WO2016175107A1 - Disc brake apparatus - Google Patents

Disc brake apparatus Download PDF

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Publication number
WO2016175107A1
WO2016175107A1 PCT/JP2016/062573 JP2016062573W WO2016175107A1 WO 2016175107 A1 WO2016175107 A1 WO 2016175107A1 JP 2016062573 W JP2016062573 W JP 2016062573W WO 2016175107 A1 WO2016175107 A1 WO 2016175107A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressing force
disc brake
brake device
cam lever
housing
Prior art date
Application number
PCT/JP2016/062573
Other languages
French (fr)
Japanese (ja)
Inventor
吉川　和宏
利史 前原
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 JP2015221212A external-priority patent/JP6572102B2/en
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
Priority to US15/569,223 priority Critical patent/US10527114B2/en
Priority to EP16786384.4A priority patent/EP3290734A4/en
Priority to CN201680024851.7A priority patent/CN107532662B/en
Publication of WO2016175107A1 publication Critical patent/WO2016175107A1/en

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Classifications

    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper 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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • 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
    • 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

Definitions

  • the present invention relates to a disc brake device.
  • Patent Documents 1 and 2 are disc brakes of a type in which a pressing force for holding a rotor by a brake pad is generated by rotating a cam using an air chamber as power (actuator). Device.
  • Patent Document 2 discloses that a sub-frame that winds the outer periphery of the caliper body straddling both side surfaces of the rotor is provided in order to compensate for the low body rigidity.
  • An object of the present invention is to provide a disc brake device having a structure capable of preventing a decrease in body rigidity even when a cam lever is employed as a booster mechanism.
  • a disc brake device having a caliper body having a frame structure, wherein the caliper body includes at least a piston that presses a brake pad, a cam lever that generates a pressing force by rotation, and the piston and the cam lever.
  • An accommodating portion for accommodating a pressing force transmission mechanism that is interposed therebetween and transmits the pressing force to the piston, and the accommodating portion connects the piston, the cam lever, and the pressing force transmission mechanism to the caliper body;
  • the disc brake device has an opening that can be assembled from the back side of the housing, and both the housing and the opening are open to a rotor arrangement side region of the caliper body.
  • a pressing force generation unit cover that seals the opening is provided, and the pressing force generation unit cover is provided with a side wall that separates the housing unit and the rotor arrangement side region,
  • the housing part opened to facilitate the housing of the housing parts and the opening are sealed and closed after housing the housing parts. Can do. Further, the piston for generating the pressing force can be inserted into the rotor arrangement side region.
  • the configuration of the actuator that operates the cam lever can be simplified. Further, since the linear motion rod is activated by the operation of the air chamber, the responsiveness is good.
  • the linear rod is based on the base in a ball screw mechanism having a base pressed by the urging mechanism and a ball screw that is rotated by the motor gear unit to move the base in the axial direction.
  • the disc brake device according to (4) which is extended as follows.
  • the brake release state can be maintained even when the electric power supplied to the motor is stopped by operating the electromagnetic clutch. Therefore, it is possible to avoid a state in which a load is always applied to the motor when the brake is released.
  • the pressing force transmission mechanism includes an adjuster screw that adjusts the pushing position of the piston, and a housing that covers the adjuster screw and receives the pressing force.
  • the disc brake device according to any one of the above.
  • the slidability between the cam portion and the housing can be improved. Therefore, the wear amount of the cam portion and the housing can be reduced. Furthermore, wear of the sliding pin can be promoted by making the constituent material of the sliding pin softer than the cam portion and the housing. This makes it possible to replace parts due to wear by replacing only the sliding pins.
  • the disc brake device having the above-described characteristics, it is possible to prevent a decrease in body rigidity even when a cam lever is employed as a booster mechanism. In addition, the assembling property of the cam lever and the pressing force transmission mechanism can be improved.
  • FIG. 1 is a front view showing a configuration of a disc brake device according to an embodiment of the present invention.
  • 2 is a cross-sectional view taken along the line (A)-(A) in FIG.
  • FIG. 3 is an exploded perspective view showing the configuration of the disc brake device according to the present embodiment.
  • FIG. 4 is a partially exploded perspective sectional view showing the relationship between the unitized pressing force generating mechanism and the caliper body.
  • FIG. 5 is a partial cross-sectional perspective view showing the configuration of the unitized pressing force generating mechanism.
  • FIG. 6 is a view for explaining the auto adjuster mechanism.
  • FIG. 7 is a perspective view showing a configuration of a disc brake device in which an actuator has a mechanical configuration.
  • FIG. 8 is a view showing a cross section (A)-(B)-(C)-(D) in FIG.
  • FIG. 9 is a partially exploded perspective view showing the structure of the mechanically structured actuator and the pressing force generating mechanism.
  • the disc brake device 10 is configured based on the caliper body 12, the support 60, and the actuator 50, and exerts braking force by pressing the brake pads 66 and 68 against the sliding surface of the rotor 70. To do.
  • the caliper body 12 is configured on the basis of a pressing force generation unit 14, a reaction force receiving unit 18, and a bridge unit 16.
  • the pressing force generation unit 14 is an element in which a pressing force generation mechanism 22 including a piston 20 that generates a pressing force is accommodated.
  • the reaction force receiving portion 18 is arranged to face the pressing force generating portion 14 via the rotor 70, and is an element for receiving the pressing force from the piston 20 when the pressing force is generated.
  • a pad pressing portion for pressing the brake pad 68 is provided on the reaction force receiving portion 18 on the side facing the rotor 70.
  • the bridge portion 16 is an element that connects the pressing force generating portion 14 and the reaction force receiving portion 18 across the outer peripheral side of the rotor 70.
  • the pressing force generation part 14, the reaction force receiving part 18, and the bridge part 16 form a frame structure formed in a frame shape in plan view. For this reason, it becomes possible to improve the rigidity with respect to the axial force by the press of the piston 20.
  • the pressing force generation unit 14 includes an accommodating portion 14 a for accommodating the pressing force generation mechanism 22.
  • the accommodating part 14a is provided with an opening on the back side of the caliper body 12, and is configured such that the pressing force generating mechanism 22 can be installed from the opening. By adopting such a structure, the workability of assembling the disc brake device 10 can be improved.
  • the pressing force generation mechanism 22 includes a piston 20, a pressing force transmission mechanism 24, and a cam lever 42.
  • the piston 20 has an oval-shaped pressing surface having a long axis in the circumferential direction of the rotor 70, and includes two pressing portions 20a in order to balance the pressing force. It is structured.
  • a convex portion 20b is provided at the center of the surface opposite to the surface including the pressing portion 20a, and is configured to be fitted to an adjuster screw 32, which will be described in detail later.
  • a through-hole having a step portion on the pressing portion forming surface side is provided at the center of the convex portion 20b, and the fixing bolt 26 can be inserted.
  • the fixing bolt 26 includes a screw portion 26a, a spacer portion 26b, and a bolt head 26c. And the dimension of each part is adjusted so that the bolt head 26c is accommodated in a step part, the spacer part 26b is accommodated in a through-hole, and the thread part 26a protrudes from the convex part 20b.
  • a boot 30 is provided between the piston 20 and a pressing force generating unit cover 28, which will be described in detail later, to prevent dust from entering.
  • the pressing force transmission mechanism 24 plays a role of transmitting the pressing force generated by the operation of the cam lever 42 described later in detail to the piston 20 described above.
  • the pressing force transmission mechanism 24 includes an adjuster screw 32 and a housing 34 as main components, and an auto adjuster mechanism 36 is attached.
  • the adjuster screw 32 is an element for adjusting a gap generated when the lining of the brake pads 66 and 68 is worn.
  • the adjuster screw 32 has an external cylindrical shape and has an external thread portion on the outer peripheral surface.
  • a partition plate 32a is provided on the inner peripheral side, and is divided into a pressing portion and a sliding portion. On the pressing portion side of the adjuster screw 32, a concave portion 32b in which the convex portion of the piston 20 can be loosely fitted is provided.
  • the partition plate 32a is provided with a female screw portion 32c into which the screw portion of the fixing bolt 26 can be screwed.
  • the female screw portion 32c may be a through hole or a bag hole as long as it has a depth to which the fixing bolt 26 can be screwed.
  • the hole 32d in which the rotary shaft 40b of the adjuster gear 40 that rotates the adjuster screw 32 is hooked.
  • the rotary shaft 40b of the adjuster gear 40 which will be described in detail later, has a tip shape (engagement portion 40c) having a hexagonal shape.
  • the hole 32d may be a hole having a side that sandwiches at least two hexagonally opposed sides. That is, the cross-sectional shape of the hole 32d can be a hexagon, a quadrangle, or an ellipse having two parallel sides as shown in FIG.
  • the housing 34 includes a cylindrical portion 34a to which the adjuster screw 32 is screwed and a pressing portion 34b to which a pressing force is applied.
  • the cylindrical portion 34a is a holder having an internal thread portion on the inner peripheral surface.
  • the pressing portion 34b is an arm that extends from the outer periphery of the cylindrical portion 34a.
  • the pressing portions 34b are provided so as to form a pair on both the turn-in side and the turn-out side in the circumferential direction of the rotor 70 with the cylindrical portion 34a as a base point.
  • a slide groove 34c is provided along the pressing direction of the brake pad 66 at the distal end of the pressing portion 34b having the cylindrical portion 34a as a base end.
  • the slide groove 34c is a groove for sliding the housing 34 along a guide bolt 52 whose details will be described later.
  • the auto adjuster mechanism 36 is configured based on an adjuster lever 38 and an adjuster gear 40.
  • the adjuster lever 38 includes a lever main body 38a and a hook portion 38b.
  • the lever body 38 a is a part that supports the hook portion 38 b and controls the behavior of the adjuster lever 38.
  • a pivot base point 38c is provided at one end of the lever main body 38a, and is fixed to the outer peripheral portion of the cylindrical portion 34a of the housing 34 so as to be rotatable.
  • the other end of the lever main body 38a is provided with a hook 38b and a spring 38d for applying a tension for pulling back the rotated lever main body 38a.
  • the lever main body 38a is provided with a cam groove 38e having an inclined surface in order to give the lever main body 38a a turning operation as the housing 34 moves.
  • a cam piece 48 provided at the upper end of a bush receiver 46, which will be described later, contacts the cam groove 38e. Therefore, when the housing 34 moves in the direction of the arrow (a), the inclined surface of the cam groove 38e slides along the cam piece 48, and the lever body 38a rotates in the direction of the arrow (b). Become.
  • the hook portion 38b is bent from the other end of the lever main body 38a in a direction in which an adjuster gear 40, which will be described in detail later, is disposed (on the lower surface side in this embodiment), and meshes with the teeth of the adjuster gear 40. It is configured as follows.
  • the adjuster gear 40 is an element for rotating the adjuster screw 32.
  • the adjuster gear 40 includes a gear body 40a and a rotation shaft 40b.
  • the gear body 40a is an element to which rotation is imparted due to the operation of the adjuster lever 38 by engaging the hook portion 38b of the adjuster lever 38 with a plurality of teeth provided on the outer periphery of the disc portion.
  • the rotating shaft 40 b is an element that is inserted into the hole 32 d provided on the sliding portion side of the adjuster screw 32, engages with the inner wall of the hole 32 d, and transmits the rotation to the adjuster screw 32.
  • the rotating shaft 40b is provided with an engaging portion 40c for catching on the inner wall of the hole 32d.
  • the engaging portion 40c has a hexagonal cross-sectional shape.
  • the housing 34 moves in the direction of the arrow (a) due to the operation of the cam lever 42, so that the adjuster lever 38 rotates the adjuster gear 40 to adjust the adjuster screw. 32 will be pushed out.
