WO2023062824A1 - ディスクブレーキ及び遊星歯車減速機構 - Google Patents
ディスクブレーキ及び遊星歯車減速機構 Download PDFInfo
- Publication number
- WO2023062824A1 WO2023062824A1 PCT/JP2021/038256 JP2021038256W WO2023062824A1 WO 2023062824 A1 WO2023062824 A1 WO 2023062824A1 JP 2021038256 W JP2021038256 W JP 2021038256W WO 2023062824 A1 WO2023062824 A1 WO 2023062824A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- disc brake
- housing
- reaction force
- reduction mechanism
- Prior art date
Links
- 238000006243 chemical reaction Methods 0.000 claims abstract description 54
- 230000002093 peripheral effect Effects 0.000 claims description 18
- 238000003466 welding Methods 0.000 claims description 4
- 230000002411 adverse Effects 0.000 abstract description 4
- 230000000694 effects Effects 0.000 abstract description 3
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 230000033001 locomotion Effects 0.000 description 15
- 238000003825 pressing Methods 0.000 description 6
- 210000000078 claw Anatomy 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 230000005489 elastic deformation Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001141 propulsive effect Effects 0.000 description 1
Images
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
- B60T13/746—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 and mechanical transmission of the braking action
-
- 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
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
-
- 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
-
- 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
- B60T13/741—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 acting on an ultimate actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
- F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
- F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
- F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
- F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
-
- 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
- F16D65/005—Components of axially engaging brakes not otherwise provided for
- F16D65/0068—Brake calipers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
- F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
- F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—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
- F16D65/183—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 with force-transmitting members arranged side by side acting on a spot type force-applying member
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/70—Gearings
- B60Y2400/73—Planetary gearings
-
- 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
- F16D2055/0004—Parts or details of disc brakes
- F16D2055/0016—Brake calipers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/18—Electric or magnetic
- F16D2121/24—Electric or magnetic using motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/44—Mechanical mechanisms transmitting rotation
- F16D2125/46—Rotating members in mutual engagement
- F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing
-
- 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
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0061—Joining
- F16D2250/0076—Welding, brazing
Definitions
- the present invention relates to a disc brake used for braking a vehicle and a planetary gear reduction mechanism provided in the disc brake.
- a disc brake described in Patent Document 1 includes a pair of pads arranged on both sides in the axial direction of the rotor with a rotor interposed therebetween, a piston that presses one of the pair of pads against the rotor, and a piston that moves.
- a caliper body having a cylinder that can be accommodated therein; a motor provided in the caliper body; a planetary gear reduction mechanism that increases and transmits rotation of the motor; rotation from the planetary gear reduction mechanism is transmitted; a piston propulsion mechanism for propelling the to a braking position.
- the planetary gear reduction mechanism includes a sun gear having an input gear portion meshing with a spur gear to which rotation from a motor is transmitted, an output gear portion extending axially from the radially central portion of the input gear portion, and an output of the sun gear. It is composed of a plurality of planetary gears that mesh with the gear portion and are arranged at intervals in the circumferential direction so as to surround the output gear portion, and an internal gear that has internal teeth that mesh with each planetary gear and is arranged so as to surround each planetary gear. be done.
- the sun gear is rotatably supported by the cylindrical support of the internal gear.
- the projections provided on the outer peripheral surface of the cylindrical engaging portion of the internal gear are engaged with the engaging grooves provided on the housing, so that the internal gear cannot rotate relative to the housing.
- one end opening of the housing is closed by a cover member.
- the planetary gear reduction mechanism is arranged so as to be sandwiched between the housing and the cover member, and axial movement of the sun gear is restricted. A slight gap is provided between the sun gear and the cover member to allow the sun gear to rotate.
- an object of the present invention is to provide a planetary gear reduction mechanism that improves the meshing state of gears during operation, and a disc brake that includes the planetary gear reduction mechanism. .
- a disc brake according to the present invention includes a mounting member that is fixed to a non-rotating portion of a vehicle and is provided across the outer peripheral side of a disc rotor; a first friction pad arranged to face one axial surface of the disk rotor; and a first friction pad movably provided on the mounting member and arranged to face the other axial surface of the disk rotor.
- the planetary gear reduction mechanism including a first gear to which rotation from the motor is transmitted; a sun gear having a second gear extending in the axial direction of the second gear; a plurality of planetary gears that mesh with the second gear and are arranged to surround the second gear; and a plurality of planetary gears that mesh with the plurality of planetary gears an internal gear arranged to surround the sun gear, the internal gear being spaced apart from the first gear by a predetermined distance in the axial direction of the first gear; and a
- the planetary gear reduction mechanism includes a first gear to which rotation from a drive source is transmitted, and a second gear extending from the axial center of the first gear in the axial direction of the first gear.
- a sun gear a plurality of planetary gears that mesh with the second gear and are arranged to surround the second gear, an internal gear that meshes with the plurality of planetary gears and is arranged to surround the plurality of planetary gears; wherein the internal gear is opposed to a supporting portion that rotatably supports the sun gear and is spaced apart from the first gear by a predetermined distance in the axial direction of the first gear.
- a reaction force receiving portion which is arranged so as to overlap with the first gear when viewed from the radial direction of the first gear and receives the reaction force accompanying the rotation of the sun gear. is.
- the disk brake and the planetary gear reduction mechanism of the present invention it is possible to improve the meshing state of the gears during operation, and as a result, it is possible to suppress adverse effects on the performance, strength, operation noise, etc. of the gears. .
- FIG. 3 is an enlarged view of a main portion of FIG. 2;
- FIG. 2 is a plan view of the disc brake according to the present embodiment, omitting illustration of a cover housing;
- FIG. 5 is a cross-sectional view taken along line AA of FIG. 4;
- FIG. 6 is a cross-sectional view similar to FIG. 5 showing a disc brake according to another embodiment;
- FIG. 1 the vehicle inner side (inner side) will be referred to as one end side (cover housing 29 side), and the vehicle outer side (outer side) will be referred to as the other end side (disk rotor D side). That is, in FIGS. 2, 3, 5 and 6, the right side is referred to as one end side, and the left side is referred to as the other end side, and will be described accordingly.
