JP2015124795A - Disc brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a disc brake device as a whole while having means for manually releasing pressing force by an operation spring, in the negative type disc brake device.SOLUTION: In a disc brake device 10 in which an inner pad 60 is pressed by pressing force from an operation spring 28, a cam mechanism for releasing the pressing force, is disposed in a caliper body 12, and a cam shaft 36 for operating the cam mechanism is projected to the external of the caliper body 12, a manual mechanism is additionally disposed on a power transmission path from an air chamber 50 to which the force to rotate the cam shaft 36 is input. Here, the power transmission path is provided with a cam lever 46 as a booster mechanism, and the manual mechanism is preferably a manual release bolt 54 for making a clevis 52 disposed at a power point side of the cam lever 46, movable.

Description

  The present invention relates to a disc brake device, and more particularly to a disc brake device of a type that generates a braking force during non-operation, which is called a negative type.

  As disclosed in Patent Document 1, the disk brake device called a negative type applies a pressing force to the brake pad by an operating spring. In a negative type disc brake device having such a basic configuration, as a means for releasing a pressing force, an electromagnetic force as disclosed in Patent Document 1 or a hydraulic pressure as disclosed in Patent Document 2 is usually used. It is known that there is something by the power of.

  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 1 discloses that a lever with a plurality of link mechanisms is swung 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. 2000-7290 Japanese Utility Model Publication No. 52-113187

  Certainly, by adopting a configuration as disclosed in Patent Document 1, it is considered that the release mechanism can be reduced in size as compared with the prior art. However, in the technique disclosed in Patent Document 1, a mechanism that releases the pressing force electromagnetically and mechanically and a mechanism that releases the pressing force manually 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.

  Accordingly, the present invention provides a disc brake device capable of reducing the size of the entire disc brake device while providing means capable of manually releasing the pressing force of the operating spring in the negative type disc brake device. With the goal.

  In order to achieve the above object, a disc brake device according to the present invention includes a cam mechanism in a caliper body that presses a brake pad by a pressing force from an operating spring and releases the pressing force, and operates the cam mechanism. In the disc brake device in which the camshaft to be projected protrudes outside the caliper body, a manual mechanism for rotating the camshaft is attached to the force transmission path from the actuator for inputting the force for rotating the camshaft. It is characterized by that.

Further, in the disk brake apparatus having the above characteristics, the said force transmission path, the cam lever is there, the leverage ratio, the distance to the point from the center of rotation of the camshaft and l _2, to force point from the center of rotation When the distance is l ₁ , it is represented by l ₁ / l ₂ . The manual mechanism may be attached to the power point side of the cam lever. With such a configuration, it is possible to release the pressing force from the operating spring with a small force.

  In the disc brake device having the above characteristics, the manual mechanism is a bolt that moves a connecting member provided on the force point side of the cam lever in a direction in which the cam shaft is rotated by a tightening action by screwing. The disc brake device according to claim 2. By setting it as such a structure, after making it the state which released the pressing force from an action | operation spring, a release state can be maintained, without making force act.

  Further, in the disc brake device having the above characteristics, a linear motion rod for operating the cam lever is provided between the actuator and the cam lever, a male screw is formed on a side surface of the linear motion rod, and the manual mechanism is The nut may be screwed into the linear motion rod to move the linear motion rod in the direction in which the cam lever is operated. Even with such a configuration, the pressing force from the operating spring can be manually released.

  According to the disc brake device having the above-described characteristics, in the negative type disc brake device, it is possible to reduce the size of the entire disc brake device while being provided with means capable of manually releasing the pressing force by the operating spring. Can do.

It is a figure showing the side composition of the disc brake device concerning an embodiment. It is a figure which shows the AA cross section in FIG. It is a figure which shows the BB cross section in FIG. It is a fragmentary sectional enlarged view for demonstrating the relationship between a cam shaft and a connecting rod. It is an external appearance perspective view of the disc brake device before screwing a manual release bolt. It is an external appearance perspective view of the disc brake device in the state where the manual release bolt is screwed. It is an external perspective view of the disc brake device in a state in which the pressing force of the operating spring is released by tightening the manual release bolt. It is a figure which shows the structural example at the time of employ | adopting a rack and pinion type mechanism as a manual mechanism.

  Hereinafter, embodiments of the disc brake device according to the present invention will be described in detail with reference to the drawings. 1 is a side view of the disc brake device according to the first embodiment, and FIG. 2 is a cross-sectional view taken along line AA in FIG. FIG. 3 is a view showing a BB 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 present embodiment is basically configured to have 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 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 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 several disc springs may be piled up alternately.

  The end of the bore 22 opposite to the connecting end with the cylinder 20 is a release end, and a plug 32 serving 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 present 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. In addition, the plug 32 according to the 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 configured to be 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 embodiment has a convex portion 30a and a flange portion 30b in appearance. When the disc spring is adopted as the operating spring 28, the outer shape of the convex portion 30a is formed to be slightly smaller than the diameter of the center hole formed in the disc spring. 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.

  The other end of the guide 30 is provided with a recess in which a female screw is formed, and the adjuster 31 can be screwed into the recess. 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 this embodiment, the guide 30 having such a configuration is arranged such that the convex portion 30a penetrates the center hole of the disc springs (actuating springs 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.

