WO2017138415A1 - Electric brake device and method for manufacturing electric brake device - Google Patents

Electric brake device and method for manufacturing electric brake device Download PDF

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Publication number
WO2017138415A1
WO2017138415A1 PCT/JP2017/003614 JP2017003614W WO2017138415A1 WO 2017138415 A1 WO2017138415 A1 WO 2017138415A1 JP 2017003614 W JP2017003614 W JP 2017003614W WO 2017138415 A1 WO2017138415 A1 WO 2017138415A1
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WO
WIPO (PCT)
Prior art keywords
brake
electric
caliper
piston
brake disc
Prior art date
Application number
PCT/JP2017/003614
Other languages
French (fr)
Japanese (ja)
Inventor
山崎　達也
雅章 江口
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017138415A1 publication Critical patent/WO2017138415A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to an electric brake device using an electric motor as a drive source, and a method for manufacturing the electric brake device.
  • a hydraulic brake device using a hydraulic pressure as a drive source has been often adopted.
  • the hydraulic brake device uses a brake oil, and thus has a high environmental load.
  • an ABS a stability control system. It is difficult to further enhance the functions such as brake assist. Therefore, an electric brake device using an electric motor as a drive source has attracted attention as means for realizing further enhancement of the function of the brake device and reduction of environmental load.
  • the electric brake device described in Patent Document 1 includes a brake disc that rotates integrally with a wheel, an inner side and an outer side brake pad that face each other in the axial direction with the brake disc interposed therebetween, and a brake disc of the outer side brake pad.
  • a caliper body having a claw portion that supports a side surface opposite to the opposing side hereinafter referred to as “the back surface of the outer brake pad”
  • the back surface of the inner brake pad a side surface opposite to the brake disc side of the inner brake pad
  • This electric linear actuator has a piston disposed facing the back surface of the inner brake pad, an electric motor, and a linear mechanism that converts the rotation of the electric motor into a linear motion of the piston.
  • the piston is housed in a housing hole formed directly in the caliper body so as to be movable in parallel with the axial direction of the brake disk.
  • the rotational driving force of the electric motor is transmitted to the piston through the linear motion mechanism, and the piston moves linearly.
  • the piston presses the back surface of the inner brake pad, so that the inner brake pad is pressed against the brake disc.
  • the caliper body that is supported so as to be movable in the axial direction with respect to the brake disc is moved axially toward the inner side by the axial reaction force that the inner brake pad receives from the brake disc, and the rear side is moved by the claw portion of the caliper body.
  • the outer brake pad that is supported by is pressed against the brake disc. In this way, the inner and outer brake pads are pressed against the brake disc, and a braking force is generated on the brake disc by friction between the contact surfaces.
  • the electric brake device described in Patent Document 1 is for a small load assumed to be used for a rear wheel of a general size automobile or a front wheel of a small automobile.
  • the inventor of the present application uses an electric brake device as disclosed in Patent Document 1 for heavy loads (for example, a brake device for a front wheel of a general size automobile, a brake for a large automobile such as a bus or a truck). We considered adopting it as a device.
  • the inventor has noticed the following problems when the electric brake device described in Patent Document 1 is used for heavy loads. That is, in the electric brake device described in Patent Document 1, the number of electric linear motion actuators that press the back surface of the inner brake pad is one, and the piston of the piston that presses the back surface of the inner brake pad accordingly. The number is also one.
  • a caliper body having a claw portion for supporting a side surface opposite to the side facing the brake disc of one brake pad of the pair of brake pads opposed in the axial direction with the brake disc interposed therebetween;
  • the first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc.
  • the electric brake device having the above configuration is configured to press the back surface of the brake pad at two locations separated in the circumferential direction, even when the pressing force acting on the brake pad is increased, the pressure between the brake pad and the brake disk is increased. It tends to be uniform over the entire surface of the brake pad. For this reason, even when a large braking force is generated, the fade phenomenon hardly occurs and the wear of the brake pad does not easily progress.
  • the inventor differs in the number of electric linear actuators between the heavy load electric brake device and the light load electric brake device. I realized the possibility of sharing the shape of the electric linear actuator with the electric brake device.
  • the problem to be solved by the present invention is to reduce the manufacturing cost of a heavy-duty electric brake device in which the fade phenomenon is unlikely to occur and the wear of the brake pad is unlikely to proceed.
  • the present invention provides an electric brake device having the following configuration.
  • a caliper body having a claw portion for supporting a side surface opposite to the side facing the brake disc of one brake pad of the pair of brake pads opposed in the axial direction with the brake disc interposed therebetween;
  • the first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc.
  • the first and second electric linear actuators are electric brake devices that are detachably attached to the caliper body, respectively.
  • the first and second electric linear actuators can be respectively attached to and detached from the caliper body, at least one of the first and second electric linear actuators is manufactured as an electric brake device for a small load.
  • the manufacturing cost of the electric brake device can be reduced. That is, by attaching an electric linear actuator having the same shape as one of the first and second electric linear actuators to the caliper body for small loads, it is possible to manufacture an electric brake device for small loads. .
  • an electric linear actuator for the electric brake device for a large load and an electric linear actuator for the electric brake device for a small load are provided. The manufacturing cost of the electric brake device can be reduced.
  • the electric brake device is preferably added with the following configuration.
  • the first electric linear actuator includes a first piston disposed opposite to a side surface of the other brake pad opposite to the side facing the brake disc, and the first piston is disposed on the shaft of the brake disc.
  • a first piston housing that is movably accommodated parallel to the direction and is detachably fixed to the caliper body, a first electric motor, and the rotation of the first electric motor is converted into a linear motion of the first piston.
  • the second electric linear actuator is opposed to the side surface of the other brake pad opposite to the side facing the brake disc at a position away from the first piston in the circumferential direction of the brake disc.
  • a second linear motion mechanism that converts the linear motion of two pistons;
  • the first and second pistons have the same shape as each other,
  • the first and second piston housings have the same shape as each other,
  • the first and second electric motors have the same shape as each other,
  • the first and second linear motion mechanisms have the same shape.
  • the electric brake device can have the following configuration.
  • the first electric linear actuator includes two first caliper arms extending on both sides in the circumferential direction of the brake disc, and the caliper body is attached to one of the two first caliper arms.
  • a first slide pin that is movably supported parallel to the axial direction of the brake disc is fixed
  • the second electric linear actuator includes two second caliper arms extending on both sides in the circumferential direction of the brake disk, and the caliper body is attached to one of the two second caliper arms.
  • a second slide pin that is supported so as to be movable in parallel with the axial direction of the brake disc is fixed.
  • first caliper arm on the side of the two first caliper arms on which the first slide pin is not fixed is fixed to the caliper body, and the first caliper arm of the two second caliper arms is fixed.
  • the second caliper arm on the side where the two slide pins are not fixed can be fixed to the caliper body.
  • the two first caliper arms are axially displaced from each other;
  • the two second caliper arms are arranged so as to be offset from each other in the axial direction;
  • the first caliper arm on the side where the first slide pin is not fixed and the second slide pin of the two second caliper arms are not fixed
  • the second caliper arm on the side is fixed to the caliper body with a common bolt while being overlapped in the axial direction.
  • the caliper body has two caliper arms extending in parallel to the circumferential direction of the brake disc, and the two caliper arms support the caliper body so as to be movable in parallel with the axial direction of the brake disc. It is also possible to adopt a configuration in which the pins are fixed.
  • the present invention also provides a method for manufacturing an electric brake device for manufacturing a heavy load and a light load electric brake device having the following configuration.
  • a caliper body for heavy loads having a claw portion for supporting a side surface opposite to the side facing the brake disc of one of the pair of brake pads facing in the axial direction with the brake disc interposed therebetween; ,
  • the first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc.
  • a large load electric brake device is manufactured by detachably attaching the first and second electric linear actuators to the caliper body for large load, A caliper body for small loads smaller than the caliper body; An electric linear actuator having the same shape as at least one of the first and second electric linear actuators; Producing an electric brake device for small load by detachably attaching the electric linear actuator of the same shape to the caliper body for small load; Manufacturing method of electric brake device.
  • the electric brake device according to the present invention is configured to press the back surface of the brake pad at two locations separated in the circumferential direction, even when the pressing force acting on the brake pad is increased, the electric brake device is not provided between the brake pad and the brake disk.
  • the pressure tends to be uniform over the entire surface of the brake pad. Therefore, when a heavy load is generated, the fade phenomenon is unlikely to occur, and wear of the brake pad is unlikely to proceed.
  • the first and second electric linear actuators can be respectively attached to and detached from the caliper body, at least one of the first and second electric linear actuators is manufactured as an electric brake device for a small load. It is possible to reduce the manufacturing cost of the electric brake device by sharing the electric linear actuator used for the electric brake.
  • FIG. 2 is an enlarged sectional view in the vicinity of the first linear motion mechanism in FIG. Sectional view along line VI-VI in FIG.
  • FIG. 7 is a view of the electric brake device for small load shown in FIG.
  • FIG. 11 is a diagram of the electric brake device shown in FIG.
  • the electric brake device 1 includes a brake disk 2 that rotates integrally with a wheel (not shown), and inner and outer brake pads that face each other in the axial direction with the brake disk 2 interposed therebetween.
  • And caliper body 6 having a claw portion 5 that supports a side surface of the outer brake pad 4 opposite to the side facing the brake disc 2 (hereinafter referred to as “the rear surface of the outer brake pad 4”);
  • the first and second sides of the inner side brake pad 3 that press the side surface opposite to the side facing the brake disc 2 (hereinafter referred to as “the back side of the inner side brake pad 3”) at two locations apart in the circumferential direction of the brake disc 2
  • Second electric linear actuators 7a and 7b see FIG. 1).
  • the inner side and the outer side in the vehicle body width direction when the electric brake device 1 is assembled to the vehicle body are referred to as an inner side and an outer side, respectively.
  • a pair of ear pieces 8 are formed at both ends of the inner brake pad 3.
  • the ear piece 8 is slidably supported by a pair of guide grooves 10 formed in the mounting bracket 9.
  • the mounting bracket 9 is fixed to the vehicle body so as not to move in the axial direction with respect to the brake disc 2.
  • the guide groove 10 is a groove extending in parallel with the axial direction of the brake disk 2. Due to the engagement of the guide groove 10 and the ear piece 8, the inner brake pad 3 is supported so as to be movable between a position contacting the inner side surface of the brake disk 2 and a position separating from the inner side brake pad 3.
  • a pair of ear pieces 11 are formed at both ends of the outer brake pad 4.
  • the ear piece 11 is slidably supported by a pair of guide grooves 12 formed in the mounting bracket 9.
  • the guide groove 12 is a groove extending in parallel with the axial direction of the brake disk 2. Due to the engagement of the guide groove 12 and the ear piece 11, the outer brake pad 4 is supported so as to be movable between a position contacting the outer side surface of the brake disk 2 and a position separating the outer brake pad 4.
  • the inner brake pad 3 and the outer brake pad 4 include a friction material 13 that contacts the brake disk 2 and a back metal 14 that is bonded to the back surface of the friction material 13.
  • Ear pieces 8 and 11 (see FIGS. 1 and 3) of the inner brake pad 3 and the outer brake pad 4 are formed integrally with the back metal 14.
  • the caliper body 6 has a claw portion 5 facing the back surface of the outer brake pad 4 in the axial direction and an outer shell portion 15 facing the outer diameter side of the brake disc 2.
  • a screw hole 16 for fixing the first and second electric linear motion actuators 7a and 7b (see FIG. 1) is formed on the inner end face of the outer shell portion 15.
  • the first electric linear actuator 7 a has two first caliper arms 17 extending on both sides of the brake disk 2 in the circumferential direction.
  • the first slide pin 18 is fixed to one first caliper arm 17 of the two, and the other first caliper arm 17 is fixed to the caliper body 6 with a bolt 19.
  • the first slide pin 18 is a rod-like member extending in parallel with the axial direction of the brake disc 2 and is slidably inserted into a first pin hole 20 provided in the mounting bracket 9.
  • the first electric linear actuator 7 a is also fixed to the caliper body 6 with two bolts 21.
  • the first electric linear actuator 7 a can be attached to and detached from the caliper body 6 by attaching and detaching the bolts 19 and 21.
  • the second electric linear motion actuator 7b also has two second caliper arms 22 extending on both sides of the brake disk 2 in the circumferential direction.
  • a second slide pin 23 is fixed to one second caliper arm 22 of the two, and the other second caliper arm 22 is fixed to the caliper body 6 with a bolt 19.
  • the second slide pin 23 is a rod-like member extending in parallel with the axial direction of the brake disc 2 and is slidably inserted into a second pin hole 24 provided in the mounting bracket 9.
  • the second electric linear actuator 7 b is also fixed to the caliper body 6 with two bolts 25.
  • the second electric linear actuator 7b can be attached to and detached from the caliper body 6 by attaching and detaching the bolts 19 and 25.
  • the caliper body 6 and the first and second electric linear motion actuators 7a and 7b fixed to the caliper body 6 are the first and second slide pins 18 and 23, and the axial direction of the brake disk 2 is It is supported so that it can move in parallel.
  • the two first caliper arms 17 of the first electric linear actuator 7 a are arranged so as to be shifted from each other in the axial direction of the brake disk 2.