- a disc brake 1 includes a pair of inner brake pads 2 and an outer brake pad 2 arranged on both sides in the axial direction across a disc rotor D attached to a rotating portion of a vehicle.
- a brake pad 3 and a caliper 4 are provided.
- This disc brake 1 is constructed as a caliper floating type.
- a pair of inner brake pad 2 and outer brake pad 3 and caliper 4 are supported by bracket 5 so as to be movable in the axial direction of disk rotor D.
- the bracket 5 is fixed to a non-rotating portion such as a knuckle of the vehicle, and is provided so as to straddle the outer peripheral side of the disk rotor D.
- the bracket 5 includes slide pins 9, 9 fixed to a pair of caliper arm portions 8, 8 extending outward from a cylinder portion 16, which will be described later, and the slide pins 9, 9. are slidably inserted along the axial direction, and are integrally connected to a pair of pin inserting portions 10, 10 extending so as to straddle the outer peripheral side of the disk rotor D, and the pair of pin inserting portions 10, 10. , an inner side support portion 11 which supports the inner brake 2 movably along the axial direction of the disc rotor D, and a pair of pin inserting portions 10, 10, which are integrally connected, and the outer brake pad 3 is connected to the disc rotor D. and an outer side support portion 12 that supports movably along the axial direction of the.
- the inner brake pad 2 is arranged to face the inner side surface of the disk rotor D in the axial direction.
- the outer brake pad 3 is arranged to face the outer side surface of the disk rotor D in the axial direction. Then, the inner side support portion 11 of the bracket 5 is fixed to the non-fixed portion of the vehicle.
- the inner brake pad 2 corresponds to a first friction pad
- the outer brake pad 3 corresponds to a second friction pad.
- the bracket 5 corresponds to the mounting member.
- a caliper body 15 which is the main body of the caliper 4, is arranged on the base end side facing the inner brake pad 2, and is a bottomed cylindrical cylinder portion that opens facing the inner brake pad 2.
- a piston 21 is accommodated in the cylinder portion 16 of the caliper body 15, that is, in the cylinder bore 20 of the cylinder portion 16 so as to be non-rotatable relative to the cylinder portion 16 and axially movable.
- the piston 21 presses the inner brake pad 2 and is shaped like a cup with a bottom.
- the piston 21 is accommodated in the cylinder bore 20 of the cylinder portion 16 so that its bottom faces the inner brake pad 2 .
- the piston 21 is supported so as not to rotate relative to the cylinder bore 20 and thus to the caliper body 15 by the anti-rotation engagement between the bottom portion of the piston 21 and the inner brake pad 2 .
- a seal member (not shown) is arranged on the inner peripheral surface of the other end of the cylinder bore 20 of the cylinder portion 16 .
- the piston 21 is housed in the cylinder bore 20 so as to be axially movable while being in contact with the seal member.
- a hydraulic pressure chamber 24 is formed which is partitioned by a seal member. Hydraulic pressure is supplied to the hydraulic pressure chamber 24 from a hydraulic pressure source (not shown) such as a master cylinder or a hydraulic pressure control unit via a hydraulic circuit (not shown) provided in the cylinder portion 16 .
- a dust boot 25 is interposed between the outer peripheral surface on the bottom side of the piston 21 and the inner peripheral surface on the other end side of the cylinder bore 20 .
- a housing 28 is attached to the bottom of the cylinder portion 16 of the caliper body 15 .
- An open portion on one end side of the housing 28 is airtightly closed by a cover housing 29 .
- the open portion on the one end side of the housing 28 is closed by fixing the cover housing 29 to the housing 28 by vibration welding.
- a seal member 36 is provided between the fitting recess 34 of the housing 28 and the cylinder portion 16 .
- the inside of the housing 28 is kept airtight by the sealing member 36 .
- the housing 28 is integrally connected to a first housing portion 31 that houses a planetary gear reduction mechanism 55 (to be described later) so as to cover the outer periphery of the bottom portion of the cylinder portion 16 so as to be aligned with the first housing portion 31.
- a second housing portion 32 is protruded from the end side in the shape of a bottomed cylinder and accommodates an electric motor 53, which will be described later.
- the first housing part 31 is formed in a substantially cylindrical shape with one end side open and the other end side having an opening 38 .
- the planetary gear reduction mechanism 55 is housed inside the first housing portion 31 .
- a fitting recess 34 is formed on the other end side of the first housing portion 31 .
- the bottom portion of the cylinder portion 16 is airtightly fitted into the fitting recess 34 by a sealing member 36 .
- An opening 38 is formed at the bottom of the fitting recess 34 .
- a stepped portion 42 having a first annular surface 40 and a peripheral wall surface 41 is formed on one end side from the opening 38 .
- a second annular surface 43 is formed on one end side of the stepped portion 42 .
- a carrier 85 of a planetary gear reduction mechanism 55 which will be described later, is rotatably supported on the first annular surface 40 of the stepped portion 42. As shown in FIG. The peripheral wall surface 41 of the stepped portion 42 restricts radial movement of the carrier 85 of the planetary gear reduction mechanism 55 .
- a pair of engaging recesses 46, 46 are formed on the inner wall surface of the first housing portion 31 at opposing positions.
- the respective engaging recesses 46 , 46 are formed on the inner wall surface of the first housing portion 31 at a pitch of 180° along the circumferential direction.
- the engagement recess 46 is formed by forming two anti-rotation protrusions 47, 47 protruding radially inward from the inner wall surface of the first housing portion 31 at intervals along the circumferential direction thereof. .
- the inner wall portion of the first housing portion 31 overlaps the peripheral wall portion of the cover housing 29 in the range where the anti-rotation protrusions 47 , 47 (engagement recess 46 ) are formed. It protrudes from one end side as shown in FIG.
- the axial length of each anti-rotation protrusion 47, 47 (engagement recess 46) corresponds to the axial length of an anti-rotation portion 113 provided on an internal gear 84, which will be described in detail later.
- the positions of the engaging recesses 46, 46 along the circumferential direction are the radial center of the reduction gear 68 (the radial center of the shaft 80) described later and the radial center of the sun gear 82 described later.