  • the adjuster lever 38 is pulled back to the original position by the force of the spring 38d when the housing 34 is pushed back by releasing the pressing force applied by the cam lever 42. Since the teeth of the adjuster gear 40 are formed in a saw blade shape, when the hook portion 38b is pulled back, it slides on its upper part without being caught. For this reason, the adjuster lever 38 is configured to be fixed with play in the vertical direction.
  • the cam lever 42 includes a cam portion 42a and a lever portion 42b.
  • the cam part 42a is comprised from the circular-arc-shaped curved part, and is comprised so that the thickness of a curved part may differ.
  • a pressing force is generated in the thickness direction of the bending portion due to the displacement of the contact portion that occurs when the cam lever 42 is tilted.
  • the cam lever 42 is a booster mechanism corresponding to the ratio between the length of the lever portion 42b (length from the rotation center) and the amount of change in the thickness of the cam portion 42a. Is changed to a pressing force.
  • the cam lever 42 includes a connecting portion with the actuator 50 on one end side and the above-described cam portion 42a on the other end side.
  • the cam lever 42 has a configuration in which the end portion on the side where the cam portion 42a is disposed is bifurcated so as to straddle the cylindrical portion 34a of the housing 34 in the assembled state, and the cam portions 42a are disposed at both ends thereof. Has been. Since the end portion on the side where the cam portion 42 a is disposed has a bifurcated structure, the rotation shaft 40 b of the adjuster gear 40 in the auto adjuster mechanism 36 can be inserted through the center of the caliper body 12. Further, since the cam portions 42a are arranged in the circumferential direction of the rotor 70 on each of the turn-in side and the turn-out side with respect to the caliper body 12, a pressing force can be generated with a good balance.
  • a sliding pin 44 is disposed between the pressing portion 34 b of the housing 34 and the cam portion 42 a of the cam lever 42.
  • a bush receiver 46 is disposed between the cam portion 42a and the inner wall surface of the accommodating portion 14a. Further, a pin bush 44a and a cam bush 46a are provided between the slide pin 44 and the cam portion 42a and between the cam portion 42a and the bush receiver 46, respectively, and the slidability between the contact portions is improved. Is planned. As described above, the cam piece 48 that contacts the adjuster lever 38 is formed at the upper end of the bush receiver 46.
  • the through-hole 14c is provided in the side wall 14b of the accommodating part 14a of the caliper body 12.
  • the actuator 50 may be an air chamber, for example, and is assembled to the caliper body 12 in a state in which the linear motion rod 50a is inserted into the through hole 14c of the accommodating portion 14a and is connected to the tip of the lever portion 42b of the cam lever 42.
  • the guide bolt 52 can also be fixed to the caliper body 12 by assembling from the outside of the side wall 14b.
  • the opening portion of the accommodating portion 14a is provided with a pressing force generating portion cover 28 that covers the pressing force generating mechanism 22 and seals the opening portion.
  • the pressing force generating unit cover 28 includes a side wall 28a positioned on the side where the rotor 70 is disposed in the accommodating unit 14a. Since the pressing force generating unit cover 28 includes the side wall 28a, both the accommodating portion 14a and the opening of the accommodating portion 14a are opened to a region where the rotor 70 is disposed (rotor disposition side region). For this reason, the assembly
  • the side wall 28a is provided with a through hole 28b through which the piston 20 arranged in the accommodating portion 14a is inserted into the rotor arrangement side region.
  • the support 60 is an element for holding the caliper body 12 described above with respect to a vehicle or a device main body (not shown).
  • the support 60 includes at least a guide pin 62 and an anchor portion 64.
  • the guide pin 62 is an element for holding the caliper body 12 slidably in the axial direction of the rotor 70.
  • guide pins 62 are arranged on both the pressing force generating portion 14 side and the reaction force receiving portion 18 side of the caliper body 12 so as to form a pair on the turn-in side and the turn-out side of the rotor 70, respectively. Yes.
  • Each guide pin 62 is provided with a boot 62a for preventing dust from adhering to the sliding portion.
  • the anchor portion 64 is an element for receiving energy when stopping the rotation of the rotor 70.
  • concave portions are provided corresponding to both the pressing force generating portion 14 and the reaction force receiving portion 18 corresponding to both main surfaces of the rotor 70, and brake pads 66 and 68 are disposed in the concave portions, respectively. Configuration is adopted. For this reason, the support 60 is provided with a bridge portion 60 a that connects portions corresponding to both of the two main surfaces of the rotor 70.
  • the disc brake device 10 configured as described above, it is possible to prevent the caliper body 12 from being lowered in rigidity while adopting the cam lever 42 as a booster mechanism.
  • the opening of the accommodating portion 14a provided in the caliper body 12 is provided on the back side of the caliper body 12, the pressing force generating mechanism 22 can be assembled in a united state. Thereby, workability
  • the auto adjuster mechanism 36 is attached, the gap can be automatically closed even when the brake pads 66 and 68 are worn, and a suitable pressing force is generated when the rotor 70 is clamped. It becomes possible.
  • the cam lever 42 has a structure in which the cam portion 42a is bent to the side opposite to the arrangement side of the rotor 70.
  • the cam portion 42a is curved toward the rotor 70, there is no problem in exerting the function of the cam lever 42.
  • it is necessary to configure the cam portion so that the lower side of the cam portion is a thin portion and the upper portion of the cam portion is a thick portion.
  • the mechanism and operation of the actuator 50 are described as being an air chamber.
  • the actuator 50 may be mechanically operated using a motor as a driving force.
  • FIGS. 7 to 9 an example in which the actuator 50 has a mechanical configuration will be described with reference to FIGS. 7 to 9. Note that, in the configuration other than the actuator 50, elements having the same functions as the components according to the above-described embodiment are denoted by the same reference numerals on the drawings, and detailed description thereof will be omitted. This is because the specific shape is not limited as long as the function can be achieved.
  • the actuator 50 shown in FIGS. 7 to 9 (hereinafter referred to as representatively shown in FIG. 7) is basically composed of an operation unit 50b and a motor gear unit 50c.
  • the operation unit 50b is configured based on a ball screw mechanism 50b1, a spring 50b4, a guide pin 50b5, and a housing 50b6.
  • the ball screw mechanism 50b1 includes a ball screw 50b2, a base 50b3 movable in the axial direction of the ball screw 50b2, and a linear rod 50a extending in the cam lever 42 direction from the base 50b3.
  • the base 50b3 moves in the axial direction of the ball screw 50b2.
  • the ball screw 50b2 rotates with the movement of the base 50b3. It becomes.
  • the linearly acting rod 50a is responsible for the movement of pushing and pulling the cam lever 42 as the base 50b3 moves.
  • the spring 50b4 may be a disc spring or a coil spring, and serves as an urging mechanism that generates a reaction force in the axial direction of the ball screw 50b2.
  • the spring 50b4 is disposed so as to surround the outer periphery of the ball screw 50b2, one end side abuts against the end surface of the housing 50b6, and the other end side engages with the ball screw 50b2.
  • the base 50b3 is in contact with the main surface.
  • the guide pin 50b5 is disposed along the axial direction of the ball screw 50b2, and serves as a guide when the base 50b3 moves in the axial direction of the ball screw 50b2.
  • the guide pin 50 b 5 fixed to the housing 50 b 6 is inserted into a through hole formed in the base 50 b 3 to exert its function.
  • the housing 50b6 is an outer shell that houses the ball screw mechanism 50b1, the spring 50b4, and the guide pin 50b5, and includes a housing body 50b7 that serves as a housing portion and a housing cover 50b8 that seals the housing body 50b7.
  • the housing cover 50 b 8 also serves as a bracket for fixing the actuator 50 to the caliper body 12.
  • the motor gear unit 50c is a unit for rotating the ball screw 50b2 in the operation unit 50b.
  • the motor gear unit 50c includes a motor 50c1, a gear unit 50c4, and an electromagnetic clutch 50c5.
  • the motor 50c1 bears power for rotating the ball screw 50b2, and in the case of the form shown in FIG. 7, a double-axis motor in which one rotating shaft penetrates the body is adopted, and one shaft through the body is used.
  • 50c2 engages with the gear unit 50c4, and the other shaft 50c3 engages with the electromagnetic clutch 50c5.
  • the configuration of the gear unit 50c4 is not particularly limited, but includes at least a pinion gear that engages with one shaft 50c2 of the motor 50c1 and a drive gear that engages with the ball screw 50b2, and the pinion gear and the drive gear.
  • the electromagnetic clutch 50c5 is an element for stopping the free rotation of the rotation shaft of the motor 50c1. Therefore, the electromagnetic clutch 50c5 may be configured to engage with the other shaft 50c3 of the motor 50c1 and to stop the free rotation of the rotating shaft by supplying power. By providing the electromagnetic clutch 50c5, it is not necessary to always apply a load to the motor 50c1 when the brake is released.
  • the motor gear unit 50c is covered with a housing 50c6.
  • the ball screw 50b2 is rotated by driving the motor 50c1, and the base 50b3 is attracted toward the gear unit 50c4 (that is, the direction in which the spring 50b4 is compressed).
  • the rotation shaft of the motor 50c1 is freely rotated.
  • the spring 50b4 compressed by the rotation of the ball screw 50b2 generates a reaction force between the base 50b3 and the housing 50b6, and generates a force to push the base 50b3 away from the gear unit 50c4.
  • the rotating shaft of the motor 50c1 is free to rotate, and the resistance against the repulsive force of the spring 50b4 is small. Therefore, the base 50b3 moves in a direction away from the gear unit 50c4 while rotating the ball screw 50b2 in the reverse direction.
  • the cam lever 42 and the linear rod 50a are connected via a connecting member 50d.
  • a connecting member 50d When such an actuator 50 has such a configuration, when both the motor 50c1 and the electromagnetic clutch 50c5 are not in operation, the base 50b3 is pressed against the walk away from the gear unit 50c4 by the force of the spring 50b4. In such a state, the cam lever 42 connected to the linear rod 50a extending from the base 50b3 is inclined to the direction in which the brake is operated.
  • the brake when the brake is operated from the state in which the brake is released, the brake is operated by releasing the electromagnetic clutch 50c5 and rotating the motor 50c1 in the direction opposite to the direction in which the spring 50b4 is compressed. It is possible to shorten the time until the operation is performed and to improve the responsiveness.
  • a disc brake device having a caliper body (12) having a frame structure, The caliper body is interposed between at least the piston (20) for pressing the brake pads (66, 68), the cam lever (42) for generating a pressing force by rotation, and the piston and the cam lever.
  • the accommodating portion has an opening capable of assembling the piston, the cam lever, and the pressing force transmission mechanism from the back side of the caliper body,
  • a pressing force generator cover (28) for sealing the opening is provided,
  • the pressing force generating unit cover is provided with a side wall (14b) that separates the accommodating unit and the rotor arrangement side region,
  • the disc brake device (10) according to [1], wherein the side wall is provided with a through hole (14c) through which the piston is inserted toward the rotor arrangement region.
  • An actuator (50) for operating the cam lever is provided, The disc brake device according to [1] or [2], wherein the actuator includes a linear motion rod (50a) engaged with the cam lever, and is an air chamber that operates the linear motion rod with an air force. .
  • An actuator for operating the cam lever is provided.
  • the actuator has a linear rod engaged with the cam lever;
  • the disc brake device according to [2].
  • the linear rod has a base (50b3) pressed by the urging mechanism and a ball screw (50b2) that is rotated by the motor gear unit to move the base in the axial direction.
  • the cam lever (42) has a bifurcated structure straddling the pressing force transmission mechanism,
  • the pressing force transmission mechanism includes: An adjuster screw (32) for adjusting the pushing position of the piston; A housing (34) for covering the adjuster screw and receiving the pressing force;
  • this invention is not limited to embodiment mentioned above, A deformation
  • the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.
  • This application is based on a Japanese patent application filed on April 27, 2015 (Japanese Patent Application No. 2015-090566) and a Japanese patent application filed on November 11, 2015 (Japanese Patent Application No. 2015-212212). The contents are incorporated herein by reference.
  • the disc brake device of the present invention it is possible to prevent a decrease in body rigidity even when a cam lever is employed in the boost mechanism. Further, it is possible to provide a disc brake device that improves the workability of the assembly work of the cam lever and the pressing force transmission mechanism.

