WO2015029989A1 - 電動パーキングブレーキ用駆動装置および電動パーキングブレーキ装置 - Google Patents
電動パーキングブレーキ用駆動装置および電動パーキングブレーキ装置 Download PDFInfo
- Publication number
- WO2015029989A1 WO2015029989A1 PCT/JP2014/072269 JP2014072269W WO2015029989A1 WO 2015029989 A1 WO2015029989 A1 WO 2015029989A1 JP 2014072269 W JP2014072269 W JP 2014072269W WO 2015029989 A1 WO2015029989 A1 WO 2015029989A1
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- WO
- WIPO (PCT)
- Prior art keywords
- gear
- electric motor
- parking brake
- brake
- electric
- Prior art date
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Classifications
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- 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
-
- 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
- B60T7/00—Brake-action initiating means
-
- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
- F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
- F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
- F16D2125/40—Screw-and-nut
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/44—Mechanical mechanisms transmitting rotation
- F16D2125/46—Rotating members in mutual engagement
- F16D2125/48—Rotating members in mutual engagement with parallel stationary axes, e.g. spur gears
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
Definitions
- the present invention relates to an electric parking brake drive device and an electric parking brake device that are driven by an electric motor when a vehicle is parked to apply braking force to wheels.
- An electric brake device disclosed in Patent Document 1 includes a small-diameter pulley fixed to an output shaft of an electric motor, a large-diameter pulley that is provided so as to be rotatable with respect to a housing, and a belt is spanned between the small-diameter pulley and Is included. Further, a two-stage planetary gear is coaxially connected to the large diameter pulley, and a gear mechanism is formed together with the large diameter pulley.
- the driving force of the electric motor is decelerated by a transmission mechanism including a belt and a plurality of planetary gears, converted to a linear pressing force, and then transmitted to the wheel brake to apply braking force to the wheel. is doing.
- the electric brake device described in Patent Document 1 has a bracket attached to one end portion in the rotation axis direction of the electric motor, and the electric motor is attached to the housing via the bracket.
- an elastic body is interposed between the bracket and the inner peripheral surface of the housing, and an elastic body is similarly interposed between the other end of the electric motor and the housing. ing.
- the housing of the electric brake device disclosed in Patent Document 1 is formed by joining a pair of bodies to each other.
- a fastening bolt or the like is used to join the bodies together, the housing becomes large for the fastening allowance, and therefore, the joining is often performed by welding or the like that does not require a fastening allowance.
- the structure is such that the electric motor is sandwiched between two bodies, so that an elastic body interposed between both ends of the electric motor is attached.
- the body receives a load in a direction in which both bodies separate from each other.
- the load applied to each body may act on the welded portion of the housing to reduce the bonding force.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a small and highly reliable driving device for an electric parking brake and an electric parking brake device.
- the structure of the electric parking brake driving device converts the rotational motion of the rotating member into a linear motion and transmits it to the moving member, and is urged by the moving member.
- An electric parking brake drive device for driving a parking brake actuator for generating a braking force on a wheel by pressing a disc rotating together with the wheel by a brake pad, wherein the first piece and the second piece are A gear body formed by joining together, an attachment member fixed to the inner periphery of the first piece, an electric motor engaged with or integrated with the attachment member and positioned in a predetermined direction in the gear body; A pressing member interposed between the inner peripheral surface of the first piece and the electric motor, and urging the electric motor toward the mounting member; and in the gear body It is volume, is that with a reduction mechanism for transmitting the driving force of the electric motor to the rotating member.
- the speed reduction mechanism is engaged with the drive gear fixed to the output shaft of the electric motor and the mounting member in a predetermined direction.
- the first gear shaft that is positioned and attached to the gear body, and is formed on the first gear shaft, has a larger number of teeth than the drive gear, meshes with the drive gear, and is connected to the rotating member.
- a first driven gear that decelerates the rotation of the electric motor and transmits it to the rotating member.
- the electric motor has a motor housing, and the fitting portion protrudes from one end surface of the motor housing in the rotation axis direction.
- the output shaft protrudes in the axial direction from the protruding end surface of the fitting portion, and the mounting member is disposed so as to face one end surface of the motor housing, and has a positioning hole.
- the elastic body holding portion protrudes from the other end surface of the motor housing, and the pressing member has a holding hole in the central portion by a rubber material. It is formed in the disk shape provided, and is arrange
- the speed reduction mechanism is provided on the first gear shaft, and the transmission gear rotates integrally with the first driven gear;
- a second gear shaft attached to the gear body, a second driven gear formed on the second gear shaft, having a larger number of teeth than the transmission gear and meshing with the transmission gear, and provided on the second gear shaft
- a sun gear that rotates integrally with the second driven gear, a plurality of planetary gears that mesh with the sun gear and revolve around the outer periphery of the sun gear by the rotation of the sun gear, and are arranged around the planetary gear and mesh with the planetary gear on the inner peripheral surface
- the ring gear which cannot be rotated by engaging with the gear body, and the plurality of planetary gears are connected to each other and coupled to the rotating member. Is rotated by the revolution is to have a carrier member that outputs the rotation member by decelerating the rotation of the sun gear, the.
- a brake housing attached to a vehicle body, a moving member attached to the brake housing so as to be axially movable and non-rotatable, and a disc rotating together with wheels.
- a brake pad interposed between the movable member and the movable member, a first piece and a second piece joined to each other, a gear body attached to the brake housing, an electric motor attached to the gear body, A reduction mechanism that is accommodated in the gear body and transmits the driving force of the electric motor, and is engaged with the moving member, and is moved by the electric motor via the reduction mechanism to move the moving member in the axial direction.
- a rotating member that urges the brake pad toward the disc via the electric parking brake device.
- the mounting member is fixed to the inner peripheral portion of the first piece, and the electric motor is engaged with or integrated with the mounting member, and is positioned in a predetermined direction in the gear body.
- a pressing member is interposed between the peripheral surface and the electric motor, and the pressing member biases the electric motor toward the mounting member.
- the mounting member fixed to the inner peripheral portion of the first piece, and the engaging member is engaged with or integrated with the first member, and is positioned in a predetermined direction in the gear body.
- An electric motor, and a pressing member that is interposed between the inner peripheral surface of the first piece and the electric motor and biases the electric motor toward the mounting member. Can be fixed without rattling.
- the urging force by the pressing member works between the inner peripheral surface of the first piece and the mounting member fixed to the first piece, a load that separates the first piece and the second piece does not occur, It is possible to prevent a decrease in the bonding force at both the joints.
