based on a rotating shaft 36a and a large diameter portion 36b. In the camshaft 36 according to the second embodiment, a rotation shaft 36a is provided so as to penetrate the large diameter portion 36b. Further, the large-diameter portion 36b of the camshaft 36 according to the second embodiment is configured such that the connecting rod 42 is in sliding contact with a concave cam portion 36c having an arcuate bottom as shown in FIG. Yes. In the cam mechanism having such a configuration, it is possible to generate a force in a direction orthogonal to the rotation shaft 36a due to the rotation of the rotation shaft 36a by changing the thickness of the arc-shaped bottom portion.

The bearing hole 24 is a hole arranged in a direction orthogonal to the forming direction of the cylinder 20 in the body main body 14. The camshaft 36 disposed in the bearing hole 24 is disposed such that the rotation shaft 36 a passes through the through hole 26 a formed in the piston 26. By adopting such an arrangement, the camshaft 36 also serves as a rotation stop for the piston 26. The inner pad 60 pressed by the piston 26 is caused to rotate by a couple generated during braking. For this reason, a rotational force is also applied to the piston 26 that is in contact with the inner pad 60 during braking. When the piston 26 rotates, an unspecified force acts on a boot, a seal, or an operating spring 28 disposed between the cylinder 20 and the piston 26. Therefore, by inhibiting the rotation of the piston 26, breakage or malfunction of these elements can be prevented.

In addition, one end (the upper end in FIG. 9) of the rotating shaft 36 a is exposed to the outside of the body main body 14 from the opening of the bearing hole 24, and a rotation operation can be applied from the outside of the body main body 14. The The large-diameter portion 36 b constituting the camshaft 36 is arranged and formed so as to be positioned inside the through hole 26 a of the piston 26 in the arrangement state in the bearing hole 24. A gap is provided between the through hole 26a and the large diameter portion 36b so that the large diameter portion 36b and the inner wall surface of the through hole 26a do not contact when the piston 26 moves in the axial direction. .

Between the cam part 36c of the large diameter part 36b in the cam shaft 36 disposed in the through hole 26a of the piston 26 and the concave part 30c of the guide 30 that receives the pressing force of the operating spring 28, an axial hole 26b is interposed. A connecting rod 42 is arranged. With such an arrangement, the contact portion between the cam portion 36c and the connecting rod 42 changes as the large-diameter portion 36b rotates as the rotating shaft 36a rotates. With this action, a part of the connecting rod 42 is pushed out from the axial hole 26b to generate a reaction force that pushes back the guide 30. Thereby, the pressing force of the operating spring 28 is released, and the urging force of the inner pad 60 against the rotor 70 is also released. At this time, the pressing force of the operating spring 28 is received by the inner peripheral wall of the bearing hole 24, that is, the body main body 14 via the rotating shaft 36 a of the camshaft 36, so that reaction force can be generated.

Here, the piston 26 according to the second embodiment is connected to the guide 30 via a connecting pin 44 as shown in FIG. For this reason, when the guide 30 is pushed back to the arrangement side of the operating spring 28 by the connecting rod 42, the piston 26 is also pulled back. Thereby, drag of the inner pad 60 pressed against the rotor 70 by the piston 26 can also be prevented.

The camshaft 36 is arranged and configured such that the rotation center O1 of the rotary shaft 36a is deviated from the extended line of the straight line L passing through the axis of the connecting rod 42. For this reason, when the rotational force with respect to the camshaft 36 is released, the connecting rod 42 transmits the pressing force of the operating spring 28 to the cam portion 36c, and the cam portion 36c is moved to a predetermined initial position (a cam formed in a concave shape). It will push back to the position where the thickness of the bottom face of the part 36c becomes thin.

In order to realize the operation as described above, it is necessary that the rotating shaft 36a of the camshaft 36 be configured to be able to apply a rotational force. For this reason, one end of the cam lever 46 is attached to an exposed portion of the rotating shaft 36a of the camshaft 36 from the bearing hole 24. Here, the booster mechanism constituted by the cam mechanism including the camshaft 36 and the connecting rod 42 and the cam lever 46 is a distance from the rotation center O1 of the rotation shaft 36a as a fulcrum to the center O3 of the pin 47 as a power point. Based on the ratio between l ₁ (see FIG. 8) and the distance l ₂ from the rotation center O1 of the rotation shaft 36a as the fulcrum to the arc center O2 of the connecting rod 42 as the action point, the lever ratio (l ₁ / l ₂ ) is determined. For this reason, by making the effective length l ₁ of the cam lever 46 longer than l ₂ , a large force can be obtained with a small operating force. Therefore, it is possible to generate a reaction force that pushes back the guide 30 against the pressing force of the operating spring 28 that generates a large load.