- the second housing portion 32 is formed in a bottomed cylindrical shape with the other end open. The other end opening of the second housing portion 32 is closed by a cap member 49 .
- a through hole 50 is formed in the bottom (one end) of the second housing portion 32 .
- the caliper body 15 includes an electric motor 53, a spur-tooth multistage reduction mechanism 54 and a planetary gear reduction mechanism 55 that increase the rotational torque from the electric motor 53, the spur-tooth multistage reduction mechanism 54 and a planetary gear reduction mechanism 55.
- a piston propulsion mechanism 56 is provided that converts the rotational motion from the planetary gear reduction mechanism 55 into linear motion, applies thrust to the piston 21, and holds the propelled piston 21 at a braking position.
- the electric motor 53 is electrically connected to an electronic control unit (ECU) 60 for controlling its rotation.
- a parking switch 61 is electrically connected to the electronic control unit 60 to be operated when the parking brake is turned ON/OFF. It should be noted that the electronic control unit 60 can also operate the parking brake based on a signal from the vehicle side without operating the parking switch 61 .
- the electric motor 53 is accommodated within the second housing portion 32 of the housing 28 as described above.
- a rotating shaft 63 of the electric motor 53 is inserted through a through hole 50 provided in the bottom of the second housing portion 32 and extends to one end side.
- a spring 65 is arranged between the electric motor 53 and the cap member 49 .
- the electric motor 53 is biased toward the one end side (cover housing 29 side) by the biasing force of the spring 65 .
- the cylinder portion 16 of the caliper body 15 and the electric motor 53 are arranged side by side.
- the spur-toothed multi-stage speed reduction mechanism 54 is housed within the cover housing 29.
- the spur-tooth multistage reduction mechanism 54 includes a pinion gear 67 and a reduction gear 68 .
- the pinion gear 67 is formed in a cylindrical shape and has a hole portion 70 into which the rotating shaft 63 of the electric motor 53 is press-fitted and fixed, and a gear 71 formed on the outer periphery.
- the reduction gear 68 has a shaft hole 74 extending axially at its radial center.
- the reduction gear 68 is constructed by integrally connecting a large-diameter large gear 77 meshing with the gear 71 of the pinion gear 67 and a small-diameter small gear 78 extending concentrically from the large gear 77 in the axial direction. ing.
- the small gear 78 integrally extends from the large gear 77 toward the other end side.
- a shaft 80 is rotatably inserted through the shaft hole 74 of the reduction gear 68 .
- the other end of the shaft 80 is integrally fixed to the wall between the first housing part 31 and the second housing part 32 of the housing.
- the reduction gear 68 is rotatably supported by the shaft 80 .
- a small gear 78 of the reduction gear 68 meshes with the planetary gear reduction mechanism 55 .
- the planetary gear reduction mechanism 55 is housed inside the first housing portion 31 of the housing 28 .
- the planetary gear reduction mechanism 55 includes a sun gear 82 , a plurality of (four in this embodiment) planetary gears 83 , an internal gear 84 and a carrier 85 .
- the sun gear 82, the internal gear 84, and the carrier 85 are arranged concentrically with each other.
- the sun gear 82 is composed of a large-diameter large gear 88 meshing with the small gear 78 of the reduction gear 68 and a small-diameter small-diameter shaft gear 89 concentrically extending from the large gear 88 along the axial direction.
- the large gear 88 is integrally provided with an annular wall portion 90 annularly extending radially inward.
- the small-diameter shaft gear 89 integrally extends concentrically from the radial inner end of the annular wall portion 90 of the large gear 88 toward the other end.
- the small-diameter shaft gear 89 is composed of a large-diameter shaft portion 92 located on one end side and a small gear 93 continuously extending from the large-diameter shaft portion 92 to the other end side in a concentric manner.
- the small-diameter shaft gear 89 is formed with a through hole 96 extending in the axial direction at its radially central portion.
- One end surface of the small-diameter shaft gear 89 is arranged as close as possible to the inner wall surface of the cover housing 29 .
- the large diameter shaft portion 92 has a larger diameter than the small gear 93 .
- the large gear 88 of the sun gear 82 corresponds to the first gear
- the small gear 93 of the sun gear 82 corresponds to the second gear.
- the planetary gear 83 has a gear 100 meshed with the small gear 93 of the sun gear 82, and a pin hole 101 through which a pin 106 erected from the carrier 85 is rotatably inserted.
- Each planetary gear 83 is arranged on the circumference of a carrier 85 to be described later at equal intervals so as to surround the small gear 93 of the sun gear 82 .
- Carrier 85 is formed in a disc shape.
- the carrier 85 is rotatably supported on the first annular surface 40 of the stepped portion 42 provided on the first housing portion 31 .
- a polygonal hole 104 is formed through substantially the center of the carrier 85 in the radial direction.
- the outer diameter of the carrier 85 is substantially the same as the outer diameter of the orbit of each planetary gear 83 .
- a plurality of pins 106 are provided on the outer peripheral side of the carrier 85 so as to protrude toward one end side. Each pin 106 protrudes at intervals along the circumferential direction. Each pin 106 is rotatably inserted through the pin hole 101 of each planetary gear 83 . Thereby, the revolution motion of each planetary gear 83 is transmitted to the carrier 85 .
- a polygonal shaft portion 126 of a spindle 125 of a piston propulsion mechanism 56 which will be described later, is fitted into the polygonal hole 104 of the carrier 85 . As a result, rotational torque can be transmitted between the carrier 85 and the spindle 125 .
- the internal gear 84 includes internal teeth 110 with which the gears 100 of the planetary gears 83 are meshed, and concentric planar teeth extending radially inward from one axial end of the internal teeth 110 .
- a cylindrical support portion 112 extending concentrically continuously from the radially inner end of the annular wall portion 111 to one end side; and a pair of detent portions 113, 113 (see FIGS. 4 and 5) continuously extending from the ring-shaped wall portion 111 to the one end side.
- the annular wall portion 111 is arranged to face the large gear 88 of the sun gear 82 , specifically, the annular wall portion 111 of the large gear 88 with a predetermined distance in the axial direction of the sun gear 82 .
- the cylindrical support portion 112 is concentrically disposed radially outward of the large diameter shaft portion 92 provided on the small diameter shaft gear 89 of the sun gear 82 .