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

Abstract

A caliper body (12) of a disc brake apparatus (10) according to the present invention comprises a housing unit (14a) that houses a piston (20) that presses a brake pad (66), a cam lever (42) that generates a pressing force through rotating, and a pressing force transmission mechanism (24) that is disposed between the piston (20) and the cam lever (42) and that transmits the pressing force to the piston (20). The housing unit (14a) comprises an opening capable of installing the piston (20), the cam lever (42), and the pressing force transmission mechanism (24) from a back side in the caliper body (12), wherein both the housing unit (14a) and the opening open into a rotor arrangement side region in the caliper body (12).

Description

ディスクブレーキ装置Disc brake device
　本発明は、ディスクブレーキ装置に関する。 The present invention relates to a disc brake device.
　特許文献１、２に開示されている技術は、いずれもエアチャンバを動力（アクチュエータ）として、カムが回動されることで、ブレーキパッドによりロータを挟持するための押圧力が生じるタイプのディスクブレーキ装置である。 The technologies disclosed in Patent Documents 1 and 2 are disc brakes of a type in which a pressing force for holding a rotor by a brake pad is generated by rotating a cam using an air chamber as power (actuator). Device.
　このような機構を持つディスクブレーキ装置では、カムがシャフトに配置され、このシャフトがボディを貫くタイプと、シャフトを持たず、回動させるレバーの先端にカムが配置されたタイプのものが知られている。 In the disc brake device having such a mechanism, there are known a type in which a cam is disposed on a shaft and the shaft penetrates the body, and a type in which the cam is disposed at a tip of a lever that does not have a shaft and rotates. ing.
日本国特開平９－３２９１６９号公報Japanese Unexamined Patent Publication No. 9-329169 日本国特表２００１－５０２７７９号公報Japanese National Table 2001-501777 Publication
　ここで、カムシャフトにカムが配置されている場合には、シャフトの両端がボディに支持される必要がある。このため、押圧力を生じさせる際の反力がシャフトに対して曲げ応力として働くこととなる。よって、押圧力を高くすればするほど、シャフト径を太くする必要が生じるといった問題があった。 Here, when the cam is arranged on the camshaft, both ends of the shaft need to be supported by the body. For this reason, the reaction force at the time of generating the pressing force acts as a bending stress on the shaft. Therefore, there has been a problem that the higher the pressing force, the greater the need to increase the shaft diameter.
　また、レバーの先端にカムが配置される構造では、レバーの形態が複雑となり、ボディを分割構造とした上で、カムレバーを組み込む構成が採られている。このような構成を採った場合、押圧力を生じさせた際のボディ剛性が低くなってしまうという問題が生じる。このため、特許文献２には、ボディ剛性の低さを補うために、ロータの両側面を跨ぐキャリパボディの外周を巻回するサブフレームが設けられることが開示されている。 Also, in the structure in which the cam is arranged at the tip of the lever, the form of the lever becomes complicated, and the structure in which the cam lever is incorporated after the body is divided is adopted. When such a configuration is adopted, there arises a problem that the body rigidity is reduced when the pressing force is generated. For this reason, Patent Document 2 discloses that a sub-frame that winds the outer periphery of the caliper body straddling both side surfaces of the rotor is provided in order to compensate for the low body rigidity.
　本発明では、倍力機構にカムレバーを採用した場合であっても、ボディ剛性の低下を防ぐことのできる構造を持つディスクブレーキ装置を提供することを目的とする。 An object of the present invention is to provide a disc brake device having a structure capable of preventing a decrease in body rigidity even when a cam lever is employed as a booster mechanism.
　本発明に係る上記目的は、下記構成により達成される。
（１）　フレーム構造のキャリパボディを有するディスクブレーキ装置であって、前記キャリパボディは、少なくとも、ブレーキパッドを押圧するピストンと、回動により押圧力を生じさせるカムレバーと、前記ピストンと前記カムレバーとの間に介在されて前記押圧力を前記ピストンに伝達する押圧力伝達機構とを収容する収容部を備え、前記収容部は、前記ピストンと、前記カムレバーと、前記押圧力伝達機構とを前記キャリパボディにおける背肉側から組付け可能な開口部を有し、前記収容部および前記開口部の双方が、前記キャリパボディにおけるロータ配置側領域に開放されているディスクブレーキ装置。 The above object of the present invention is achieved by the following configuration.
(1) A disc brake device having a caliper body having a frame structure, wherein the caliper body includes at least a piston that presses a brake pad, a cam lever that generates a pressing force by rotation, and the piston and the cam lever. An accommodating portion for accommodating a pressing force transmission mechanism that is interposed therebetween and transmits the pressing force to the piston, and the accommodating portion connects the piston, the cam lever, and the pressing force transmission mechanism to the caliper body; The disc brake device has an opening that can be assembled from the back side of the housing, and both the housing and the opening are open to a rotor arrangement side region of the caliper body.
（２）　前記開口部を封止する押圧力発生部カバーを備え、前記押圧力発生部カバーには、前記収容部と前記ロータ配置側領域とを隔てる側壁が設けられ、前記側壁には、前記ピストンを前記ロータ配置領域側へ挿通させる貫通孔が設けられている上記（１）に記載のディスクブレーキ装置。 (2) A pressing force generation unit cover that seals the opening is provided, and the pressing force generation unit cover is provided with a side wall that separates the housing unit and the rotor arrangement side region, The disc brake device according to the above (1), wherein a through-hole through which the piston is inserted into the rotor arrangement region side is provided.
　上記（１）および（２）のような構成を有することによれば、収容部品の収容が容易となるように開放されている収容部、および開口部を収容部品収容後に封止、閉塞することができる。また、押圧力を生じさせるためのピストンについては、ロータ配置側領域への挿通が可能となる。 According to the configuration as described in the above (1) and (2), the housing part opened to facilitate the housing of the housing parts and the opening are sealed and closed after housing the housing parts. Can do. Further, the piston for generating the pressing force can be inserted into the rotor arrangement side region.
（３）　前記カムレバーを稼働させるアクチュエータを備え、前記アクチュエータは、前記カムレバーに係合される直動ロッドを有し、前記直動ロッドをエアの力で作動させるエアチャンバである上記（１）または（２）に記載のディスクブレーキ装置。 (3) The above-mentioned (1) or (1), further comprising an actuator that operates the cam lever, wherein the actuator is an air chamber that has a linear rod that is engaged with the cam lever and that operates the linear rod with the force of air. The disc brake device according to (2).
　上記（３）のような構成を有することによれば、カムレバーを稼働させるアクチュエータの構成を簡単化することができる。また、エアチャンバの動作により直動ロッドが作動するため、応答性が良い。 According to the configuration as described in (3) above, the configuration of the actuator that operates the cam lever can be simplified. Further, since the linear motion rod is activated by the operation of the air chamber, the responsiveness is good.
（４）　前記カムレバーを稼働させるアクチュエータを備え、前記アクチュエータは、前記カムレバーに係合される直動ロッドを有し、前記直動ロッドを介して、前記カムレバーをブレーキ稼働側に傾倒させる付勢機構と、前記カムレバーをブレーキ解除側に傾倒させるモータギアユニットと、を備えた上記（１）または（２）に記載のディスクブレーキ装置。 (4) An actuator for operating the cam lever, the actuator having a linear motion rod engaged with the cam lever, and biasing mechanism for tilting the cam lever toward the brake operating side via the linear motion rod And a motor gear unit that tilts the cam lever toward the brake release side. The disc brake device according to (1) or (2).
　上記（４）のような構成を有することによれば、アクチュエータ周りの配管を無くすことができる。また、作動用の流体を貯留するタンクやコンプレッサを排除することができる。 According to the above configuration (4), piping around the actuator can be eliminated. Moreover, the tank and compressor which store the working fluid can be excluded.
（５）　前記直動ロッドは、前記付勢機構によって押圧されるベースと、前記モータギアユニットによって回動されて前記ベースを軸線方向に移動させるボールねじとを有するボールねじ機構における前記ベースを基点として延設されている上記（４）に記載のディスクブレーキ装置。 (5) The linear rod is based on the base in a ball screw mechanism having a base pressed by the urging mechanism and a ball screw that is rotated by the motor gear unit to move the base in the axial direction. The disc brake device according to (4), which is extended as follows.
　上記（５）のような構成を有することによれば、ボールねじの回動力と付勢機構による反力を合わせる事で、ブレーキ作動時の応答性を高めることができる。 According to the configuration as described in (5) above, by combining the turning force of the ball screw and the reaction force by the urging mechanism, it is possible to improve the responsiveness at the time of braking operation.
（６）　前記モータギアユニットは、モータの回転軸の回動を自由にする電磁クラッチを備えた上記（５）に記載のディスクブレーキ装置。 (6) The disc brake device according to (5), wherein the motor gear unit includes an electromagnetic clutch that freely rotates the rotation shaft of the motor.
　上記（６）のような構成を有することによれば、電磁クラッチを稼働させることで、モータに供給する電力を停止させた場合であっても、ブレーキ解除状態を維持することができる。よって、ブレーキ解除時に常にモータに負荷をかけるという状態を避けることができる。 According to the above configuration (6), the brake release state can be maintained even when the electric power supplied to the motor is stopped by operating the electromagnetic clutch. Therefore, it is possible to avoid a state in which a load is always applied to the motor when the brake is released.
（７）　前記カムレバーは、前記押圧力伝達機構を跨ぐ二股構造とされ、各二股部の先端側に、カム部を備える上記（１）～（６）のいずれか１つに記載のディスクブレーキ装置。 (7) The disc brake device according to any one of (1) to (6), wherein the cam lever has a bifurcated structure straddling the pressing force transmission mechanism, and a cam portion is provided on a distal end side of each bifurcated portion. .
　上記（７）のような構成を有することによれば、押圧力伝達機構に対する押圧力付与のバランスをとることができる。 According to the configuration as described in (7) above, it is possible to balance the pressing force applied to the pressing force transmission mechanism.
（８）　前記押圧力伝達機構は、前記ピストンの押し出し位置を調整するアジャスタねじと、前記アジャスタねじを覆い、前記押圧力を受けるハウジングと、により構成されている上記（１）～（７）のいずれか１つに記載のディスクブレーキ装置。 (8) The pressing force transmission mechanism includes an adjuster screw that adjusts the pushing position of the piston, and a housing that covers the adjuster screw and receives the pressing force. The disc brake device according to any one of the above.
　上記（８）のような構成を有することによれば、ブレーキパッドのライニングが摩耗した場合であっても、アジャスタねじを回動させるだけで、ブレーキパッドとハウジングとの位置調整が可能となる。 According to the configuration as described in (8) above, even when the brake pad lining is worn, it is possible to adjust the position of the brake pad and the housing only by rotating the adjuster screw.
（９）　前記ハウジングの少なくとも一部に、前記ブレーキパッドの押圧方向に沿ったスライド溝が設けられ、前記キャリパボディに固定されたガイドボルトが前記スライド溝に沿って配置された上記（８）に記載のディスクブレーキ装置。
　上記（９）のような構成を有することによれば、ハウジングの回動を防ぐことができる。 (9) In the above (8), at least a part of the housing is provided with a slide groove along the pressing direction of the brake pad, and a guide bolt fixed to the caliper body is arranged along the slide groove. Disc brake device as described.
With the configuration as described in (9) above, the rotation of the housing can be prevented.
（１０）　前記押圧力伝達機構に、前記ハウジングのストロークを用いて前記アジャスタねじによる位置調整が成されるオートアジャスタ機構が付帯された上記（８）または（９）に記載のディスクブレーキ装置。 (10) The disc brake device according to (8) or (9), wherein the pressing force transmission mechanism is attached with an auto adjuster mechanism that adjusts a position by the adjuster screw using a stroke of the housing.
　上記（１０）のような構成を有することによれば、ブレーキパッドのライニングが摩耗した場合に、ブレーキパッドとハウジングとの位置調整が自動で行われることとなる。これにより、ロータの摺動面に対して、常に適正な押圧力を発生させることが可能となる。 According to the configuration as described in (10) above, when the lining of the brake pad is worn, the position adjustment between the brake pad and the housing is automatically performed. Thereby, it is possible to always generate an appropriate pressing force against the sliding surface of the rotor.
（１１）　前記カムレバーのカム部と前記ハウジングとの間に、摺動ピンが配置された上記（３）を含む上記（８）～（１０）のいずれか１つに記載のディスクブレーキ装置。 (11) The disc brake device according to any one of (8) to (10), including (3) above, wherein a sliding pin is disposed between the cam portion of the cam lever and the housing.
　上記（１１）のような構成を有することによれば、カム部とハウジングとの間の摺動性を向上させることができる。よって、カム部、およびハウジングの摩耗量の低減を図ることができる。さらに、摺動ピンの構成素材をカム部やハウジングよりも軟らかいものとすることで、摺動ピンの摩耗を促すことができる。これにより、摩耗による部品交換を摺動ピンのみの交換で対応することが可能となる。 According to the above configuration (11), the slidability between the cam portion and the housing can be improved. Therefore, the wear amount of the cam portion and the housing can be reduced. Furthermore, wear of the sliding pin can be promoted by making the constituent material of the sliding pin softer than the cam portion and the housing. This makes it possible to replace parts due to wear by replacing only the sliding pins.