The other end of the cam lever 46 is connected to a linear rod 48 that is operated by the air chamber 50. The linear motion rod 48 that moves linearly by the operation of the air chamber 50 is connected to the other end of the cam lever 46, so that the linear motion generated by the operation of the air chamber rotates the rotating shaft 36a of the camshaft 36. It is converted into rotating motion. When the cam lever 46 is rotated, even if the rotation angle is small, the trajectory is slightly arcuate. For this reason, the connection between the cam lever 46 and the linear motion rod 48 is a pin connection via the clevis (connection member) 152, so that the distortion due to the difference in the movement locus can be absorbed.

The claw portion 18 is a reaction force receiver that faces the body main body 14, and is configured such that the outer pad 62 can be disposed at a position facing the inner pad 60. The claw portion 18 in the second embodiment is provided with a through hole 18a from the outer surface of the claw portion 18 toward the inner surface on which the outer pad 62 is disposed (see FIG. 9). The through-hole 18a is subjected to female threading at least on the outer surface side. An adjuster bolt 64 can be disposed in the through hole 18a, and the axis of the rotor 70 of the outer pad 62 (actually supported by a support 66 described in detail later) assembled to the inner surface of the claw portion 18 is provided. The direction position can be adjusted.

Since the pressing force of the disc brake device 110 according to the second embodiment is generated by the displacement of the operating spring 28, the sliding amount (protruding amount) of the piston 26 is small. For this reason, the clearance for the pad wear can be adjusted by tightening the adjuster bolt 64. The bridge portion 16 is a connecting portion that connects the body main body 14 and the claw portion 18.

In the disc brake device 110 according to the second embodiment, a force transmission path between the actuator such as the air chamber 50 and the camshaft 36 is used to release the pressing force by the operating spring 28 without depending on the force of the actuator. A manual mechanism is attached. Specifically, a manual release bolt 54 is provided on a clevis 152 that pin-couples the other end of the cam lever 46 and the linear motion rod 48. The manual release bolt 54 is screwed into the internal thread portion provided in the through hole 152a formed in parallel to the operation direction of the linear motion rod 48 with respect to the clevis 152. The distal end of the manual release bolt 54 that protrudes from the through hole 152 a of the clevis 152 is configured to abut on a receiving seat 56 provided on the caliper body 12. In the form shown in FIG. 8, the receiving seat 56 is provided in a bracket portion for fixing the air chamber 50.

The manual release bolt 54 arranged in this way is given a force in the tightening direction, so that the length of the tip protruding from the clevis 152 becomes longer. In contrast, since the advance of the manual release bolt 54 is blocked by the receiving seat 56, the clevis 152 moves to the bolt head side of the manual release bolt 54 due to the reaction force. Since this operation is common to the operation of the linearly acting rod 48 in the air chamber 50, the rotating shaft 36a of the cam shaft 36 can be rotated to release the pressing force of the operating spring 28.

In the disc brake device 110 configured as described above, as a mechanism for releasing the pressing force by the operating spring 28, a part of the force transmission path interposed when releasing the pressing force by the actuator such as the air chamber 50 is a manual mechanism. It is configured to be shared with. For this reason, the disc brake device 110 as a whole can be reduced in size. Further, since the force transmission direction is converted using a cam mechanism disposed in the caliper body 12 as a mechanism for releasing the pressing force, the manual mechanism can be downsized. In other words, since the force applied in the axial direction of the rotor 70 is converted to the force in the rotational direction via the cam mechanism, it is not necessary to earn a force and a distance using a large lever or the like. Further, by adopting the manual release bolt 54 as a specific means of the manual mechanism, it is possible to maintain the released state without applying force after the pressing force is released.

Next, the operation of the disc brake device 110 configured as described above will be described.
First, when the air chamber 50 is not in operation, the guide 30 and the piston 26 are pressed by the pressing force of the operating spring 28, and the piston 26 is pushed out to the rotor side. In this state, the inner pad 60 is pushed toward the rotor side by receiving a pressing force from the piston 26 and is urged toward the rotor 70. When the inner pad 60 is urged against the rotor 70, the caliper body 12 is pushed back via the guide pins 68 by the reaction force. By this action, the outer pad 62 disposed on the claw portion 18 is pushed out to the rotor side, the rotor 70 is sandwiched between the inner pad 60 and the outer pad 62, and a braking force is generated.

Next, when the air chamber 50 is operated, the linear motion rod 48 moves in a direction protruding from the air chamber 50, and the cam lever 46 is rotated (swinged) in the direction of arrow B (see FIG. 8). Thereby, the rotating shaft 36a rotates and the large diameter part 36b rotates. When the large-diameter portion 36b rotates, the connecting rod 42 that is in sliding contact with the cam portion 36c is pushed out toward the operating spring 28, and a reaction force that pushes back the guide 30 is generated.