- the speed reduction mechanism is positioned in a predetermined direction by engaging the drive gear fixed to the output shaft of the electric motor and the mounting member, and in the gear body.
- An attached first gear shaft, formed on the first gear shaft has a larger number of teeth than the drive gear, meshes with the drive gear, and is connected to a rotating member to reduce the rotation of the electric motor. Since the electric motor and the first gear shaft are both positioned on the mounting member by including the first driven gear transmitted to the rotating member, the output shaft of the electric motor and the first gear shaft are The dimensional variation between the two depends only on the manufacturing error of the mounting member.
- the mounting member is disposed so as to face the one end surface of the motor housing, and has the positioning hole, and the positioning hole is an output shaft of the electric motor.
- the electric motor is positioned in the radial direction with respect to the mounting member by being fitted to the outer peripheral surface of the fitting portion from which the protrusion protrudes, thereby further improving the positional accuracy of the output shaft relative to the first gear shaft on the mounting member. And dimensional variations between the two can be further reduced.
- the pressing member urges the other end surface of the motor housing toward the mounting member, and the one end surface of the motor housing is brought into contact with the mounting member, so that the electric motor is stable without rattling in the gear body. Can be attached.
- the elastic body holding portion protrudes from the other end surface of the motor housing, and the pressing member is formed in a disc shape having a holding hole in the center portion by a rubber material.
- the displacement of the pressing member in the gear body is eliminated by being arranged between the inner peripheral surface and the other end surface of the first piece so that the elastic body holding portion is fitted in the holding hole, and the electric motor Can be stably biased toward the mounting member.
- the speed reduction mechanism is provided on the first gear shaft, the transmission gear that rotates integrally with the first driven gear, and the second gear shaft attached to the gear body.
- a second driven gear that is formed on the second gear shaft and has a larger number of teeth than the transmission gear and meshes with the transmission gear, and is provided on the second gear shaft and is integrated with the second driven gear.
- An impossible ring gear and a plurality of planetary gears are connected to each other, coupled to a rotating member, rotated by the revolution of the planetary gear, Since the rotation of the electric motor is decelerated by the two-stage gear mechanism and the planetary gear mechanism by having the carrier member that decelerates the rotation of the motor and outputs it to the rotating member, the electric parking is small and has a large decelerating effect. It can be set as the drive device for brakes.
- the mounting member is fixed to the inner peripheral portion of the first piece, and the electric motor is engaged with or integrated with the mounting member, and the gear body has a predetermined direction.
- the pressing member is interposed between the inner peripheral surface of the first piece and the electric motor, and the pressing member urges the electric motor toward the mounting member, thereby causing the electric motor to move against the gear body.
- the urging force by the pressing member works between the inner peripheral surface of the first piece and the mounting member fixed to the first piece, a load that separates the first piece and the second piece does not occur, It is possible to prevent a decrease in the bonding force at both the joints.
- FIG. 1 is an external perspective view of an electric parking brake device attached to a wheel according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the electric parking brake drive device shown in FIG. 2 cut in the axial direction of the output shaft of the electric motor.
- An exploded perspective view of the bracket member, the electric motor and the rubber disc of the electric parking brake drive device as seen from the bracket member side 4 is an exploded perspective view when the configuration shown in FIG. 4 is viewed from the rubber disk side.
- FIG. 2 is a schematic cross-sectional view of the electric parking brake device P, and does not accurately represent an actual cross-sectional shape.
- a disc rotor 9 (corresponding to a disc) that is outside the configuration of the present invention is formed around a hat portion 91 that protrudes outward from the vehicle at the center of rotation thereof, and the first portion as will be described later.
- a plate portion 92 sandwiched between the brake pad 22a and the second brake pad 22b.
- a plurality of stud bolts 93 protrude from the end surface of the hat portion 91.
- the disc rotor 9 is attached to the disc wheel of the wheel W using these stud bolts 93, and can rotate integrally with the wheel W.
- the mounting 11 of the electric parking brake device P is attached and fixed to a knuckle arm N (corresponding to a vehicle body) of the vehicle.
- the mounting 11 holds a first brake pad 22a and a second brake pad 22b (only the second brake pad 22b is shown in FIG. 1).
- the first brake pad 22a is disposed between the disk rotor 9 and a piston 20 described later.
- a brake housing 13 is attached to the mounting 11 via a pair of slide pins 12 so as to be movable in the rotation axis ⁇ direction of the disk rotor 9 (hereinafter simply referred to as the rotation axis ⁇ direction).
- the brake housing 13 has a substantially U-shaped cross section so as to straddle the plate portion 92 of the disk rotor 9 (shown in FIGS.
- the brake housing 13 is formed with a pair of claw portions 13a for pressing the second brake pad 22b.
- an electric parking brake drive device 3 including an electric motor 34 and a speed reduction mechanism R is attached to the brake housing 13. The electric parking brake driving device 3 will be described later.
- a cylinder portion 13b is formed inside the brake housing 13, and a screw member 14 (corresponding to a rotating member) is provided so as to protrude into the cylinder portion 13b.
- the screw member 14 extending in the direction of the rotation axis ⁇ is rotatably attached to the bottom portion 13c of the cylinder portion 13b via a bearing 15, and a synthetic resin is provided between the outer peripheral surface 14a and the bottom portion 13c of the screw member 14.
- a seal member 16 formed of a material or a synthetic rubber material is interposed.
- a presser plate 17 is disposed on the bottom portion 13c of the cylinder portion 13b.
- a snap ring 18 for preventing the presser plate 17 from being detached is mounted on the inner peripheral surface of the cylinder portion 13b.
- a nut member 19 is provided in the cylinder portion 13b so as to be located outward of the screw member 14 in the radial direction.
- the nut member 19 has a substantially cylindrical shape, and a female screw portion 19b is formed at an axial end portion of the inner peripheral surface 19a.
- the female screw portion 19 b of the nut member 19 is screwed with a male screw portion 14 b formed on the outer peripheral surface 14 a of the screw member 14.
- a plurality of engaging portions 19d extend radially outward from the outer peripheral surface.
- the piston 20 is fitted to the cylinder portion 13b so as to be movable in the direction of the rotation axis ⁇ .
- a piston seal 21 is mounted on the cylinder portion 13b so as to engage with the outer peripheral surface 20a of the piston 20.
- the piston seal 21 liquid-tightly blocks the inside of the cylinder portion 13b from the outside together with the seal member 16 described above.