　上記のような特徴を有するディスクブレーキ装置によれば、倍力機構にカムレバーを採用した場合であっても、ボディ剛性の低下を防ぐことが可能となる。また、カムレバー、および押圧力伝達機構の組付け性を向上させることができる。 According to the disc brake device having the above-described characteristics, it is possible to prevent a decrease in body rigidity even when a cam lever is employed as a booster mechanism. In addition, the assembling property of the cam lever and the pressing force transmission mechanism can be improved.
図１は本発明の実施形態に係るディスクブレーキ装置の構成を示す正面図である。FIG. 1 is a front view showing a configuration of a disc brake device according to an embodiment of the present invention. 図２は図１における（Ａ）－（Ａ）断面図である。2 is a cross-sectional view taken along the line (A)-(A) in FIG. 図３は本実施形態に係るディスクブレーキ装置の構成を示す分解斜視図である。FIG. 3 is an exploded perspective view showing the configuration of the disc brake device according to the present embodiment. 図４はユニット化された押圧力発生機構とキャリパボディとの関係を示す部分分解斜視断面図である。FIG. 4 is a partially exploded perspective sectional view showing the relationship between the unitized pressing force generating mechanism and the caliper body. 図５はユニット化された押圧力発生機構の構成を示す部分断面斜視図である。FIG. 5 is a partial cross-sectional perspective view showing the configuration of the unitized pressing force generating mechanism. 図６はオートアジャスタ機構の説明を行うための図である。FIG. 6 is a view for explaining the auto adjuster mechanism. 図７はアクチュエータを機械的構成としたディスクブレーキ装置の構成を示す斜視図である。FIG. 7 is a perspective view showing a configuration of a disc brake device in which an actuator has a mechanical configuration. 図８は図７における（Ａ）－（Ｂ）－（Ｃ）－（Ｄ）断面を示す図である。FIG. 8 is a view showing a cross section (A)-(B)-(C)-(D) in FIG. 図９は機械的構成のアクチュエータおよび押圧力発生機構の構成を示す部分分解斜視図である。FIG. 9 is a partially exploded perspective view showing the structure of the mechanically structured actuator and the pressing force generating mechanism.
　以下、本発明のディスクブレーキ装置に係る実施の形態について、図面を参照しつつ詳細に説明する。まず、図１から図６を参照して、本発明の実施形態に係るディスクブレーキ装置の構成を説明する。 Hereinafter, embodiments of the disc brake device of the present invention will be described in detail with reference to the drawings. First, the configuration of a disc brake device according to an embodiment of the present invention will be described with reference to FIGS.
　本実施形態に係るディスクブレーキ装置１０は、キャリパボディ１２と、サポート６０と、アクチュエータ５０とを基本として構成され、ロータ７０の摺動面にブレーキパッド６６，６８を押し付けることで、制動力を発揮する。 The disc brake device 10 according to the present embodiment is configured based on the caliper body 12, the support 60, and the actuator 50, and exerts braking force by pressing the brake pads 66 and 68 against the sliding surface of the rotor 70. To do.
　キャリパボディ１２は、押圧力発生部１４と、反力受け部１８と、ブリッジ部１６とを基本として構成されている。押圧力発生部１４は、押圧力を生じさせるピストン２０を含む押圧力発生機構２２が収容される要素である。 The caliper body 12 is configured on the basis of a pressing force generation unit 14, a reaction force receiving unit 18, and a bridge unit 16. The pressing force generation unit 14 is an element in which a pressing force generation mechanism 22 including a piston 20 that generates a pressing force is accommodated.
　反力受け部１８は、ロータ７０を介して押圧力発生部１４と対向配置され、押圧力発生時にピストン２０からの押圧力を受けるための要素である。反力受け部１８におけるロータ７０との対向面側には、ブレーキパッド６８を押えるためのパッド押え部が設けられている。 The reaction force receiving portion 18 is arranged to face the pressing force generating portion 14 via the rotor 70, and is an element for receiving the pressing force from the piston 20 when the pressing force is generated. A pad pressing portion for pressing the brake pad 68 is provided on the reaction force receiving portion 18 on the side facing the rotor 70.
　ブリッジ部１６は、ロータ７０の外周側を跨いで、押圧力発生部１４と反力受け部１８とを連結する要素である。 The bridge portion 16 is an element that connects the pressing force generating portion 14 and the reaction force receiving portion 18 across the outer peripheral side of the rotor 70.
　本実施形態に係るディスクブレーキ装置１０では、押圧力発生部１４と、反力受け部１８と、ブリッジ部１６とが、平面視で枠状に形成されたフレーム構造を成している。このため、ピストン２０の押圧による軸力に対する剛性を高めることが可能となる。また、押圧力発生部１４は、押圧力発生機構２２を収容するための収容部１４ａを備えている。収容部１４ａは、キャリパボディ１２の背肉側に開口部を備え、この開口部から押圧力発生機構２２を内装可能な構成とされている。このような構造を採用することにより、ディスクブレーキ装置１０の組み付け作業性を向上させることができる。 In the disc brake device 10 according to the present embodiment, the pressing force generation part 14, the reaction force receiving part 18, and the bridge part 16 form a frame structure formed in a frame shape in plan view. For this reason, it becomes possible to improve the rigidity with respect to the axial force by the press of the piston 20. The pressing force generation unit 14 includes an accommodating portion 14 a for accommodating the pressing force generation mechanism 22. The accommodating part 14a is provided with an opening on the back side of the caliper body 12, and is configured such that the pressing force generating mechanism 22 can be installed from the opening. By adopting such a structure, the workability of assembling the disc brake device 10 can be improved.
　押圧力発生機構２２には、ピストン２０と、押圧力伝達機構２４と、カムレバー４２とが含まれる。ピストン２０は、本実施形態に係る例の場合、ロータ７０の円周方向に長軸を持つ長円形状の押圧面を持ち、押圧力のバランスをとるために、２つの押圧部２０ａを備えた構造とされている。また、押圧部２０ａを備える面と反対側の面には、中心部に凸部２０ｂが設けられ、詳細を後述するアジャスタねじ３２に対する嵌合を可能な構成とされている。凸部２０ｂの中心には、押圧部形成面側に段部を持つ貫通孔が設けられており、固定ボルト２６の挿通が可能とされている。 The pressing force generation mechanism 22 includes a piston 20, a pressing force transmission mechanism 24, and a cam lever 42. In the case of the example according to the present embodiment, the piston 20 has an oval-shaped pressing surface having a long axis in the circumferential direction of the rotor 70, and includes two pressing portions 20a in order to balance the pressing force. It is structured. In addition, a convex portion 20b is provided at the center of the surface opposite to the surface including the pressing portion 20a, and is configured to be fitted to an adjuster screw 32, which will be described in detail later. A through-hole having a step portion on the pressing portion forming surface side is provided at the center of the convex portion 20b, and the fixing bolt 26 can be inserted.
　固定ボルト２６は、ねじ部２６ａと、スペーサ部２６ｂと、ボルト頭２６ｃとから成る。そして、ボルト頭２６ｃが段部に収容され、スペーサ部２６ｂが貫通孔に収容され、ねじ部２６ａが凸部２０ｂから突出するように各部の寸法が調整されている。 The fixing bolt 26 includes a screw portion 26a, a spacer portion 26b, and a bolt head 26c. And the dimension of each part is adjusted so that the bolt head 26c is accommodated in a step part, the spacer part 26b is accommodated in a through-hole, and the thread part 26a protrudes from the convex part 20b.
　また、ピストン２０と詳細を後述する押圧力発生部カバー２８との間には、塵埃の混入を防ぐブーツ３０が備えられている。 Also, a boot 30 is provided between the piston 20 and a pressing force generating unit cover 28, which will be described in detail later, to prevent dust from entering.
　押圧力伝達機構２４は、詳細を後述するカムレバー４２の操作によって生じる押圧力を上述したピストン２０に伝達する役割を担う。本実施形態の場合、押圧力伝達機構２４は、アジャスタねじ３２と、ハウジング３４とを主な構成要素とし、オートアジャスタ機構３６が付帯されている。 The pressing force transmission mechanism 24 plays a role of transmitting the pressing force generated by the operation of the cam lever 42 described later in detail to the piston 20 described above. In the case of the present embodiment, the pressing force transmission mechanism 24 includes an adjuster screw 32 and a housing 34 as main components, and an auto adjuster mechanism 36 is attached.
　アジャスタねじ３２は、ブレーキパッド６６，６８におけるライニングが摩耗した際に生ずる隙間を調整するための要素である。アジャスタねじ３２は、外観円筒形状を成し、外周面に雄ねじ部を有する。内周側には仕切板３２ａが設けられ、押圧部と摺動部に隔てられている。アジャスタねじ３２の押圧部側には、ピストン２０における凸部が遊嵌可能な凹部３２ｂが備えられる。仕切板３２ａには、固定ボルト２６のねじ部が螺合可能な雌ねじ部３２ｃが設けられている。なお、雌ねじ部３２ｃは、固定ボルト２６を螺着可能な深さを備えていれば、貫通孔であっても、袋穴とされていても良い。このような構成とすることで、固定ボルト２６が締めつけられた際に、スペーサ部２６ｂが仕切板３２aに当接することとなり、アジャスタねじ３２を回動させた場合であっても、ピストン２０は回動することなく、姿勢を保ち、かつピストン２０をアジャスタねじ３２の挙動に追従させることが可能となる。 The adjuster screw 32 is an element for adjusting a gap generated when the lining of the brake pads 66 and 68 is worn. The adjuster screw 32 has an external cylindrical shape and has an external thread portion on the outer peripheral surface. A partition plate 32a is provided on the inner peripheral side, and is divided into a pressing portion and a sliding portion. On the pressing portion side of the adjuster screw 32, a concave portion 32b in which the convex portion of the piston 20 can be loosely fitted is provided. The partition plate 32a is provided with a female screw portion 32c into which the screw portion of the fixing bolt 26 can be screwed. The female screw portion 32c may be a through hole or a bag hole as long as it has a depth to which the fixing bolt 26 can be screwed. With such a configuration, when the fixing bolt 26 is tightened, the spacer portion 26b comes into contact with the partition plate 32a, and the piston 20 can be rotated even when the adjuster screw 32 is rotated. Without moving, the posture can be maintained and the piston 20 can follow the behavior of the adjuster screw 32.
　一方、アジャスタねじ３２の摺動部側には、アジャスタねじ３２を回転させるアジャスタギア４０の回転軸４０ｂが引っ掛かりを持つ形態の穴３２ｄが備えられている。図５に示す実施形態では、詳細を後述するアジャスタギア４０の回転軸４０ｂは、先端形状（係合部４０ｃ）が六角形とされている。このため、穴３２ｄは、少なくとも六角形の対向配置された２辺を挟み込む辺を持った穴とされれば良い。すなわち、穴３２ｄの断面形状としては、図５に示すように、六角形や四角形、あるいは、平行な２辺を持つ長円形状などとすることができる。 On the other hand, on the sliding portion side of the adjuster screw 32, there is provided a hole 32d in which the rotary shaft 40b of the adjuster gear 40 that rotates the adjuster screw 32 is hooked. In the embodiment shown in FIG. 5, the rotary shaft 40b of the adjuster gear 40, which will be described in detail later, has a tip shape (engagement portion 40c) having a hexagonal shape. For this reason, the hole 32d may be a hole having a side that sandwiches at least two hexagonally opposed sides. That is, the cross-sectional shape of the hole 32d can be a hexagon, a quadrangle, or an ellipse having two parallel sides as shown in FIG.
　ハウジング３４は、アジャスタねじ３２が螺合される筒部３４ａと、押圧力が付与される押圧部３４ｂとから成る。筒部３４ａは、内周面に雌ねじ部を備えたホルダである。押圧部３４ｂは、筒部３４ａの外周から延設されている腕である。押圧部３４ｂは、筒部３４ａを基点として、ロータ７０の円周方向における回入側と回出側の双方に、対を成すように設けられている。このような配置形態とすることで、押圧力付加のバランスがとれ、押圧力伝達機構２４にこじれが生ずることを防止することができる。また、筒部３４ａを基端とする押圧部３４ｂの先端には、ブレーキパッド６６の押圧方向に沿ったスライド溝３４ｃが設けられている。スライド溝３４ｃは、詳細を後述するガイドボルト５２に沿ってハウジング３４を摺動させるための溝である。スライド溝３４ｃとガイドボルト５２を備えることで、アジャスタ時にハウジング３４が回転することを防止することができる。また、ロータ７０の円周方向におけるハウジング３４の両端をガイドすることで、ブレーキ制動時におけるロータ７０の回入側と回出側とのエネルギー差による偏荷重がカムレバー４２におけるカム部４２ａに作用することを抑制することができる。 The housing 34 includes a cylindrical portion 34a to which the adjuster screw 32 is screwed and a pressing portion 34b to which a pressing force is applied. The cylindrical portion 34a is a holder having an internal thread portion on the inner peripheral surface. The pressing portion 34b is an arm that extends from the outer periphery of the cylindrical portion 34a. The pressing portions 34b are provided so as to form a pair on both the turn-in side and the turn-out side in the circumferential direction of the rotor 70 with the cylindrical portion 34a as a base point. By adopting such an arrangement, it is possible to balance the pressing force application and prevent the pressing force transmission mechanism 24 from being twisted. Further, a slide groove 34c is provided along the pressing direction of the brake pad 66 at the distal end of the pressing portion 34b having the cylindrical portion 34a as a base end. The slide groove 34c is a groove for sliding the housing 34 along a guide bolt 52 whose details will be described later. By providing the slide groove 34c and the guide bolt 52, the housing 34 can be prevented from rotating during the adjustment. Further, by guiding both ends of the housing 34 in the circumferential direction of the rotor 70, an offset load due to an energy difference between the turning-in side and the feeding-out side of the rotor 70 during braking is applied to the cam portion 42 a of the cam lever 42. This can be suppressed.