  • the two second caliper arms 22 of the second electric linear actuator 7b are also displaced from each other in the axial direction.
  • the arm 17 and the second caliper arm 22 on the side where the second slide pin 23 is not fixed overlap in the axial direction, and the first and second caliper arms 17 and 22 are fixed to the caliper body 6 by a common bolt 19. Has been.
  • the first electric linear actuator 7 a includes a first piston 26 a disposed so as to face the back surface of the inner brake pad 3, and the first piston 26 a is disposed in the axial direction of the brake disk 2.
  • a first piston housing 27a movably accommodated in parallel; a first electric motor 28a; a first linear motion mechanism 29a that converts the rotation of the first electric motor 28a into a linear motion of the first piston 26a;
  • a first reduction gear train 30a that reduces and transmits the rotation of the electric motor 28a to the first linear motion mechanism 29a.
  • the second electric linear actuator 7b is provided with a second piston 26b (opposed to the rear surface of the inner brake pad 3 at a position away from the first piston 26a in the circumferential direction of the brake disc 2). 4), a second piston housing 27b (see FIG. 4) for accommodating the second piston 26b so as to be movable in parallel with the axial direction of the inner brake disc 2, and a second electric motor 28b (see FIG. 1). And a second linear motion mechanism 29b (see FIG. 4) that converts the rotation of the second electric motor 28b into a linear motion of the second piston 26b, and the rotation of the second electric motor 28b is decelerated to the second linear motion mechanism 29b. And a second reduction gear train 30b (see FIG. 1) for transmission.
  • each component of the first electric linear actuator 7a and each component of the second electric linear actuator 7b have the same shape (in the figure, the first and second electric linear actuators).
  • Actuators 7a and 7b are the same). That is, the first and second pistons 26a and 26b have the same shape, the first and second piston housings 27a and 27b have the same shape, and the first and second electric motors 28a and 28b have the same shape.
  • the first and second linear motion mechanisms 29a and 29b have the same shape, and the first and second reduction gear trains 30a and 30b have the same shape. Therefore, hereinafter, regarding the second electric linear actuator 7b, portions corresponding to those of the first electric linear actuator 7a are denoted by the same reference numerals and description thereof is omitted.
  • the first piston housing 27a is configured such that the claw portion 5 of the caliper body 6 and the first piston housing 27a face each other in the axial direction with the inner side and outer side brake pads 3 and 4 therebetween. Is arranged.
  • the first piston housing 27 a is formed with a piston accommodation hole 31 that accommodates the first piston 26 a so as to be slidable in parallel with the axial direction of the brake disk 2.
  • the first electric motor 28a is disposed radially inward of the brake disk 2 with respect to the first piston 26a.
  • the first linear motion mechanism 29 a has a rotation shaft 32 disposed on the center line of the piston accommodation hole 31.
  • the first electric motor 28a is disposed so that the motor shaft 33 of the first electric motor 28a and the rotation shaft 32 of the first linear motion mechanism 29a are parallel to each other.
  • the first reduction gear train 30a includes an input gear 34 to which the rotation of the first electric motor 28a is input, an output gear 35 that outputs the rotation to the first linear motion mechanism 29a, and the input gear 34 and the output gear 35. And a plurality of intermediate gears 36 for transmitting the rotation.
  • the first linear motion mechanism 29a converts the rotation input to the rotary shaft 32 from the first electric motor 28a via the first reduction gear train 30a into the axial movement of the first piston 26a.
  • the first reduction gear train 30a is accommodated in a gear case 37 attached to the first piston housing 27a.
  • the gear case 37 includes a side plate 38 and a lid 39.
  • the side plate 38 is attached in parallel to the brake disc 2 at the end of the first piston housing 27a opposite to the brake disc 2 side.
  • the first electric motor 28 a is attached to the side plate 38.
  • the first piston housing 27a is formed with a bolt insertion hole 40 penetrating in parallel with the axial direction of the brake disc 2.
  • the first piston housing 27 a is fixed to the caliper body 6 by tightening the bolt 21 inserted into the bolt insertion hole 40.
  • the first caliper arm 17 (see FIG. 1) is formed integrally with the first piston housing 27a.
  • the first linear motion mechanism 29 a includes a plurality of planetary rollers 41 that are provided between the inner periphery of the first piston 26 a and the outer periphery of the rotary shaft 32 at intervals in the circumferential direction. And a carrier 42 for holding the planetary rollers 41 so as to be capable of rotating and revolving.
  • the first piston 26a is formed in a cylindrical shape that faces the outer periphery of the rotary shaft 32 in the radial direction.
  • Each planetary roller 41 is in rolling contact with the outer periphery of the rotating shaft 32.
  • the contact portion of the rotating shaft 32 with respect to the planetary roller 41 is a cylindrical surface.
  • each planetary roller 41 revolves around the rotating shaft 32 along the inner periphery of the first piston 26a while rotating around the roller shaft 43.
  • a spiral ridge 44 is provided on the inner periphery of the first piston 26a.
  • the spiral ridge 44 is a ridge that extends obliquely with a predetermined lead angle with respect to the circumferential direction.
  • On the outer periphery of each planetary roller 41 a plurality of circumferential grooves 45 that engage with the spiral ridges 44 are formed at intervals in the axial direction. The interval between the circumferential grooves 45 adjacent to each other in the axial direction on the outer periphery of each planetary roller 41 is the same as the pitch of the spiral ridges 44.
  • the circumferential groove 45 having a lead angle of 0 degree is provided on the outer periphery of the planetary roller 41, but a spiral groove having a lead angle different from that of the spiral protrusion 44 may be provided instead of the circumferential groove 45. .
  • the carrier 42 is provided at the center of each planetary roller 41, and is provided at the center of each planetary roller 41 and a pair of discs 46, 47 facing each other in the axial direction with the planetary roller 41 therebetween, a connecting portion 48 for connecting the discs 46, 47 together.
  • a roller shaft 43 to be supported. Both ends of each roller shaft 43 are supported by disks 46 and 47, respectively.
  • Each of the disks 46 and 47 is formed in an annular shape that penetrates the rotating shaft 32, and a sliding bearing 49 that is in sliding contact with the outer periphery of the rotating shaft 32 is mounted on the inner periphery thereof.
  • a thrust bearing 50 is incorporated that supports the planetary roller 41 in the axial direction in a rotatable state. Further, between the thrust bearing 50 and the disk 47, an aligning seat 51 that supports the planetary roller 41 so as to be tiltable via the thrust bearing 50 is incorporated.
  • the rotary shaft 32 penetrates at a position away from the brake disc 2 (see FIG. 2) when viewed from the first piston 26a.
  • a reaction force receiving member 52 formed in an annular shape is provided on the inner periphery of the reaction force receiving member 52.
  • a plurality of rolling bearings 53 that support the rotary shaft 32 in a rotatable manner are incorporated.
  • a thrust bearing 54 that supports the carrier 42 in the axial direction in a revolving state is incorporated.
  • a spacer 55 that revolves integrally with the carrier 42 is incorporated between the carrier 42 and the thrust bearing 54.
  • a boot 56 is attached to the opening edge of the piston receiving hole 31 on the brake disc 2 side.
  • the boot 56 is a cylindrical member that can be expanded and contracted in the axial direction, folded in a bellows shape.
  • One end of the boot 56 is connected to the inner periphery of the piston accommodation hole 31, and the other end of the boot 56 is connected to the outer periphery of the first piston 26a.
  • the boot 56 prevents foreign matter from entering between the sliding surfaces of the piston accommodation hole 31 and the first piston 26a.
  • an engagement recess 58 that engages with an engagement projection 57 formed on the back surface of the inner brake pad 3 is formed. The engagement of the engagement recess 58 prevents the first piston 26a from rotating.
  • the first linear motion mechanism 29 a transmits the rotation to the planetary roller 41 that is in rolling contact with the outer periphery of the rotation shaft 32, and each planetary roller 41 rotates around the roller shaft 43. Revolves around the rotating shaft 32. At this time, the planetary roller 41 and the first piston 26a are relatively moved in the axial direction by the engagement between the circumferential groove 45 on the outer periphery of the planetary roller 41 and the spiral protrusion 44 on the inner periphery of the first piston 26a.
  • the roller 41 Since the roller 41 is restricted from moving in the axial direction together with the carrier 42, the planetary roller 41 does not move in the axial direction with respect to the first piston housing 27a, and the first piston 26a does not move in the axial direction with respect to the first piston housing 27a. Move in the direction.
  • the 1st linear motion mechanism 29a converts rotation of the rotating shaft 32 into the linear motion of the 1st piston 26a.
  • the second linear motion mechanism 29b also converts the rotation transmitted from the second electric motor 28b (see FIG. 1) to the rotating shaft 32 into the linear motion of the second piston 26b (see FIG. 4).
  • the caliper body 6 slides with respect to the mounting bracket 9 due to the axial reaction force received by the first and second pistons 26a, 26b from the brake disc 2, and the claw portion 5 of the caliper body 6 moves to the outer brake.
  • the back surface of the pad 4 is pressed, and the outer brake pad 4 is pressed against the outer side surface of the brake disc 2.
  • the inner brake pad 3 and the outer brake pad 4 are pressed against the brake disc 2, and braking force is generated on the brake disc 2 due to friction between the contact surfaces of the brake pads 3, 4 and the brake disc 2.
  • the electric brake device 1 is configured to press the back surface of the inner brake pad 3 at two locations separated in the circumferential direction, the inner brake is applied even when the pressing force acting on the inner brake pad 3 is increased.
  • the pressure between the pad 3 and the brake disc 2 tends to be uniform over the entire surface of the inner brake pad 3. Therefore, even when a large braking force (a large load) is generated, a fade phenomenon (the friction material 13 of the inner brake pad 3 becomes hot and generates gas, and the gas causes the inner brake pad 3 and the brake disc 2 to be generated. It is possible to effectively prevent the frictional force between the inner brake pad 3 and the inner brake pad 3 from being worn locally.
  • the first and second electric linear actuators 7a and 7b are detachably attached to the caliper body 6, respectively. Therefore, the first and second electric linear actuators 7a and 7b are provided.
  • the manufacturing cost of the electric brake device 1 can be reduced by sharing at least one of them with the electric linear actuator 7a used for manufacturing the electric brake device 60 for small load as shown in FIGS. It is possible.
  • an electric linear actuator 7a (see FIG. 10) having the same shape as the first electric linear actuator 7a shown in FIGS. 1 to 4, and the electric linear actuator A small load caliper body 61 that can be attached to only one 7a is used, and the electric linear actuator 7a is attached to the caliper body 61 for small load to manufacture an electric brake device 60 for small load. can do.
  • the electric brake device 60 for small loads shown in FIGS. 7 to 9 differs from the electric brake device 1 for heavy loads shown in FIGS. 1 to 4 only in the number of electric linear actuators. Other basic configurations are the same.
  • slide pins 63 are fixed to the two first caliper arms 17 extending from the first piston housing 27a to both sides in the circumferential direction of the brake disc 62 (see FIG. 8).
  • Each slide pin 63 is slidably inserted into a pin hole 65 formed in the mounting bracket 64 for small load, and the slide pin 63 slides to cause the caliper body 61 for small load and the first electric linear motion.
  • the actuator 7a is movable in parallel with the axial direction of the brake disc 62 for light load with respect to the mounting bracket 64 for light load.
  • each component of the first electric linear actuator 7a and each component of the second electric linear actuator 7b have the same shape, so that the manufacturing cost of the electric brake device 1 can be further increased. It can be effectively reduced.
  • the first caliper arm 17 on the side where the first slide pin 18 is not fixed and the second caliper arm 22 on the side where the second slide pin 23 is not fixed are in the axial direction. Since the arms 17 and 22 overlap each other, the size of the electric brake device 1 can be reduced.
  • the first and second electric linear motion actuators 7a and 7b are provided with the first and second caliper arms 17 and 22 for fixing the first and second slide pins 18 and 23, respectively.
  • a caliper arm 66 for fixing the first and second slide pins 18 and 23 can be provided on the caliper body 6 side.
  • the electric brake device 1 shown in FIG. 11 and FIG. 12 is different from the electric brake device 1 of the above embodiment only in the caliper arm 66, and the other portions are the same.
  • the parts corresponding to are denoted by the same reference numerals and description thereof is omitted.
  • the caliper body 6 for heavy loads to which both the first and second electric linear motion actuators 7a and 7b can be attached has a circumferential direction of the brake disc 2 (see FIG. 2).
  • Two caliper arms 66 extending in parallel are provided.
  • the caliper body 61 for a small load to which only one electric linear actuator 7a having the same shape as the first electric linear actuator 7a can be attached is also provided on the brake disc 62 (FIG. 8). 2) and two caliper arms 67 extending in parallel with the circumferential direction.
  • the first and second linear motion mechanisms 29a and 29b that convert the rotations transmitted from the first and second electric motors 28a and 28b into linear motions of the first and second pistons 26a and 26b, respectively.
  • the planetary roller mechanism using the planetary roller 41 is employed
  • other types of linear motion mechanisms feed screw mechanism, ball ramp mechanism, etc.