- the piston 20 is formed in a substantially cylindrical shape whose one end is closed by an end wall 20b, and can be brought into contact with the first brake pad 22a by the end wall 20b.
- the nut member 19 is engaged with the inner peripheral surface 20c of the piston 20 so as to be relatively movable in the direction of the rotation axis ⁇ .
- a protrusion 20d is formed on the outer peripheral surface 20a of the piston 20, and a slit 13d is formed in the cylinder portion 13b so as to extend in the direction of the rotation axis ⁇ .
- the projecting portion 20d of the piston 20 is engaged with the slit 13d, whereby the piston 20 is formed so as not to rotate with respect to the cylinder portion 13b.
- a plurality of sliding grooves 20e extending in the direction of the rotation axis ⁇ are formed on the inner peripheral surface 20c of the piston 20, and the engaging portions 19d of the nut member 19 described above are inserted therein. Therefore, since the nut member 19 cannot rotate with respect to the piston 20, the nut member 19 is formed non-rotatable with respect to the cylinder portion 13 b via the piston 20.
- a configuration including the piston 20 and the nut member 19 corresponds to the moving member.
- the screw member 14 is formed to be rotatable by the electric motor 34 through the speed reduction mechanism R described above.
- the screw member 14 When the screw member 14 is rotated when the vehicle is parked, the nut member 19 cannot rotate, so that the piston 20 moves toward the disk rotor 9 in the direction of the rotation axis ⁇ (leftward in FIG. 2).
- the end 19 c of the nut member 19 presses the piston 20 and biases the first brake pad 22 a toward the disc rotor 9 via the piston 20.
- the reaction force generated in the first brake pad 22a acts on the brake housing 13 via the piston 20, the nut member 19, the screw member 14 and the speed reduction mechanism R, and causes the brake housing 13 to move away from the piston 20 (FIG. 2). To the right).
- the brake housing 13 moves in the direction of the rotation axis ⁇ , and the claw portion 13 a biases the second brake pad 22 b toward the disc rotor 9. Therefore, the disc rotor 9 is pinched by the first brake pad 22a and the second brake pad 22b, and a braking force is applied to the wheel W.
- the brake fluid pressure discharged from the master cylinder (not shown) is transferred into the cylinder portion 13b via the brake pipe (not shown).
- the brake hydraulic pressure supplied into the cylinder portion 13b is pressed in the direction of the rotation axis ⁇ (to the left in FIG. 2) with the piston 20 disconnected from the nut member 19, and the first brake pad 22a is applied to the disc rotor 9.
- the parking brake actuator 1 is constituted by the mounting 11, the slide pin 12, the brake housing 13, the first brake pad 22a, the second brake pad 22b, the screw member 14, the nut member 19 and the piston 20 described above.
- the electric parking brake drive device 3 (hereinafter referred to as the drive device 3) for driving the parking brake actuator 1 will be described in detail with reference to FIGS.
- the upper side in FIG. 3 is the upper side of the driving device 3 and the lower side in FIG.
- the drive device 3 is formed by a gear body 31, an electric motor 34, a bracket member 35, a rubber disk 36, a screw 37 and a speed reduction mechanism R.
- the gear body 31 of the driving device 3 includes a lower body 32 (corresponding to the first piece) and an upper body 33 (corresponding to the second piece), which are integrally formed of a synthetic resin material. It is formed by joining to each other.
- the gear body 31 is fixed to the brake housing 13 described above.
- An outer peripheral edge of the lower body 32 extends in the direction of the rotational axis ⁇ of the electric motor 34 (the vertical direction in FIG. 3 and the same direction as the rotational axis ⁇ of the disk rotor 9, but hereinafter simply referred to as the rotational axis ⁇ direction).
- the surrounding wall 32a is formed over the entire circumference.
- an opposing portion 33a having a substantially L-shaped cross section is formed on the entire circumference.
- the outer peripheral edges are first opposed to each other so that the surrounding wall 32a and the facing portion 33a are brought into contact with each other to perform positioning.
- an adhesive is filled in an application space (indicated by F in FIG. 3) surrounded by the surrounding wall 32a and the facing portion 33a.
- the outer peripheral edges of the lower body 32 and the upper body 33 are joined to each other by solidifying the adhesive.
- the lower body 32 and the upper body 33 are joined in a liquid-tight manner so as to prevent entry of water or the like from the outside.
- the motor housing 34a of the electric motor 34 has a substantially cylindrical shape. From the upper end surface 34a1 (corresponding to one end surface), the shaft protrusion 34a2 (corresponding to the fitting portion). ) Protrudes upward.
- the shaft protrusion 34a2 is formed in a columnar shape at the center of the upper end surface 34a1, and an output shaft 34b (corresponding to an output shaft) protrudes from the protrusion end surface 34a3.
- a pair of motor slits 34a4 are formed on the upper end surface 34a1 of the motor housing 34a so as to face each other on the circumference so as to cut out the peripheral edge.
- a pair of engaging pieces 34a5 extend vertically from the upper end surface 34a1 (shown in FIG. 4).
- a disk holder 34a7 (corresponding to an elastic body holding portion) protrudes downward from a lower end surface 34a6 (corresponding to the other end surface) of the motor housing 34a (shown in FIG. 5).
- the disc holder 34a7 protrudes in a cylindrical shape at the center of the lower end surface 34a6.
- the bracket member 35 (corresponding to the mounting member) is formed in a substantially flat plate shape with a synthetic resin material. At the center of the lower end surface 35a of the bracket member 35, a concave portion 35b having a perfectly circular inner peripheral surface 35b1 is formed (shown in FIG. 5). A perfect support hole 35 c (corresponding to a positioning hole) is formed above the recess 35 b, and the support hole 35 c is open to the upper end surface 35 d of the bracket member 35. The inner diameter of the support hole 35c is set to a size that can be fitted to the shaft protrusion 34a2 of the electric motor 34 described above.
- a pair of engaging protrusions 35f protrude downward from the ceiling surface 35e of the recess 35b. Furthermore, a pair of insertion grooves 35g penetrate upward from the ceiling surface 35e (shown in FIG. 5).
- a plurality of mounting surfaces 35h that are one step lower than the upper end surface 35d are formed around the upper end surface 35d.
- Three screw holes 35j penetrating to the lower end surface 35a are formed in the mounting surface 35h.
- a pin holding hole 35k passes through the mounting surface 35h (shown in FIGS. 4 and 5).
- the rubber disk 36 (corresponding to a pressing member) is integrally formed of a synthetic rubber material such as butyl rubber, acrylic rubber, or EPDM, and has an elastic force.