- a slide bearing 120 is arranged between the cylindrical support portion 112 and the large diameter shaft portion 92 of the sun gear 82 .
- the sliding bearing 120 is composed of a cylindrical bearing portion 121 and an annular flange portion 122 extending radially outward from one end of the bearing portion 121 .
- the bearing portion 121 is arranged between the inner peripheral surface of the cylindrical support portion 112 of the internal gear 84 and the outer peripheral surface of the large diameter shaft portion 92 of the sun gear 82 .
- the annular flange portion 122 of the slide bearing 120 is sandwiched between one end surface of the cylindrical support portion 112 of the internal gear 84 and the other end surface of the annular wall portion 90 of the sun gear 82 .
- the slide bearing 120 rotatably supports the large-diameter shaft portion 92 of the sun gear 82 with respect to the cylindrical support portion 112 of the internal gear 84 . Consequently, the sun gear 82 is rotatably supported with respect to the internal gear 84 .
- the cylindrical support portion 112 corresponds to the support portion.
- the annular wall portion 111 corresponds to the plane portion. As shown in FIGS.
- the internal gear 84 has a pair of detents 113, 113 protruding radially outward from the outer peripheral surface of the portion where the internal teeth 110 are formed. It extends continuously from the annular wall portion 111 to one end side.
- the pair of anti-rotation portions 113, 113 are positioned corresponding to the pair of engaging recesses 46, 46 provided in the first housing portion 31. More specifically, they extend 180 along the circumferential direction of the internal gear 84. ° Formed with a pitch.
- the anti-rotation portion 113 has a substantially rectangular cross section. As described above, the anti-rotation portion 113 projects radially outward from the outer peripheral surface of the portion of the internal gear 84 where the internal teeth 110 are formed, and continues from the annular wall portion 111 to one end side. is extended. Specifically, referring to FIG. 5, the anti-rotation portion 113 extends from the annular wall portion 111 of the internal gear 84 to a position beyond the axial center position of the large gear 88 and below one end of the large gear 88 in the axial direction. procrastinating.
- the anti-rotation portion 113 extends to one end side so that one end thereof is located between the axial center position of the large gear 88 and one axial end of the large gear 88 .
- a portion of the detent portion 113 extending from the annular wall portion 111 to one end side is arranged so as to overlap the large gear 88 when viewed from the radial direction of the large gear 88 of the sun gear 82 .
- the pair of anti-rotation portions 113, 113 of the internal gear 84 are engaged with the respective engaging recesses 46, 46 of the first housing portion 31 by loose fit.
- the fitting dimensional tolerance is set so that a clearance is provided, and the fitting dimensional tolerance is set so that a slight clearance is provided between the top surface of the anti-rotation portion 113 and the bottom surface of the engaging recess 46. be done. Then, the other end surface of the internal gear 84 is brought into contact with the second annular surface 43 of the first housing portion 31 , and the pair of detent portions 113 , 113 of the internal gear 84 are engaged with the first housing portion 31 .
- the null gear 84 is restricted from moving axially and radially with respect to the first housing portion 31 and is supported so as not to rotate relative to the first housing portion 31 .
- the engagement points between the pair of anti-rotation portions 113, 113 of the internal gear 84 and the engagement recesses 46, 46 of the first housing portion 31 are arranged radially of the reduction gear 68. It is located along a straight line L2 extending in a direction orthogonal to a straight line L1 connecting the center (the radial center of the shaft 80) and the radial center of the sun gear 82.
- the abutting portions with the anti-rotation protrusions 47 provided on the first housing portion 31 are arranged so that the sun gear 82 rotates. act as reaction force receiving portions 114, 114 that receive the reaction force from the first housing portion 31 associated with this.
- the piston propulsion mechanism 56 is composed of a rotation/linear motion conversion mechanism. As shown in FIG. 2, the piston propulsion mechanism 56 converts the rotary motion from the spur-tooth multistage reduction mechanism 54 and the planetary gear reduction mechanism 55, that is, the rotary motion of the spindle 125, into linear motion, and converts the linear motion member (not shown) into linear motion. ) gives a thrust to the piston 21 to propel the piston 21 (move it to the other end side) and hold the piston 21 at the braking position.
- the spindle 125 has a polygonal shaft portion 126 at one end thereof. The polygonal shaft portion 126 is fitted into the polygonal hole 104 provided in the carrier 85 of the planetary gear reduction mechanism 55 .
- the piston propulsion mechanism 56 is arranged within the cylinder bore 20 between its bottom surface and the piston 21 .
- the spindle 125 rotates with the rotation of the carrier 85, the linear motion member advances toward the other end side due to the action of the piston driving mechanism 56, thereby advancing the piston 21.
- the braking state can be maintained.
- the action of the disc brake 1 according to this embodiment will be described.
- a hydraulic pressure corresponding to the force applied to the brake pedal is sent from a hydraulic pressure source such as a master cylinder through a hydraulic circuit (both not shown) to the cylinder portion 16 (cylinder bore 20) of the caliper body 15. is supplied to the hydraulic chamber 24 inside.
- the piston 21 moves forward (moves leftward in FIG. 2) from its original position during non-braking, pressing the inner brake pad 2 against the disc rotor D while elastically deforming the seal member.
- the caliper body 15 moves toward the inner side (rightward in FIG. 2) with respect to the bracket 5 due to the reaction force against the pressing force of the piston 21 against the inner brake pad 2, and the claw portions 17, 17 act as outer brakes.
- the pad 3 is pressed against the disk rotor D.
- the disc rotor D is sandwiched between the pair of inner and outer brake pads 2 and 3 to generate frictional force, which in turn generates braking force for the vehicle.
- the operation as a parking brake which is an example of the operation for maintaining the stopped state of the vehicle, will be described.
- the parking switch 61 is operated to operate (apply) the parking brake from the released state of the parking brake
- the electric motor 53 is driven in the apply direction by a command from the electronic control unit 60, and the spur gear multistage deceleration is performed.
- the sun gear 82 of the planetary gear reduction mechanism 55 is rotated via the mechanism 54 .