  • the first and second electric motors 28a and 28b are disposed radially inward of the brake disc 2 with respect to the first and second pistons 26a and 26b, respectively. You may arrange

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Abstract

An electric brake device having: a caliper body (6) that has a claw part (5) for supporting the side surface of an outer-side brake pad (4) on the opposite side from that facing a brake disc (2); and first and second electric linear actuators (7a, 7b) for pressing, at two locations set at a distance in the circumferential direction of the brake disc (2), the side surface of an inner-side brake pad (3) on the opposite side from that facing the brake disc (2). Each of the first and second electric linear actuators (7a, 7b) is detachably attached to the caliper body (6).

Description

電動ブレーキ装置および電動ブレーキ装置の製造方法Electric brake device and method of manufacturing electric brake device
　この発明は、電動モータを駆動源とする電動ブレーキ装置、および電動ブレーキ装置の製造方法に関する。 The present invention relates to an electric brake device using an electric motor as a drive source, and a method for manufacturing the electric brake device.
　従来、車両用ブレーキ装置として、油圧を駆動源とする油圧ブレーキ装置が多く採用されてきたが、油圧ブレーキ装置は、ブレーキオイルを使用するので環境負荷が高く、またＡＢＳ、スタビリティ・コントロール・システム、ブレーキアシスト等といった機能の更なる高機能化が難しい。そこで、ブレーキ装置の更なる高機能化と環境負荷の低減を実現する手段として、電動モータを駆動源とする電動ブレーキ装置が注目されている。 Conventionally, as a brake device for a vehicle, a hydraulic brake device using a hydraulic pressure as a drive source has been often adopted. However, the hydraulic brake device uses a brake oil, and thus has a high environmental load. Also, an ABS, a stability control system. It is difficult to further enhance the functions such as brake assist. Therefore, an electric brake device using an electric motor as a drive source has attracted attention as means for realizing further enhancement of the function of the brake device and reduction of environmental load.
　電動ブレーキ装置として、例えば、下記特許文献１に記載のものが知られている。特許文献１に記載の電動ブレーキ装置は、車輪と一体に回転するブレーキディスクと、ブレーキディスクを間に挟んで軸方向に対向するインナ側およびアウタ側ブレーキパッドと、アウタ側ブレーキパッドのブレーキディスクに対向する側とは反対側の側面（以下「アウタ側ブレーキパッドの背面」という）を支持する爪部をもつキャリパボディと、インナ側ブレーキパッドのブレーキディスクに対向する側とは反対側の側面（以下「インナ側ブレーキパッドの背面」という）を押圧する単一の電動式直動アクチュエータとを有する。 As an electric brake device, for example, the one described in Patent Document 1 below is known. The electric brake device described in Patent Document 1 includes a brake disc that rotates integrally with a wheel, an inner side and an outer side brake pad that face each other in the axial direction with the brake disc interposed therebetween, and a brake disc of the outer side brake pad. A caliper body having a claw portion that supports a side surface opposite to the opposing side (hereinafter referred to as “the back surface of the outer brake pad”), and a side surface opposite to the brake disc side of the inner brake pad ( Hereinafter referred to as “the back surface of the inner brake pad”).
　この電動式直動アクチュエータは、インナ側ブレーキパッドの背面に対向して配置されたピストンと、電動モータと、その電動モータの回転をピストンの直線運動に変換する直動機構とを有する。ここで、ピストンは、キャリパボディに直接形成した収容孔にブレーキディスクの軸方向と平行に移動可能に収容されている。 This electric linear actuator has a piston disposed facing the back surface of the inner brake pad, an electric motor, and a linear mechanism that converts the rotation of the electric motor into a linear motion of the piston. Here, the piston is housed in a housing hole formed directly in the caliper body so as to be movable in parallel with the axial direction of the brake disk.
　この電動ブレーキ装置は、電動モータが回転すると、その電動モータの回転駆動力が直動機構を介してピストンに伝達し、ピストンが直線移動する。そして、このピストンがインナ側ブレーキパッドの背面を押圧することで、インナ側ブレーキパッドがブレーキディスクに押し付けられる。このとき、インナ側ブレーキパッドがブレーキディスクから受ける軸方向反力によって、ブレーキディスクに対し軸方向に移動可能に支持されたキャリパボディが、インナ側に軸方向移動し、キャリパボディの爪部によって背面を支持されたアウタ側ブレーキパッドがブレーキディスクに押し付けられる。このようにして、インナ側およびアウタ側ブレーキパッドがブレーキディスクに押し付けられ、その接触面間の摩擦によって、ブレーキディスクに制動力が発生する。 In this electric brake device, when the electric motor rotates, the rotational driving force of the electric motor is transmitted to the piston through the linear motion mechanism, and the piston moves linearly. The piston presses the back surface of the inner brake pad, so that the inner brake pad is pressed against the brake disc. At this time, the caliper body that is supported so as to be movable in the axial direction with respect to the brake disc is moved axially toward the inner side by the axial reaction force that the inner brake pad receives from the brake disc, and the rear side is moved by the claw portion of the caliper body. The outer brake pad that is supported by is pressed against the brake disc. In this way, the inner and outer brake pads are pressed against the brake disc, and a braking force is generated on the brake disc by friction between the contact surfaces.
特開２０１５－１３７６６７号公報JP2015-137667A
　特許文献１に記載の電動ブレーキ装置は、一般的な大きさの自動車の後輪や小型自動車の前輪に使用することを想定した小荷重用のものである。ここで本願の発明者は、特許文献１のような電動ブレーキ装置を、大荷重用のもの（例えば、一般的な大きさの自動車の前輪のブレーキ装置や、バスやトラック等の大型自動車のブレーキ装置など）として採用することを検討した。 The electric brake device described in Patent Document 1 is for a small load assumed to be used for a rear wheel of a general size automobile or a front wheel of a small automobile. Here, the inventor of the present application uses an electric brake device as disclosed in Patent Document 1 for heavy loads (for example, a brake device for a front wheel of a general size automobile, a brake for a large automobile such as a bus or a truck). We considered adopting it as a device.
　ところが、発明者は、特許文献１に記載の電動ブレーキ装置を、大荷重用のものとして使用したときに、次のような問題があることに気付いた。すなわち、特許文献１に記載の電動ブレーキ装置においては、インナ側ブレーキパッドの背面を押圧する電動式直動アクチュエータの個数が１つであり、これに伴いインナ側ブレーキパッドの背面を押圧するピストンの個数も１つとされている。 However, the inventor has noticed the following problems when the electric brake device described in Patent Document 1 is used for heavy loads. That is, in the electric brake device described in Patent Document 1, the number of electric linear motion actuators that press the back surface of the inner brake pad is one, and the piston of the piston that presses the back surface of the inner brake pad accordingly. The number is also one.
　そのため、大荷重（大きな制動力）を発生するため、ピストンからインナ側ブレーキパッドに作用する押圧力を大きくすると、インナ側ブレーキパッドとブレーキディスクの間の圧力がインナ側ブレーキパッドの全面において均一とならない。この結果、フェード現象（ブレーキパッドの摩擦部分が高温となってガスを発生し、そのガスによってインナ側ブレーキパッドとブレーキディスクの間の摩擦力が低下する現象）が生じやすくなるという問題や、インナ側ブレーキパッドが局所的に摩耗しやすくなるという問題があることが分かった。 For this reason, in order to generate a large load (a large braking force), if the pressing force acting on the inner brake pad from the piston is increased, the pressure between the inner brake pad and the brake disk is uniform over the entire surface of the inner brake pad. Don't be. As a result, a fading phenomenon (a phenomenon in which the frictional portion of the brake pad becomes hot and generates gas, which reduces the frictional force between the inner brake pad and the brake disk) is likely to occur. It has been found that there is a problem that the side brake pads are likely to be locally worn.
　そして、発明者は、大荷重を発生するときにもフェード現象が生じにくく、またブレーキパッドの局所的な摩耗が生じにくい大荷重用の電動ブレーキ装置として、以下の構成のものを社内において発案した。
　ブレーキディスクを間に挟んで軸方向に対向する一対のブレーキパッドのうち一方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を支持する爪部をもつキャリパボディと、
　前記一対のブレーキパッドのうち他方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を前記ブレーキディスクの周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータと、
　を有する電動ブレーキ装置。 Then, the inventor has invented an in-house configuration of the following configuration as an electric brake device for a heavy load that hardly causes a fade phenomenon even when a heavy load is generated, and that does not easily cause local wear of a brake pad. .
A caliper body having a claw portion for supporting a side surface opposite to the side facing the brake disc of one brake pad of the pair of brake pads opposed in the axial direction with the brake disc interposed therebetween;
The first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc. When,
Electric brake device having
　上記構成の電動ブレーキ装置は、ブレーキパッドの背面を周方向に離れた２箇所で押圧する構成なので、ブレーキパッドに作用する押圧力を大きくした場合にも、ブレーキパッドとブレーキディスクの間の圧力がブレーキパッドの全面において均一となりやすい。そのため、大きな制動力を発生したときにも、フェード現象が生じにくく、またブレーキパッドの摩耗が進行しにくい。 Since the electric brake device having the above configuration is configured to press the back surface of the brake pad at two locations separated in the circumferential direction, even when the pressing force acting on the brake pad is increased, the pressure between the brake pad and the brake disk is increased. It tends to be uniform over the entire surface of the brake pad. For this reason, even when a large braking force is generated, the fade phenomenon hardly occurs and the wear of the brake pad does not easily progress.
　ここで、発明者は、大荷重用の電動ブレーキ装置と、小荷重用の電動ブレーキ装置とで、電動式直動アクチュエータの個数が異なるが、大荷重用の電動ブレーキ装置と、小荷重用の電動ブレーキ装置とで、電動式直動アクチュエータの形状を共通化することができる可能性に気付いた。 Here, the inventor differs in the number of electric linear actuators between the heavy load electric brake device and the light load electric brake device. I realized the possibility of sharing the shape of the electric linear actuator with the electric brake device.
　この発明が解決しようとする課題は、フェード現象が生じにくく、またブレーキパッドの摩耗が進行しにくい大荷重用の電動ブレーキ装置の製造コストを低減することである。 The problem to be solved by the present invention is to reduce the manufacturing cost of a heavy-duty electric brake device in which the fade phenomenon is unlikely to occur and the wear of the brake pad is unlikely to proceed.
　上記課題を解決するため、この発明では、以下の構成の電動ブレーキ装置を提供する。
　ブレーキディスクを間に挟んで軸方向に対向する一対のブレーキパッドのうち一方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を支持する爪部をもつキャリパボディと、
　前記一対のブレーキパッドのうち他方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を前記ブレーキディスクの周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータとを有し、
　前記第１および第２電動式直動アクチュエータは、それぞれ前記キャリパボディに着脱可能に取り付けられている電動ブレーキ装置。 In order to solve the above problems, the present invention provides an electric brake device having the following configuration.
A caliper body having a claw portion for supporting a side surface opposite to the side facing the brake disc of one brake pad of the pair of brake pads opposed in the axial direction with the brake disc interposed therebetween;
The first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc. And
The first and second electric linear actuators are electric brake devices that are detachably attached to the caliper body, respectively.
　このようにすると、ブレーキパッドの背面を周方向に離れた２箇所で押圧する構成であるため、ブレーキパッドに作用する押圧力を大きくした場合にも、ブレーキパッドとブレーキディスクの間の圧力がブレーキパッドの全面において均一となりやすい。そのため、大荷重を発生するときに、フェード現象が生じにくく、またブレーキパッドの摩耗が進行しにくい。 In this case, since the rear surface of the brake pad is pressed at two locations separated in the circumferential direction, the pressure between the brake pad and the brake disk is maintained even when the pressing force acting on the brake pad is increased. It tends to be uniform over the entire surface of the pad. Therefore, when a heavy load is generated, the fade phenomenon is unlikely to occur, and wear of the brake pad is unlikely to proceed.
　また、第１および第２電動式直動アクチュエータがそれぞれキャリパボディに着脱可能とされているので、その第１および第２電動式直動アクチュエータの少なくとも一方を、小荷重用の電動ブレーキ装置の製造に用いられる電動式直動アクチュエータと共通化することで、電動ブレーキ装置の製造コストを低減することができる。すなわち、第１および第２電動式直動アクチュエータのいずれかと同一形状の電動式直動アクチュエータを小荷重用のキャリパボディに取り付けることで、小荷重用の電動ブレーキ装置を製造することが可能である。このように、大荷重用および小荷重用の電動ブレーキ装置を製造するに際し、大荷重用の電動ブレーキ装置の電動式直動アクチュエータと、小荷重用の電動ブレーキ装置の電動式直動アクチュエータとを共通化することができ、電動ブレーキ装置の製造コストを低減することができる。 Further, since the first and second electric linear actuators can be respectively attached to and detached from the caliper body, at least one of the first and second electric linear actuators is manufactured as an electric brake device for a small load. By making it common with the electric linear actuator used in the above, the manufacturing cost of the electric brake device can be reduced. That is, by attaching an electric linear actuator having the same shape as one of the first and second electric linear actuators to the caliper body for small loads, it is possible to manufacture an electric brake device for small loads. . As described above, when manufacturing an electric brake device for a large load and a small load, an electric linear actuator for the electric brake device for a large load and an electric linear actuator for the electric brake device for a small load are provided. The manufacturing cost of the electric brake device can be reduced.