- the rubber disk 36 is formed in a substantially disk shape by having a perfectly circular motor engagement hole 36a (corresponding to a holding hole) penetrating in the thickness direction at the center thereof.
- the inner diameter of the motor engagement hole 36a is set to a size that can be fitted to the disk holder 34a7 of the electric motor 34 described above.
- the motor engagement hole 36 a does not necessarily have to penetrate the rubber disk 36, and may be formed in a bag shape on the rubber disk 36.
- a plurality of contact portions 36c are formed on the lower surface 36b of the rubber disk 36 so as to be arranged at intervals on the circumference.
- the contact portion 36c is formed to stabilize the pressing force characteristic that the rubber disk 36 applies to the electric motor 34, and protrudes one step downward from the lower surface 36b (shown in FIG. 5).
- the bracket member 35 is fixed on the lower body 32 with its lower end surface 35a abutting against an inner peripheral surface 32b (corresponding to the inner peripheral portion) of the lower body 32.
- the bracket member 35 is fixed to the lower body 32 by screwing screws 37 (only one shown in FIG. 3) inserted through the respective screw holes 35 j into the lower body 32.
- the electric motor 34 is accommodated in a motor storage portion 32 c formed in a shape deeply dug in the lower body 32, and the upper end surface 34 a 1 of the electric motor 34 is disposed so as to face the bracket member 35.
- the electric motor 34 is positioned in the radial direction (the horizontal direction in FIG. 3 and corresponding to a predetermined direction) in the gear body 31 by fitting the shaft protrusion 34a2 into the support hole 35c. Is done.
- the motor slit 34a4 of the motor housing 34a is engaged with the engagement protrusions 35f of the bracket member 35, and the engagement pieces 34a5 of the motor housing 34a are engaged with the insertion grooves 35g of the bracket member 35.
- a slight gap is formed between the outer peripheral surface of the motor housing 34a and the inner peripheral surface 35b1 of the bracket member 35 (shown in FIG. 3).
- the above-described rubber disk 36 is interposed between the lower end surface 34a6 of the motor housing 34a and the bottom surface 32d of the motor storage portion 32c.
- the rubber disk 36 is sandwiched between the disk holder 34a7 and the lower body 32 when the disk holder 34a7 of the motor housing 34a is fitted into the motor engagement hole 36a, and is positioned in the radial direction (shown in FIG. 3).
- the rubber disc 36 has a contact portion 36c compressed in the thickness direction by the electric motor 34 and the lower body 32 to generate a biasing force, the lower end surface 34a6 of the electric motor 34 faces the bracket member 35. It is pressing in the direction of the rotation axis ⁇ (upward in FIG. 3).
- the electric motor 34 is attached to the gear body 31 with the upper end surface 34a1 of the motor housing 34a being in contact with the ceiling surface 35e of the bracket member 35. A gap is formed between them (shown in FIG. 3).
- a power connector 32 e for connecting an external connector is formed at the end of the lower body 32.
- a power supply line (not shown) connected from the power connector portion 32e to the electric motor 34 is inserted.
- the speed reduction mechanism R is housed in the gear body 31, and reduces the driving force of the electric motor 34 and transmits it to the screw member 14.
- a pinion gear 38 (corresponding to a drive gear) having inclined teeth 38a on its outer peripheral surface is fixed to the output shaft 34b of the electric motor 34 by press fitting or the like.
- a pivot pin 39 (corresponding to the first gear shaft) is fixed to the pin holding hole 35k of the bracket member 35 described above by press-fitting or insert molding.
- the lower end portion of the pivot pin 39 is fitted in the pin fixing hole 32 f of the lower body 32, and the upper end portion is fitted in the pin holding hole 33 b of the upper body 33. Both ends of the pivot pin 39 may be press-fitted or insert-molded with respect to the lower body 32 and the upper body 33.
- a gear member 41 is rotatably attached to the pivot pin 39 via a pair of bushes 40a and 40b. Above the gear member 41, a first flange portion 41a protruding in the radial direction is formed.
- a first wheel gear 42 (corresponding to a first driven gear) is fixed to the first flange 41a by insert molding. As will be described later, the first wheel gear 42 is connected to the screw member 14 via a plurality of members.
- the first wheel gear 42 is a helical gear formed of a synthetic resin material, and inclined teeth 42a are provided on the outer peripheral surface. The first wheel gear 42 meshes with the inclined teeth 38a of the pinion gear 38 described above.
- the first wheel gear 42 has a larger diameter than the pinion gear 38, and the number of teeth of the inclined teeth 42 a of the first wheel gear 42 is larger than the number of teeth of the inclined teeth 38 a of the pinion gear 38.
- a gear part 41b (corresponding to a transmission gear) is integrally formed on the outer peripheral surface.
- the gear portion 41 b is formed by inclined teeth similarly to the pinion gear 38 and rotates integrally with the first wheel gear 42.
- An upper bearing member 43 a is attached to the upper surface 33 c of the upper body 33.
- a bearing fixing surface 32j extends in the horizontal direction in FIG. 3 from the outer peripheral wall 32g of the lower body 32 and the motor wall portion 32h.
- the bearing fixing surface 32j extends toward the rotation center of the gear shaft 44 described later, and partitions the planetary gear 46 and the second wheel gear 45 from each other.
- the outer surface of the bearing fixing surface 32j is formed into a perfect circle, and a support hole 32k passes through the center of the bearing fixing surface 32j, and a boss portion 32m extending in the vertical direction is provided.
- a lower bearing member 43b is attached to the boss portion 32m.
- Each of the upper bearing member 43a and the lower bearing member 43b is formed of a metal material, and is fixed to the upper body 33 or the lower body 32 by insert molding or induction heating welding.
- a gear shaft 44 (corresponding to the second gear shaft) made of a metal material is rotatably supported by the lower bearing member 43b. Above the gear shaft 44, a second flange 44a protruding in the radial direction is formed.
- a second wheel gear 45 (corresponding to a second driven gear) is fixed to the second flange portion 44a by insert molding.
- the gear shaft 44 is rotatably supported by the upper bearing member 43a via the second wheel gear 45 (shown in FIG. 3).
- the second wheel gear 45 is a helical gear formed of a synthetic resin material in the same manner as the first wheel gear 42, and inclined teeth 45a are provided on the outer peripheral surface.
- the second wheel gear 45 meshes with the gear portion 41b of the gear member 41 described above.
