WO2014148514A1 - Actionneur linéaire électrique - Google Patents

Actionneur linéaire électrique Download PDF

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Publication number
WO2014148514A1
WO2014148514A1 PCT/JP2014/057413 JP2014057413W WO2014148514A1 WO 2014148514 A1 WO2014148514 A1 WO 2014148514A1 JP 2014057413 W JP2014057413 W JP 2014057413W WO 2014148514 A1 WO2014148514 A1 WO 2014148514A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
linear actuator
electric linear
intermediate gear
bearing
Prior art date
Application number
PCT/JP2014/057413
Other languages
English (en)
Japanese (ja)
Inventor
崇夫 水内
健介 船田
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 WO2014148514A1 publication Critical patent/WO2014148514A1/fr

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Classifications

    • 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
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
    • 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
    • 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
    • F16H2025/204—Axial sliding means, i.e. for rotary support and axial guiding of nut or screw shaft
    • 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
    • F16H2025/2081—Parallel arrangement of drive motor to screw axis
    • 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

Definitions

  • the present invention relates to an electric linear actuator provided with a ball screw mechanism used in a drive unit of a general industrial electric motor or automobile, and more specifically, a rotational input from an electric motor is applied to the ball screw in an automobile transmission or a parking brake.
  • the present invention relates to an electric linear actuator that converts a linear motion of a drive shaft through a mechanism.
  • 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 motion in the axial direction. 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.
  • a ball screw shaft constituting a ball screw can be driven to rotate by an electric motor supported by a housing, and an output member coupled to a nut by rotating the ball screw shaft. Can be displaced in the axial direction. Since the ball screw mechanism has very low friction and the ball screw shaft easily rotates due to the thrust load acting on the output member side, it is necessary to hold the position of the output member when the electric motor is stopped.
  • a brake means is provided in an electric motor, or a low-efficiency thing such as a worm gear is provided as a transmission means.
  • an electric linear actuator as shown in FIG. It has been known.
  • the electric linear actuator 50 includes a ball screw shaft 51 that is rotationally driven by an electric motor (not shown), and a ball screw nut 52 that is screwed onto the ball screw shaft 51 via a ball (not shown).
  • a ball screw mechanism 53 provided is employed.
  • the ball screw shaft 51 is rotatably supported by cylindrical housings 54 and 55 by two rolling bearings 56 and 57. These rolling bearings 56 and 57 are fixed by a locking member 59 for preventing loosening via a fixing lid 58.
  • a spiral screw groove 51a is formed on the outer periphery of the ball screw shaft 51, and a cylindrical ball screw nut 52 is screwed through the ball.
  • a spiral screw groove 52a is formed on the inner periphery of the ball screw nut 52, and a large diameter portion 60 is formed at the end.
  • a flat portion 61 is formed on the side surface of the large-diameter portion 60 and is cut so that the end surface is flat.
  • a cam follower (rotation stop means) 62 projects from the substantially central portion of the flat portion 61 toward the outside in the radial direction. The cam follower 62 is engaged with a notch (not shown) formed in the housing 54.
  • the present invention has been made in view of such problems of the prior art, and an object of the present invention is to provide an electric linear actuator having a simple structure and a low-cost detent mechanism for a screw shaft.
  • the invention according to claim 1 of the present invention includes a housing, an electric motor attached to the housing, and a speed reduction mechanism that transmits the rotational force of the electric motor via a motor shaft.
  • 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 the ball screw mechanism rotates via a support bearing mounted on the housing.
  • a nut that is supported so as not to move in the axial direction and has a spiral thread groove formed on the inner periphery, and is inserted into the nut via a number of balls and is coaxially integrated with the drive shaft.
  • a steel sleeve is fixed to the bag hole of the housing, A groove extending in the axial direction is formed on the inner periphery of the sleeve of the sleeve, and a guide ball is engaged with the end of the screw shaft and engaged with the groove, and the screw shaft rotates relative to the housing. It is supported so as to be movable in the axial direction.
  • a reduction mechanism that transmits the rotational force of the electric motor and a ball screw mechanism that converts the rotational movement of the electric motor into the linear movement in the axial direction of the drive shaft via the reduction mechanism are provided.
  • a nut rotatably supported through a pair of support bearings mounted on the housing and not axially movable, and having a helical thread groove formed on the inner periphery, and a number of balls on the nut
  • an electric linear actuator composed of a screw shaft that is interpolated and integrated coaxially with the drive shaft, and that has a helical thread groove corresponding to the thread groove of the nut on the outer periphery, a steel hole is formed in the bag hole of the housing.
  • a sleeve made of metal is fixed, and a groove extending in the axial direction is formed on the inner periphery of the sleeve.
  • a guide ball is engaged with the end of the screw shaft and engaged with the groove.