  A cam shaft 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 embodiment, a rotation shaft 36a is provided so as to penetrate the large diameter portion 36b. Further, as shown in FIG. 4, the large-diameter portion 36b of the camshaft 36 according to the embodiment is configured such that the connecting rod 42 is in sliding contact with a concave cam portion 36c having an arcuate bottom portion. 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 disposed in a direction orthogonal to the direction in which the cylinder 20 of the body main body 14 is formed. 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 of the rotation 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 large-diameter portion 36 b constituting the camshaft 36 is disposed and formed so as to be positioned inside the through hole 26 a of the piston 26 in the state of being disposed 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 of the necessity of inserting 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 portion 36c of the large diameter portion 36b of the camshaft 36 disposed in the through hole 26a of the piston 26 and the concave portion 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 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, as shown in FIG. 2, the piston 26 according to the embodiment is coupled to the guide 30 via a coupling pin 44. 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 by the piston 26 can also be prevented.

  Further, 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 l ₁ from the center O1 of the rotating shaft 36a as the fulcrum to the center O3 of the pin as the power point. (See FIG. 1), the lever ratio (l ₁ / l ₂ ) is based on the ratio of the distance l ₂ from the center O1 of the rotating shaft 36a as the fulcrum to the arc center O2 of the connecting rod 42 as the action point. 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. By connecting a linearly acting rod 48 that moves linearly by the operation of the air chamber 50 to the other end of the cam lever 46, the rotation of the rotating shaft 36a of the camshaft 36 is rotated by the linear motion that occurs by the operation of the air chamber. It can be converted into rotational motion. When the cam lever 46 is rotated, even if the rotation angle is small, the trajectory is slightly arcuate. For this reason, by connecting the cam lever 46 and the linearly acting rod 48 through pin coupling via the clevis 52, distortion due to a difference in the movement trajectory 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 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. 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 axial direction of the rotor of the outer pad 62 (actually supported by a support 66 described in detail later) assembled to the inner surface of the claw 18 is provided. The position can be adjusted.

  Since the pressing force of the disc brake device 10 according to the 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 10 according to the embodiment, a manual mechanism for releasing the pressing force by the operating spring 28 without depending on the force of the actuator is provided in the force transmission path between the actuator such as the air chamber 50 and the camshaft 36. It is attached. Specifically, a manual release bolt 54 is provided on a clevis 52 that pin-couples the other end of the cam lever 46 and the linearly acting rod 48. The manual release bolt 54 is screwed into a female screw portion provided in a through hole formed in parallel to the operation direction of the linear motion rod 48 with respect to the clevis 52. The tip of the manual release bolt 54 that protrudes from the through hole of the clevis 52 is configured to abut a receiving seat 56 provided on the caliper body 12. In the form shown in FIG. 1, 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, and the length of the tip that protrudes from the clevis 52 becomes longer. On the other hand, since the advance of the manual release bolt 54 is blocked by the receiving seat 56, the clevis 52 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.

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

  In the disc brake device 10 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 manually operated. To share with. For this reason, the disc brake device 10 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. That is, since the force applied in the axial direction of the rotor is converted into 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 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 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 a pressing force from the piston 26 and urges the rotor. When the inner pad 60 is urged to the rotor, the caliper body 12 is pushed back through the guide pin 68 by the reaction force. By this action, the outer pad 62 arranged on the claw portion 18 is pushed out to the rotor side, and the rotor is sandwiched between the inner pad 60 and the outer pad 62 to generate a braking force.

  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). As a result, the rotation shaft 36a rotates and the large diameter portion 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 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 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.

  When releasing the pressing force by the operating spring 28 without using an actuator, the manual release bolt 54 is screwed into the clevis 52 as shown in FIG. 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 further rotated in the direction in which the manual release bolt 54 is further tightened in a state in which the tip of the manual release bolt 54 is in contact with the receiving seat 56, the clevis 52 is moved to the bolt head side of the manual release bolt 54 as shown in FIG. Slide to the side. By this operation, the cam lever 46 is rotated (swinged) in the direction of arrow B (see FIG. 1), and the same action as that in the state in which the air chamber 50 is operated is produced, and the operating spring 28 (see FIGS. 2 and 3). ) Is released, and the braking of the rotor is released.

  In the description of the operation, it is described that the manual release bolt 54 is 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 10 is not affected.

  Moreover, in the said embodiment, although the air chamber 50 is mentioned as an example as an actuator, a motor etc. can also be employ | adopted (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.

  Another example of the manual release mechanism may be a mechanism as shown in FIG. 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. Then, 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 move toward the air chamber 50, and the nut 58 is brought into contact with the projecting portion of the linear motion rod 48 in the air chamber 50. If 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 10 as a whole can be made compact as in the above embodiment.

10 ......... Disc brake device, 12 ......... Caliper body, 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 ......... Connecting pin, 46 ...... Cam lever, 48 ... …… Direct acting rod, 50 ……… Air chamber 52 ......... Clevis, 54 ......... Manual release bolt, 56 ......... Reception seat, 60 ......... Inner pad, 62 ......... Outer pad, 64 ......... Adjust bolt, 66 ......... Support, 68 ... …guide pin.

Claims (4)

A disc brake that includes a cam mechanism in the caliper body that presses a brake pad by a pressing force from an operating spring and releases the pressing force, and a cam shaft that operates the cam mechanism protrudes to the outside of the caliper body. In the device
A disc brake device characterized in that 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 Provide a cam lever,
The disc brake device according to claim 1, wherein the manual mechanism is attached to the power point side of the cam lever.   The said manual mechanism is a volt | bolt which moves the connecting member provided in the said force point side of the said cam lever in the direction which rotates the said camshaft by the tightening effect | action by screwing. Disc brake device. A linear rod for operating the cam lever is provided between the actuator and the cam lever,
On the side of the linear motion rod, a male screw is formed,
3. The disc brake device according to claim 2, wherein the manual mechanism is a nut that is screwed into the linear motion rod and moves the linear motion rod in a direction in which the cam lever is operated.

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