- the second wheel gear 45 is formed to have a larger diameter than the gear portion 41b, and the number of teeth of the inclined teeth 45a of the second wheel gear 45 is larger than the number of teeth of the gear portion 41b.
- a sun gear portion 44 b (corresponding to a sun gear) is integrally formed at the lower end of the gear shaft 44.
- the sun gear portion 44 b rotates integrally with the second wheel gear 45.
- a plurality of planetary gears 46 that mesh with the sun gear portion 44b are disposed around the sun gear portion 44b.
- four planetary gears 46 are provided (only two are shown in FIG. 3), but the present invention is not limited to this.
- Each planetary gear 46 is formed of a metal material, and revolves around the outer periphery of the sun gear portion 44b by the rotation of the sun gear portion 44b.
- a ring gear 47 made of a synthetic resin material is disposed around the planetary gear 46.
- An annular ring gear 47 meshes with each of the planetary gears 46 on the inner peripheral surface and engages with the lower body 32 so as not to rotate.
- the above-mentioned planetary gear 46 is engaged with a carrier member 48 so as to connect the plurality of planetary gears 46 to each other.
- the carrier member 48 is formed of a synthetic resin material, and an output member 49 is connected to the lower end portion thereof.
- the output member 49 is formed of a metal material and is connected to the screw member 14 described above. Accordingly, the carrier member 48 is connected to the screw member 14 via the output member 49.
- the above-described sun gear portion 44b, planetary gear 46, ring gear 47 and carrier member 48 form a planetary gear mechanism YG.
- the carrier member 48 is rotated by the revolution of the planetary gear 46, and can reduce the rotation of the sun gear portion 44 b and output it to the screw member 14.
- the driving force of the electric motor 34 is first decelerated (first-stage deceleration) by the meshing of the pinion gear 38 and the first wheel gear 42. Thereafter, the gear portion 41b and the second wheel gear 45 are engaged to reduce the speed (second speed reduction). Further, after being decelerated by the planetary gear mechanism YG (deceleration at the third stage), it is transmitted to the screw member 14.
- a rubber disc 36 is provided between the bottom surface 32d and the electric motor 34 and biases the electric motor 34 toward the bracket member 35 in the direction of the rotation axis ⁇ . It can be fixed without rattling. Further, since the urging force by the rubber disk 36 works between the bottom surface 32d of the lower body 32 and the bracket member 35 fixed to the lower body 32, a load for separating the lower body 32 and the upper body 33 is not generated, and both are joined. It is possible to prevent a decrease in bonding force at the portion.
- the bracket member 35 is formed separately from the electric motor 34 and a general-purpose electric motor having no mounting portion on the outer periphery can be used, the low-cost driving device 3 can be obtained.
- the electric motor 34 receives a pressing force from the rubber disk 36, the rubber disk 36 absorbs vibrations when the vehicle travels, and damage to the electric motor 34 can be reduced.
- the speed reduction mechanism R is engaged with the pinion gear 38 fixed to the output shaft 34 b of the electric motor 34 and the bracket member 35 to be positioned in the radial direction of the electric motor 34, and is pivotally attached to the gear body 31.
- the pin 39 is formed on the pivot pin 39, has a larger number of teeth than the pinion gear 38, meshes with the pinion gear 38, is connected to the screw member 14, and reduces the rotation of the electric motor 34 to reduce the screw member. 14, since the electric motor 34 and the pivot pin 39 are both positioned on the bracket member 35, the output shaft 34 b and the pivot pin 39 of the electric motor 34 are The dimensional variation between them depends only on the manufacturing error of the bracket member 35.
- the dimensional variation between the two can be reduced, and abnormal noise during transmission of the speed reduction mechanism R and reduction in transmission efficiency can be prevented. Further, since the dimensional accuracy between the output shaft 34b of the electric motor 34 and the pivot pin 39 can be improved, it is unnecessary to adjust the backlash between the pinion gear 38 and the first wheel gear 42 when the speed reduction mechanism R is manufactured. can do.
- the bracket member 35 is disposed so as to face the upper end surface 34a1 of the motor housing 34a, and has a support hole 35c.
- the electric motor 34 is fitted to the outer peripheral surface of 34 a 2 and positioned in the radial direction with respect to the bracket member 35, thereby further improving the positional accuracy of the output shaft 34 b with respect to the pivot pin 39 on the bracket member 35. It is possible to reduce the dimensional variation between the two.
- the rubber disk 36 urges the lower end surface 34a6 of the motor housing 34a toward the bracket member 35 so that the upper end surface 34a1 of the motor housing 34a is in contact with the bracket member 35. It can be mounted more stably in the gear body 31.
- a disk holder 34a7 protrudes from the lower end surface 34a6 of the motor housing 34a, and the rubber disk 36 is formed in a disk shape having a motor engagement hole 36a at the center by a rubber material, and is formed in the motor engagement hole 36a. Since the disc holder 34a7 is disposed between the bottom surface 32d and the lower end surface 34a6 of the lower body 32 so that the disc holder 34a7 is fitted, the position of the rubber disc 36 in the gear body 31 is eliminated, and the electric motor 34 is attached to the bracket member 35. It can be urged stably toward
- the speed reduction mechanism R is provided on the pivot pin 39, is formed on the gear shaft 44, the gear portion 41b that rotates integrally with the first wheel gear 42, the gear body 31, and the gear shaft 44.
- the second wheel gear 45 having a larger number of teeth than the portion 41b and meshing with the gear portion 41b, a sun gear portion 44b provided on the gear shaft 44 and rotating integrally with the second wheel gear 45, and a sun gear portion 44b
- a plurality of planetary gears 46 that mesh with each other and revolve around the outer periphery of the sun gear portion 44b by rotation of the sun gear portion 44b, and are arranged around the planetary gear 46, mesh with the planetary gear 46 on the inner peripheral surface, and engage with the gear body 31.
- the electric motor 34 While connecting the non-rotatable ring gear 47 and a plurality of planetary gears 46
- the electric motor 34 is coupled to the clewing member 14, rotated by the revolution of the planetary gear 46, decelerated the rotation of the sun gear portion 44 b, and output to the screw member 14, so that the rotation of the electric motor 34 is a two-stage gear mechanism.
- the planetary gear mechanism YG, the electric parking brake drive device 3 can be made small and has a large deceleration effect.
- the present invention is not limited to the above-described embodiments, and can be modified or expanded as follows.