　オートアジャスタ機構３６は、アジャスタレバー３８とアジャスタギア４０を基本として構成されている。アジャスタレバー３８は、レバー本体３８ａとフック部３８ｂから構成されている。レバー本体３８ａは、フック部３８ｂを支持すると共に、アジャスタレバー３８の挙動を制御する部位である。レバー本体３８ａの一方の端部には、回動基点３８ｃが設けられ、ハウジング３４における筒部３４ａの外周部に回動自在に固定される。レバー本体３８ａの他方の端部には、フック部３８ｂが連設される他、回動したレバー本体３８ａを引き戻すための張力を付加するためのスプリング３８ｄが取り付けられている。また、レバー本体３８ａには、ハウジング３４の移動に伴ってレバー本体３８ａに回動動作を付与するために、傾斜面を備えたカム溝３８ｅが設けられている。カム溝３８ｅには、配置形態を後述するブッシュ受け４６の上端に設けられたカム片４８が当接する。このため、ハウジング３４が矢印（ａ）の方向へ移動することにより、カム溝３８ｅの傾斜面がカム片４８に沿ってスライドし、レバー本体３８ａが矢印（ｂ）の方向へ回動することとなる。 The auto adjuster mechanism 36 is configured based on an adjuster lever 38 and an adjuster gear 40. The adjuster lever 38 includes a lever main body 38a and a hook portion 38b. The lever body 38 a is a part that supports the hook portion 38 b and controls the behavior of the adjuster lever 38. A pivot base point 38c is provided at one end of the lever main body 38a, and is fixed to the outer peripheral portion of the cylindrical portion 34a of the housing 34 so as to be rotatable. The other end of the lever main body 38a is provided with a hook 38b and a spring 38d for applying a tension for pulling back the rotated lever main body 38a. The lever main body 38a is provided with a cam groove 38e having an inclined surface in order to give the lever main body 38a a turning operation as the housing 34 moves. A cam piece 48 provided at the upper end of a bush receiver 46, which will be described later, contacts the cam groove 38e. Therefore, when the housing 34 moves in the direction of the arrow (a), the inclined surface of the cam groove 38e slides along the cam piece 48, and the lever body 38a rotates in the direction of the arrow (b). Become.
　フック部３８ｂは、レバー本体３８ａの他方の端部から、詳細を後述するアジャスタギア４０が配置された方向（本実施形態では下面側）へ屈曲形成されており、アジャスタギア４０の歯と噛合うように構成されている。 The hook portion 38b is bent from the other end of the lever main body 38a in a direction in which an adjuster gear 40, which will be described in detail later, is disposed (on the lower surface side in this embodiment), and meshes with the teeth of the adjuster gear 40. It is configured as follows.
　アジャスタギア４０は、アジャスタねじ３２を回動させるための要素である。アジャスタギア４０は、ギア本体４０ａと、回転軸４０ｂとを備える。ギア本体４０ａは、円板部の外周に備えた複数の歯に、アジャスタレバー３８のフック部３８ｂが係合することで、アジャスタレバー３８の動作に起因して回転が付与される要素である。一方、回転軸４０ｂは、アジャスタねじ３２の摺動部側に設けられた穴３２ｄに挿入され、穴３２ｄの内壁に係合し、アジャスタねじ３２に回転を伝達する要素である。このため、回転軸４０ｂには、穴３２ｄの内壁に引っ掛かりを持つための係合部４０ｃが備えられている。なお、本実施形態では、係合部４０ｃの形態は、断面形状が六角形とされている。 The adjuster gear 40 is an element for rotating the adjuster screw 32. The adjuster gear 40 includes a gear body 40a and a rotation shaft 40b. The gear body 40a is an element to which rotation is imparted due to the operation of the adjuster lever 38 by engaging the hook portion 38b of the adjuster lever 38 with a plurality of teeth provided on the outer periphery of the disc portion. On the other hand, the rotating shaft 40 b is an element that is inserted into the hole 32 d provided on the sliding portion side of the adjuster screw 32, engages with the inner wall of the hole 32 d, and transmits the rotation to the adjuster screw 32. For this reason, the rotating shaft 40b is provided with an engaging portion 40c for catching on the inner wall of the hole 32d. In the present embodiment, the engaging portion 40c has a hexagonal cross-sectional shape.
　このような構成のオートアジャスタ機構３６によれば、カムレバー４２の動作に起因してハウジング３４が矢印（ａ）の方向へ移動することで、アジャスタレバー３８がアジャスタギア４０を回動させてアジャスタねじ３２を押し出すこととなる。なお、アジャスタレバー３８は、カムレバー４２による押圧力の付与が解除されることによりハウジング３４が押し戻されると、スプリング３８ｄの力によって元の位置に引き戻される。アジャスタギア４０の歯は、鋸刃状に形成されているため、フック部３８ｂが引き戻される際には、引っ掛かりを持つことなく、その上部を摺動することとなる。このため、アジャスタレバー３８は、上下方向への遊びを持たせて固定するように構成されている。 According to the auto adjuster mechanism 36 having such a configuration, the housing 34 moves in the direction of the arrow (a) due to the operation of the cam lever 42, so that the adjuster lever 38 rotates the adjuster gear 40 to adjust the adjuster screw. 32 will be pushed out. The adjuster lever 38 is pulled back to the original position by the force of the spring 38d when the housing 34 is pushed back by releasing the pressing force applied by the cam lever 42. Since the teeth of the adjuster gear 40 are formed in a saw blade shape, when the hook portion 38b is pulled back, it slides on its upper part without being caught. For this reason, the adjuster lever 38 is configured to be fixed with play in the vertical direction.
　カムレバー４２は、カム部４２ａとレバー部４２ｂにより構成されている。カム部４２ａは、円弧状の湾曲部より構成され、湾曲部の厚みを異ならせるように構成されている。このような構成とすることで、カムレバー４２が傾倒した際に生ずる接触部のズレにより、湾曲部の厚み方向へ押圧力が生ずることとなる。すなわち、カムレバー４２は、レバー部４２ｂの長さ（回転中心からの長さ）と、カム部４２ａの厚みの変化量との比率に応じた倍力機構として、詳細を後述するアクチュエータ５０からの動力を押圧力に変化させることとなる。 The cam lever 42 includes a cam portion 42a and a lever portion 42b. The cam part 42a is comprised from the circular-arc-shaped curved part, and is comprised so that the thickness of a curved part may differ. With such a configuration, a pressing force is generated in the thickness direction of the bending portion due to the displacement of the contact portion that occurs when the cam lever 42 is tilted. That is, the cam lever 42 is a booster mechanism corresponding to the ratio between the length of the lever portion 42b (length from the rotation center) and the amount of change in the thickness of the cam portion 42a. Is changed to a pressing force.
　カムレバー４２は、その一端側にアクチュエータ５０との接続部を備え、他端側に上述したカム部４２ａを備える。カムレバー４２は、組付け状態においてハウジング３４の筒部３４ａを跨ぐように、カム部４２ａが配置されている側の端部が二股とされ、その両端それぞれに、カム部４２ａが配置される構成とされている。カム部４２ａが配置されている側の端部が二股構造とされることで、オートアジャスタ機構３６におけるアジャスタギア４０の回転軸４０ｂをキャリパボディ１２の中心に挿通させることが可能となる。また、ロータ７０の円周方向であって、キャリパボディ１２に対する回入側と回出側のそれぞれにカム部４２ａが配置されることで、押圧力をバランス良く生じさせることができる。 The cam lever 42 includes a connecting portion with the actuator 50 on one end side and the above-described cam portion 42a on the other end side. The cam lever 42 has a configuration in which the end portion on the side where the cam portion 42a is disposed is bifurcated so as to straddle the cylindrical portion 34a of the housing 34 in the assembled state, and the cam portions 42a are disposed at both ends thereof. Has been. Since the end portion on the side where the cam portion 42 a is disposed has a bifurcated structure, the rotation shaft 40 b of the adjuster gear 40 in the auto adjuster mechanism 36 can be inserted through the center of the caliper body 12. Further, since the cam portions 42a are arranged in the circumferential direction of the rotor 70 on each of the turn-in side and the turn-out side with respect to the caliper body 12, a pressing force can be generated with a good balance.
　ハウジング３４の押圧部３４ｂと、カムレバー４２のカム部４２ａとの間には、摺動ピン４４が配置される。また、カム部４２ａと収容部１４ａの内壁面との間には、ブッシュ受け４６が配置されている。さらに、摺動ピン４４とカム部４２ａとの間、およびカム部４２ａとブッシュ受け４６との間には、それぞれ、ピンブッシュ４４ａとカムブッシュ４６ａが設けられ、接触部間の摺動性の向上が図られている。なお、ブッシュ受け４６の上端には、上述したように、アジャスタレバー３８と接触するカム片４８が形成されている。 A sliding pin 44 is disposed between the pressing portion 34 b of the housing 34 and the cam portion 42 a of the cam lever 42. A bush receiver 46 is disposed between the cam portion 42a and the inner wall surface of the accommodating portion 14a. Further, a pin bush 44a and a cam bush 46a are provided between the slide pin 44 and the cam portion 42a and between the cam portion 42a and the bush receiver 46, respectively, and the slidability between the contact portions is improved. Is planned. As described above, the cam piece 48 that contacts the adjuster lever 38 is formed at the upper end of the bush receiver 46.
　キャリパボディ１２の収容部１４ａの側壁１４ｂには、貫通孔１４ｃが設けられている。アクチュエータ５０は、例えばエアチャンバなどであれば良く、収容部１４ａの貫通孔１４ｃに直動ロッド５０ａが挿通され、カムレバー４２におけるレバー部４２ｂの先端に接続された状態でキャリパボディ１２に組付けられる。また、ガイドボルト５２も、側壁１４ｂの外部から組み付けることで、キャリパボディ１２に固定することが可能となる。 The through-hole 14c is provided in the side wall 14b of the accommodating part 14a of the caliper body 12. FIG. The actuator 50 may be an air chamber, for example, and is assembled to the caliper body 12 in a state in which the linear motion rod 50a is inserted into the through hole 14c of the accommodating portion 14a and is connected to the tip of the lever portion 42b of the cam lever 42. . The guide bolt 52 can also be fixed to the caliper body 12 by assembling from the outside of the side wall 14b.
　収容部１４ａの開口部には、押圧力発生機構２２を覆い、当該開口部を封止する押圧力発生部カバー２８が備えられる。押圧力発生部カバー２８には、収容部１４ａにおけるロータ７０の配置側に位置する側壁２８ａが備えられている。押圧力発生部カバー２８が側壁２８ａを備えることで、収容部１４ａおよび収容部１４ａの開口部の双方が、ロータ７０を配置する領域（ロータ配置側領域）に開放されることとなる。このため、狭隘部となる収容部１４ａに対する収容部品の組み付け性を向上させることができる。また、ピストン２０などを配置する際に、側壁に設けられた孔への挿通を目的として、部品を傾けるといった必要が無くなる。このため、収容部１４ａの側壁と収容部品とのクリアランスを狭めることができる。よって、キャリパボディ１２の小型化や、収容部１４ａに対する収容部品の高密度化を図ることができる。なお、側壁２８ａには、収容部１４ａに配置したピストン２０をロータ配置側領域へ挿通させるための貫通孔２８ｂが設けられている。 The opening portion of the accommodating portion 14a is provided with a pressing force generating portion cover 28 that covers the pressing force generating mechanism 22 and seals the opening portion. The pressing force generating unit cover 28 includes a side wall 28a positioned on the side where the rotor 70 is disposed in the accommodating unit 14a. Since the pressing force generating unit cover 28 includes the side wall 28a, both the accommodating portion 14a and the opening of the accommodating portion 14a are opened to a region where the rotor 70 is disposed (rotor disposition side region). For this reason, the assembly | attachment property of the accommodating component with respect to the accommodating part 14a used as a narrow part can be improved. Further, when the piston 20 or the like is disposed, it is not necessary to incline the parts for the purpose of insertion into the hole provided in the side wall. For this reason, the clearance between the side wall of the accommodating portion 14a and the accommodating component can be narrowed. Therefore, it is possible to reduce the size of the caliper body 12 and to increase the density of the housing components with respect to the housing portion 14a. The side wall 28a is provided with a through hole 28b through which the piston 20 arranged in the accommodating portion 14a is inserted into the rotor arrangement side region.
　サポート６０は、図示しない車両や機器本体に対して、上述したキャリパボディ１２を保持するための要素である。サポート６０には、少なくとも、ガイドピン６２と、アンカ部６４とが備えられている。ガイドピン６２は、キャリパボディ１２をロータ７０の軸方向へ摺動自在に保持するための要素である。本実施形態では、キャリパボディ１２における押圧力発生部１４側と反力受け部１８側の双方に、ロータ７０の回入側と回出側に対を成すようにガイドピン６２がそれぞれ配置されている。各ガイドピン６２には、摺動部への塵埃の付着を防止すためのブーツ６２ａが設けられている。 The support 60 is an element for holding the caliper body 12 described above with respect to a vehicle or a device main body (not shown). The support 60 includes at least a guide pin 62 and an anchor portion 64. The guide pin 62 is an element for holding the caliper body 12 slidably in the axial direction of the rotor 70. In the present embodiment, guide pins 62 are arranged on both the pressing force generating portion 14 side and the reaction force receiving portion 18 side of the caliper body 12 so as to form a pair on the turn-in side and the turn-out side of the rotor 70, respectively. Yes. Each guide pin 62 is provided with a boot 62a for preventing dust from adhering to the sliding portion.
　アンカ部６４は、ロータ７０の回転を止める際のエネルギーを受け止めるための要素である。本実施形態では、ロータ７０の両主面に対応する押圧力発生部１４と反力受け部１８の双方に対応して凹部が設けられ、当該凹部のそれぞれにブレーキパッド６６，６８が配置される構成が採られている。このため、サポート６０には、ロータ７０の２つの主面の双方に対応する部位を連結するブリッジ部６０ａが設けられている。 The anchor portion 64 is an element for receiving energy when stopping the rotation of the rotor 70. In the present embodiment, concave portions are provided corresponding to both the pressing force generating portion 14 and the reaction force receiving portion 18 corresponding to both main surfaces of the rotor 70, and brake pads 66 and 68 are disposed in the concave portions, respectively. Configuration is adopted. For this reason, the support 60 is provided with a bridge portion 60 a that connects portions corresponding to both of the two main surfaces of the rotor 70.
