WO2011013744A1 - Actionneur électrique - Google Patents

Actionneur électrique Download PDF

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Publication number
WO2011013744A1
WO2011013744A1 PCT/JP2010/062781 JP2010062781W WO2011013744A1 WO 2011013744 A1 WO2011013744 A1 WO 2011013744A1 JP 2010062781 W JP2010062781 W JP 2010062781W WO 2011013744 A1 WO2011013744 A1 WO 2011013744A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball screw
shaft
electric actuator
ball
motor
Prior art date
Application number
PCT/JP2010/062781
Other languages
English (en)
Japanese (ja)
Inventor
池田良則
佐藤光司
立石康司
齋藤隆英
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2011013744A1 publication Critical patent/WO2011013744A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • 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
    • 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
    • F16D2125/20—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
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/06—Locking mechanisms, e.g. acting on actuators, on release mechanisms or on force transmission mechanisms
    • 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
    • F16D2129/00—Type of operation source for auxiliary mechanisms
    • F16D2129/06—Electric or magnetic
    • F16D2129/08—Electromagnets
    • 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
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2087—Arrangements for driving the actuator using planetary gears

Definitions

  • the present invention relates to an electric actuator having a ball screw mechanism used in a pulley drive unit of a continuously variable transmission (CVT) of an automobile and a drive unit of a brake device, and more specifically, a rotation input from an electric motor is input to the ball screw mechanism. It is related with the electric actuator which converts into linear motion of a drive shaft via.
  • CVT continuously variable transmission
  • a gear mechanism such as a trapezoidal screw or a rack and pinion is generally used as a mechanism for converting the rotational motion of the electric motor into a linear linear motion. Since these conversion mechanisms involve a sliding contact portion, the power loss is large, and it is necessary to increase the size of the electric motor and increase the power consumption. Therefore, a ball screw mechanism has been adopted as a more efficient actuator.
  • an electric disc brake in which a friction pad is pressed and slid on a disc rotor via a pressing member by an advance / retreat mechanism that is operated by a driving force of an electric motor. It has been. As shown in FIG. 4, this electric disc brake is connected to a wheel of an automobile and rotates together with the disc rotor 51 and the friction surfaces 52 on both sides of the disc rotor 51.
  • the caliper support arm is provided so as to hang and protrude so that the friction pads 54 and 55 are slidable.
  • the caliper body 58 presses the friction pads 54 and 55 against the disc rotor 51.
  • the caliper body 58 includes an action portion 59 disposed on the back surface of one friction pad 54 and a reaction portion 60 provided with a reaction force claw 57 disposed on the back surface of the other friction pad 55 with the disc rotor 51 interposed therebetween.
  • a bridge portion 61 that connects the action portion 59 and the reaction portion 60 across the outer periphery of the disc rotor 51 is provided.
  • the action unit 59 includes a brushless electric motor 63 in the cylinder 62, a ball screw mechanism 64 that generates a pressing force of the friction pads 54 and 55, and a driving force of the electric motor 63 to the ball screw mechanism 64.
  • a reduction gear mechanism 65 that transmits the reduced speed is accommodated.
  • the reduction gear mechanism 65 is a planetary arm that is a driving component 66 that can be rotated by the driving force of the electric motor 63, a planetary gear 67 that is rotatably supported by the planetary arm, and the planetary gear 67. And a sun gear 68.
  • the planetary arm which is the drive component 66, is provided on the outer periphery of the cylindrical portion 70 having a magnet 69 acting as a rotor of the electric motor 63, and on the outer side opposite to the friction pad 54.
  • the large-diameter portion 71 is configured to receive the driving force of the electric motor 63 and rotate in the cylinder 62 via the bearing portion 72.
  • the ball screw nut 73 of the ball screw mechanism 64 is rotatably accommodated in the planetary arm as the driving component 66 via the bearing portion 72 so as not to advance and retreat.
  • a nut gear 74 having fewer teeth than the sun gear 68 is fixed as one of the reduction gears on the outer periphery of the rear end disposed on the large diameter portion 71 side of the drive component 66.
  • the nut gear 74 is engaged with the second gear portion 75 of the planetary gear 67, and the ball screw nut 73 can be rotated by the rotation of the planetary gear 67.
  • a ball screw shaft 78 is engaged with a ball groove 76 provided on the inner diameter side of the ball screw nut 73 through a plurality of balls 77 so as to be capable of moving forward and backward.
  • a hollow electric motor 63 is disposed so as to cover the outer periphery of the ball screw nut 73, and the driving force of the electric motor 63 is transmitted to the ball screw nut 73 via the planetary gear 67.
  • a gear is required on the outer periphery of the ball screw nut 73.
  • the motor layout is designed so that the nut gear 74 does not interfere with the motor coil. Must be formed out of range. This increases the overall length of the ball screw nut 73.
  • the planetary gear 67 must also be disposed outside the range of the motor layout, so that it is difficult to reduce the size of the electric disc brake in the axial direction. Furthermore, since the electric motor 63 is inserted as a hollow structure, it is necessary to design and manufacture a dedicated motor, which is not only expensive, but also its maintenance is not easy.