- the bracket member 35 may be fixed in advance to the motor housing 34a before being attached to the lower body 32, or may be integrated into the motor housing 34a. Further, the bracket member 35 may be attached to the lower body 32 while fitting the pin holding hole 35k of the bracket member 35 to the pivot pin 39 fixed to the lower body 32 or the upper body 33. Further, instead of the pivot pin 39, a shaft shaft may be rotatably attached to the gear body 31 via a bearing, and the first wheel gear 42 and the gear portion 41b may be formed on the shaft shaft.
- a plate spring formed of a metal material or a coil spring formed of a metal wire may be used instead of the rubber disk 36.
- the present invention is not limited to the floating type disc brake that clamps the disc rotor 9 between the claw portion 13a of the brake housing 13 and the piston 20 via the brake pads 22a and 22b, but also the side surfaces of the disc rotor 9.
- the present invention can also be applied to an opposed type disc brake that is pressed by an individual piston.
- the electric motor 34 any motor such as a synchronous machine, an induction machine, and a DC machine can be used.
- 1 is a parking brake actuator
- 3 is a drive device for an electric parking brake
- 9 is a disk rotor (disk)
- 13 is a brake housing
- 14 is a screw member (rotating member)
- 19 is a nut member (moving member)
- 20 is a piston (moving member)
- 22a is a first brake pad (brake pad)
- 22b is a second brake pad (brake pad)
- 31 is a gear body
- 32 is a lower body (first piece)
- 32b is an inner peripheral surface (inner (Circumferential portion)
- 32d is a bottom surface (inner peripheral surface)
- 33 is an upper body (second piece)
- 34 is an electric motor
- 34a is a motor housing
- 34a1 is an upper end surface (one end surface)
- 34a2 is a shaft protrusion (fitting portion)
- 34a3 is a protruding end surface
- 34a6 is a lower end surface (the other
- (Sun gear), 45 is a second wheel gear (second driven gear), 46 is a planetary gear, 47 is a ring gear, 48 is a carrier member, N is a knuckle arm (vehicle body), P is an electric parking brake device, R is a reduction mechanism, W Indicates a wheel.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Power Engineering (AREA)
- Braking Arrangements (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Braking Systems And Boosters (AREA)
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- Retarders (AREA)
Abstract
Description
これによって、電動モータの駆動力は、ベルトを含んだ伝達機構と複数段の遊星歯車にて減速され、直線方向の押圧力に変換された後、車輪ブレーキに伝達されて車輪に制動力を付与している。
これによって、特許文献1に開示された電動ブレーキ装置においては、ハウジングとその中に収容される部材寸法のバラツキを吸収できるとともに、車輪振動に起因して駆動装置に発生する衝撃を低減することができる。
しかしながら、上述した従来技術による電動ブレーキ装置において、溶着によって接合されたハウジングを使用した場合、2つのボデーにより電動モータを挟み込む構造であるため、電動モータの両端部に介装された弾性体の付勢力によって、双方のボデーが互いに分離する方向に荷重を受ける。各々のボデーに加えられた荷重は、ハウジングの溶着部に働いて、その接合力を低下させる虞がある。溶着部の接合力の低下は、ハウジング内の各部材のがたつき、それに起因するギヤ同士の噛み合い不良等を招き、電動ブレーキ装置の信頼性を低下させることになる。
本発明は上記事情に鑑みてなされたものであり、その目的は、小型で信頼性の高い電動パーキングブレーキ用駆動装置および電動パーキングブレーキ装置を提供することにある。
また、押圧部材による付勢力が、第1ピースの内周面と第1ピースに固定された取付部材との間において働くため、第1ピースと第2ピースとを分離させる荷重が発生せず、双方の接合部における接合力の低下を防ぐことができる。
また、電動モータの出力軸と第1ギヤ軸との間の寸法精度を向上できるため、減速機構の製造時における、駆動ギヤと第1従動ギヤとの間のバックラッシュ調整を不要にすることができる。
また、押圧部材は、モータハウジングの他端面を取付部材に向けて付勢して、モータハウジングの一端面を取付部材に当接させていることにより、電動モータをギヤボデー内にがたつきなく安定して取り付けることができる。
また、押圧部材による付勢力が、第1ピースの内周面と第1ピースに固定された取付部材との間において働くため、第1ピースと第2ピースとを分離させる荷重が発生せず、双方の接合部における接合力の低下を防ぐことができる。