　上記電動ブレーキ装置は、以下の構成を加えると好ましい。
　第１電動式直動アクチュエータは、前記他方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面に対向して配置された第１ピストンと、その第１ピストンを前記ブレーキディスクの軸方向と平行に移動可能に収容し、前記キャリパボディに着脱可能に固定される第１ピストンハウジングと、第１電動モータと、その第１電動モータの回転を前記第１ピストンの直線運動に変換する第１直動機構とを有し、
　第２電動式直動アクチュエータは、前記第１ピストンに対して前記ブレーキディスクの周方向に離れた位置で、前記他方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面に対向して配置された第２ピストンと、その第２ピストンを前記ブレーキディスクの軸方向と平行に移動可能に収容する第２ピストンハウジングと、第２電動モータと、その第２電動モータの回転を前記第２ピストンの直線運動に変換する第２直動機構とを有し、
　前記第１および第２ピストンは、互いに同一形状とされ、
　前記第１および第２ピストンハウジングは、互いに同一形状とされ、
　前記第１および第２電動モータは、互いに同一形状とされ、
　前記第１および第２直動機構は、互いに同一形状とされている。 The electric brake device is preferably added with the following configuration.
The first electric linear actuator includes a first piston disposed opposite to a side surface of the other brake pad opposite to the side facing the brake disc, and the first piston is disposed on the shaft of the brake disc. A first piston housing that is movably accommodated parallel to the direction and is detachably fixed to the caliper body, a first electric motor, and the rotation of the first electric motor is converted into a linear motion of the first piston. A first linear motion mechanism;
The second electric linear actuator is opposed to the side surface of the other brake pad opposite to the side facing the brake disc at a position away from the first piston in the circumferential direction of the brake disc. The second piston, the second piston housing that accommodates the second piston so as to be movable parallel to the axial direction of the brake disc, the second electric motor, and the rotation of the second electric motor. A second linear motion mechanism that converts the linear motion of two pistons;
The first and second pistons have the same shape as each other,
The first and second piston housings have the same shape as each other,
The first and second electric motors have the same shape as each other,
The first and second linear motion mechanisms have the same shape.
　このようにすると、前記第１電動式直動アクチュエータの各構成部品と前記第２電動式直動アクチュエータの各構成部品とが同一形状なので、電動ブレーキ装置の製造コストをより効果的に低減することが可能となる。 If it does in this way, since each component of the said 1st electric linear actuator and each component of the said 2nd electric linear actuator are the same shape, the manufacturing cost of an electric brake device can be reduced more effectively. Is possible.
　また上記電動ブレーキ装置は、以下の構成を加えることができる。
　前記第１電動式直動アクチュエータは、前記ブレーキディスクの周方向の両側に延びる２本の第１キャリパアームを有し、その２本の第１キャリパアームのうちの一方に、前記キャリパボディを前記ブレーキディスクの軸方向と平行に移動可能に支持する第１スライドピンが固定され、
　前記第２電動式直動アクチュエータは、前記ブレーキディスクの周方向の両側に延びる２本の第２キャリパアームを有し、その２本の第２キャリパアームのうちの一方に、前記キャリパボディを前記ブレーキディスクの軸方向と平行に移動可能に支持する第２スライドピンが固定されている。 The electric brake device can have the following configuration.
The first electric linear actuator includes two first caliper arms extending on both sides in the circumferential direction of the brake disc, and the caliper body is attached to one of the two first caliper arms. A first slide pin that is movably supported parallel to the axial direction of the brake disc is fixed,
The second electric linear actuator includes two second caliper arms extending on both sides in the circumferential direction of the brake disk, and the caliper body is attached to one of the two second caliper arms. A second slide pin that is supported so as to be movable in parallel with the axial direction of the brake disc is fixed.
　さらに、前記２本の第１キャリパアームのうちの前記第１スライドピンが固定されていない側の第１キャリパアームを前記キャリパボディに固定し、前記２本の第２キャリパアームのうちの前記第２スライドピンが固定されていない側の第２キャリパアームを前記キャリパボディに固定することができる。 Furthermore, the first caliper arm on the side of the two first caliper arms on which the first slide pin is not fixed is fixed to the caliper body, and the first caliper arm of the two second caliper arms is fixed. The second caliper arm on the side where the two slide pins are not fixed can be fixed to the caliper body.
　この場合、さらに以下の構成を採用すると好ましい。
　前記２本の第１キャリパアームは互いに軸方向にずれて配置され、
　前記２本の第２キャリパアームは互いに軸方向にずれて配置され、
　前記２本の第１キャリパアームのうちの前記第１スライドピンが固定されていない側の第１キャリパアームと、前記２本の第２キャリパアームのうちの前記第２スライドピンが固定されていない側の第２キャリパアームとが、軸方向に重なった状態で共通のボルトで前記キャリパボディに固定されている。 In this case, it is preferable to further adopt the following configuration.
The two first caliper arms are axially displaced from each other;
The two second caliper arms are arranged so as to be offset from each other in the axial direction;
Of the two first caliper arms, the first caliper arm on the side where the first slide pin is not fixed and the second slide pin of the two second caliper arms are not fixed The second caliper arm on the side is fixed to the caliper body with a common bolt while being overlapped in the axial direction.
　このようにすると、第１スライドピンが固定されていない側の第１キャリパアームと、第２スライドピンが固定されていない側の第２キャリパアームとが軸方向に重なった配置となるため、そのアーム同士が重なっている分、電動ブレーキ装置のサイズを小型化することが可能となる。 In this case, since the first caliper arm on the side where the first slide pin is not fixed and the second caliper arm on the side where the second slide pin is not fixed overlap with each other in the axial direction, Since the arms overlap each other, the size of the electric brake device can be reduced.
　前記キャリパボディは、前記ブレーキディスクの周方向と平行に延びる２本のキャリパアームを有し、その２本のキャリパアームに、キャリパボディを前記ブレーキディスクの軸方向と平行に移動可能に支持するスライドピンがそれぞれ固定されている構成を採用することも可能である。 The caliper body has two caliper arms extending in parallel to the circumferential direction of the brake disc, and the two caliper arms support the caliper body so as to be movable in parallel with the axial direction of the brake disc. It is also possible to adopt a configuration in which the pins are fixed.
　またこの発明では、大荷重用および小荷重用の電動ブレーキ装置を製造する電動ブレーキ装置の製造方法として、以下の構成のものを提供する。
　ブレーキディスクを間に挟んで軸方向に対向する一対のブレーキパッドのうち一方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を支持する爪部をもつ大荷重用のキャリパボディと、
　前記一対のブレーキパッドのうち他方のブレーキパッドの前記ブレーキディスクに対向する側とは反対側の側面を前記ブレーキディスクの周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータとを使用し、
　その第１および第２電動式直動アクチュエータを、いずれも前記大荷重用のキャリパボディに着脱可能に取り付けることにより大荷重用の電動ブレーキ装置を製造し、
　前記キャリパボディよりも小型の小荷重用のキャリパボディと、
　前記第１および第２電動式直動アクチュエータの少なくとも一方と同一形状の電動式直動アクチュエータとを使用し、
　前記同一形状の電動式直動アクチュエータを前記小荷重用のキャリパボディに着脱可能に取り付けることにより小荷重用の電動ブレーキ装置を製造する、
　電動ブレーキ装置の製造方法。 The present invention also provides a method for manufacturing an electric brake device for manufacturing a heavy load and a light load electric brake device having the following configuration.
A caliper body for heavy loads having a claw portion for supporting a side surface opposite to the side facing the brake disc of one of the pair of brake pads facing in the axial direction with the brake disc interposed therebetween; ,
The first and second electric linear motion actuators that press the side surface of the other brake pad opposite to the side facing the brake disc at two locations apart in the circumferential direction of the brake disc. And use
A large load electric brake device is manufactured by detachably attaching the first and second electric linear actuators to the caliper body for large load,
A caliper body for small loads smaller than the caliper body;
An electric linear actuator having the same shape as at least one of the first and second electric linear actuators;
Producing an electric brake device for small load by detachably attaching the electric linear actuator of the same shape to the caliper body for small load;
Manufacturing method of electric brake device.
　このようにすると、大荷重用の電動ブレーキ装置の電動式直動アクチュエータと、小荷重用の電動ブレーキ装置の電動式直動アクチュエータとを共通化することができ、電動ブレーキ装置の製造コストを低減することができる。 In this way, the electric linear actuator of the electric brake device for heavy loads and the electric linear actuator of the electric brake device for small loads can be shared, and the manufacturing cost of the electric brake device is reduced. can do.
　この発明の電動ブレーキ装置は、ブレーキパッドの背面を周方向に離れた２箇所で押圧する構成であるため、ブレーキパッドに作用する押圧力を大きくした場合にも、ブレーキパッドとブレーキディスクの間の圧力がブレーキパッドの全面において均一となりやすい。そのため、大荷重を発生するときに、フェード現象が生じにくく、またブレーキパッドの摩耗が進行しにくい。また、第１および第２電動式直動アクチュエータがそれぞれキャリパボディに着脱可能とされているので、その第１および第２電動式直動アクチュエータの少なくとも一方を、小荷重用の電動ブレーキ装置の製造に用いられる電動式直動アクチュエータと共通化することで、電動ブレーキ装置の製造コストを低減することが可能である。 Since the electric brake device according to the present invention is configured to press the back surface of the brake pad at two locations separated in the circumferential direction, even when the pressing force acting on the brake pad is increased, the electric brake device is not provided between the brake pad and the brake disk. The pressure tends to be uniform over the entire surface of the brake pad. Therefore, when a heavy load is generated, the fade phenomenon is unlikely to occur, and wear of the brake pad is unlikely to proceed. Further, since the first and second electric linear actuators can be respectively attached to and detached from the caliper body, at least one of the first and second electric linear actuators is manufactured as an electric brake device for a small load. It is possible to reduce the manufacturing cost of the electric brake device by sharing the electric linear actuator used for the electric brake.
この発明の実施形態の電動ブレーキ装置の一部を切り欠いてインナ側から見た図The figure which notched some electric brake devices of this embodiment of this invention, and was seen from the inner side 図１のII－II線に沿った断面図Sectional view along the line II-II in FIG. 図１に示す電動ブレーキ装置をアウタ側から見た図The figure which looked at the electric brake device shown in FIG. 1 from the outer side 図１に示す電動ブレーキ装置の一部を切り欠いてブレーキディスクの半径方向外側から見た図The figure which notched a part of electric brake device shown in FIG. 1, and was seen from the radial direction outer side of the brake disc 図２の第１直動機構の近傍の拡大断面図FIG. 2 is an enlarged sectional view in the vicinity of the first linear motion mechanism in FIG. 図５のVI－VI線に沿った断面図Sectional view along line VI-VI in FIG. 図１に示す第１電動式直動アクチュエータと同一形状の電動式直動アクチュエータを用いて製造した小荷重用の電動ブレーキ装置の一例を示す図The figure which shows an example of the electric brake device for small loads manufactured using the electric linear actuator of the same shape as the 1st electric linear actuator shown in FIG. 図７に示す小荷重用の電動ブレーキ装置の左側面図Left side view of the electric brake device for small load shown in FIG. 図７に示す小荷重用の電動ブレーキ装置をブレーキディスクの半径方向外側から見た図FIG. 7 is a view of the electric brake device for small load shown in FIG. 図１に示す第１電動式直動アクチュエータと同一形状の電動式直動アクチュエータを示す斜視図The perspective view which shows the electric linear actuator of the same shape as the 1st electric linear actuator shown in FIG. 図１に示す大荷重用の電動ブレーキ装置の変形例を示す図The figure which shows the modification of the electric brake device for heavy loads shown in FIG. 図１１に示す電動ブレーキ装置をブレーキディスクの半径方向外側から見た図FIG. 11 is a diagram of the electric brake device shown in FIG. 図１１に示す第１電動式直動アクチュエータと同一形状の電動式直動アクチュエータを用いて製造した小荷重用の電動ブレーキ装置の一例を示す図The figure which shows an example of the electric brake device for small loads manufactured using the electric linear actuator of the same shape as the 1st electric linear actuator shown in FIG. 図１３に示す電動ブレーキ装置をブレーキディスクの半径方向外側から見た図The figure which looked at the electric brake device shown in FIG. 13 from the radial direction outer side of the brake disc
　図１～図４に、この発明の第１実施形態の電動ブレーキ装置１を示す。この電動ブレーキ装置１は、図２に示すように、車輪（図示せず）と一体に回転するブレーキディスク２と、ブレーキディスク２を間に挟んで軸方向に対向するインナ側およびアウタ側ブレーキパッド３，４と、アウタ側ブレーキパッド４のブレーキディスク２に対向する側とは反対側の側面（以下「アウタ側ブレーキパッド４の背面」という）を支持する爪部５をもつキャリパボディ６と、インナ側ブレーキパッド３のブレーキディスク２に対向する側とは反対側の側面（以下「インナ側ブレーキパッド３の背面」という）をブレーキディスク２の周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータ７ａ，７ｂ（図１参照）とを有する。ここで、電動ブレーキ装置１を車体に組み付けた状態で車体幅方向の内側および外側をそれぞれインナ側およびアウタ側という。 1 to 4 show an electric brake device 1 according to a first embodiment of the present invention. As shown in FIG. 2, the electric brake device 1 includes a brake disk 2 that rotates integrally with a wheel (not shown), and inner and outer brake pads that face each other in the axial direction with the brake disk 2 interposed therebetween. And caliper body 6 having a claw portion 5 that supports a side surface of the outer brake pad 4 opposite to the side facing the brake disc 2 (hereinafter referred to as “the rear surface of the outer brake pad 4”); The first and second sides of the inner side brake pad 3 that press the side surface opposite to the side facing the brake disc 2 (hereinafter referred to as “the back side of the inner side brake pad 3”) at two locations apart in the circumferential direction of the brake disc 2 Second electric linear actuators 7a and 7b (see FIG. 1). Here, the inner side and the outer side in the vehicle body width direction when the electric brake device 1 is assembled to the vehicle body are referred to as an inner side and an outer side, respectively.