　上記のような構成のディスクブレーキ装置１０によれば、倍力機構としてカムレバー４２を採用しつつ、キャリパボディ１２の剛性の低下を防ぐことが可能となる。また、キャリパボディ１２に設けた収容部１４ａの開口部がキャリパボディ１２の背肉側に設けられたことより、押圧力発生機構２２をユニット化した状態で組み付けることが可能となる。これにより、組付け作業の作業性を向上させることができる。さらに、オートアジャスタ機構３６が付帯されたことにより、ブレーキパッド６６，６８が摩耗した場合であっても、隙間を自動で詰めることができ、ロータ７０を挟持する際に好適な押圧力を生じさせることが可能となる。 According to the disc brake device 10 configured as described above, it is possible to prevent the caliper body 12 from being lowered in rigidity while adopting the cam lever 42 as a booster mechanism. In addition, since the opening of the accommodating portion 14a provided in the caliper body 12 is provided on the back side of the caliper body 12, the pressing force generating mechanism 22 can be assembled in a united state. Thereby, workability | operativity of an assembly | attachment operation | work can be improved. Further, since the auto adjuster mechanism 36 is attached, the gap can be automatically closed even when the brake pads 66 and 68 are worn, and a suitable pressing force is generated when the rotor 70 is clamped. It becomes possible.
　上記のような構成のディスクブレーキ装置１０の動作について説明する。まず、アクチュエータ５０であるエアチャンバにエアが導入されて直動ロッド５０ａが押し出されると、直動ロッド５０ａに連結されたカムレバー４２が、摺動ピン４４を基点として矢印（ｃ）の方向へ傾倒する（図２参照）。 The operation of the disc brake device 10 configured as described above will be described. First, when air is introduced into the air chamber which is the actuator 50 and the linear rod 50a is pushed out, the cam lever 42 connected to the linear rod 50a tilts in the direction of the arrow (c) with the slide pin 44 as a base point. (See FIG. 2).
　カムレバー４２が傾倒することにより、ハウジング３４の押圧部３４ｂとブッシュ受け４６との間に位置するカム部４２ａの厚みが、薄肉から厚肉へと移行する。これにより、厚み変化分だけ摺動ピン４４がロータ７０の配置方向へ押し出されることとなり、押圧力が発生する。押圧力の発生により、押圧力発生部１４側に配置されたブレーキパッド６６がロータ７０の摺動面に当接すると、押圧力の反力により、キャリパボディ１２は、押圧力発生部１４がロータ７０から離間する方向へと摺動する。これにより、反力受け部１８側に配置されていたブレーキパッド６８がロータ７０の摺動面に押し当てられ、ブレーキパッド６６，６８の双方により、ロータ７０が挟持されることとなる。 When the cam lever 42 is tilted, the thickness of the cam portion 42a located between the pressing portion 34b of the housing 34 and the bush receiver 46 is changed from thin to thick. As a result, the sliding pin 44 is pushed out in the arrangement direction of the rotor 70 by the thickness change, and a pressing force is generated. When the brake pad 66 arranged on the side of the pressing force generating unit 14 abuts against the sliding surface of the rotor 70 due to the generation of the pressing force, the caliper body 12 causes the pressing force generating unit 14 to move to the rotor by the reaction force of the pressing force. Slide in a direction away from 70. As a result, the brake pad 68 disposed on the reaction force receiving portion 18 side is pressed against the sliding surface of the rotor 70, and the rotor 70 is sandwiched between the brake pads 66 and 68.
　ここで、押圧力の発生によりハウジングが矢印（ａ）の方向へ移動すると（図６参照）、オートアジャスタ機構３６の作用により、アジャスタねじ３２が回動し、ピストン２０がロータ７０の配置側へ押し出されることとなる。 Here, when the housing is moved in the direction of the arrow (a) due to the generation of the pressing force (see FIG. 6), the adjuster screw 32 is rotated by the action of the auto adjuster mechanism 36, and the piston 20 moves to the arrangement side of the rotor 70. It will be pushed out.
　アクチュエータ５０であるエアチャンバへのエアの導入が停止されて直動ロッド５０ａが引き戻されると、カムレバー４２の傾倒も解除され、ハウジング３４が元の位置に押し戻される。この動作により、オートアジャスタ機構３６におけるアジャスタレバー３８も、スプリング３８ｄの作用によって元に戻されることとなる。 When the introduction of air into the air chamber, which is the actuator 50, is stopped and the linear rod 50a is pulled back, the tilting of the cam lever 42 is released and the housing 34 is pushed back to the original position. By this operation, the adjuster lever 38 in the auto adjuster mechanism 36 is also returned to the original state by the action of the spring 38d.
　上記実施形態では、カムレバー４２の構造について、カム部４２ａがロータ７０の配置側と逆側に湾曲する構造とされることを図示している。しかし、カム部４２ａの湾曲方向がロータ７０側とされた場合であっても、カムレバー４２の機能を発揮させることに支障は無い。なお、このような構成とする場合、カム部の下部側が薄肉部となり、カム部の上部側が厚肉部となるように、カム部を構成する必要がある。 In the above-described embodiment, the cam lever 42 has a structure in which the cam portion 42a is bent to the side opposite to the arrangement side of the rotor 70. However, even if the cam portion 42a is curved toward the rotor 70, there is no problem in exerting the function of the cam lever 42. In the case of such a configuration, it is necessary to configure the cam portion so that the lower side of the cam portion is a thin portion and the upper portion of the cam portion is a thick portion.
　また、上記実施形態では、アクチュエータ５０については、エアチャンバであるとしてその機構、および動作についての説明を行った。しかしながら、アクチュエータ５０は、モータを原動力として機械的に作動するものであっても良い。以下、アクチュエータ５０を機械的構成とする場合の一例について、図７から図９を参照して説明する。なお、アクチュエータ５０以外の構成において、上記実施形態に係る構成要素と同一の機能を果たす要素については、図面上に同一符号を付して、その詳細な説明は省略するものとする。その機能を果たす事ができれば、具体的形状は問わないからである。 In the above embodiment, the mechanism and operation of the actuator 50 are described as being an air chamber. However, the actuator 50 may be mechanically operated using a motor as a driving force. Hereinafter, an example in which the actuator 50 has a mechanical configuration will be described with reference to FIGS. 7 to 9. Note that, in the configuration other than the actuator 50, elements having the same functions as the components according to the above-described embodiment are denoted by the same reference numerals on the drawings, and detailed description thereof will be omitted. This is because the specific shape is not limited as long as the function can be achieved.
　図７から図９に示す（以下、代表して図７に示すと称す）アクチュエータ５０は、作動ユニット５０ｂと、モータギアユニット５０ｃとを基本として構成されている。作動ユニット５０ｂは、ボールねじ機構５０ｂ１と、スプリング５０ｂ４と、ガイドピン５０ｂ５と、ハウジング５０ｂ６とを基本として構成されている。 The actuator 50 shown in FIGS. 7 to 9 (hereinafter referred to as representatively shown in FIG. 7) is basically composed of an operation unit 50b and a motor gear unit 50c. The operation unit 50b is configured based on a ball screw mechanism 50b1, a spring 50b4, a guide pin 50b5, and a housing 50b6.
　ボールねじ機構５０ｂ１は、ボールねじ５０ｂ２と、このボールねじ５０ｂ２の軸線方向に移動可能なベース５０ｂ３と、ベース５０ｂ３を基点としてカムレバー４２方向へ延設される直動ロッド５０ａとを有する。このような構成のボールねじ機構５０ｂ１では、ボールねじ５０ｂ２に回動方向の力が加えられた場合には、ベース５０ｂ３が、ボールねじ５０ｂ２の軸線方向に移動する。一方、ベース５０ｂ３に対してボールねじ５０ｂ２の軸線方向への力が加えられた際、ボールねじ５０ｂ２が回転自在とされている場合には、ベース５０ｂ３の移動に伴ってボールねじ５０ｂ２が回転することとなる。そして、直動ロッド５０ａは、ベース５０ｂ３の移動に伴い、カムレバー４２の押し引き動作を行う動きを担うこととなる。 The ball screw mechanism 50b1 includes a ball screw 50b2, a base 50b3 movable in the axial direction of the ball screw 50b2, and a linear rod 50a extending in the cam lever 42 direction from the base 50b3. In the ball screw mechanism 50b1 having such a configuration, when a force in the rotation direction is applied to the ball screw 50b2, the base 50b3 moves in the axial direction of the ball screw 50b2. On the other hand, when a force in the axial direction of the ball screw 50b2 is applied to the base 50b3, if the ball screw 50b2 is rotatable, the ball screw 50b2 rotates with the movement of the base 50b3. It becomes. The linearly acting rod 50a is responsible for the movement of pushing and pulling the cam lever 42 as the base 50b3 moves.
　スプリング５０ｂ４は、皿ばねやコイルスプリングなどであれば良く、ボールねじ５０ｂ２の軸線方向への反力を生じさせる付勢機構としての役割を担う。図７に示す形態では、スプリング５０ｂ４は、ボールねじ５０ｂ２の外周を囲うように配置され、一方の端部側がハウジング５０ｂ６の端面へ当接し、他方の端部側がボールねじ５０ｂ２に係合しているベース５０ｂ３の主面に当接する構成とされている。 The spring 50b4 may be a disc spring or a coil spring, and serves as an urging mechanism that generates a reaction force in the axial direction of the ball screw 50b2. In the form shown in FIG. 7, the spring 50b4 is disposed so as to surround the outer periphery of the ball screw 50b2, one end side abuts against the end surface of the housing 50b6, and the other end side engages with the ball screw 50b2. The base 50b3 is in contact with the main surface.
　ガイドピン５０ｂ５は、ボールねじ５０ｂ２の軸線方向に沿って配置され、ベース５０ｂ３がボールねじ５０ｂ２の軸線方向へ移動する際のガイドをする役割を担う。図７に示す実施形態では、ハウジング５０ｂ６に固定されたガイドピン５０ｂ５が、ベース５０ｂ３に形成された貫通孔に挿通されることで、その機能を発揮している。 The guide pin 50b5 is disposed along the axial direction of the ball screw 50b2, and serves as a guide when the base 50b3 moves in the axial direction of the ball screw 50b2. In the embodiment shown in FIG. 7, the guide pin 50 b 5 fixed to the housing 50 b 6 is inserted into a through hole formed in the base 50 b 3 to exert its function.
　ハウジング５０ｂ６は、上述したボールねじ機構５０ｂ１とスプリング５０ｂ４と、ガイドピン５０ｂ５とを収容する外郭であり、収容部となるハウジング本体５０ｂ７と、ハウジング本体５０ｂ７を封止するハウジングカバー５０ｂ８とを有する。図７に示す形態では、ハウジングカバー５０ｂ８は、アクチュエータ５０をキャリパボディ１２に固定するためのブラケットとしての役割も担う。 The housing 50b6 is an outer shell that houses the ball screw mechanism 50b1, the spring 50b4, and the guide pin 50b5, and includes a housing body 50b7 that serves as a housing portion and a housing cover 50b8 that seals the housing body 50b7. In the form shown in FIG. 7, the housing cover 50 b 8 also serves as a bracket for fixing the actuator 50 to the caliper body 12.
　モータギアユニット５０ｃは、作動ユニット５０ｂにおけるボールねじ５０ｂ２を回動させるためのユニットである。モータギアユニット５０ｃは、モータ５０ｃ１と、ギアユニット５０ｃ４と、電磁クラッチ５０ｃ５とを有する。モータ５０ｃ１は、ボールねじ５０ｂ２を回動させるための動力を担い、図７に示す形態の場合、１本の回転軸がボディを貫いている両軸モータが採用され、ボディを介した一方の軸５０ｃ２がギアユニット５０ｃ４に係合し、他方の軸５０ｃ３が電磁クラッチ５０ｃ５に係合する構成とされている。 The motor gear unit 50c is a unit for rotating the ball screw 50b2 in the operation unit 50b. The motor gear unit 50c includes a motor 50c1, a gear unit 50c4, and an electromagnetic clutch 50c5. The motor 50c1 bears power for rotating the ball screw 50b2, and in the case of the form shown in FIG. 7, a double-axis motor in which one rotating shaft penetrates the body is adopted, and one shaft through the body is used. 50c2 engages with the gear unit 50c4, and the other shaft 50c3 engages with the electromagnetic clutch 50c5.
　ギアユニット５０ｃ４の構成は、特に限定するものでは無いが、少なくとも、モータ５０ｃ１の一方の軸５０ｃ２に係合するピニオンギアと、ボールねじ５０ｂ２に係合する駆動ギアとを備え、ピニオンギアと駆動ギアとの間に１つ乃至複数の減速ギアを備える構成とすれば良い。 The configuration of the gear unit 50c4 is not particularly limited, but includes at least a pinion gear that engages with one shaft 50c2 of the motor 50c1 and a drive gear that engages with the ball screw 50b2, and the pinion gear and the drive gear. A configuration in which one or a plurality of reduction gears is provided between the two.
　電磁クラッチ５０ｃ５は、モータ５０ｃ１の回転軸の自由回転を止めるための要素である。よって、電磁クラッチ５０ｃ５は、モータ５０ｃ１の他方の軸５０ｃ３に係合し、電力供給により、回転軸の自由回転を停止させることができる構成であれば良い。電磁クラッチ５０ｃ５を設ける事で、ブレーキ解除時に常にモータ５０ｃ１に負荷をかけておく必要が無くなる。なお、モータギアユニット５０ｃは、ハウジング５０ｃ６により外装を覆われている。 The electromagnetic clutch 50c5 is an element for stopping the free rotation of the rotation shaft of the motor 50c1. Therefore, the electromagnetic clutch 50c5 may be configured to engage with the other shaft 50c3 of the motor 50c1 and to stop the free rotation of the rotating shaft by supplying power. By providing the electromagnetic clutch 50c5, it is not necessary to always apply a load to the motor 50c1 when the brake is released. The motor gear unit 50c is covered with a housing 50c6.
　このような構成のモータギアユニット５０ｃによれば、モータ５０ｃ１を駆動させる事でボールねじ５０ｂ２が回動され、ベース５０ｂ３がギアユニット５０ｃ４側（すなわちスプリング５０ｂ４を圧縮させる方向）に引き付けられることとなる。一方、モータ５０ｃ１に対する電力の供給が停止されると、モータ５０ｃ１の回転軸は自由回転となる。ボールねじ５０ｂ２の回動により圧縮されたスプリング５０ｂ４は、ベース５０ｂ３とハウジング５０ｂ６の間で反力を生じさせ、ベース５０ｂ３をギアユニット５０ｃ４から離間させる方向へ押し戻す力を生じさせる。モータ５０ｃ１の回転軸は自由回転となり、スプリング５０ｂ４の反発力に対する抗力が小さい。このため、ベース５０ｂ３はボールねじ５０ｂ２を逆回転させながらギアユニット５０ｃ４から離間する方向へと移動することとなる。 According to the motor gear unit 50c having such a configuration, the ball screw 50b2 is rotated by driving the motor 50c1, and the base 50b3 is attracted toward the gear unit 50c4 (that is, the direction in which the spring 50b4 is compressed). . On the other hand, when the supply of power to the motor 50c1 is stopped, the rotation shaft of the motor 50c1 is freely rotated. The spring 50b4 compressed by the rotation of the ball screw 50b2 generates a reaction force between the base 50b3 and the housing 50b6, and generates a force to push the base 50b3 away from the gear unit 50c4. The rotating shaft of the motor 50c1 is free to rotate, and the resistance against the repulsive force of the spring 50b4 is small. Therefore, the base 50b3 moves in a direction away from the gear unit 50c4 while rotating the ball screw 50b2 in the reverse direction.