図1に示すように、ハット部91の端面からは、複数のスタッドボルト93が突出している。ディスクロータ9は、これらのスタッドボルト93を用いて、車輪Wのディスクホイールに取り付けられており、これにより車輪Wと一体回転可能とされている。
マウンティング11には、一対のスライドピン12を介して、ブレーキハウジング13がディスクロータ9の回転軸φ方向(以下、単に回転軸φ方向という)に移動可能に取り付けられている。ブレーキハウジング13は、ディスクロータ9のプレート部92を跨ぐように、その断面形状が略コの字状に形成されている(図1および図2示)。また、ブレーキハウジング13には、第2ブレーキパッド22bを押圧するための一対の爪部13aが形成されている。
図2に示すように、ブレーキハウジング13には、電動モータ34および減速機構Rを含んだ電動パーキングブレーキ用駆動装置3が取り付けられている。電動パーキングブレーキ用駆動装置3については後述する。
シール部材16が回転軸φ方向に移動することを防止するために、シリンダ部13bの底部13cには、押えプレート17が配置されている。さらに、シリンダ部13bの内周面には、押えプレート17の抜け止めを行うスナップリング18が装着されている。
ピストン20は一端が端部壁20bにより閉じられた略円筒状に形成され、端部壁20bによって第1ブレーキパッド22aと当接可能になっている。ピストン20の内周面20cには、前述したナット部材19が回転軸φ方向に相対移動可能に係合している。また、ピストン20の外周面20aには突部20dが形成され、シリンダ部13bには、スリット13dが回転軸φ方向に延びるように形成されている。ピストン20の突部20dはスリット13dと係合しており、これによって、ピストン20はシリンダ部13bに対して回転不能に形成されている。
上述したマウンティング11、スライドピン12、ブレーキハウジング13、第1ブレーキパッド22a、第2ブレーキパッド22b、スクリュー部材14、ナット部材19およびピストン20により、パーキングブレーキアクチュエータ1を構成している。
駆動装置3は、ギヤボデー31、電動モータ34、ブラケットメンバ35、ゴムディスク36、スクリュー37および減速機構Rにより形成されている。駆動装置3のギヤボデー31は、それぞれ合成樹脂材料にて一体的に形成されたロアボデー32(第1ピースに該当する)およびアッパボデー33(第2ピースに該当する)が、内部に所定容量の空間を有するように互いに接合することにより形成されている。ギヤボデー31は、前述したブレーキハウジング13に固定されている。
ロアボデー32の外周縁には、電動モータ34の回転軸ψ方向(図3の上下方向であってディスクロータ9の回転軸φと同方向であるが、以下、単に回転軸ψ方向という)に延びる囲繞壁32aが全周に渡って形成されている。一方、アッパボデー33の外周縁には、断面形状が略L字状の対向部33aが全周に形成されている。
また、モータハウジング34aの上端面34a1上には、周縁部を切欠くように一対のモータスリット34a4が、円周上において互いに対向するように形成されている。さらに、上端面34a1からは、一対の係合片34a5が垂直に延びている(図4示)。
一方、モータハウジング34aの下端面34a6(他端面に該当する)からは、ディスクホルダ34a7(弾性体保持部に該当する)が下方に突出している(図5示)。ディスクホルダ34a7は、下端面34a6の中央部において円柱状に突出している。
また、凹部35bの天井面35eからは、一対の係合突部35fが下方に突出している。さらに、天井面35eからは、一対の挿入溝35gが上方に向けて貫通している(図5示)。
また、上端面35dの周囲には、上端面35dよりも一段低い複数の取付面35hが形成されている。取付面35hには、下端面35aまで貫通した3個のネジ孔35jが形成されている。さらに、取付面35hには、ピン保持穴35kが貫通している(図4および図5示)。
ゴムディスク36の下面36bには、複数の当接部36cが円周上に互いに間隔を有して並ぶように形成されている。当接部36cは、ゴムディスク36が電動モータ34に付与する押圧力特性を安定させるために形成されており、下面36bから下方に向けて一段突出している(図5示)。
また、ゴムディスク36は、電動モータ34とロアボデー32とによって当接部36cが厚み方向に圧縮されて付勢力を発生しているため、電動モータ34の下端面34a6を、ブラケットメンバ35に向けて回転軸ψ方向(図3における上方)に押圧している。したがって、電動モータ34は、モータハウジング34aの上端面34a1が、ブラケットメンバ35の天井面35eに当接した状態でギヤボデー31に取り付けられ、モータハウジング34aのディスクホルダ34a7とロアボデー32の底面32dとの間には隙間が形成されている(図3示)。
図3に示したように、ロアボデー32の端部には、外部コネクタ(図示せず)を接続するための電源コネクタ部32eが形成されている。ロアボデー32内には、電源コネクタ部32eから電動モータ34へとつながる電力供給線(図示せず)がインサートされている。
上述したブラケットメンバ35のピン保持穴35kには、枢支ピン39(第1ギヤ軸に該当する)が、圧入またはインサート成形により固定されている。枢支ピン39の下端部はロアボデー32のピン固定孔32fと嵌合し、上端部はアッパボデー33のピン保持穴33bに嵌合している。枢支ピン39の両端部は、ロアボデー32およびアッパボデー33に対して圧入またはインサート成形されていてもよい。
第1ホイルギヤ42は合成樹脂材料にて形成されたヘリカルギヤで、外周面には斜歯42aが設けられている。第1ホイルギヤ42は、前述したピニオンギヤ38の斜歯38aと噛合している。第1ホイルギヤ42はピニオンギヤ38よりも大径に形成され、第1ホイルギヤ42の斜歯42aの歯数は、ピニオンギヤ38の斜歯38aの歯数よりも多く形成されている。
ギヤメンバ41の下方には、外周面上にギヤ部41b(伝達ギヤに該当する)が一体に形成されている。ギヤ部41bは、ピニオンギヤ38と同様に斜歯によって形成されており、第1ホイルギヤ42と一体に回転する。
また、ロアボデー32の外周壁32gおよびモータ壁部32hからは、軸受固定面32jが図3における水平方向に延在している。軸受固定面32jは、後述するギヤシャフト44の回転中心に向けて延び、プラネタリギヤ46と第2ホイルギヤ45との間を仕切っている。
軸受固定面32jは外形が真円状に形成され、その中心には支持孔32kが貫通するとともに、上下方向に延びたボス部32mが設けられている。ボス部32mには、ロア軸受部材43bが取り付けられている。アッパ軸受部材43aおよびロア軸受部材43bは、いずれも金属材料にて形成され、インサート成形または誘導加熱溶着等によりアッパボデー33あるいはロアボデー32に固定されている。
第2ホイルギヤ45は、第1ホイルギヤ42と同様に合成樹脂材料にて形成されたヘリカルギヤで、外周面には斜歯45aが設けられている。第2ホイルギヤ45は、前述したギヤメンバ41のギヤ部41bと噛合している。第2ホイルギヤ45はギヤ部41bよりも大径に形成され、第2ホイルギヤ45の斜歯45aの歯数は、ギヤ部41bの歯数よりも多く形成されている。
サンギヤ部44bの周囲には、サンギヤ部44bと噛合する複数のプラネタリギヤ46が配置されている。本実施形態においては、4個のプラネタリギヤ46が設けられている(図3において2個のみ示す)が、これに限られるものではない。各々のプラネタリギヤ46は金属材料により形成され、サンギヤ部44bの回転によってサンギヤ部44bの外周を公転する。