　図１に示すように、インナ側ブレーキパッド３の両端には一対の耳片８が形成されている。耳片８は、マウンティングブラケット９に形成された一対のガイド溝１０でスライド可能に支持されている。マウンティングブラケット９は、ブレーキディスク２に対して軸方向に移動不能に車体に固定されている。ガイド溝１０は、ブレーキディスク２の軸方向と平行に延びる溝である。このガイド溝１０と耳片８の係合により、インナ側ブレーキパッド３は、ブレーキディスク２のインナ側の側面に接触する位置と離反する位置との間で移動可能に支持されている。 As shown in FIG. 1, a pair of ear pieces 8 are formed at both ends of the inner brake pad 3. The ear piece 8 is slidably supported by a pair of guide grooves 10 formed in the mounting bracket 9. The mounting bracket 9 is fixed to the vehicle body so as not to move in the axial direction with respect to the brake disc 2. The guide groove 10 is a groove extending in parallel with the axial direction of the brake disk 2. Due to the engagement of the guide groove 10 and the ear piece 8, the inner brake pad 3 is supported so as to be movable between a position contacting the inner side surface of the brake disk 2 and a position separating from the inner side brake pad 3.
　図３に示すように、アウタ側ブレーキパッド４の両端には一対の耳片１１が形成されている。耳片１１は、マウンティングブラケット９に形成された一対のガイド溝１２でスライド可能に支持されている。ガイド溝１２は、ブレーキディスク２の軸方向と平行に延びる溝である。このガイド溝１２と耳片１１の係合により、アウタ側ブレーキパッド４は、ブレーキディスク２のアウタ側の側面に接触する位置と離反する位置との間で移動可能に支持されている。 As shown in FIG. 3, a pair of ear pieces 11 are formed at both ends of the outer brake pad 4. The ear piece 11 is slidably supported by a pair of guide grooves 12 formed in the mounting bracket 9. The guide groove 12 is a groove extending in parallel with the axial direction of the brake disk 2. Due to the engagement of the guide groove 12 and the ear piece 11, the outer brake pad 4 is supported so as to be movable between a position contacting the outer side surface of the brake disk 2 and a position separating the outer brake pad 4.
　図２に示すように、インナ側ブレーキパッド３およびアウタ側ブレーキパッド４は、ブレーキディスク２に接触する摩擦材１３と、摩擦材１３の裏面に接着して設けられた裏金１４とからなる。インナ側ブレーキパッド３およびアウタ側ブレーキパッド４の耳片８，１１（図１、図３参照）は、裏金１４に一体に形成されている。 As shown in FIG. 2, the inner brake pad 3 and the outer brake pad 4 include a friction material 13 that contacts the brake disk 2 and a back metal 14 that is bonded to the back surface of the friction material 13. Ear pieces 8 and 11 (see FIGS. 1 and 3) of the inner brake pad 3 and the outer brake pad 4 are formed integrally with the back metal 14.
　キャリパボディ６は、アウタ側ブレーキパッド４の背面に軸方向に対向する爪部５と、ブレーキディスク２の外径側に対向する外殻部１５とを有する。外殻部１５のインナ側の端面には、第１および第２電動式直動アクチュエータ７ａ，７ｂ（図１参照）を固定するためのねじ孔１６が形成されている。 The caliper body 6 has a claw portion 5 facing the back surface of the outer brake pad 4 in the axial direction and an outer shell portion 15 facing the outer diameter side of the brake disc 2. A screw hole 16 for fixing the first and second electric linear motion actuators 7a and 7b (see FIG. 1) is formed on the inner end face of the outer shell portion 15.
　図１、図４に示すように、第１電動式直動アクチュエータ７ａは、ブレーキディスク２の周方向の両側に延びる２本の第１キャリパアーム１７を有する。２本のうち一方の第１キャリパアーム１７には第１スライドピン１８が固定され、他方の第１キャリパアーム１７は、キャリパボディ６にボルト１９で固定されている。第１スライドピン１８は、ブレーキディスク２の軸方向と平行に延びる棒状の部材であり、マウンティングブラケット９に設けられた第１ピン孔２０にスライド可能に挿入されている。また、第１電動式直動アクチュエータ７ａは、２本のボルト２１でもキャリパボディ６に固定されている。第１電動式直動アクチュエータ７ａは、ボルト１９，２１の着脱操作によりキャリパボディ６に着脱可能とされている。 As shown in FIGS. 1 and 4, the first electric linear actuator 7 a has two first caliper arms 17 extending on both sides of the brake disk 2 in the circumferential direction. The first slide pin 18 is fixed to one first caliper arm 17 of the two, and the other first caliper arm 17 is fixed to the caliper body 6 with a bolt 19. The first slide pin 18 is a rod-like member extending in parallel with the axial direction of the brake disc 2 and is slidably inserted into a first pin hole 20 provided in the mounting bracket 9. The first electric linear actuator 7 a is also fixed to the caliper body 6 with two bolts 21. The first electric linear actuator 7 a can be attached to and detached from the caliper body 6 by attaching and detaching the bolts 19 and 21.
　同様に、第２電動式直動アクチュエータ７ｂも、ブレーキディスク２の周方向の両側に延びる２本の第２キャリパアーム２２を有する。２本のうち一方の第２キャリパアーム２２には第２スライドピン２３が固定され、他方の第２キャリパアーム２２は、キャリパボディ６にボルト１９で固定されている。第２スライドピン２３は、ブレーキディスク２の軸方向と平行に延びる棒状の部材であり、マウンティングブラケット９に設けられた第２ピン孔２４にスライド可能に挿入されている。また、第２電動式直動アクチュエータ７ｂは、２本のボルト２５でもキャリパボディ６に固定されている。第２電動式直動アクチュエータ７ｂは、ボルト１９，２５の着脱操作によりキャリパボディ６に着脱可能とされている。 Similarly, the second electric linear motion actuator 7b also has two second caliper arms 22 extending on both sides of the brake disk 2 in the circumferential direction. A second slide pin 23 is fixed to one second caliper arm 22 of the two, and the other second caliper arm 22 is fixed to the caliper body 6 with a bolt 19. The second slide pin 23 is a rod-like member extending in parallel with the axial direction of the brake disc 2 and is slidably inserted into a second pin hole 24 provided in the mounting bracket 9. The second electric linear actuator 7 b is also fixed to the caliper body 6 with two bolts 25. The second electric linear actuator 7b can be attached to and detached from the caliper body 6 by attaching and detaching the bolts 19 and 25.
　ここで、キャリパボディ６と、キャリパボディ６に固定された第１および第２電動式直動アクチュエータ７ａ，７ｂとは、第１および第２スライドピン１８，２３で、ブレーキディスク２の軸方向と平行に移動可能に支持されている。 Here, the caliper body 6 and the first and second electric linear motion actuators 7a and 7b fixed to the caliper body 6 are the first and second slide pins 18 and 23, and the axial direction of the brake disk 2 is It is supported so that it can move in parallel.
　図４に示すように、第１電動式直動アクチュエータ７ａの２本の第１キャリパアーム１７は、ブレーキディスク２の軸方向に互いにずれた配置とされている。同様に、第２電動式直動アクチュエータ７ｂの２本の第２キャリパアーム２２も互いに軸方向にずれて配置されている。そして、第１電動式直動アクチュエータ７ａの軸方向位置と第２電動式直動アクチュエータ７ｂの軸方向位置とを一致させた状態で、第１スライドピン１８が固定されていない側の第１キャリパアーム１７と、第２スライドピン２３が固定されていない側の第２キャリパアーム２２とが軸方向に重なり合い、その第１および第２キャリパアーム１７，２２が共通のボルト１９でキャリパボディ６に固定されている。 As shown in FIG. 4, the two first caliper arms 17 of the first electric linear actuator 7 a are arranged so as to be shifted from each other in the axial direction of the brake disk 2. Similarly, the two second caliper arms 22 of the second electric linear actuator 7b are also displaced from each other in the axial direction. The first caliper on the side where the first slide pin 18 is not fixed in a state where the axial position of the first electric linear actuator 7a and the axial position of the second electric linear actuator 7b are matched. The arm 17 and the second caliper arm 22 on the side where the second slide pin 23 is not fixed overlap in the axial direction, and the first and second caliper arms 17 and 22 are fixed to the caliper body 6 by a common bolt 19. Has been.
　図２に示すように、第１電動式直動アクチュエータ７ａは、インナ側ブレーキパッド３の背面に対向して配置された第１ピストン２６ａと、その第１ピストン２６ａをブレーキディスク２の軸方向と平行に移動可能に収容する第１ピストンハウジング２７ａと、第１電動モータ２８ａと、その第１電動モータ２８ａの回転を第１ピストン２６ａの直線運動に変換する第１直動機構２９ａと、第１電動モータ２８ａの回転を第１直動機構２９ａに減速して伝達する第１減速歯車列３０ａとを有する。 As shown in FIG. 2, the first electric linear actuator 7 a includes a first piston 26 a disposed so as to face the back surface of the inner brake pad 3, and the first piston 26 a is disposed in the axial direction of the brake disk 2. A first piston housing 27a movably accommodated in parallel; a first electric motor 28a; a first linear motion mechanism 29a that converts the rotation of the first electric motor 28a into a linear motion of the first piston 26a; A first reduction gear train 30a that reduces and transmits the rotation of the electric motor 28a to the first linear motion mechanism 29a.
　同様に、第２電動式直動アクチュエータ７ｂは、第１ピストン２６ａに対してブレーキディスク２の周方向に離れた位置でインナ側ブレーキパッド３の背面に対向して配置された第２ピストン２６ｂ（図４参照）と、その第２ピストン２６ｂをインナ側ブレーキディスク２の軸方向と平行に移動可能に収容する第２ピストンハウジング２７ｂ（図４参照）と、第２電動モータ２８ｂ（図１参照）と、その第２電動モータ２８ｂの回転を第２ピストン２６ｂの直線運動に変換する第２直動機構２９ｂ（図４参照）と、第２電動モータ２８ｂの回転を第２直動機構２９ｂに減速して伝達する第２減速歯車列３０ｂ（図１参照）とを有する。 Similarly, the second electric linear actuator 7b is provided with a second piston 26b (opposed to the rear surface of the inner brake pad 3 at a position away from the first piston 26a in the circumferential direction of the brake disc 2). 4), a second piston housing 27b (see FIG. 4) for accommodating the second piston 26b so as to be movable in parallel with the axial direction of the inner brake disc 2, and a second electric motor 28b (see FIG. 1). And a second linear motion mechanism 29b (see FIG. 4) that converts the rotation of the second electric motor 28b into a linear motion of the second piston 26b, and the rotation of the second electric motor 28b is decelerated to the second linear motion mechanism 29b. And a second reduction gear train 30b (see FIG. 1) for transmission.
　ここで、第１電動式直動アクチュエータ７ａの各構成部品と第２電動式直動アクチュエータ７ｂの各構成部品は、互いに同一形状とされている（図では、第１および第２電動式直動アクチュエータ７ａ，７ｂは同一物である）。すなわち、第１および第２ピストン２６ａ，２６ｂは互いに同一形状とされ、第１および第２ピストンハウジング２７ａ，２７ｂは互いに同一形状とされ、第１および第２電動モータ２８ａ，２８ｂは互いに同一形状とされ、第１および第２直動機構２９ａ，２９ｂは互いに同一形状とされ、第１および第２減速歯車列３０ａ，３０ｂも互いに同一形状とされている。そのため、以下、第２電動式直動アクチュエータ７ｂについては、第１電動式直動アクチュエータ７ａと対応する部分に同一の符号を付して説明を省略する。 Here, each component of the first electric linear actuator 7a and each component of the second electric linear actuator 7b have the same shape (in the figure, the first and second electric linear actuators). Actuators 7a and 7b are the same). That is, the first and second pistons 26a and 26b have the same shape, the first and second piston housings 27a and 27b have the same shape, and the first and second electric motors 28a and 28b have the same shape. The first and second linear motion mechanisms 29a and 29b have the same shape, and the first and second reduction gear trains 30a and 30b have the same shape. Therefore, hereinafter, regarding the second electric linear actuator 7b, portions corresponding to those of the first electric linear actuator 7a are denoted by the same reference numerals and description thereof is omitted.