  • the present invention has been made in view of the problems of the prior art, and an object of the present invention is to provide an electric actuator that can achieve a large reduction ratio and that is simple in structure and compact.
  • the invention according to claim 1 of the present invention is coupled to a cylindrical housing, an electric motor attached to the housing, and a motor shaft of the electric motor so as to transmit torque.
  • the ball screw mechanism is formed in a hollow shape in which a spiral thread groove is formed on the outer periphery, and is supported by the input shaft so as to be rotatable via a rolling bearing and not axially movable.
  • the cylindrical housing the electric motor attached to the housing, the input shaft coupled to the motor shaft of the electric motor so as to transmit torque, and the rotational force of the electric motor via the input shaft.
  • an electric actuator including a transmission speed reduction mechanism and a ball screw mechanism that converts the rotational motion of the electric motor into a linear motion in the axial direction of the drive shaft via the speed reduction mechanism
  • the ball screw mechanism is spirally formed on the outer periphery.
  • a threaded groove is formed, a hollow ball screw shaft that is rotatably supported by a rolling bearing on the input shaft and is not movable in the axial direction, and a spiral thread groove is formed on the inner periphery, and the drive shaft is It is composed of a ball screw nut that is connected coaxially so as to be non-rotatable and supported so as to be axially movable, and a large number of balls that are rotatably accommodated between both screw grooves. Since it is mounted in an annular space formed between the input shaft and the ball screw shaft, it is possible to provide an electric actuator which is compactified by a simple structure.
  • a disk-shaped motor bracket is attached to the opening of the housing and the electric motor is fixed to the motor bracket, the opening of the housing is secured by the motor bracket. Can be blocked, and rainwater and foreign matter can be prevented from entering from the outside.
  • the speed reduction mechanism includes a ball screw shaft having a plurality of internal teeth formed on the inner periphery at equal intervals in the circumferential direction, and an outer ring of a rolling bearing that is externally fitted to the input shaft.
  • An engagement element made of cylindrical rollers respectively contacting the outer periphery of the ball screw shaft and the inner teeth of the ball screw shaft, and a cage for holding these engagement elements in a circumferentially equal distribution, the number of the inner teeth being Since the ball screw shaft is slightly decentered with respect to the motor shaft, a reduction ratio larger than that obtained with a conventional spur gear or planetary gear mechanism can be obtained.
  • a compact structure can be achieved with a simple structure.
  • a desired reduction ratio can be obtained by appropriately changing the number of inner teeth and engagement elements and the amount of eccentricity.
  • the land angle between the adjacent screw grooves in the axial direction of the ball screw shaft is such that the lead angles of the two screw grooves are set to be the same. If the portion is constituted by a shaft circulation type ball screw provided with a ball circulation groove in which the screw groove is individually closed loop, a compact structure can be achieved with a simple structure.
  • the lead angle of the screw groove is set to 1 ° or less as in the invention described in claim 5, the angle between the screw groove and the ball circulation groove approaches approximately 180 °, and the circulation of the ball Can be performed smoothly.
  • both the screw grooves are formed in a Gothic arc shape combining two arcs having a curvature radius slightly larger than the radius of the ball, Since the contact angle with the ball can be increased and the axial clearance can be set small, the rigidity with respect to the axial load is increased and the occurrence of vibration can be suppressed.
  • the ratio of the outer diameter of the balls to the leads of the both screw grooves is set to be 0.8 or more, the strength and rigidity are high. And can receive a high load.
  • an axial groove extending in the axial direction is formed on the outer periphery of the ball screw nut, and a protrusion extending in the axial direction is formed on the inner periphery of the housing. If the shaft groove of the ball screw nut is engaged with the strip, the ball screw nut can be supported so as to be movable in the axial direction and non-rotatable with a simple structure.
  • a thrust bearing is interposed between the end of the ball screw shaft and the motor bracket, a reaction force of the ball screw nut is loaded by the thrust bearing. This can increase the rigidity of the ball screw mechanism.
  • a cylindrical position holding ring is fitted and fixed to the outer periphery of the one end portion of the input shaft, and an electromagnetic solenoid is attached to the motor bracket, and the electromagnetic solenoid protrudes. If the position holding ring is pressed, the rotation of the input shaft can be temporarily stopped. When this electric actuator is applied to the drive unit of the brake device, a parking brake function can be achieved.
  • the position holding ring includes a first cylindrical portion fitted to the input shaft, and an axial direction from the first cylindrical portion via the disk portion. And a second cylindrical portion formed larger in diameter than the first cylindrical portion, and if the electromagnetic solenoid is pressed against the second cylindrical portion, the diameter of the pressing portion of the electromagnetic solenoid is increased. It can be set large, and the torque applied to the tip of the electromagnetic solenoid can be reduced. Therefore, position retainability and durability can be improved.