- the rotation of the sun gear 82 causes the planetary gears 83 to revolve around the axis of the sun gear 82 while rotating around its own axis, thereby rotating the carrier 85 . Rotation from the carrier 85 is then transmitted to the spindle 125 .
- the pair of detents 113, 113 provided on the internal gear 84 are A position symmetrical with respect to the radial center of the gear 84 and along a straight line L2 extending in a direction orthogonal to a straight line L1 connecting the radial center of the reduction gear 68 and the radial center of the sun gear 82 receives the reaction force from the anti-rotation protrusions 47, 47 of the first housing portion 31, and the anti-rotation portion 113 (reaction force receiving portion 114) of the internal gear 84 receives the reaction force of the large gear 88 of the sun gear 82. Seen from the radial direction, it receives a reaction force from each anti-rotation protrusion 47 , 47 of the first housing portion 31 at a position overlapping the large gear 88 .
- the internal gear 84 rotatably supports the sun gear 82 by its cylindrical support portion 112
- the large gear 88 of the sun gear 82 is positioned as the small gear of the reduction gear 68.
- the load received from 78 is also supported by the internal gear 84, but the position of the load received by the large gear 88 of the sun gear 82 from the small gear 78 of the reduction gear 68 and the detent portion 113 of the internal gear 84 (reverse
- the position where the force receiving portion 114 receives the reaction force from the anti-rotation protrusions 47 of the first housing portion 31 is substantially the same position along the axial direction of the internal gear 84 .
- the linear motion member advances due to the action of the piston driving mechanism 56 to move the piston 21 forward.
- the inner brake pad 2 is pressed against the disc rotor D by advancing the piston 21 .
- the caliper body 15 moves toward the inner side (rightward in FIG. 2) with respect to the bracket 5 due to the reaction force against the pressing force of the piston 21 against the inner brake pad 2, and the claw portions 17, 17 act as outer brakes.
- the pad 3 is pressed against the disk rotor D.
- the disc rotor D is sandwiched between the pair of inner and outer brake pads 2 and 3 to generate a frictional force, which in turn generates a braking force for the vehicle, and the braking state can be maintained.
- the electric motor 53 is controlled until the pressing force from the pair of inner and outer brake pads 2 and 3 to the disk rotor D reaches a predetermined value, for example, until the current value of the electric motor 53 reaches a predetermined value. 53 is driven. After that, when the electronic control unit 60 detects that the pressing force on the disc rotor D has reached a predetermined value by detecting that the current value of the electric motor 53 has reached a predetermined value, the electric current to the electric motor 53 is stopped. .
- the rotation shaft 63 of the electric motor 53 rotates in the opposite direction, that is, in the release direction, by a command from the electronic control unit 60. It is transmitted to spindle 125 via mechanism 55 .
- the piston driving mechanism 56 causes the direct-acting member to retreat and return to its initial state. 3 is released.
- the anti-rotation portion 113 provided on the internal gear 84 is engaged with the inner wall surface of the first housing portion 31 of the housing 28.
- the engaging recess 46 (a pair of anti-rotation protrusions 47, 47) is provided, and as shown in FIG.
- An engagement recess 46 (a pair of anti-rotation protrusions 47, 47) may be provided.
- this embodiment as can be seen from FIG. It protrudes toward the other end so as to overlap the inner side of the peripheral wall.
- the internal gear 84 has the reaction force receiving portions 114, 114 that receive the reaction force accompanying the rotation of the sun gear 82.
- a stop portion 113 is provided, and the stop portion 113 is arranged so as to overlap the large gear 88 of the sun gear 82 when viewed from the radial direction of the large gear 88 .
- the position of the load received by the large gear 88 of the sun gear 82 from the small gear 78 of the reduction gear 68 and the detent portion 113 (reaction force receiving portion 114) of the internal gear 84 are
- the position where the reaction force is received from the anti-rotation protrusions 47 of the first housing portion 31 is substantially the same position along the axial direction of the internal gear 84 .
- the planetary gear reduction mechanism 55 when the planetary gear reduction mechanism 55 operates, it is possible to suppress the generation of a moment in the direction of rotation about an arbitrary straight line along the radial direction of the sun gear 82 and the internal gear 84 .
- the inclination of the sun gear 82 and the internal gear 84 can be suppressed, and the meshing state of the planetary gear reduction mechanism 55 is improved, thereby suppressing adverse effects on gear performance, strength, operation noise, etc., and improving reliability. can be made
- the anti-rotation portion 113 provided in the internal gear 84 extends from the annular wall portion 111 of the internal gear 84 to the axial center position of the large gear 88 and It extends to a position below one axial end of 88 .
- the portion of the anti-rotation portion 113 extending from the annular wall portion 111 to the one end side is arranged so as to maximally overlap in the axial direction of the large gear 88 when viewed from the radial direction of the large gear 88 of the sun gear 82 . Therefore, when the planetary gear reduction mechanism 55 operates, it is possible to suppress the generation of a moment in the direction of rotation about an arbitrary straight line along the radial direction of the sun gear 82 and the internal gear 84 to the maximum extent possible.
- the reaction force receiving portion 114 that receives the reaction force accompanying the rotation of the sun gear 82 is provided in the detent portion 113, and the reaction force receiving portion 114 is newly provided. Since it is provided in the existing anti-rotation portion 113, the structure can be simplified.
- the internal gear 84 has a plurality of rotation stop portions 113 having the reaction force receiving portions 114, 114 at equal intervals along the circumferential direction (two pieces at a pitch of 180°). Because of this arrangement, the reaction force from the first housing or the cover housing 29 that accompanies the rotation of the sun gear 82 is substantially evenly distributed to the engaging portions (the detent portions 113, 113 and the engaging recesses 46, 46). It is possible to improve the durability of the engaging portion.
- the anti-rotation portion 113 provided on the internal gear 84 is engaged with the engaging recess 46 provided on the first housing portion 31 or the cover housing 29 by loose fit. Therefore, the assembly work is facilitated, and the manufacturing cost can be reduced by reducing the number of assembly man-hours.
- the cover housing 29 is fixed to the housing by vibration welding.