また、プラネタリギヤ46の周囲には、合成樹脂材料にて形成されたリングギヤ47が配置されている。円環状をしたリングギヤ47は、内周面においてプラネタリギヤ46のそれぞれと噛合するとともに、ロアボデー32と係合し回転不能に形成されている。
電動モータ34の駆動力は、最初に、ピニオンギヤ38と第1ホイルギヤ42との噛み合いによって減速(1段目の減速)される。その後、ギヤ部41bと第2ホイルギヤ45との噛み合いによって減速(2段目の減速)される。さらに遊星歯車機構YGによって減速(3段目の減速)された後、スクリュー部材14へと伝達される。
また、ゴムディスク36による付勢力が、ロアボデー32の底面32dとロアボデー32に固定されたブラケットメンバ35との間において働くため、ロアボデー32とアッパボデー33とを分離させる荷重が発生せず、双方の接合部における接合力の低下を防ぐことができる。
また、ブラケットメンバ35は、電動モータ34とは別体に形成されており、外周に取付部を有しない汎用の電動モータを使用可能であるため、低コストの駆動装置3にすることができる。
また、電動モータ34はゴムディスク36から押圧力を受けているため、ゴムディスク36によって車両走行時の振動が吸収され、電動モータ34へのダメージを低減することができる。
また、電動モータ34の出力シャフト34bと枢支ピン39との間の寸法精度を向上できるため、減速機構Rの製造時における、ピニオンギヤ38と第1ホイルギヤ42との間のバックラッシュ調整を不要にすることができる。
また、ゴムディスク36は、モータハウジング34aの下端面34a6をブラケットメンバ35に向けて付勢して、モータハウジング34aの上端面34a1をブラケットメンバ35に当接させていることにより、電動モータ34をギヤボデー31内にいっそう安定して取り付けることができる。
本発明は、上述した実施形態に限定されるものではなく、次のように変形または拡張することができる。
ブラケットメンバ35は、ロアボデー32に取り付ける以前に、モータハウジング34aに予め固定されていてもよいし、あるいはモータハウジング34aに一体化されていてもよい。
また、ロアボデー32またはアッパボデー33に固定された枢支ピン39に対し、ブラケットメンバ35のピン保持穴35kを嵌合させながら、ブラケットメンバ35をロアボデー32に取り付けてもよい。
また、枢支ピン39の代わりに、ギヤボデー31に対し軸受を介してシャフト軸を回転可能に取り付け、第1ホイルギヤ42およびギヤ部41bを当該シャフト軸に形成してもよい。
また、ゴムディスク36に代えて、金属材料にて形成された板バネまたは金属製の線材により形成されたコイルスプリングを使用してもよい。
また、本発明は、ディスクロータ9を、ブレーキパッド22a、22bを介してブレーキハウジング13の爪部13aとピストン20とで挟圧する浮動型のディスクブレーキのみではなく、ディスクロータ9の双方の側面を個別のピストンにて押圧する対向型のディスクブレーキにも適用可能である。
また、電動モータ34には、同期機、誘導機、直流機等のあらゆるモータが使用可能である。
Claims (6)
- 回動部材の回転運動を直進運動に変換して移動部材に伝達し、前記移動部材によって付勢されたブレーキパッドが、車輪とともに回転するディスクを押圧することにより前記車輪に制動力を発生させるパーキングブレーキアクチュエータを駆動するための電動パーキングブレーキ用駆動装置であって、
第1ピースと第2ピースとが互いに接合して形成されたギヤボデーと、
前記第1ピースの内周部に固定される取付部材と、
該取付部材と係合または一体化されて、前記ギヤボデー内において所定の方向に位置決めされる電動モータと、
前記第1ピースの内周面と前記電動モータとの間に介装され、前記電動モータを前記取付部材に向けて付勢する押圧部材と、
前記ギヤボデー内に収容され、前記電動モータの駆動力を前記回動部材に伝達する減速機構と、
を備えた電動パーキングブレーキ用駆動装置。 - 前記減速機構は、
前記電動モータの出力軸に固着された駆動ギヤと、
前記取付部材と係合して前記所定の方向に位置決めされるとともに、前記ギヤボデーに取り付けられた第1ギヤ軸と、
該第1ギヤ軸上に形成され、前記駆動ギヤよりも多数の歯数を有し、前記駆動ギヤと噛合するとともに、前記回動部材に連結されることにより、前記電動モータの回転を減速して前記回動部材に伝達する第1従動ギヤと、
を含む請求項1記載の電動パーキングブレーキ用駆動装置。 - 前記電動モータはモータハウジングを有し、該モータハウジングの回転軸方向の一端面からは、嵌合部が突出するとともに、該嵌合部の突端面からは前記出力軸が軸方向に突出しており、
前記取付部材は、前記モータハウジングの前記一端面と対向するように配置されるとともに、位置決め孔を有しており、該位置決め孔が前記嵌合部の外周面と嵌合することにより、前記電動モータは前記取付部材に対し半径方向に位置決めされ、
前記押圧部材は、前記モータハウジングの他端面を、前記取付部材に向けて付勢することにより、前記一端面を前記取付部材に当接させている請求項2記載の電動パーキングブレーキ用駆動装置。 - 前記モータハウジングの前記他端面からは、弾性体保持部が突出し、
前記押圧部材は、
ゴム材料により中央部に保持孔を備えた円板状に形成され、前記保持孔に前記弾性体保持部が嵌合するように、前記第1ピースの内周面と前記他端面との間に配置されている請求項3記載の電動パーキングブレーキ用駆動装置。 - 前記減速機構は、
前記第1ギヤ軸上に設けられ、前記第1従動ギヤと一体に回転する伝達ギヤと、
前記ギヤボデーに取り付けられた第2ギヤ軸と、
該第2ギヤ軸上に形成され、前記伝達ギヤよりも多数の歯数を有するとともに、前記伝達ギヤと噛合する第2従動ギヤと、
前記第2ギヤ軸上に設けられ、前記第2従動ギヤと一体に回転するサンギヤと、
前記サンギヤと噛合し、前記サンギヤの回転によって前記サンギヤの外周を公転する複数のプラネタリギヤと、
前記プラネタリギヤの周囲に配置され、内周面において前記プラネタリギヤと噛合するとともに、前記ギヤボデーと係合することによって回転不能なリングギヤと、
複数の前記プラネタリギヤ同士を接続するとともに前記回動部材に連結され、前記プラネタリギヤの公転によって回転され、前記サンギヤの回転を減速して前記回動部材に出力するキャリヤ部材と、
を有する請求項2乃至4のうちのいずれか一項に記載の電動パーキングブレーキ用駆動装置。 - 車体に取り付けられたブレーキハウジングと、
前記ブレーキハウジングに対し、軸方向に移動可能かつ回転不能に取り付けられた移動部材と、
車輪とともに回転するディスクと前記移動部材との間に介装されたブレーキパッドと、
第1ピースと第2ピースとが互いに接合して形成され、前記ブレーキハウジングに取り付けられたギヤボデーと、
前記ギヤボデー内に取り付けられた電動モータと、
前記ギヤボデー内に収容され、前記電動モータの駆動力を伝達する減速機構と、
前記移動部材と噛合しており、前記減速機構を介して前記電動モータによって駆動されることにより前記移動部材を軸方向に移動させ、前記移動部材を介して前記ブレーキパッドを前記ディスクに向けて付勢する回動部材と、
を備えた電動パーキングブレーキ装置であって、
前記第1ピースの内周部には、取付部材が固定され、
前記電動モータは、前記取付部材と係合または一体化されて、前記ギヤボデー内において所定の方向に位置決めされ、
前記第1ピースの内周面と前記電動モータとの間には押圧部材が介装され、該押圧部材は、前記電動モータを前記取付部材に向けて付勢する電動パーキングブレーキ装置。
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