  • An electric actuator includes a cylindrical housing, an electric motor attached to the housing, an input shaft coupled to the motor shaft of the electric motor so as to transmit torque, and the electric motor via the input shaft.
  • An electric actuator comprising: a reduction mechanism that transmits the rotational force of the motor; and a ball screw mechanism that converts the rotational movement of the electric motor into a linear movement in the axial direction of the drive shaft via the reduction mechanism.
  • a hollow ball screw shaft having a spiral thread groove formed on the outer periphery, supported on the input shaft via a rolling bearing and not axially movable, and a spiral screw on the inner periphery A groove is formed, and the drive shaft is connected coaxially so as to be non-rotatable and supported so as to be axially movable, and is rotatably accommodated between the both screw grooves. Since the speed reduction mechanism is mounted in an annular space formed between the input shaft and the ball screw shaft, an electric actuator that has a simple structure and is made compact is configured. Can be provided.
  • FIG. 3 is a transverse sectional view taken along line III-III in FIG. It is a longitudinal cross-sectional view which shows the conventional electric disc brake.
  • a cylindrical housing an electric motor attached to the housing, an input shaft coupled to the motor shaft of the electric motor so as to be able to transmit torque, and a deceleration that transmits the rotational force of the electric motor via the input shaft
  • An electric actuator comprising a mechanism and a ball screw mechanism that converts the rotational motion of the electric motor into a linear motion in the axial direction of the drive shaft via the speed reduction mechanism, and a disk-shaped motor bracket at the opening of the housing
  • the electric motor is fixed to the motor bracket, the ball screw mechanism is formed with a helical thread groove on the outer periphery, is rotatable on the input shaft via a rolling bearing, and is axially
  • a hollow ball screw shaft that is immovably supported, and a spiral thread groove is formed on the inner periphery, and the drive shaft is connected coaxially so that it cannot rotate.
  • a ball screw nut supported so as to be movable in the axial direction, and a large number of balls accommodated so as to be able to roll between the two screw grooves.
  • a ball screw shaft having a plurality of inner teeth formed, an outer periphery of a rolling bearing that is externally fitted to the input shaft, and an engagement element comprising cylindrical rollers that are in contact with the inner teeth of the ball screw shaft, respectively,
  • FIG. 1 is a longitudinal sectional view showing an embodiment of an electric actuator according to the present invention
  • FIG. 2 is an explanatory view showing a ball screw mechanism of FIG. 1, (a) is a front view, and (b) is a transverse section.
  • FIG. FIG. 3 is a sectional view taken along line III-III in FIG.
  • the electric actuator 1 includes a cylindrical housing 2, an electric motor 3 attached to the housing 2, an input shaft 4 externally fitted to the motor shaft 3 a of the electric motor 3 so that torque can be transmitted, and the input shaft 4 and a ball screw that converts the rotational motion of the electric motor 3 into the linear motion in the axial direction of the drive shaft (caliper) 6 through the speed reduction mechanism 5. And a mechanism 7.
  • the housing 2 includes a large-diameter portion 2 a that houses the input shaft 4, the speed reduction mechanism 5, and the ball screw mechanism 7, and a small-diameter portion 2 b that houses the drive shaft 6.
  • the drive shaft 6 includes a fitting portion 6 a that is fitted and fixed to a ball screw nut 15 that constitutes a ball screw mechanism 7 that will be described later, and a braking portion 6 b that presses the friction surfaces 8 a on both sides of the disk rotor 8. .
  • a boot 9 is mounted between the braking portion 6b and the small-diameter portion 2b of the housing 2 to prevent rainwater and foreign matter from entering from the outside.
  • the electric motor 3 is fixed to a disk-shaped motor bracket 10.
  • the motor bracket 10 is attached so as to close the opening of the housing 2.
  • the motor shaft 3a is connected to the input shaft 4 via a serration.
  • a cylindrical roller bearing 11 and a deep groove ball bearing 12 are mounted between the input shaft 4 and a ball screw shaft 14 sheathed on the input shaft 4 so that the ball screw shaft 14 can rotate with respect to the input shaft 4.
  • it is disposed so as not to move in the axial direction.
  • a cup-like position retaining ring 13 is attached to one end of the input shaft 4 and engages with an annular groove 10a formed on the side surface of the motor bracket 10 to prevent rainwater and foreign matter from entering from the outside. ing.
  • the ball screw mechanism 7 has a ball screw shaft 14 having spiral thread grooves 14a and 14b formed on the outer periphery, and is externally fitted to the ball screw shaft 14 and spirals on the inner periphery.
  • a ball screw nut 15 having a thread-like thread groove 15a and a large number of balls 16 accommodated between the ball screw shaft 14 and the ball screw nut 15 constitute an axial circulation type ball screw mechanism 7. .
  • the ball screw shaft 14 has a hollow cylindrical shape, and a speed reduction mechanism 5 described later is accommodated in this inner diameter portion.
  • a plurality of (here, two turns) screw grooves 14a and 14b that are not continuous in the axial middle region are formed on the outer periphery.
  • the thread grooves 14a and 14b of the ball screw shaft 14 and the thread groove 15a of the ball screw nut 15 are set to have the same lead angle ⁇ .