- the spur-tooth multi-stage speed reduction mechanism 54 (reduction gear 68) and the planetary gear speed reduction mechanism 55 cannot be rotatably supported on the cover housing 29 side, and the cover housing 29 side cannot be rotatably supported. need to support In this case, there is a possibility that the planetary gear reduction mechanism 55 may have poor meshing, and the present embodiment is adopted to solve this problem.
- the present embodiment is applied to the disc brake 1 that drives the electric motor 53 to generate a braking force when operating the parking disc brake used for parking braking or the like.
- This embodiment may be applied to an electric disc brake in which the electric motor 53 is driven to generate a braking force during normal braking.
- the planetary gear reduction mechanism 55 may be applied not only to the disk brake 1 described above, but also to other devices that increase and output the rotation or the like from the motor.
- a first aspect includes a mounting member (5) that is fixed to a non-rotating portion of a vehicle and is provided across the outer peripheral side of a disk rotor (D); A first friction pad (2) arranged to face one surface of the rotor (D) in the axial direction, and a first friction pad (2) provided movably on the mounting member (5), a second friction pad (3) arranged to face the other surface of the disk rotor (D ), a housing (28) provided in the caliper (4), a motor (53) housed in the housing (28), and the housing (28).
- the sun gear (82) having a first gear (88) and a second gear (93) extending from the axial center of the first gear (88) in the axial direction of the first gear (88); a plurality of planetary gears (83) meshing with a second gear (93) and arranged to surround the second gear (93); and a plurality of planetary gears (83) meshing with the plurality of planetary gears (83) and surrounding the plurality of planetary gears (83).
- an internal gear (84) arranged as follows: the internal gear (84) includes a support (112) that rotatably supports the sun gear (82); and the first gear (88).
- a flat portion (111) arranged to face the first gear (88) at a predetermined distance in the axial direction of the first gear (88) so as to overlap the first gear (88) when viewed in the radial direction of the first gear (88). and a reaction force receiving portion (114) that receives the reaction force associated with the rotation of the sun gear (82).
- reaction force receiving portion (114) receives reaction force from the housing (28). In a third aspect, in the first aspect, the reaction force receiving portion (114) receives reaction force from the cover housing (29).
- the reaction force receiving portion (114) extends from the flat portion (111) to the first gear (88) when viewed from the radial direction of the first gear (88). It extends to a position beyond the center position in the axial direction and is arranged so as to overlap with the first gear (88).
- the reaction force receiving portion (114) extends from the flat portion (111) to the first gear (88) when viewed from the radial direction of the first gear (88). It extends beyond the center position in the axial direction and extends to a position below the axial end of the first gear (88) so as to overlap the first gear (88).
- the reaction force receiving portion (114) is configured to restrict relative rotation of the internal gear (84) with respect to the housing (28) or the cover housing (29). It is provided on the stop (113).
- a plurality of the anti-rotation portions (113) are arranged at regular intervals in the circumferential direction of the internal gear (84).
- the anti-rotation portion (113) is engaged with the housing (28) or the cover housing (29) with a loose fit.
- the cover housing (29) is fixed to the housing (28) by vibration welding.
- the planetary gear reduction mechanism 55 provided in the disc brake 1 includes a first gear (88) to which rotation from the drive source (53) is transmitted, A sun gear (82) having a second gear (93) extending from the axial center of the first gear (88) in the axial direction of the first gear (88) meshes with the second gear (93) to a plurality of planetary gears (83) arranged to surround a second gear (93); and an internal gear (84) meshing with the plurality of planetary gears (83) and arranged to surround the plurality of planetary gears (83).
