WO2015098782A1 - Dispositif de frein à disque - Google Patents

Dispositif de frein à disque Download PDF

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Publication number
WO2015098782A1
WO2015098782A1 PCT/JP2014/083807 JP2014083807W WO2015098782A1 WO 2015098782 A1 WO2015098782 A1 WO 2015098782A1 JP 2014083807 W JP2014083807 W JP 2014083807W WO 2015098782 A1 WO2015098782 A1 WO 2015098782A1
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WO
WIPO (PCT)
Prior art keywords
force
disc brake
brake device
cam
pressing force
Prior art date
Application number
PCT/JP2014/083807
Other languages
English (en)
Japanese (ja)
Inventor
吉川　和宏
Original Assignee
曙ブレーキ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2013267837A external-priority patent/JP6288580B2/ja
Priority claimed from JP2013267828A external-priority patent/JP6277514B2/ja
Application filed by 曙ブレーキ工業株式会社 filed Critical 曙ブレーキ工業株式会社
Publication of WO2015098782A1 publication Critical patent/WO2015098782A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/42—Slack adjusters mechanical non-automatic
    • F16D65/46—Slack adjusters mechanical non-automatic with screw-thread and nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • F16D2121/16—Mechanical for releasing a normally applied brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2123/00—Multiple operation forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/32—Cams; Levers with cams acting on one cam follower

Definitions

  • the present invention relates to a disc brake device.
  • a spring mechanism (actuating spring) is employed as a power source for generating a pressing force against the brake pad.
  • 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 for releasing the battery has been employed.
  • 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.
  • a cam shaft for operating the cam mechanism protrudes from the body main body on the extension line of the bridge portion.
  • Patent Document 2 discloses that a lever with a plurality of link mechanisms is oscillated as means for manually releasing a pressing force.
  • the release mechanism that releases the pressing force by the electromagnetic force having the configuration as disclosed in Patent Document 2
  • the release mechanism can be made smaller than before.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the rigidity of the caliper body 12 can be maintained even when the through hole 17 is provided in the back portion 13.
  • the caliper body 12 may be increased in size.
  • 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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. 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. 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.
  • FIG. 1 is a side view of the disc brake device according to the first embodiment of the present invention
  • 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 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 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.
  • adopting a disc spring it is good to set it as the structure arrange
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a rotation shaft 36a is provided so as to penetrate the large diameter portion 36b.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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. .
  • 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.
  • an axial hole 26b is interposed 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
  • 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.
  • the rotating shaft 36a of the camshaft 36 be configured to be able to apply a rotational force.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the operation of the disc brake device 10 configured as described above will be described.
  • 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.
  • 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.
  • the caliper body 12 is pushed back through the guide pin 68 by the reaction force P2.
  • 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.
  • the air chamber 50 is taken as an example of the actuator, but a motor or the like may be employed (not shown).
  • 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.
  • FIG. 8 is a side view of the disc brake device according to the second embodiment
  • 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.
  • 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 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 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 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.
  • adopting a disc spring it is good to set it as the structure arrange
  • 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.
  • 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 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a rotation shaft 36a is provided so as to penetrate the large diameter portion 36b.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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. .
  • 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.
  • an axial hole 26b is interposed 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.
  • 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.
  • the rotating shaft 36a of the camshaft 36 be configured to be able to apply a rotational force.
  • 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.
  • 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.
  • 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.
  • 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.
  • the bridge portion 16 is a connecting portion that connects the body main body 14 and the claw portion 18.
  • 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.
  • 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.
  • 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.
  • 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.
  • the operation of the disc brake device 110 configured as described above will be described.
  • 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.
  • 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.
  • the caliper body 12 is pushed back via the guide pins 68 by the reaction force.
  • 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.
  • the manual release bolt 54 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.
  • the clevis 152 becomes a bolt of the manual release bolt 54 as shown in FIG. Slide to the head side.
  • 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.
  • 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.
  • the air chamber 50 is taken as an example of the actuator, but a motor or the like may be employed (not shown).
  • 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.
  • 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.
  • 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),
  • 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).
  • 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 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).
  • 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).
  • 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)
  • 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.
  • 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.
  • 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. .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Braking Arrangements (AREA)

Abstract

　L'invention concerne un dispositif (10) de frein à disque, lequel est conçu de façon que l'axe d'un arbre à cames possédant une section de came (36c) est disposé en dehors des limites de la largeur (W) d'une section de paroi arrière dans un corps (12) d'étrier de frein. Cette section de came (36c) repousse un piston (26) en générant une force de réaction pour libérer la force de pression d'un ressort (28), cette force de pression agissant sur le piston et la force de réaction étant générée par une force de rotation entrée. La section de came (36c) repousse ensuite le piston (26) dans une position initiale lorsqu'elle est soumise à une force de pression au moment où l'entrée de la force de rotation est supprimée.
PCT/JP2014/083807 2013-12-25 2014-12-19 Dispositif de frein à disque WO2015098782A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2013-267837 2013-12-25
JP2013267837A JP6288580B2 (ja) 2013-12-25 2013-12-25 ディスクブレーキ装置
JP2013-267828 2013-12-25
JP2013267828A JP6277514B2 (ja) 2013-12-25 2013-12-25 ディスクブレーキ装置

Publications (1)

Publication Number Publication Date
WO2015098782A1 true WO2015098782A1 (fr) 2015-07-02

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Application Number Title Priority Date Filing Date
PCT/JP2014/083807 WO2015098782A1 (fr) 2013-12-25 2014-12-19 Dispositif de frein à disque

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WO (1) WO2015098782A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10364857B2 (en) * 2014-12-16 2019-07-30 Akebono Brake Industry Co., Ltd. Disc brake apparatus
CN113090689A (zh) * 2021-03-31 2021-07-09 玉环思安安全设备股份有限公司 一种改良版制动钳缸体结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5076401A (en) * 1990-07-27 1991-12-31 Westinghouse Air Brake Company Spring-applied, hydraulically released brake actuator having positive clearance slack adjuster mechanism
JPH0754885A (ja) * 1993-08-09 1995-02-28 Tokico Ltd ディスクブレーキ
JP2010064569A (ja) * 2008-09-10 2010-03-25 Advics Co Ltd 電動パーキングブレーキ装置
JP2010116935A (ja) * 2008-11-11 2010-05-27 Tsubaki Emerson Co 電磁ブレーキの手動解放機構
JP2012527582A (ja) * 2009-05-19 2012-11-08 ヴィーイー・ヴィエナ・エンジニアリング・フォルシュングス−ウント・エントヴィックルングス・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 摩擦ブレーキ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5076401A (en) * 1990-07-27 1991-12-31 Westinghouse Air Brake Company Spring-applied, hydraulically released brake actuator having positive clearance slack adjuster mechanism
JPH0754885A (ja) * 1993-08-09 1995-02-28 Tokico Ltd ディスクブレーキ
JP2010064569A (ja) * 2008-09-10 2010-03-25 Advics Co Ltd 電動パーキングブレーキ装置
JP2010116935A (ja) * 2008-11-11 2010-05-27 Tsubaki Emerson Co 電磁ブレーキの手動解放機構
JP2012527582A (ja) * 2009-05-19 2012-11-08 ヴィーイー・ヴィエナ・エンジニアリング・フォルシュングス−ウント・エントヴィックルングス・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 摩擦ブレーキ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10364857B2 (en) * 2014-12-16 2019-07-30 Akebono Brake Industry Co., Ltd. Disc brake apparatus
CN113090689A (zh) * 2021-03-31 2021-07-09 玉环思安安全设备股份有限公司 一种改良版制动钳缸体结构

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