  • These thread grooves 14 a, 14 b and 15 a are formed in a so-called gothic arc shape in which two arcs having a curvature radius slightly larger than the radius of the ball 16 are combined.
  • the contact angle with the ball 16 can be increased and the axial clearance can be set small, so that the rigidity against the axial load is increased and the occurrence of vibration can be suppressed.
  • the thread grooves 14a, 14b, and 15a may have a circular arc shape having a single radius of curvature slightly larger than the radius of the ball 16 in addition to the gothic arc shape.
  • the ball screw shaft 14 and the ball screw nut 15 are made of medium carbon steel such as S55C or case-hardened steel such as SCM415 or SCM420.
  • medium carbon steel the surface is hardened to a range of 55 to 62 HRC by induction hardening. Is given.
  • case-hardened steel the surface is hardened in the range of 55 to 62 HRC by carburizing and quenching.
  • the plurality of screw grooves 14a and 14b of the ball screw shaft 14 are closed loops, and the balls 16 respectively accommodated in the plurality of screw grooves 14a and 14b are independently and endlessly circulated.
  • the ball circulation grooves 18 and 19 each having a plurality of screw grooves 14a and 14b as closed loops are provided in the land portion 14c existing between the screw grooves 14a and 14b adjacent in the axial direction of the ball screw shaft 14. Yes.
  • the ball circulation grooves 18 and 19 individually connect the upstream side and the downstream side of the thread grooves 14a and 14b. As shown in FIG. 2B, the ball circulation grooves 18 and 19 are connected to the balls downstream of the thread grooves 14a and 14b. 6 is submerged to the inner diameter side so that the ball circulation grooves 18 and 19 are returned to the upstream side by getting over the land portion of the ball screw nut 15, and the ball 16 has a depth within the ball circulation grooves 18 and 19. The depth is such that the land of the screw groove 15a in the screw nut 15 can be overcome.
  • the ball circulation grooves 18 and 19 are formed to meander in a substantially straight line.
  • the lead angle ⁇ is set to 1 ° or less.
  • the angle between the screw grooves 14a and 14b and the ball circulation grooves 18 and 19 is substantially equal.
  • the ball circulation grooves 18 and 19 are not necessarily formed to meander in an S-shape, and the balls 16 are smoothly circulated even if they are straight.
  • the outer diameter d of the ball 16 is set so that the ratio of the outer diameter d of the ball 16 to the lead L of the screw grooves 14a and 14b is 0.8 or more (d ⁇ 0.8L). Thereby, strength and rigidity become high and can receive a high load.
  • a thrust bearing 20 made of cylindrical rollers is interposed between the left end portion of the ball screw shaft 14 and the motor bracket 10, and the reaction force of the ball screw nut 15 is loaded. is doing. Thereby, the rigidity of the ball screw mechanism 7 can be increased.
  • an axial groove 15 b extending in the axial direction is formed at one circumferential position on the outer periphery of the ball screw nut 15, and a protrusion extending in the axial direction on the inner periphery of the large-diameter portion 2 a of the housing 2.
  • a strip 21 is formed, and the shaft groove 15 b of the ball screw nut 15 is engaged with the projection 21. Thereby, it is possible to support the ball screw nut 15 so as to be axially movable and non-rotatable with a simple structure.
  • the speed reduction mechanism 5 includes a ball screw shaft 14 having a plurality of inner teeth 22 formed on the inner periphery at equal intervals in the circumferential direction, an engagement element 23 that engages with the inner teeth 22, and a motor.
  • a cage 24 is provided that is fixed to the bracket 10 and holds the engagement elements 23 made of cylindrical rollers at equal intervals in the circumferential direction.
  • the ball screw shaft 14 is rotatably supported with respect to the input shaft 4 by the cylindrical roller bearing 11 and the deep groove ball bearing 12, and is mounted with a slight eccentricity ⁇ with respect to the shaft center of the motor shaft 3a.
  • the engaging element 23 is in contact with the outer periphery of the outer ring 11 a of the cylindrical roller bearing 11, is in contact with the inner teeth 22 of the ball screw shaft 14, and is disposed so as to be able to engage with and disengage from the inner teeth 22.
  • the number of the internal teeth 22 of the ball screw shaft 14 is such that a reduction ratio 1:30 corresponding to the number of engagement elements 23 (here, 30) is obtained.
  • the outer periphery of one end portion of the input shaft 4 is subjected to rotation prevention processing such as knurling, and the position holding ring 13 is fitted and fixed to this end portion.
  • the position holding ring 13 extends in the axial direction from the first cylindrical portion 13a, which is fitted to the input shaft 4, and from the first cylindrical portion 13a via the disc portion 13b. And a second cylindrical portion 13c having a large diameter. Then, if the electromagnetic cylinder 25 mounted on the motor bracket 10 protrudes to press the second cylindrical portion 13c of the position holding ring 13, the rotation of the input shaft 4 is temporarily stopped, and the parking brake functions. Can be fulfilled.
  • the position holding ring 13 has a two-stage structure having the first cylindrical portion 13a and the second cylindrical portion 13c, and the diameter of the pressing portion of the electromagnetic solenoid 25 is set large, so that the tip of the electromagnetic solenoid 25 is loaded. Torque can be reduced, and position retention and durability can be improved.
  • the electric actuator according to the present invention can be applied to an electric actuator provided with a ball screw mechanism that converts rotational input from an electric motor into linear motion of a drive shaft via the ball screw mechanism.