　ここで、スプリング５０ｂ４が圧縮された状態において、電磁クラッチ５０ｃ５を作動させた場合、モータ５０ｃ１の回転軸の自由回転は妨げられる。このため、モータ５０ｃ１に対する電力の供給を停止させた場合であっても、ベース５０ｂ３が押し戻されることは無い。 Here, when the electromagnetic clutch 50c5 is operated in a state where the spring 50b4 is compressed, the free rotation of the rotating shaft of the motor 50c1 is prevented. For this reason, even if it is a case where supply of electric power to motor 50c1 is stopped, base 50b3 is not pushed back.
　なお、図７に示す形態では、カムレバー４２と直動ロッド５０ａとが接続部材５０ｄを介して接続される構成とされている。このようなアクチュエータ５０がこのような構成とされた場合、モータ５０ｃ１、および電磁クラッチ５０ｃ５が双方とも非稼働な状態では、スプリング５０ｂ４の力によりベース５０ｂ３がギアユニット５０ｃ４から離間する歩行へ押し付けられる。このような状態では、ベース５０ｂ３から延設されている直動ロッド５０ａに接続されたカムレバー４２は、ブレーキを作動させる方向へと傾倒する状態となる。 In the embodiment shown in FIG. 7, the cam lever 42 and the linear rod 50a are connected via a connecting member 50d. When such an actuator 50 has such a configuration, when both the motor 50c1 and the electromagnetic clutch 50c5 are not in operation, the base 50b3 is pressed against the walk away from the gear unit 50c4 by the force of the spring 50b4. In such a state, the cam lever 42 connected to the linear rod 50a extending from the base 50b3 is inclined to the direction in which the brake is operated.
　これに対し、モータ５０ｃ１が駆動されると、ボールねじ５０ｂ２が回動され、ベース５０ｂ３がギアユニット５０ｃ４側へ引き付けられるように移動される。これにより、カムレバー４２は、ブレーキを解除させる方向へ引き戻される状態となる。また、この状態で電磁クラッチ５０ｃ５を稼働させる事で、モータ５０ｃ１への電力の供給を停止した場合でも、ブレーキを解除させた状態を維持することができる。 In contrast, when the motor 50c1 is driven, the ball screw 50b2 is rotated, and the base 50b3 is moved so as to be attracted to the gear unit 50c4 side. As a result, the cam lever 42 is pulled back in the direction of releasing the brake. Further, by operating the electromagnetic clutch 50c5 in this state, it is possible to maintain the state in which the brake is released even when the supply of power to the motor 50c1 is stopped.
　さらに、ブレーキを解除した状態からブレーキを作動させる際には、電磁クラッチ５０ｃ５の解除と共に、モータ５０ｃ１が、スプリング５０ｂ４を圧縮させる方向と逆方向に回転するように稼働される事で、ブレーキが作動するまでの時間を短縮することができ、応答性の向上を図ることができる。 Further, when the brake is operated from the state in which the brake is released, the brake is operated by releasing the electromagnetic clutch 50c5 and rotating the motor 50c1 in the direction opposite to the direction in which the spring 50b4 is compressed. It is possible to shorten the time until the operation is performed and to improve the responsiveness.
　アクチュエータ５０をこのような構成とした場合であっても、上記実施形態に係るディスクブレーキ装置１０と同様な効果を得る事ができる。 Even when the actuator 50 has such a configuration, the same effect as that of the disc brake device 10 according to the above embodiment can be obtained.
　ここで、上述した本発明に係るディスクブレーキ装置の実施の形態の特徴をそれぞれ以下に簡潔に纏めて列記する。
　［１］　フレーム構造のキャリパボディ（１２）を有するディスクブレーキ装置であって、
　前記キャリパボディは、少なくとも、ブレーキパッド（６６，６８）を押圧するピストン（２０）と、回動により押圧力を生じさせるカムレバー（４２）と、前記ピストンと前記カムレバーとの間に介在されて前記押圧力を前記ピストンに伝達する押圧力伝達機構（２４）とを収容する収容部（１４ａ）を備え、
　前記収容部は、前記ピストンと、前記カムレバーと、前記押圧力伝達機構とを前記キャリパボディにおける背肉側から組付け可能な開口部を有し、
　前記収容部および前記開口部の双方が、前記キャリパボディにおけるロータ配置側領域に開放されているディスクブレーキ装置（１０）。
　［２］　前記開口部を封止する押圧力発生部カバー（２８）を備え、
　前記押圧力発生部カバーには、前記収容部と前記ロータ配置側領域とを隔てる側壁（１４ｂ）が設けられ、
　前記側壁には、前記ピストンを前記ロータ配置領域側へ挿通させる貫通孔（１４ｃ）が設けられている上記［１］に記載のディスクブレーキ装置（１０）。
　［３］　前記カムレバーを稼働させるアクチュエータ（５０）を備え、
　前記アクチュエータは、前記カムレバーに係合される直動ロッド（５０ａ）を有し、前記直動ロッドをエアの力で作動させるエアチャンバである上記［１］または［２］に記載のディスクブレーキ装置。
　［４］　前記カムレバーを稼働させるアクチュエータを備え、
　前記アクチュエータは、前記カムレバーに係合される直動ロッドを有し、
　前記直動ロッドを介して、前記カムレバーをブレーキ稼働側に傾倒させる付勢機構（スプリング５０ｂ４）と、前記カムレバーをブレーキ解除側に傾倒させるモータギアユニット（５０ｃ）と、を備えた上記［１］または［２］に記載のディスクブレーキ装置。
　［５］　前記直動ロッドは、前記付勢機構によって押圧されるベース（５０ｂ３）と、前記モータギアユニットによって回動されて前記ベースを軸線方向に移動させるボールねじ（５０ｂ２）とを有するボールねじ機構（５０ｂ１）における前記ベースを基点として延設されている上記［４］に記載のディスクブレーキ装置。
　［６］　前記モータギアユニットは、モータ（５０ｃ１）の回転軸（他方の軸５０ｃ３）の回動を自由にする電磁クラッチ（５０ｃ５）を備えた上記［５］に記載のディスクブレーキ装置。
　［７］　前記カムレバー（４２）は、前記押圧力伝達機構を跨ぐ二股構造とされ、
　各二股部の先端側に、カム部（４２ａ）を備える上記［１］乃至［６］のいずれか１つに記載のディスクブレーキ装置。
　［８］　前記押圧力伝達機構は、
　前記ピストンの押し出し位置を調整するアジャスタねじ（３２）と、
　前記アジャスタねじを覆い、前記押圧力を受けるハウジング（３４）と、
により構成されている上記［１］乃至［７］のいずれか１つに記載のディスクブレーキ装置。
　［９］　前記ハウジングの少なくとも一部に、前記ブレーキパッドの押圧方向に沿ったスライド溝（３４ｃ）が設けられ、
　前記キャリパボディに固定されたガイドボルト（５２）が前記スライド溝に沿って配置された上記［８］に記載のディスクブレーキ装置。
　［１０］　前記押圧力伝達機構に、前記ハウジングのストロークを用いて前記アジャスタねじによる位置調整が成されるオートアジャスタ機構（３６）が付帯された上記［８］または［９］に記載のディスクブレーキ装置。
　［１１］　前記カムレバーのカム部と前記ハウジングとの間に、摺動ピン（４４）が配置された上記［３］を含む上記［８］乃至［１０］のいずれか１つに記載のディスクブレーキ装置。 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] A disc brake device having a caliper body (12) having a frame structure,
The caliper body is interposed between at least the piston (20) for pressing the brake pads (66, 68), the cam lever (42) for generating a pressing force by rotation, and the piston and the cam lever. An accommodating portion (14a) for accommodating a pressing force transmission mechanism (24) for transmitting a pressing force to the piston;
The accommodating portion has an opening capable of assembling the piston, the cam lever, and the pressing force transmission mechanism from the back side of the caliper body,
A disc brake device (10) in which both the accommodating portion and the opening portion are open to a rotor arrangement side region in the caliper body.
[2] A pressing force generator cover (28) for sealing the opening is provided,
The pressing force generating unit cover is provided with a side wall (14b) that separates the accommodating unit and the rotor arrangement side region,
The disc brake device (10) according to [1], wherein the side wall is provided with a through hole (14c) through which the piston is inserted toward the rotor arrangement region.
[3] An actuator (50) for operating the cam lever is provided,
The disc brake device according to [1] or [2], wherein the actuator includes a linear motion rod (50a) engaged with the cam lever, and is an air chamber that operates the linear motion rod with an air force. .
[4] An actuator for operating the cam lever is provided.
The actuator has a linear rod engaged with the cam lever;
The above [1], comprising: an urging mechanism (spring 50b4) for tilting the cam lever toward the brake operating side via the linear motion rod; and a motor gear unit (50c) for tilting the cam lever toward the brake release side. Or the disc brake device according to [2].
[5] The linear rod has a base (50b3) pressed by the urging mechanism and a ball screw (50b2) that is rotated by the motor gear unit to move the base in the axial direction. The disc brake device according to [4], wherein the disc brake device is extended from the base of the mechanism (50b1).
[6] The disc brake device according to [5], wherein the motor gear unit includes an electromagnetic clutch (50c5) that freely rotates the rotation shaft (the other shaft 50c3) of the motor (50c1).
[7] The cam lever (42) has a bifurcated structure straddling the pressing force transmission mechanism,
The disc brake device according to any one of [1] to [6], wherein a cam portion (42a) is provided on a distal end side of each bifurcated portion.
[8] The pressing force transmission mechanism includes:
An adjuster screw (32) for adjusting the pushing position of the piston;
A housing (34) for covering the adjuster screw and receiving the pressing force;
The disc brake device according to any one of [1] to [7], configured by:
[9] At least a part of the housing is provided with a slide groove (34c) along the pressing direction of the brake pad,
The disc brake device according to the above [8], wherein the guide bolt (52) fixed to the caliper body is disposed along the slide groove.
[10] The disc brake according to [8] or [9], wherein the pressing force transmission mechanism is attached with an auto adjuster mechanism (36) in which position adjustment is performed by the adjuster screw using a stroke of the housing. apparatus.
[11] The disc brake according to any one of [8] to [10], including the above [3], wherein a sliding pin (44) is disposed between the cam portion of the cam lever and the housing. apparatus.
　なお、本発明は、上述した実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。その他、上述した実施形態における各構成要素の材質、形状、寸法、数、配置箇所、等は本発明を達成できるものであれば任意であり、限定されない。
　また、本出願は、２０１５年４月２７日出願の日本特許出願（特願２０１５－０９０５６６）および２０１５年１１月１１日出願の日本特許出願（特願２０１５－２２１２１２）に基づくものであり、その内容はここに参照として取り込まれる。 In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.
This application is based on a Japanese patent application filed on April 27, 2015 (Japanese Patent Application No. 2015-090566) and a Japanese patent application filed on November 11, 2015 (Japanese Patent Application No. 2015-212212). The contents are incorporated herein by reference.
　本発明のディスクブレーキ装置によれば、倍力機構にカムレバーを採用した場合であっても、ボディ剛性の低下を防ぐことが可能となる。また、カムレバー、および押圧力伝達機構の組付け作業の作業性を向上させたディスクブレーキ装置を提供できる。 According to the disc brake device of the present invention, it is possible to prevent a decrease in body rigidity even when a cam lever is employed in the boost mechanism. Further, it is possible to provide a disc brake device that improves the workability of the assembly work of the cam lever and the pressing force transmission mechanism.
１０………ディスクブレーキ装置、１２………キャリパボディ、１４………押圧力発生部、１４ａ………収容部、１４ｂ………側壁、１４ｃ………貫通孔、１６………ブリッジ部、１８………反力受け部、２０………ピストン、２０ａ………押圧部、２０ｂ………凸部、２２………押圧力発生機構、２４………押圧力伝達機構、２６………固定ボルト、２６ａ………ねじ部、２６ｂ………スペーサ部、２６ｃ………ボルト頭、２８………押圧力発生部カバー、２８ａ………側壁、２８ｂ………貫通孔、３０………ブーツ、３２………アジャスタねじ、３２ａ………仕切板、３２ｂ………凹部、３２ｃ………雌ねじ部、３２ｄ………穴、３４………ハウジング、３４ａ………筒部、３４ｂ………押圧部、３４ｃ………スライド溝、３６………オートアジャスタ機構、３８………アジャスタレバー、３８ａ………レバー本体、３８ｂ………フック部、３８ｃ………回動基点、３８ｄ………スプリング、３８ｅ………カム溝、４０………アジャスタギア、４０ａ………ギア本体、４０ｂ………回転軸、４０ｃ………係合部、４２………カムレバー、４２ａ………カム部、４２ｂ………レバー部、４４………摺動ピン、４４ａ………ピンブッシュ、４６………ブッシュ受け、４６ａ………カムブッシュ、４８………カム片、５０………アクチュエータ、５０ａ………直動ロッド、５０ｂ………作動ユニット、５０ｂ１………ボールねじ機構、５０ｂ２………ボールねじ、５０ｂ３………ベース、５０ｂ４………スプリング、５０ｂ５………ガイドピン、５０ｂ６………ハウジング、５０ｂ７………ハウジング本体、５０ｂ８………ハウジングカバー、５０ｃ………モータギアユニット、５０ｃ１………モータ、５０ｃ２………一方の軸、５０ｃ３………他方の軸、５０ｃ４………ギアユニット、５０ｃ５………電磁クラッチ、５０ｃ６………ハウジング、５０ｄ………接続部材、５２………ガイドボルト、６０………サポート、６０ａ………ブリッジ部、６２………ガイドピン、６２ａ………ブーツ、６４………アンカ部、６６，６８………ブレーキパッド、７０………ロータ。 DESCRIPTION OF SYMBOLS 10 ......... Disc brake device, 12 ......... Caliper body, 14 ......... Pressure generating part, 14a ......... Accommodating part, 14b ......... Side wall, 14c ...... Through hole, 16 ......... Bridge part , 18... Reaction force receiving portion, 20... Piston, 20 a... Pressing portion, 20 b... Convex portion, 22 Pressing force generating mechanism, 24. ...... Fixing bolt, 26a ......... Screw part, 26b ......... Spacer part, 26c ......... Bolt head, 28 ......... Pressure generating part cover, 28a ......... Side wall, 28b ......... Through hole, 30 ......... Boots, 32 .... Adjuster screw, 32a ......... Partition plate, 32b ......... Recess, 32c ......... Female thread, 32d ......... Hole, 34 ......... Housing, 34a ......... Cylinder , 34b ......... Pressing part, 34c ......... Slide groove, 36 ......... O To adjuster mechanism, 38 ......... Adjuster lever, 38a ......... Lever body, 38b ......... Hook, 38c ......... Rotation base point, 38d ......... Spring, 38e ......... Cam groove, 40 ......... Adjuster gear, 40a ......... gear body, 40b ......... rotary shaft, 40c ......... engagement part, 42 ...... cam lever, 42a ......... cam part, 42b ......... lever part, 44 ......... slider Moving pin, 44a ......... Pin bushing, 46 ......... Bushing receiver, 46a ......... Cam bushing, 48 ......... Cam piece, 50 ......... Actuator, 50a ......... Direct acting rod, 50b ......... Activation Unit, 50b1 ......... Ball screw mechanism, 50b2 ......... Ball screw, 50b3 ......... Base, 50b4 ......... Spring, 50b5 ......... Guide pin, 50b6 ......... Housing, 50b7 ... Housing body, 50b8 ......... Housing cover, 50c ......... Motor gear unit, 50c1 ......... Motor, 50c2 ......... One shaft, 50c3 ......... Other shaft, 50c4 ......... Gear unit, 50c5 ......... Electromagnetic clutch, 50c6 ......... Housing, 50d ......... Connecting member, 52 ......... Guide bolt, 60 ......... Support, 60a ......... Bridge part, 62 ......... Guide pin, 62a ......... Boots, 64 ......... Anchor part, 66, 68 ......... Brake pads, 70 ...... Rotor.