When the guide 30 is pushed back by the generation of reaction force, the pressing force applied to the piston 26 connected to the guide 30 by the connecting pin 44 is also released. As a result, the braking of the rotor 70 caused by being sandwiched between the inner pad 60 and the outer pad 62 is released.

On the other hand, when the operation of the air chamber 50 is released, the reaction force via the connecting rod 42 is released. As a result, the connecting rod 42 and the piston 26 are pushed back together with the guide 30 by the pressing force of the operating spring 28, and a pressing force against the inner pad 60 is generated. At this time, the large diameter portion 36 b is pushed back to the initial position via the connecting rod 42.

Further, when releasing the pressing force by the operating spring 28 without using the actuator, the manual release bolt 54 is screwed to the clevis 152 as shown in FIG. 12 in a state where the braking force is generated. The screwed manual release bolt 54 is rotated in the direction in which the bolt is tightened, so that its tip abuts against the receiving seat 56 as shown in FIG. When the manual release bolt 54 is rotated in the direction in which the manual release bolt 54 is further tightened in a state where the tip of the manual release bolt 54 is in contact with the receiving seat 56, the clevis 152 becomes a bolt of the manual release bolt 54 as shown in FIG. Slide to the head side. By this operation, the cam lever 46 is rotated (swinged) in the direction of arrow B (see FIG. 8), and the same action as that in the state in which the air chamber 50 is operated is obtained, and the operating spring 28 (see FIGS. 9 and 10). ) Is released, and the braking of the rotor 70 is released.

In the above description of the operation, the manual release bolt 54 is described as being screwed when performing the manual release operation. However, if the bolt tip is not in contact with the receiving seat 56, the manual release bolt 54 is always screwed. Can be maintained. This is because the normal operation of the disc brake device 110 is not affected.

In the second embodiment, the air chamber 50 is taken as an example of the actuator, but a motor or the like may be employed (not shown). When a motor is used as an actuator, a crank lever (not shown) or the like is interposed between the linear motion rod 48 and the motor rotation shaft in order to convert the rotational force into a linear force. You can make it.

Further, as another example of the manual release mechanism, for example, a mechanism as shown in FIG. 15 may be used. Specifically, a male screw is formed on the outer periphery of the linear motion rod 48 of the air chamber 50 that is an actuator. A nut 58 that is screwed onto the male screw is disposed. In the case of the manual release mechanism having such a configuration, the nut 58 is turned so as to be moved toward the air chamber 50, and the nut 58 is brought into contact with the protruding portion of the linear motion rod 48 in the air chamber 50. When the nut 58 is further swung after the nut 58 is brought into contact with the air chamber 50, the linear rod 48 protrudes so as to be pulled out from the air chamber 50 in accordance with the swirling of the nut 58.

This action gives the linear motion rod 48 the same motion as that when the air chamber 50 is operated. Therefore, the cam lever 46 can be moved in the direction of arrow B. Further, even with such a mechanism, the disc brake device 110 as a whole can be made compact as in the second embodiment.

Here, the features of the above-described embodiments of the disc brake device according to the present invention will be summarized and listed below.
[1] The piston (26) disposed in the cylinder (20) formed on the caliper body (12) receives a pressing force from the operating spring (28), so that the brake pad (inner A disc brake device (10) for pressing a pad 60),
When a rotational force is input, a reaction force for releasing the pressing force against the piston (26) is generated to push back the piston (26), and the pressing force is received when the input of the rotating force is released. The shaft center (S) of the camshaft (36) having the cam portion (36c) to be pushed back to the initial position is disposed so as to avoid the range of the width (W) of the back portion (13) in the caliper body (12). Disc brake device (10).
[2] The shaft center (S) includes at least a part of the camshaft (36) passing through the center of the cylinder (20), and the arrangement surface of the back portion (13) and the brake pad (inner pad). 60) The disc brake device (10) according to the above [1], which is arranged so as to be parallel to both of the arrangement surfaces.
[3] The brake pad (inner pad 60) is pressed by the pressing force from the operating spring (28), and a cam mechanism for releasing the pressing force is provided in the caliper body (12), and the cam mechanism is operated. A force from an actuator (air chamber 50) which is a disc brake device (110) in which a camshaft (36) protrudes outside the caliper body (12) and inputs a force for rotating the camshaft (36). A disc brake device (110) in which a manual mechanism (manual release bolt 54, nut 58) for rotating the camshaft (36) is attached to the transmission path.
[4] The said force transmitting path, the distance to the point (arc center O2 of the connecting rod 42) from the rotation center (O1) of the camshaft (36) in the case of the _{l 2,} the rotation center (O1 ) from the distance to the power point (the center O3 of the pin 47) and _{l 1,} and _l 1> cam lever having a relationship of _{l 2} (46) is provided,
The disc brake device (110) according to the above [3], wherein the manual mechanism (manual release bolt 54, nut 58) is attached to the power point side of the cam lever (46).
[5] The manual mechanism is a bolt that moves a connecting member (clevis 52) provided on the force point side of the cam lever (46) in a direction in which the cam shaft (36) is rotated by a tightening action by screwing. The disc brake device (110) according to the above [4], which is a (manual release bolt 54).
[6] A linear rod (48) for operating the cam lever (46) is provided between the actuator (air chamber 50) and the cam lever (46).
A male screw is formed on the side surface of the linear rod (48),
[4] In the above [4], the manual mechanism is a nut (58) that is screwed to the linear motion rod (48) and moves the linear motion rod (48) in a direction in which the cam lever (46) operates. Disc brake device (110).