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

Abstract

L'invention porte sur un actionneur électrique dans lequel on peut obtenir un grand rapport de réduction de vitesse et où la dimension de l'actionneur électrique peut être réduite grâce à une structure simple. Dans l'actionneur électrique, un support de moteur en forme de disque (10) est attaché à l'ouverture d'un carter (2) ; un moteur électrique (3) est fixé au support de moteur ; un mécanisme de vis à billes (7) est composé d'un arbre de vis à billes creux (14) supporté par un arbre d'entrée (4) par l'intermédiaire de roulements (11, 12), de manière à tourner mais à ne pas se déplacer dans la direction axiale, et un écrou de vis à billes (15) qui est relié coaxialement à un arbre d'entraînement (6) et supporté par celui-ci de manière à se déplacer dans la direction axiale mais à ne pas tourner ; et un mécanisme réducteur de vitesse (5) est composé de l'arbre à vis à billes (14) qui comporte une pluralité de dents intérieures (22) qui sont agencées à égale distance dans la direction circonférentielle sur la périphérie intérieure, des éléments de prise (23) qui sont en contact avec la périphérie extérieure d'une bague extérieure (11a) du roulement (11) et avec les dents intérieures (22), et un élément de retenue (24) qui retient les éléments de prise (23) agencés à égale distance dans la direction circonférentielle, le nombre des dents intérieures étant plus grand que celui des éléments de prise (23) et l'arbre à vis à bille (14) étant légèrement excentré par rapport à l'arbre du moteur (3a).
PCT/JP2010/062781 2009-07-30 2010-07-29 Actionneur électrique WO2011013744A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-177900 2009-07-30
JP2009177900A JP2011033080A (ja) 2009-07-30 2009-07-30 電動アクチュエータ

Publications (1)

Publication Number Publication Date
WO2011013744A1 true WO2011013744A1 (fr) 2011-02-03

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107269787A (zh) * 2016-04-08 2017-10-20 纳博特斯克有限公司 齿轮装置
US9939054B2 (en) 2015-10-09 2018-04-10 Command Access Technology, Inc. Actuator with ball screw drive
CN112739934A (zh) * 2018-10-19 2021-04-30 Thk株式会社 滚珠丝杠装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013186867A1 (fr) * 2012-06-13 2013-12-19 株式会社日立製作所 Dispositif de relâchement de frein électromagnétique pour ascenseurs
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