　図２に示すように、第１ピストンハウジング２７ａは、キャリパボディ６の爪部５と第１ピストンハウジング２７ａとがインナ側およびアウタ側のブレーキパッド３，４を間に挟んで軸方向に向き合うように配置されている。第１ピストンハウジング２７ａには、第１ピストン２６ａをブレーキディスク２の軸方向と平行にスライド可能に収容するピストン収容孔３１が形成されている。第１電動モータ２８ａは、第１ピストン２６ａに対してブレーキディスク２の半径方向内方に配置されている。 As shown in FIG. 2, the first piston housing 27a is configured such that the claw portion 5 of the caliper body 6 and the first piston housing 27a face each other in the axial direction with the inner side and outer side brake pads 3 and 4 therebetween. Is arranged. The first piston housing 27 a is formed with a piston accommodation hole 31 that accommodates the first piston 26 a so as to be slidable in parallel with the axial direction of the brake disk 2. The first electric motor 28a is disposed radially inward of the brake disk 2 with respect to the first piston 26a.
　第１直動機構２９ａは、ピストン収容孔３１の中心線上に配置された回転軸３２を有する。第１電動モータ２８ａは、第１電動モータ２８ａのモータ軸３３と第１直動機構２９ａの回転軸３２とが平行になるように配置されている。第１減速歯車列３０ａは、第１電動モータ２８ａの回転が入力される入力歯車３４と、第１直動機構２９ａに回転を出力する出力歯車３５と、入力歯車３４と出力歯車３５の間で回転を伝達する複数の中間歯車３６とを有する。第１直動機構２９ａは、第１電動モータ２８ａから第１減速歯車列３０ａを介して回転軸３２に入力された回転を第１ピストン２６ａの軸方向移動に変換する。 The first linear motion mechanism 29 a has a rotation shaft 32 disposed on the center line of the piston accommodation hole 31. The first electric motor 28a is disposed so that the motor shaft 33 of the first electric motor 28a and the rotation shaft 32 of the first linear motion mechanism 29a are parallel to each other. The first reduction gear train 30a includes an input gear 34 to which the rotation of the first electric motor 28a is input, an output gear 35 that outputs the rotation to the first linear motion mechanism 29a, and the input gear 34 and the output gear 35. And a plurality of intermediate gears 36 for transmitting the rotation. The first linear motion mechanism 29a converts the rotation input to the rotary shaft 32 from the first electric motor 28a via the first reduction gear train 30a into the axial movement of the first piston 26a.
　第１減速歯車列３０ａは、第１ピストンハウジング２７ａに取り付けられたギアケース３７に収容されている。ギアケース３７は、側板３８と蓋体３９とからなる。側板３８は、第１ピストンハウジング２７ａのブレーキディスク２の側とは反対側の端部にブレーキディスク２と平行に取り付けられている。第１電動モータ２８ａは側板３８に取り付けられている。 The first reduction gear train 30a is accommodated in a gear case 37 attached to the first piston housing 27a. The gear case 37 includes a side plate 38 and a lid 39. The side plate 38 is attached in parallel to the brake disc 2 at the end of the first piston housing 27a opposite to the brake disc 2 side. The first electric motor 28 a is attached to the side plate 38.
　第１ピストンハウジング２７ａには、ブレーキディスク２の軸方向と平行に貫通するボルト挿通孔４０が形成されている。第１ピストンハウジング２７ａは、ボルト挿通孔４０に挿入したボルト２１の締め込みによりキャリパボディ６に固定されている。第１キャリパアーム１７（図１参照）は、第１ピストンハウジング２７ａに一体に形成されている。 The first piston housing 27a is formed with a bolt insertion hole 40 penetrating in parallel with the axial direction of the brake disc 2. The first piston housing 27 a is fixed to the caliper body 6 by tightening the bolt 21 inserted into the bolt insertion hole 40. The first caliper arm 17 (see FIG. 1) is formed integrally with the first piston housing 27a.
　図５、図６に示すように、第１直動機構２９ａは、第１ピストン２６ａの内周と回転軸３２の外周との間に周方向に間隔をおいて設けられた複数の遊星ローラ４１と、その各遊星ローラ４１を自転可能かつ公転可能に保持するキャリヤ４２とを有する。第１ピストン２６ａは、回転軸３２の外周と半径方向に対向する円筒状に形成されている。 As shown in FIGS. 5 and 6, the first linear motion mechanism 29 a includes a plurality of planetary rollers 41 that are provided between the inner periphery of the first piston 26 a and the outer periphery of the rotary shaft 32 at intervals in the circumferential direction. And a carrier 42 for holding the planetary rollers 41 so as to be capable of rotating and revolving. The first piston 26a is formed in a cylindrical shape that faces the outer periphery of the rotary shaft 32 in the radial direction.
　各遊星ローラ４１は、回転軸３２の外周に転がり接触している。回転軸３２の遊星ローラ４１に対する接触部分は円筒面とされている。回転軸３２が回転したとき、各遊星ローラ４１はローラ軸４３を中心に自転しながら、回転軸３２のまわりを第１ピストン２６ａの内周に沿って公転する。 Each planetary roller 41 is in rolling contact with the outer periphery of the rotating shaft 32. The contact portion of the rotating shaft 32 with respect to the planetary roller 41 is a cylindrical surface. When the rotating shaft 32 rotates, each planetary roller 41 revolves around the rotating shaft 32 along the inner periphery of the first piston 26a while rotating around the roller shaft 43.
　第１ピストン２６ａの内周には、螺旋凸条４４が設けられている。螺旋凸条４４は、円周方向に対して所定のリード角をもって斜めに延びる凸条である。各遊星ローラ４１の外周には、螺旋凸条４４に係合する複数の円周溝４５が軸方向に間隔をおいて形成されている。各遊星ローラ４１の外周の軸方向に隣り合う円周溝４５の間隔は、螺旋凸条４４のピッチと同一の大きさとされている。ここでは、遊星ローラ４１の外周にリード角が０度の円周溝４５を設けているが、円周溝４５のかわりに、螺旋凸条４４と異なるリード角をもつ螺旋溝を設けてもよい。 A spiral ridge 44 is provided on the inner periphery of the first piston 26a. The spiral ridge 44 is a ridge that extends obliquely with a predetermined lead angle with respect to the circumferential direction. On the outer periphery of each planetary roller 41, a plurality of circumferential grooves 45 that engage with the spiral ridges 44 are formed at intervals in the axial direction. The interval between the circumferential grooves 45 adjacent to each other in the axial direction on the outer periphery of each planetary roller 41 is the same as the pitch of the spiral ridges 44. Here, the circumferential groove 45 having a lead angle of 0 degree is provided on the outer periphery of the planetary roller 41, but a spiral groove having a lead angle different from that of the spiral protrusion 44 may be provided instead of the circumferential groove 45. .
　キャリヤ４２は、遊星ローラ４１を間にして軸方向に対向する一対のディスク４６，４７と、ディスク４６，４７同士を連結する連結部４８と、各遊星ローラ４１の中心に設けられこれを自転可能に支持するローラ軸４３とを有する。各ローラ軸４３の両端部は、各ディスク４６，４７でそれぞれ支持されている。各ディスク４６，４７は、回転軸３２を貫通させる環状に形成され、その内周には、回転軸３２の外周に摺接する滑り軸受４９がそれぞれ装着されている。 The carrier 42 is provided at the center of each planetary roller 41, and is provided at the center of each planetary roller 41 and a pair of discs 46, 47 facing each other in the axial direction with the planetary roller 41 therebetween, a connecting portion 48 for connecting the discs 46, 47 together. And a roller shaft 43 to be supported. Both ends of each roller shaft 43 are supported by disks 46 and 47, respectively. Each of the disks 46 and 47 is formed in an annular shape that penetrates the rotating shaft 32, and a sliding bearing 49 that is in sliding contact with the outer periphery of the rotating shaft 32 is mounted on the inner periphery thereof.
　各遊星ローラ４１とディスク４７との間には、遊星ローラ４１を自転可能な状態で軸方向に支持するスラスト軸受５０が組み込まれている。また、スラスト軸受５０とディスク４７の間には、スラスト軸受５０を介して遊星ローラ４１を傾動可能に支持する調心座５１が組み込まれている。 Between each planetary roller 41 and the disk 47, a thrust bearing 50 is incorporated that supports the planetary roller 41 in the axial direction in a rotatable state. Further, between the thrust bearing 50 and the disk 47, an aligning seat 51 that supports the planetary roller 41 so as to be tiltable via the thrust bearing 50 is incorporated.
　第１ピストンハウジング２７ａのピストン収容孔３１の内部には、第１ピストン２６ａから見てブレーキディスク２（図２参照）の側とは反対側に離れた位置に、回転軸３２が貫通した状態となるように円環状に形成された反力受け部材５２が設けられている。反力受け部材５２の内周には、回転軸３２を回転可能に支持する複数の転がり軸受５３が組み込まれている。 In the piston housing hole 31 of the first piston housing 27a, the rotary shaft 32 penetrates at a position away from the brake disc 2 (see FIG. 2) when viewed from the first piston 26a. A reaction force receiving member 52 formed in an annular shape is provided. On the inner periphery of the reaction force receiving member 52, a plurality of rolling bearings 53 that support the rotary shaft 32 in a rotatable manner are incorporated.
　キャリヤ４２と反力受け部材５２の間には、キャリヤ４２を公転可能な状態で軸方向に支持するスラスト軸受５４が組み込まれている。また、キャリヤ４２とスラスト軸受５４の間には、キャリヤ４２と一体に公転する間座５５が組み込まれている。 Between the carrier 42 and the reaction force receiving member 52, a thrust bearing 54 that supports the carrier 42 in the axial direction in a revolving state is incorporated. A spacer 55 that revolves integrally with the carrier 42 is incorporated between the carrier 42 and the thrust bearing 54.
　ピストン収容孔３１のブレーキディスク２の側の開口縁には、ブーツ５６が取り付けられている。ブーツ５６は、蛇腹状に折りたたまれた軸方向に伸縮可能な筒状の部材である。ブーツ５６の一端は、ピストン収容孔３１の内周に接続され、ブーツ５６の他端は、第１ピストン２６ａの外周に接続されている。このブーツ５６は、ピストン収容孔３１と第１ピストン２６ａの摺動面間に異物が侵入するのを防止している。 A boot 56 is attached to the opening edge of the piston receiving hole 31 on the brake disc 2 side. The boot 56 is a cylindrical member that can be expanded and contracted in the axial direction, folded in a bellows shape. One end of the boot 56 is connected to the inner periphery of the piston accommodation hole 31, and the other end of the boot 56 is connected to the outer periphery of the first piston 26a. The boot 56 prevents foreign matter from entering between the sliding surfaces of the piston accommodation hole 31 and the first piston 26a.
　第１ピストン２６ａのブレーキディスク２の側の端部には、インナ側ブレーキパッド３の背面に形成された係合凸部５７に係合する係合凹部５８が形成され、この係合凸部５７と係合凹部５８の係合によって、第１ピストン２６ａが回り止めされている。 At the end of the first piston 26a on the brake disc 2 side, an engagement recess 58 that engages with an engagement projection 57 formed on the back surface of the inner brake pad 3 is formed. The engagement of the engagement recess 58 prevents the first piston 26a from rotating.
　この第１直動機構２９ａは、回転軸３２が回転したとき、その回転が回転軸３２の外周に転がり接触する遊星ローラ４１に伝達し、各遊星ローラ４１がローラ軸４３を中心に自転しながら回転軸３２のまわりを公転する。このとき、遊星ローラ４１の外周の円周溝４５と第１ピストン２６ａの内周の螺旋凸条４４との係合によって、遊星ローラ４１と第１ピストン２６ａが軸方向に相対移動するが、遊星ローラ４１はキャリヤ４２と共に軸方向の移動が規制されているので、遊星ローラ４１は第１ピストンハウジング２７ａに対して軸方向に移動せず、第１ピストン２６ａが第１ピストンハウジング２７ａに対して軸方向に移動する。このようにして、第１直動機構２９ａは、回転軸３２の回転を第１ピストン２６ａの直線運動に変換する。これと同様にして、第２直動機構２９ｂも、第２電動モータ２８ｂ（図１参照）から回転軸３２に伝達する回転を第２ピストン２６ｂ（図４参照）の直線運動に変換する。 When the rotation shaft 32 rotates, the first linear motion mechanism 29 a transmits the rotation to the planetary roller 41 that is in rolling contact with the outer periphery of the rotation shaft 32, and each planetary roller 41 rotates around the roller shaft 43. Revolves around the rotating shaft 32. At this time, the planetary roller 41 and the first piston 26a are relatively moved in the axial direction by the engagement between the circumferential groove 45 on the outer periphery of the planetary roller 41 and the spiral protrusion 44 on the inner periphery of the first piston 26a. Since the roller 41 is restricted from moving in the axial direction together with the carrier 42, the planetary roller 41 does not move in the axial direction with respect to the first piston housing 27a, and the first piston 26a does not move in the axial direction with respect to the first piston housing 27a. Move in the direction. Thus, the 1st linear motion mechanism 29a converts rotation of the rotating shaft 32 into the linear motion of the 1st piston 26a. Similarly, the second linear motion mechanism 29b also converts the rotation transmitted from the second electric motor 28b (see FIG. 1) to the rotating shaft 32 into the linear motion of the second piston 26b (see FIG. 4).