As mentioned above, the invention made by the present inventor has been specifically described based on the embodiment of the invention described above, but the invention is not limited to the embodiment of the invention described above, and various modifications can be made without departing from the scope of the invention. It can be changed.
This application is based on Japanese patent applications (Japanese Patent Application Nos. 2013-267828 and 2013-267837) filed on December 25, 2013, the contents of which are incorporated herein by reference.

In the disc brake device of the present invention, even when a cam mechanism is employed as a mechanism for releasing the pressing force generated by the operating spring, the caliper body is downsized with the bridge portion as one place, and the axial direction of the rotor is reduced. This is useful for a negative type disc brake device that can suppress a decrease in rigidity to a force.
In addition, the disc brake device of the present invention is useful for a negative type disc brake device that is provided with means that can manually release the pressing force by the operating spring and that can reduce the size of the entire disc brake device. .

10, 110 ......... Disc brake device, 12 ......... Caliper body, 13 ......... Back meat part, 14 ......... Body body, 16 ......... Bridge part, 18 ......... Nail part, 18a ......... Through hole, 20 ......... Cylinder, 22 ......... Bore, 24 ......... Bearing hole, 26 ......... Piston, 26a ......... Through hole, 26b ......... Axial hole, 28 ......... Operating spring, 30 ......... Guide, 30a ......... Projection, 30b ......... Flange, 31 ......... Adjuster, 31a ......... Slider, 32 ...... Plug, 32a ...... Through hole, 34 ......... Fastening Plate, 36 ......... Camshaft, 36a ......... Rotating shaft, 36b ......... Large diameter part, 36c ......... Cam part, 38 ......... Shaft holder, 42 ......... Connecting rod, 44 ......... Connected Pin, 46 ... …… Cam lever, 47 ... …… Pin, 4 ......... Linear rod, 50 ......... Air chamber, 52 ......... Clevis, 60 ......... Inner pad, 62 ......... Outer pad, 64 ......... Adjust bolt, 66 ......... Support, 68 ......... Guide pin, 70... Rotor, 152... Clevis (connection member).

Claims

A disc brake device that presses a brake pad via one end face by a piston disposed in a cylinder formed in a caliper body receiving a pressing force from an operating spring,
When a rotational force is input, a reaction force that releases the pressing force against the piston is generated to push back the piston, and when the rotational force input is released, the pressing force is received to push back to the initial position. A disc brake device in which an axis of a camshaft having a cam portion is arranged so as to avoid a range of a width of a back portion of the caliper body.
2. The shaft center is disposed such that at least a part of the cam shaft passes through the center of the cylinder and is parallel to both the placement surface of the back portion and the placement surface of the brake pad. Disc brake device according to
A disc brake in which a brake pad is pressed by a pressing force from an operating spring, a cam mechanism for releasing the pressing force is provided in the caliper body, and a camshaft for operating the cam mechanism protrudes to the outside of the caliper body A device,
A disc brake device in which a manual mechanism for rotating the camshaft is attached to a force transmission path from an actuator for inputting a force for rotating the camshaft.
The said force transmitting path, the distance to the point from the center of rotation of the cam shaft when the l 2, the distance from the rotation center to the force point and l 1, and has a relation of l 1> l 2 A cam lever is provided,
The disc brake device according to claim 3, wherein the manual mechanism is attached to the power point side of the cam lever.
5. The disc brake device according to claim 4, wherein the manual mechanism is a bolt that moves a connecting member provided on the power point side of the cam lever in a direction in which the cam shaft is rotated by a tightening action by screwing.
A linear rod for operating the cam lever is provided between the actuator and the cam lever,
A male screw is formed on the side surface of the linear rod,
The disc brake device according to claim 4, wherein the manual mechanism is a nut that is screwed to the linear motion rod to move the linear motion rod in a direction in which the cam lever operates.