- the internal gear (84) includes a support portion (112) that rotatably supports the sun gear (82), and the first gear (88) A flat portion (111) arranged to face the first gear (88) at a predetermined distance in the axial direction of the first gear (88) so as to overlap the first gear (88) when viewed in the radial direction of the first gear (88). and a reaction force receiving portion (114) that receives the reaction force associated with the rotation of the sun gear (82).
- the reaction force receiving portion (114) extends from the flat portion (111) to the first gear (88) when viewed from the radial direction of the first gear (88). It extends to a position beyond the center position in the axial direction and is arranged so as to overlap with the first gear (88).
- the reaction force receiving portion (114) extends from the flat portion (111) to the first gear (88) when viewed from the radial direction of the first gear (88). It extends beyond the center position in the axial direction and extends to a position below the axial end of the first gear (88) so as to overlap the first gear (88).
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Braking Arrangements (AREA)
- Retarders (AREA)
Abstract
Description
まず、ブレーキペダル(図示略)の操作による通常の液圧ブレーキとしてのディスクブレーキ1の制動時における作用を説明する。
運転者によりブレーキペダルが踏み込まれると、ブレーキペダルの踏力に応じた液圧がマスタシリンダ等の液圧源から液圧回路(共に図示省略)を経て、キャリパ本体15のシリンダ部16(シリンダボア20)内の液圧室24に供給される。これにより、ピストン21がシール部材を弾性変形させながら非制動時の原位置から前進(図2の左方向に移動)して、インナブレーキパッド2をディスクロータDに押し付ける。そして、ピストン21によるインナブレーキパッド2への押圧力に対する反力により、キャリパ本体15がブラケット5に対してインナ側(図2における右方向)に移動して、各爪部17、17によってアウタブレーキパッド3をディスクロータDに押し付ける。その結果、ディスクロータDが一対のインナ及びアウタブレーキパッド2、3により挟みつけられて摩擦力が発生し、ひいては、車両の制動力が発生することになる。
まず、駐車ブレーキの解除状態からパーキングスイッチ61が操作されて駐車ブレーキを作動(アプライ)させる際に、電子制御ユニット60からの指令により、電動モータ53をアプライ方向に駆動させて、平歯多段減速機構54を介して遊星歯車減速機構55のサンギヤ82を回転させる。このサンギヤ82の回転により、各プラネタリギヤ83が自身の軸心を中心に自転しながらサンギヤ82の軸心を中心に公転することで、キャリア85が回転する。そして、キャリア85からの回転がスピンドル125に伝達される。
第1の態様は、車両の非回転部に固定され、ディスクロータ(D)の外周側を跨いで設けられる取付部材(5)と、該取付部材(5)に移動可能に設けられ、前記ディスクロータ(D)の軸方向における一方の面と対向して配置される第1の摩擦パッド(2)と、前記取付部材(5)に移動可能に設けられ、前記ディスクロータ(D)の軸方向における他方の面と対向して配置される第2の摩擦パッド(3)と、前記第1の摩擦パッド(2)を押圧するピストン(21)と、該ピストン(21)を前記ディスクロータ(D)の軸方向に移動可能に収容するキャリパ(4)と、該キャリパ(4)に設けられるハウジング(28)と、該ハウジング(28)に収容されるモータ(53)と、前記ハウジング(28)に収容され、前記モータ(53)からの回転を伝達する遊星歯車減速機構(55)と、該遊星歯車減速機構(55)からの回転力を前記ピストン(21)の推進力に変換するピストン推進機構(56)と、前記ハウジング(28)の開口を覆うように取り付けられるカバーハウジング(29)と、を備え、前記遊星歯車減速機構(55)は、前記モータ(53)からの回転が伝達される第1ギヤ(88)、及び該第1ギヤ(88)の軸心部から前記第1ギヤ(88)の軸方向に延出した第2ギヤ(93)を有するサンギヤ(82)と、前記第2ギヤ(93)と噛み合い、前記第2ギヤ(93)を囲むように配置される複数のプラネタリギヤ(83)と、前記複数のプラネタリギヤ(83)と噛み合い、前記複数のプラネタリギヤ(83)を囲むように配置されるインターナルギヤ(84)と、を備え、該インターナルギヤ(84)は、前記サンギヤ(82)を回転可能に支持する支持部(112)と、前記第1ギヤ(88)の軸方向において前記第1ギヤ(88)と所定距離離間して対向配置される平面部(111)と、前記第1ギヤ(88)の径方向からみて前記第1ギヤ(88)と重なるように配置される、前記サンギヤ(82)の回転に伴う反力を受ける反力受け部(114)と、を有する。
第3の態様は、第1の態様において、前記反力受け部(114)は、前記カバーハウジング(29)から反力を受ける。
第5の態様は、第4の態様において、前記反力受け部(114)は、前記第1ギヤ(88)の径方向からみて、前記平面部(111)から前記第1ギヤ(88)の軸方向の中心位置を超え、かつ前記第1ギヤ(88)の軸方向端部以下の位置まで延出して、前記第1ギヤ(88)と重なるように配置される。
第7の態様は、第6の態様において、前記回り止め部(113)は、前記インターナルギヤ(84)の周方向において等間隔で複数配置されている。
第9の態様は、第1の態様において、前記カバーハウジング(29)は、前記ハウジング(28)に対して振動溶着により固定されている。
第12の態様は、第11の態様において、前記反力受け部(114)は、前記第1ギヤ(88)の径方向からみて、前記平面部(111)から前記第1ギヤ(88)の軸方向の中心位置を超え、かつ前記第1ギヤ(88)の軸方向端部以下の位置まで延出して、前記第1ギヤ(88)と重なるように配置される。
Claims (12)
- 車両の非回転部に固定され、ディスクロータの外周側を跨いで設けられる取付部材と、
該取付部材に移動可能に設けられ、前記ディスクロータの軸方向における一方の面と対向して配置される第1の摩擦パッドと、
前記取付部材に移動可能に設けられ、前記ディスクロータの軸方向における他方の面と対向して配置される第2の摩擦パッドと、
前記第1の摩擦パッドを押圧するピストンと、
該ピストンを前記ディスクロータの軸方向に移動可能に収容するキャリパと、
該キャリパに設けられるハウジングと、
該ハウジングに収容されるモータと、
前記ハウジングに収容され、前記モータからの回転を伝達する遊星歯車減速機構と、
該遊星歯車減速機構からの回転力を前記ピストンの推進力に変換するピストン推進機構と、
前記ハウジングの開口を覆うように取り付けられるカバーハウジングと、
を備え、
前記遊星歯車減速機構は、前記モータからの回転が伝達される第1ギヤ、及び該第1ギヤの軸心部から前記第1ギヤの軸方向に延出した第2ギヤを有するサンギヤと、前記第2ギヤと噛み合い、前記第2ギヤを囲むように配置される複数のプラネタリギヤと、前記複数のプラネタリギヤと噛み合い、前記複数のプラネタリギヤを囲むように配置されるインターナルギヤと、を備え、
該インターナルギヤは、前記サンギヤを回転可能に支持する支持部と、前記第1ギヤの軸方向において前記第1ギヤと所定距離離間して対向配置される平面部と、前記第1ギヤの径方向からみて前記第1ギヤと重なるように配置される、前記サンギヤの回転に伴う反力を受ける反力受け部と、を有することを特徴とするディスクブレーキ。 - 請求項1に記載のディスクブレーキであって、
前記反力受け部は、前記ハウジングから反力を受けることを特徴とするディスクブレーキ。 - 請求項1に記載のディスクブレーキであって、
前記反力受け部は、前記カバーハウジングから反力を受けることを特徴とするディスクブレーキ。 - 請求項1に記載のディスクブレーキであって、
前記反力受け部は、前記第1ギヤの径方向からみて、前記平面部から前記第1ギヤの軸方向の中心位置を超える位置まで延出して、前記第1ギヤと重なるように配置されることを特徴とするディスクブレーキ。 - 請求項4に記載のディスクブレーキであって、
前記反力受け部は、前記第1ギヤの径方向からみて、前記平面部から前記第1ギヤの軸方向の中心位置を超え、かつ前記第1ギヤの軸方向端部以下の位置まで延出して、前記第1ギヤと重なるように配置されることを特徴とするディスクブレーキ。 - 請求項1に記載のディスクブレーキであって、
前記反力受け部は、前記インターナルギヤの、前記ハウジングまたは前記カバーハウジングに対する相対回転を規制する回り止め部に設けられていることを特徴とするディスクブレーキ。 - 請求項6に記載のディスクブレーキであって、