　上記の電動ブレーキ装置１の動作例を説明する。 An example of the operation of the electric brake device 1 will be described.
　第１および第２電動モータ２８ａ，２８ｂの各モータ軸３３（図１参照）が回転すると、その回転が第１および第２減速歯車列３０ａ，３０ｂを介して第１および第２直動機構２９ａ，２９ｂ（図４参照）の各回転軸３２に伝達し、その回転がそれぞれ第１および第２ピストン２６ａ，２６ｂ（図４参照）の直線運動に変換される。この結果、第１および第２ピストン２６ａ，２６ｂが、インナ側ブレーキパッド３をブレーキディスク２の周方向に離れた２箇所で押圧し、インナ側ブレーキパッド３をブレーキディスク２のインナ側の側面に押し付ける。またこのとき、第１および第２ピストン２６ａ，２６ｂがブレーキディスク２から受ける軸方向反力によって、キャリパボディ６がマウンティングブラケット９に対してスライド移動し、キャリパボディ６の爪部５がアウタ側ブレーキパッド４の背面を押圧し、アウタ側ブレーキパッド４をブレーキディスク２のアウタ側の側面に押し付ける。このようにして、インナ側ブレーキパッド３およびアウタ側ブレーキパッド４がブレーキディスク２に押し付けられ、そのブレーキパッド３，４とブレーキディスク２の接触面間の摩擦によって、ブレーキディスク２に制動力が発生する。 When the motor shafts 33 (see FIG. 1) of the first and second electric motors 28a and 28b are rotated, the rotation is caused by the first and second linear motion mechanisms 29a via the first and second reduction gear trains 30a and 30b. , 29b (see FIG. 4) are transmitted to the rotary shafts 32, and the rotation is converted into linear motions of the first and second pistons 26a, 26b (see FIG. 4), respectively. As a result, the first and second pistons 26a and 26b press the inner brake pad 3 at two locations away from each other in the circumferential direction of the brake disk 2, and the inner brake pad 3 is pressed against the inner side surface of the brake disk 2. Press. At this time, the caliper body 6 slides with respect to the mounting bracket 9 due to the axial reaction force received by the first and second pistons 26a, 26b from the brake disc 2, and the claw portion 5 of the caliper body 6 moves to the outer brake. The back surface of the pad 4 is pressed, and the outer brake pad 4 is pressed against the outer side surface of the brake disc 2. In this way, the inner brake pad 3 and the outer brake pad 4 are pressed against the brake disc 2, and braking force is generated on the brake disc 2 due to friction between the contact surfaces of the brake pads 3, 4 and the brake disc 2. To do.
　この電動ブレーキ装置１は、インナ側ブレーキパッド３の背面を周方向に離れた２箇所で押圧する構成であるため、インナ側ブレーキパッド３に作用する押圧力を大きくした場合にも、インナ側ブレーキパッド３とブレーキディスク２の間の圧力がインナ側ブレーキパッド３の全面において均一となりやすい。そのため、大きな制動力（大荷重）を発生したときにも、フェード現象（インナ側ブレーキパッド３の摩擦材１３が高温となってガスを発生し、そのガスによってインナ側ブレーキパッド３とブレーキディスク２の間の摩擦力が低下する現象）を効果的に防止することが可能であり、またインナ側ブレーキパッド３の局所的な摩耗を防止することが可能である。 Since the electric brake device 1 is configured to press the back surface of the inner brake pad 3 at two locations separated in the circumferential direction, the inner brake is applied even when the pressing force acting on the inner brake pad 3 is increased. The pressure between the pad 3 and the brake disc 2 tends to be uniform over the entire surface of the inner brake pad 3. Therefore, even when a large braking force (a large load) is generated, a fade phenomenon (the friction material 13 of the inner brake pad 3 becomes hot and generates gas, and the gas causes the inner brake pad 3 and the brake disc 2 to be generated. It is possible to effectively prevent the frictional force between the inner brake pad 3 and the inner brake pad 3 from being worn locally.
　また、この電動ブレーキ装置１は、第１および第２電動式直動アクチュエータ７ａ，７ｂがそれぞれキャリパボディ６に着脱可能とされているので、その第１および第２電動式直動アクチュエータ７ａ，７ｂの少なくとも一方を、図７～図９に示すような小荷重用の電動ブレーキ装置６０の製造に用いられる電動式直動アクチュエータ７ａと共通化することで、電動ブレーキ装置１の製造コストを低減することが可能である。 In the electric brake device 1, the first and second electric linear actuators 7a and 7b are detachably attached to the caliper body 6, respectively. Therefore, the first and second electric linear actuators 7a and 7b are provided. The manufacturing cost of the electric brake device 1 can be reduced by sharing at least one of them with the electric linear actuator 7a used for manufacturing the electric brake device 60 for small load as shown in FIGS. It is possible.
　例えば、図７～図９に示すように、図１～図４に示す第１電動式直動アクチュエータ７ａと同一形状の電動式直動アクチュエータ７ａ（図１０参照）と、その電動式直動アクチュエータ７ａを１つだけ取り付け可能な小型の小荷重用のキャリパボディ６１とを使用し、電動式直動アクチュエータ７ａを小荷重用のキャリパボディ６１に取り付けて、小荷重用の電動ブレーキ装置６０を製造することができる。図７～図９に示す小荷重用の電動ブレーキ装置６０は、図１～図４に示す大荷重用の電動ブレーキ装置１と比較して、電動式直動アクチュエータの個数が異なるだけであり、その他の基本的な構成は同一である。 For example, as shown in FIGS. 7 to 9, an electric linear actuator 7a (see FIG. 10) having the same shape as the first electric linear actuator 7a shown in FIGS. 1 to 4, and the electric linear actuator A small load caliper body 61 that can be attached to only one 7a is used, and the electric linear actuator 7a is attached to the caliper body 61 for small load to manufacture an electric brake device 60 for small load. can do. The electric brake device 60 for small loads shown in FIGS. 7 to 9 differs from the electric brake device 1 for heavy loads shown in FIGS. 1 to 4 only in the number of electric linear actuators. Other basic configurations are the same.
　図７～図９において、第１ピストンハウジング２７ａからブレーキディスク６２（図８参照）の周方向両側に延びる２本の第１キャリパアーム１７には、それぞれスライドピン６３が固定されている。各スライドピン６３は、小荷重用のマウンティングブラケット６４に形成されたピン孔６５にそれぞれスライド可能に挿入され、このスライドピン６３のスライドによって、小荷重用のキャリパボディ６１と第１電動式直動アクチュエータ７ａは、小荷重用のマウンティングブラケット６４に対して小荷重用のブレーキディスク６２の軸方向と平行に移動可能とされている。 7 to 9, slide pins 63 are fixed to the two first caliper arms 17 extending from the first piston housing 27a to both sides in the circumferential direction of the brake disc 62 (see FIG. 8). Each slide pin 63 is slidably inserted into a pin hole 65 formed in the mounting bracket 64 for small load, and the slide pin 63 slides to cause the caliper body 61 for small load and the first electric linear motion. The actuator 7a is movable in parallel with the axial direction of the brake disc 62 for light load with respect to the mounting bracket 64 for light load.
　このように、大荷重用および小荷重用の電動ブレーキ装置１，６０を製造するにあたり、図１～図４に示す大荷重用の電動ブレーキ装置１の電動式直動アクチュエータ７ａと、図７～図９に示す小荷重用の電動ブレーキ装置６０の電動式直動アクチュエータ７ａとを共通化することができるため、大荷重用および小荷重用の電動ブレーキ装置１，６０の製造コストを低減することが可能である。 As described above, in manufacturing the electric brake devices 1 and 60 for heavy loads and light loads, the electric linear actuator 7a of the electric brake device 1 for heavy loads shown in FIGS. 1 to 4 and FIGS. Since the electric direct acting actuator 7a of the electric brake device 60 for small loads shown in FIG. 9 can be shared, the manufacturing cost of the electric brake devices 1 and 60 for heavy loads and small loads can be reduced. Is possible.
　また、上記の電動ブレーキ装置１は、第１電動式直動アクチュエータ７ａの各構成部品と第２電動式直動アクチュエータ７ｂの各構成部品とが同一形状なので、電動ブレーキ装置１の製造コストをより効果的に低減することが可能となっている。 Further, in the electric brake device 1 described above, each component of the first electric linear actuator 7a and each component of the second electric linear actuator 7b have the same shape, so that the manufacturing cost of the electric brake device 1 can be further increased. It can be effectively reduced.
　また、上記の電動ブレーキ装置１は、第１スライドピン１８が固定されていない側の第１キャリパアーム１７と、第２スライドピン２３が固定されていない側の第２キャリパアーム２２とが軸方向に重なった配置となっているため、そのアーム１７，２２同士が重なっている分、電動ブレーキ装置１のサイズを小型化することが可能となっている。 Further, in the electric brake device 1 described above, the first caliper arm 17 on the side where the first slide pin 18 is not fixed and the second caliper arm 22 on the side where the second slide pin 23 is not fixed are in the axial direction. Since the arms 17 and 22 overlap each other, the size of the electric brake device 1 can be reduced.
　上記実施形態では、第１および第２スライドピン１８，２３をそれぞれ固定する第１および第２キャリパアーム１７，２２を、第１および第２電動式直動アクチュエータ７ａ，７ｂに設けた例を挙げて説明したが、図１１および図１２に示すように、第１および第２スライドピン１８，２３をそれぞれ固定するキャリパアーム６６をキャリパボディ６の側に設けることも可能である。図１１および図１２に示す電動ブレーキ装置１は、上記実施形態の電動ブレーキ装置１とキャリパアーム６６の部分だけが異なり、その他の部分は同一であるため、以下、上記実施形態の電動ブレーキ装置１と対応する部分は、同一の符号を付して説明を省略する。 In the above embodiment, the first and second electric linear motion actuators 7a and 7b are provided with the first and second caliper arms 17 and 22 for fixing the first and second slide pins 18 and 23, respectively. However, as shown in FIGS. 11 and 12, a caliper arm 66 for fixing the first and second slide pins 18 and 23 can be provided on the caliper body 6 side. The electric brake device 1 shown in FIG. 11 and FIG. 12 is different from the electric brake device 1 of the above embodiment only in the caliper arm 66, and the other portions are the same. The parts corresponding to are denoted by the same reference numerals and description thereof is omitted.
　図１１および図１２に示すように、第１および第２電動式直動アクチュエータ７ａ，７ｂを両方とも取り付け可能な大荷重用のキャリパボディ６は、ブレーキディスク２（図２参照）の周方向と平行に延びる２本のキャリパアーム６６を有する。 As shown in FIG. 11 and FIG. 12, the caliper body 6 for heavy loads to which both the first and second electric linear motion actuators 7a and 7b can be attached has a circumferential direction of the brake disc 2 (see FIG. 2). Two caliper arms 66 extending in parallel are provided.
　図１３および図１４に示すように、第１電動式直動アクチュエータ７ａと同一形状の電動式直動アクチュエータ７ａを１つだけ取り付け可能な小荷重用のキャリパボディ６１も、ブレーキディスク６２（図８参照）の周方向と平行に延びる２本のキャリパアーム６７を有する。 As shown in FIGS. 13 and 14, the caliper body 61 for a small load to which only one electric linear actuator 7a having the same shape as the first electric linear actuator 7a can be attached is also provided on the brake disc 62 (FIG. 8). 2) and two caliper arms 67 extending in parallel with the circumferential direction.
　上記各実施形態では、第１および第２電動モータ２８ａ，２８ｂから伝達する回転をそれぞれ第１および第２ピストン２６ａ，２６ｂの直線運動に変換する第１および第２直動機構２９ａ，２９ｂとして、遊星ローラ４１を使用した遊星ローラ機構を採用した例を挙げて説明したが、他の形式の直動機構（送りねじ機構、ボールランプ機構等）を用いてもよい。また、第１および第２電動モータ２８ａ，２８ｂは、それぞれ第１および第２ピストン２６ａ，２６ｂに対してブレーキディスク２の半径方向内方に配置されていたが、それ以外の位置（例えば、ブレーキディスク２の半径方向外方等）に配置してもよい。 In the above embodiments, the first and second linear motion mechanisms 29a and 29b that convert the rotations transmitted from the first and second electric motors 28a and 28b into linear motions of the first and second pistons 26a and 26b, respectively. Although an example in which the planetary roller mechanism using the planetary roller 41 is employed has been described, other types of linear motion mechanisms (feed screw mechanism, ball ramp mechanism, etc.) may be used. The first and second electric motors 28a and 28b are disposed radially inward of the brake disc 2 with respect to the first and second pistons 26a and 26b, respectively. You may arrange | position in the radial direction outer side etc. of the disk 2.
　今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.