Claims (11)

  1. 　フレーム構造のキャリパボディを有するディスクブレーキ装置であって、
    　前記キャリパボディは、少なくとも、ブレーキパッドを押圧するピストンと、回動により押圧力を生じさせるカムレバーと、前記ピストンと前記カムレバーとの間に介在されて前記押圧力を前記ピストンに伝達する押圧力伝達機構とを収容する収容部を備え、
    　前記収容部は、前記ピストンと、前記カムレバーと、前記押圧力伝達機構とを前記キャリパボディにおける背肉側から組付け可能な開口部を有し、
    　前記収容部および前記開口部の双方が、前記キャリパボディにおけるロータ配置側領域に開放されているディスクブレーキ装置。     A disc brake device having a caliper body having a frame structure,
    The caliper body includes at least a piston that presses a brake pad, a cam lever that generates a pressing force by rotation, and a pressing force transmission that is interposed between the piston and the cam lever and transmits the pressing force to the piston. A housing portion for housing the mechanism;
    The accommodating portion has an opening capable of assembling the piston, the cam lever, and the pressing force transmission mechanism from the back side of the caliper body,
    A disc brake device in which both the housing portion and the opening portion are opened to a rotor arrangement side region in the caliper body.
  2. 　前記開口部を封止する押圧力発生部カバーを備え、
    　前記押圧力発生部カバーには、前記収容部と前記ロータ配置側領域とを隔てる側壁が設けられ、
    　前記側壁には、前記ピストンを前記ロータ配置領域側へ挿通させる貫通孔が設けられている請求項１に記載のディスクブレーキ装置。     A pressing force generator cover for sealing the opening;
    The pressing force generating part cover is provided with a side wall that separates the accommodating part and the rotor arrangement side region,
    The disc brake device according to claim 1, wherein the side wall is provided with a through-hole through which the piston is inserted into the rotor arrangement region.
  3. 　前記カムレバーを稼働させるアクチュエータを備え、
    　前記アクチュエータは、前記カムレバーに係合される直動ロッドを有し、前記直動ロッドをエアの力で作動させるエアチャンバである請求項１または２に記載のディスクブレーキ装置。     An actuator for operating the cam lever;
    3. The disc brake device according to claim 1, wherein the actuator includes a linear motion rod engaged with the cam lever, and is an air chamber that operates the linear motion rod with an air force. 4.
  4. 　前記カムレバーを稼働させるアクチュエータを備え、
    　前記アクチュエータは、前記カムレバーに係合される直動ロッドを有し、
    　前記直動ロッドを介して、前記カムレバーをブレーキ稼働側に傾倒させる付勢機構と、前記カムレバーをブレーキ解除側に傾倒させるモータギアユニットと、を備えた請求項１または２に記載のディスクブレーキ装置。     An actuator for operating the cam lever;
    The actuator has a linear rod engaged with the cam lever;
    3. The disc brake device according to claim 1, further comprising: an urging mechanism for tilting the cam lever toward a brake operating side via the linear motion rod; and a motor gear unit for tilting the cam lever toward a brake release side. .
  5. 　前記直動ロッドは、前記付勢機構によって押圧されるベースと、前記モータギアユニットによって回動されて前記ベースを軸線方向に移動させるボールねじとを有するボールねじ機構における前記ベースを基点として延設されている請求項４に記載のディスクブレーキ装置。 The linear rod extends from the base in a ball screw mechanism having a base pressed by the urging mechanism and a ball screw rotated by the motor gear unit to move the base in the axial direction. The disc brake device according to claim 4.
  6. 　前記モータギアユニットは、モータの回転軸の回動を自由にする電磁クラッチを備えた請求項５に記載のディスクブレーキ装置。 The disc brake device according to claim 5, wherein the motor gear unit includes an electromagnetic clutch that freely rotates the rotation shaft of the motor.
  7. 　前記カムレバーは、前記押圧力伝達機構を跨ぐ二股構造とされ、
    　各二股部の先端側に、カム部を備える請求項１乃至６のいずれか１項に記載のディスクブレーキ装置。     The cam lever has a bifurcated structure straddling the pressing force transmission mechanism,
    The disc brake device according to any one of claims 1 to 6, further comprising a cam portion at a distal end side of each bifurcated portion.
  8. 　前記押圧力伝達機構は、
    　前記ピストンの押し出し位置を調整するアジャスタねじと、
    　前記アジャスタねじを覆い、前記押圧力を受けるハウジングと、
    により構成されている請求項１乃至７のいずれか１項に記載のディスクブレーキ装置。     The pressing force transmission mechanism is
    An adjuster screw for adjusting the push-out position of the piston;
    A housing that covers the adjuster screw and receives the pressing force;
    The disc brake device according to any one of claims 1 to 7, comprising:
  9. 　前記ハウジングの少なくとも一部に、前記ブレーキパッドの押圧方向に沿ったスライド溝が設けられ、
    　前記キャリパボディに固定されたガイドボルトが前記スライド溝に沿って配置された請求項８に記載のディスクブレーキ装置。     At least a part of the housing is provided with a slide groove along the pressing direction of the brake pad,
    The disc brake device according to claim 8, wherein a guide bolt fixed to the caliper body is disposed along the slide groove.
  10. 　前記押圧力伝達機構に、前記ハウジングのストロークを用いて前記アジャスタねじによる位置調整が成されるオートアジャスタ機構が付帯された請求項８または９に記載のディスクブレーキ装置。 10. The disc brake device according to claim 8, wherein an automatic adjuster mechanism that adjusts a position by the adjuster screw using a stroke of the housing is attached to the pressing force transmission mechanism.
  11. 　前記カムレバーのカム部と前記ハウジングとの間に、摺動ピンが配置された請求項３を含む請求項８乃至１０のいずれか１項に記載のディスクブレーキ装置。 The disc brake device according to any one of claims 8 to 10, including a slide pin disposed between a cam portion of the cam lever and the housing.
PCT/JP2016/062573 2015-04-27 2016-04-20 Disc brake apparatus WO2016175107A1 (en)

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US15/569,223 US10527114B2 (en) 2015-04-27 2016-04-20 Disc brake apparatus
EP16786384.4A EP3290734A4 (en) 2015-04-27 2016-04-20 Disc brake apparatus
CN201680024851.7A CN107532662B (en) 2015-04-27 2016-04-20 Disc brake assembly

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JP2015-221212 2015-11-11
JP2015221212A JP6572102B2 (en) 2015-04-27 2015-11-11 Disc brake device

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CN112334677A (en) * 2018-06-26 2021-02-05 日立汽车***株式会社 Disc brake
CN112539235A (en) * 2019-09-20 2021-03-23 现代摩比斯株式会社 Vehicle parking brake device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112334677A (en) * 2018-06-26 2021-02-05 日立汽车***株式会社 Disc brake
CN112539235A (en) * 2019-09-20 2021-03-23 现代摩比斯株式会社 Vehicle parking brake device
CN112539235B (en) * 2019-09-20 2022-12-20 现代摩比斯株式会社 Vehicle parking brake device

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