前記回り止め部は、前記インターナルギヤの周方向において等間隔で複数配置されていることを特徴とするディスクブレーキ。 - 請求項6に記載のディスクブレーキであって、
前記回り止め部は、前記ハウジングまたは前記カバーハウジングに対して、すきまばめにて係合されていることを特徴とするディスクブレーキ。 - 請求項1に記載のディスクブレーキであって、
前記カバーハウジングは、前記ハウジングに対して振動溶着により固定されていることを特徴とするディスクブレーキ。 - 駆動源からの回転が伝達される第1ギヤ、及び前記第1ギヤの軸心部から前記第1ギヤの軸方向に延出した第2ギヤを有するサンギヤと、
前記第2ギヤと噛み合い、前記第2ギヤを囲むように配置される複数のプラネタリギヤと、
前記複数のプラネタリギヤと噛み合い、前記複数のプラネタリギヤを囲むように配置されるインターナルギヤと、を備えた遊星歯車減速機構であって、
前記インターナルギヤは、
前記サンギヤを回転可能に支持する支持部と、
前記第1ギヤの軸方向において前記第1ギヤと所定距離離間して対向配置される平面部と、
前記第1ギヤの径方向からみて前記第1ギヤと重なるように配置される、前記サンギヤの回転に伴う反力を受ける反力受け部と、を有することを特徴とする遊星歯車減速機構。 - 請求項10に記載の遊星歯車減速機構であって、
前記反力受け部は、前記第1ギヤの径方向からみて、前記平面部から前記第1ギヤの軸方向の中心位置を超える位置まで延出して、前記第1ギヤと重なるように配置されることを特徴とする遊星歯車減速機構。 - 請求項11に記載の遊星歯車減速機構であって、
前記反力受け部は、前記第1ギヤの径方向からみて、前記平面部から前記第1ギヤの軸方向の中心位置を超え、かつ前記第1ギヤの軸方向端部以下の位置まで延出して、前記第1ギヤと重なるように配置されることを特徴とする遊星歯車減速機構。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US18/281,621 US20240157924A1 (en) | 2021-10-15 | 2021-10-15 | Disc brake and planetary gear speed reduction mechanism |
PCT/JP2021/038256 WO2023062824A1 (ja) | 2021-10-15 | 2021-10-15 | ディスクブレーキ及び遊星歯車減速機構 |
CN202180095842.8A CN117098698A (zh) | 2021-10-15 | 2021-10-15 | 盘式制动器和行星齿轮减速机构 |
KR1020237029020A KR20230135649A (ko) | 2021-10-15 | 2021-10-15 | 디스크 브레이크 및 유성 기어 감속 기구 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2021/038256 WO2023062824A1 (ja) | 2021-10-15 | 2021-10-15 | ディスクブレーキ及び遊星歯車減速機構 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2023062824A1 true WO2023062824A1 (ja) | 2023-04-20 |
Family
ID=85988199
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/038256 WO2023062824A1 (ja) | 2021-10-15 | 2021-10-15 | ディスクブレーキ及び遊星歯車減速機構 |
Country Status (4)
Country | Link |
---|---|
US (1) | US20240157924A1 (ja) |
KR (1) | KR20230135649A (ja) |
CN (1) | CN117098698A (ja) |
WO (1) | WO2023062824A1 (ja) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019198509A1 (ja) | 2018-04-11 | 2019-10-17 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ及び遊星歯車減速機構 |
JP2020008134A (ja) * | 2018-07-11 | 2020-01-16 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ |
WO2020217788A1 (ja) * | 2019-04-22 | 2020-10-29 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6541842B1 (ja) | 2018-05-17 | 2019-07-10 | 株式会社ハシモトBaggage | 背負い鞄用肩ベルト及び背負い鞄 |
-
2021
- 2021-10-15 CN CN202180095842.8A patent/CN117098698A/zh active Pending
- 2021-10-15 KR KR1020237029020A patent/KR20230135649A/ko unknown
- 2021-10-15 WO PCT/JP2021/038256 patent/WO2023062824A1/ja active Application Filing
- 2021-10-15 US US18/281,621 patent/US20240157924A1/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019198509A1 (ja) | 2018-04-11 | 2019-10-17 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ及び遊星歯車減速機構 |
JP2020008134A (ja) * | 2018-07-11 | 2020-01-16 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ |
WO2020217788A1 (ja) * | 2019-04-22 | 2020-10-29 | 日立オートモティブシステムズ株式会社 | ディスクブレーキ |
Also Published As
Publication number | Publication date |
---|---|
KR20230135649A (ko) | 2023-09-25 |
CN117098698A (zh) | 2023-11-21 |
US20240157924A1 (en) | 2024-05-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US11453374B2 (en) | Disc brake and planetary gear reduction mechanism | |
JP6124669B2 (ja) | ディスクブレーキ | |
JP2014070670A (ja) | ディスクブレーキ | |
WO2018003393A1 (ja) | ディスクブレーキ | |
JP6316456B2 (ja) | ディスクブレーキ | |
JP4304418B2 (ja) | 電動ディスクブレーキ | |
JP5968192B2 (ja) | ディスクブレーキ | |
JP2016125544A (ja) | ディスクブレーキ | |
JP5552839B2 (ja) | ディスクブレーキ | |
JP6341851B2 (ja) | ディスクブレーキ | |
WO2023062824A1 (ja) | ディスクブレーキ及び遊星歯車減速機構 | |
JP7034023B2 (ja) | ディスクブレーキ | |
JP2018017300A (ja) | ディスクブレーキ | |
JP7220292B2 (ja) | ディスクブレーキ | |
WO2021215156A1 (ja) | ブレーキ装置 | |
JP7398345B2 (ja) | ディスクブレーキ及び遊星歯車減速機構 | |
JP6353784B2 (ja) | ディスクブレーキ | |
JP6373188B2 (ja) | ディスクブレーキ | |
JP2017133584A (ja) | ディスクブレーキ | |
JP2019132294A (ja) | ディスクブレーキ | |
WO2018123562A1 (ja) | ディスクブレーキ | |
JP2022181429A (ja) | 電動ブレーキ装置及び遊星歯車減速機構 | |
JP2016125548A (ja) | ディスクブレーキ | |
JP2016033413A (ja) | ディスクブレーキ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 21960678 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20237029020 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020237029020 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 18281621 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 202180095842.8 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2021960678 Country of ref document: EP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2021960678 Country of ref document: EP Effective date: 20240515 |