１　　　　　大荷重用の電動ブレーキ装置
２　　　　　ブレーキディスク
３　　　　　インナ側ブレーキパッド
４　　　　　アウタ側ブレーキパッド
５　　　　　爪部
６　　　　　大荷重用のキャリパボディ
７ａ，７ｂ　第１および第２電動式直動アクチュエータ
１７　　　　第１キャリパアーム
１８　　　　第１スライドピン
１９　　　　ボルト
２２　　　　第２キャリパアーム
２３　　　　第２スライドピン
２６ａ　　　第１ピストン
２６ｂ　　　第２ピストン
２７ａ　　　第１ピストンハウジング
２７ｂ　　　第２ピストンハウジング
２８ａ　　　第１電動モータ
２８ｂ　　　第２電動モータ
２９ａ　　　第１直動機構
２９ｂ　　　第２直動機構
３０ａ　　　第１減速歯車列
３０ｂ　　　第２減速歯車列
６０　　　　小荷重用の電動ブレーキ装置
６１　　　　小荷重用のキャリパボディ
６６　　　　キャリパアーム DESCRIPTION OF SYMBOLS 1 Electric brake device 2 for heavy loads 2 Brake disc 3 Inner side brake pad 4 Outer side brake pad 5 Claw part 6 Large load caliper bodies 7a, 7b First and second electric linear actuators 17 First caliper arm 18 First slide pin 19 Bolt 22 Second caliper arm 23 Second slide pin 26a First piston 26b Second piston 27a First piston housing 27b Second piston housing 28a First electric motor 28b Second electric motor 29a First linear motion mechanism 29b 2nd linear motion mechanism 30a 1st reduction gear train 30b 2nd reduction gear train 60 Electric brake device 61 for small load 61 Caliper body 66 for small load Caliper arm

Claims (7)

  1. 　ブレーキディスク（２）を間に挟んで軸方向に対向する一対のブレーキパッド（３，４）のうち一方のブレーキパッド（４）の前記ブレーキディスク（２）に対向する側とは反対側の側面を支持する爪部（５）をもつキャリパボディ（６）と、
    　前記一対のブレーキパッド（３，４）のうち他方のブレーキパッド（３）の前記ブレーキディスク（２）に対向する側とは反対側の側面を前記ブレーキディスク（２）の周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータ（７ａ，７ｂ）とを有し、
    　前記第１および第２電動式直動アクチュエータ（７ａ，７ｂ）は、それぞれ前記キャリパボディ（６）に着脱可能に取り付けられている電動ブレーキ装置。     Of the pair of brake pads (3, 4) facing in the axial direction with the brake disc (2) in between, one side of the brake pad (4) opposite to the side facing the brake disc (2) A caliper body (6) having a claw portion (5) for supporting
    Of the pair of brake pads (3, 4), the side surface of the other brake pad (3) opposite to the side facing the brake disc (2) is spaced apart in the circumferential direction of the brake disc (2). First and second electric linear actuators (7a, 7b) that are pressed at points,
    The first and second electric linear actuators (7a, 7b) are electric brake devices that are detachably attached to the caliper body (6), respectively.
  2. 　第１電動式直動アクチュエータ（７ａ）は、前記他方のブレーキパッド（３）の前記ブレーキディスク（２）に対向する側とは反対側の側面に対向して配置された第１ピストン（２６ａ）と、その第１ピストン（２６ａ）を前記ブレーキディスク（２）の軸方向と平行に移動可能に収容し、前記キャリパボディ（６）に着脱可能に固定される第１ピストンハウジング（２７ａ）と、第１電動モータ（２８ａ）と、その第１電動モータ（２８ａ）の回転を前記第１ピストン（２６ａ）の直線運動に変換する第１直動機構（２９ａ）とを有し、
    　第２電動式直動アクチュエータ（７ｂ）は、前記第１ピストン（２６ａ）に対して前記ブレーキディスク（２）の周方向に離れた位置で、前記他方のブレーキパッド（３）の前記ブレーキディスク（２）に対向する側とは反対側の側面に対向して配置された第２ピストン（２６ｂ）と、その第２ピストン（２６ｂ）を前記ブレーキディスク（２）の軸方向と平行に移動可能に収容する第２ピストンハウジング（２７ｂ）と、第２電動モータ（２８ｂ）と、その第２電動モータ（２８ｂ）の回転を前記第２ピストン（２６ｂ）の直線運動に変換する第２直動機構（２９ｂ）とを有し、
    　前記第１および第２ピストン（２６ａ，２６ｂ）は、互いに同一形状とされ、
    　前記第１および第２ピストンハウジング（２７ａ，２７ｂ）は、互いに同一形状とされ、
    　前記第１および第２電動モータ（２８ａ，２８ｂ）は、互いに同一形状とされ、
    　前記第１および第２直動機構（２９ａ，２９ｂ）は、互いに同一形状とされている、
    　請求項１に記載の電動ブレーキ装置。     The first electric linear actuator (7a) has a first piston (26a) disposed opposite to the side of the other brake pad (3) opposite to the side facing the brake disc (2). A first piston housing (27a) that accommodates the first piston (26a) so as to be movable parallel to the axial direction of the brake disc (2) and is detachably fixed to the caliper body (6); A first electric motor (28a) and a first linear motion mechanism (29a) for converting the rotation of the first electric motor (28a) into a linear motion of the first piston (26a);
    The second electric linear actuator (7b) is located at a position away from the first piston (26a) in the circumferential direction of the brake disk (2), and the brake disk ( 2) The second piston (26b) disposed opposite to the side opposite to the side opposite to the side, and the second piston (26b) can be moved in parallel with the axial direction of the brake disc (2). A second piston housing (27b) to be accommodated, a second electric motor (28b), and a second linear motion mechanism (converting the rotation of the second electric motor (28b) into a linear motion of the second piston (26b) ( 29b)
    The first and second pistons (26a, 26b) have the same shape as each other,
    The first and second piston housings (27a, 27b) have the same shape as each other,
    The first and second electric motors (28a, 28b) have the same shape as each other,
    The first and second linear motion mechanisms (29a, 29b) have the same shape.
    The electric brake device according to claim 1.
  3. 　前記第１電動式直動アクチュエータ（７ａ）は、前記ブレーキディスク（２）の周方向の両側に延びる２本の第１キャリパアーム（１７）を有し、その２本の第１キャリパアーム（１７）のうちの一方に、前記キャリパボディ（６）を前記ブレーキディスク（２）の軸方向と平行に移動可能に支持する第１スライドピン（１８）が固定され、
    　前記第２電動式直動アクチュエータ（７ｂ）は、前記ブレーキディスク（２）の周方向の両側に延びる２本の第２キャリパアーム（２２）を有し、その２本の第２キャリパアーム（２２）のうちの一方に、前記キャリパボディ（６）を前記ブレーキディスク（２）の軸方向と平行に移動可能に支持する第２スライドピン（２３）が固定されている、
    　請求項１または２に記載の電動ブレーキ装置。     The first electric linear actuator (7a) has two first caliper arms (17) extending on both sides in the circumferential direction of the brake disk (2), and the two first caliper arms (17). ), A first slide pin (18) that supports the caliper body (6) so as to be movable parallel to the axial direction of the brake disc (2) is fixed,
    The second electric linear actuator (7b) has two second caliper arms (22) extending on both sides in the circumferential direction of the brake disk (2), and the two second caliper arms (22). ), A second slide pin (23) that supports the caliper body (6) so as to be movable parallel to the axial direction of the brake disc (2) is fixed.
    The electric brake device according to claim 1 or 2.
  4. 　前記２本の第１キャリパアーム（１７）のうちの前記第１スライドピン（１８）が固定されていない側の第１キャリパアーム（１７）が前記キャリパボディ（６）に固定され、
    　前記２本の第２キャリパアーム（２２）のうちの前記第２スライドピン（２３）が固定されていない側の第２キャリパアーム（２２）が前記キャリパボディ（６）に固定されている、
    　請求項３に記載の電動ブレーキ装置。     Of the two first caliper arms (17), the first caliper arm (17) on the side where the first slide pin (18) is not fixed is fixed to the caliper body (6),
    Of the two second caliper arms (22), the second caliper arm (22) on the side where the second slide pin (23) is not fixed is fixed to the caliper body (6).
    The electric brake device according to claim 3.
  5. 　前記２本の第１キャリパアーム（１７）は互いに軸方向にずれて配置され、
    　前記２本の第２キャリパアーム（２２）は互いに軸方向にずれて配置され、
    　前記２本の第１キャリパアーム（１７）のうちの前記第１スライドピン（１８）が固定されていない側の第１キャリパアーム（１７）と、前記２本の第２キャリパアーム（２２）のうちの前記第２スライドピン（２３）が固定されていない側の第２キャリパアーム（２２）とが、軸方向に重なった状態で共通のボルト（１９）で前記キャリパボディ（６）に固定されている、
    　請求項３または４に記載の電動ブレーキ装置。     The two first caliper arms (17) are arranged so as to be offset from each other in the axial direction,
    The two second caliper arms (22) are axially offset from each other;
    Of the two first caliper arms (17), the first caliper arm (17) on the side where the first slide pin (18) is not fixed, and the two second caliper arms (22) The second caliper arm (22) on the side where the second slide pin (23) is not fixed is fixed to the caliper body (6) with a common bolt (19) in a state of overlapping in the axial direction. ing,
    The electric brake device according to claim 3 or 4.
  6. 　前記キャリパボディ（６）は、前記ブレーキディスク（２）の周方向と平行に延びる２本のキャリパアーム（６６）を有し、その２本のキャリパアーム（６６）に、キャリパボディ（６）を前記ブレーキディスク（２）の軸方向と平行に移動可能に支持するスライドピン（１８，２３）がそれぞれ固定されている、
    　請求項１または２に記載の電動ブレーキ装置。     The caliper body (6) has two caliper arms (66) extending parallel to the circumferential direction of the brake disk (2), and the caliper body (6) is attached to the two caliper arms (66). Slide pins (18, 23) that are movably supported in parallel with the axial direction of the brake disc (2) are fixed, respectively.
    The electric brake device according to claim 1 or 2.
  7. 　ブレーキディスク（２）を間に挟んで軸方向に対向する一対のブレーキパッド（３，４）のうち一方のブレーキパッド（４）の前記ブレーキディスク（２）に対向する側とは反対側の側面を支持する爪部（５）をもつ大荷重用のキャリパボディ（６）と、
    　前記一対のブレーキパッド（３，４）のうち他方のブレーキパッド（３）の前記ブレーキディスク（２）に対向する側とは反対側の側面を前記ブレーキディスク（２）の周方向に離れた２箇所で押圧する第１および第２電動式直動アクチュエータ（７ａ，７ｂ）とを使用し、
    　その第１および第２電動式直動アクチュエータ（７ａ，７ｂ）を、いずれも前記大荷重用のキャリパボディ（６）に着脱可能に取り付けることにより大荷重用の電動ブレーキ装置（１）を製造し、
    　前記キャリパボディ（６）よりも小型の小荷重用のキャリパボディ（６１）と、
    　前記第１および第２電動式直動アクチュエータ（７ａ，７ｂ）の少なくとも一方と同一形状の電動式直動アクチュエータ（７ａ）とを使用し、
    　前記同一形状の電動式直動アクチュエータ（７ａ）を前記小荷重用のキャリパボディ（６１）に着脱可能に取り付けることにより小荷重用の電動ブレーキ装置（６０）を製造する、
    　電動ブレーキ装置の製造方法。     Of the pair of brake pads (3, 4) facing in the axial direction with the brake disc (2) in between, one side of the brake pad (4) opposite to the side facing the brake disc (2) A caliper body (6) for heavy loads having a claw part (5) for supporting
    Of the pair of brake pads (3, 4), the side surface of the other brake pad (3) opposite to the side facing the brake disc (2) is spaced apart in the circumferential direction of the brake disc (2). Using the first and second electric linear motion actuators (7a, 7b) that press at a point,
    The first and second electric linear actuators (7a, 7b) are both detachably attached to the heavy load caliper body (6) to produce a heavy load electric brake device (1). ,
    A caliper body (61) for small load smaller than the caliper body (6),
    An electric linear actuator (7a) having the same shape as at least one of the first and second electric linear actuators (7a, 7b);
    A small load electric brake device (60) is manufactured by detachably attaching the electric linear actuator (7a) having the same shape to the caliper body (61) for small load.
    Manufacturing method of electric brake device.
PCT/JP2017/003614 2016-02-09 2017-02-01 Electric brake device and method for manufacturing electric brake device WO2017138415A1 (en)

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US20220396251A1 (en) * 2019-06-26 2022-12-15 Hitachi Astemo, Ltd. Electric brake device

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JPH10181578A (en) * 1996-12-26 1998-07-07 Akebono Brake Ind Co Ltd Motor-driven brake
JP2008222069A (en) * 2007-03-13 2008-09-25 Kayaba Ind Co Ltd Electric brake
JP2010025222A (en) * 2008-07-18 2010-02-04 Nissin Kogyo Co Ltd Electrically-operated disc brake device

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JP2015124811A (en) * 2013-12-26 2015-07-06 曙ブレーキ工業株式会社 Disc brake device

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JPH10181578A (en) * 1996-12-26 1998-07-07 Akebono Brake Ind Co Ltd Motor-driven brake
JP2008222069A (en) * 2007-03-13 2008-09-25 Kayaba Ind Co Ltd Electric brake
JP2010025222A (en) * 2008-07-18 2010-02-04 Nissin Kogyo Co Ltd Electrically-operated disc brake device

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