  • the screw shaft is supported so as to be movable in the axial direction, so that it is possible to suppress bending, bending and deflection of the end of the screw shaft, and the screw shaft cannot be rotated and can move stably in the axial direction without play. It is possible to provide an electric linear actuator that can be supported and includes a screw shaft rotation prevention mechanism with a simple structure and low cost.
  • a substantially hemispherical concave portion is formed at the end of the screw shaft, and when the radius of curvature R2 is defined as Ra of the guide ball, R2 ⁇ 1. If it is set to 2Ra, the guide ball can be locked without play.
  • the screw fastening of the housing and the sleeve each having a different linear expansion coefficient, it is possible to suppress a change in axial force accompanying a temperature rise.
  • a cap is externally fitted to the end of the sleeve, and is integrally fitted to the bottom of the bag hole of the housing, and the cap is pressed from a steel plate.
  • the screw shaft is formed in a substantially U-shaped cross section, and has a bottom portion that comes into contact with the bottom portion of the bag hole of the housing and a flange portion that is bent from the edge of the bottom portion into a ring shape. There is no direct collision with the housing, and damage and wear of the housing can be reduced.
  • the output gear constituting the speed reduction mechanism is fixed to the nut, and support bearings are disposed on both sides of the output gear, and the support bearing is formed in a ring shape. If the housing is mounted via a washer made of an elastic member, the axial play of the pair of support bearings can be eliminated, and smooth rotation performance can be obtained.
  • the housing comprises a first housing and a second housing abutted on an end surface thereof, and the electric motor is attached to the first housing.
  • a bag hole for accommodating the screw shaft is formed in an abutting portion of the first housing and the second housing, and the speed reduction mechanism is an input gear fixed to the motor shaft, and the input gear.
  • the bearing attached to the intermediate gear is accommodated so as to be able to roll through a steel plate press outer ring press-fitted into the inner diameter of the intermediate gear and a cage. If it is constituted by a shell-type needle roller bearing provided with a plurality of needle rollers, the availability is high and the cost can be reduced.
  • the width of the bearing is set smaller than the tooth width of the intermediate gear as in the invention described in claim 11, it is possible to prevent wear and deformation of the bearing side surface due to friction, and smooth Rotational performance can be obtained.
  • ring-shaped washers are mounted on both sides of the intermediate gear and the width of the tooth portion of the intermediate gear is formed to be smaller than the tooth width, While preventing a gear from contacting a housing directly, the contact area with a washer can be made small, the frictional resistance at the time of rotation can be suppressed, and smooth rotation performance can be obtained.
  • the bearing mounted on the intermediate gear is a sliding bearing
  • the sliding bearing is composed of an oil-impregnated bearing made of a porous metal to which fine graphite powder is added
  • An electric linear actuator includes a housing, an electric motor attached to the housing, a reduction mechanism that transmits the rotational force of the electric motor through a motor shaft, and the electric motor through the reduction mechanism.
  • a ball screw mechanism that converts rotational motion into linear motion in the axial direction of the drive shaft, and this ball screw mechanism is supported by a support bearing mounted on the housing so as to be rotatable and not movable in the axial direction.
  • an electric linear actuator composed of a screw shaft formed with a helical thread groove, a steel sleeve is fixed to the bag hole of the housing, and the inner periphery of the sleeve A concave groove extending in the axial direction is formed, and a guide ball is locked to an end of the screw shaft and engaged with the concave groove, so that the screw shaft cannot rotate with respect to the housing and is axially Since it is supported so that it can move, it can suppress bending, bending, and deflection of the end of the screw shaft, and it can support the screw shaft so that it cannot rotate and can move stably in the axial direction without play.
  • An electric linear actuator provided with a simple structure and a low-cost screw shaft detent mechanism can
  • FIG. 1 is a longitudinal sectional view showing an embodiment of an electric linear actuator according to the present invention. It is a longitudinal cross-sectional view which shows the actuator main body of FIG. It is a principal part enlarged view which shows the intermediate
  • a ball screw mechanism that converts the linear screw motion into an axial linear motion of the motor, and the ball screw mechanism is supported by a support bearing mounted on the housing so as to be rotatable and non-movable in the axial direction.
  • a helical thread groove that is inserted into the nut through a large number of balls, is coaxially integrated with the drive shaft, and corresponds to the thread groove of the nut on the outer periphery.
  • a steel sleeve is fastened to the bag hole of the housing via a threaded portion, and extends axially around the inner periphery of the sleeve.
  • a groove having a substantially semicircular cross section is formed, and a guide ball is engaged with the end of the screw shaft and engaged with the groove, and a radius of curvature R1 of the groove is defined by the guide ball.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of an electric linear actuator according to the present invention
  • FIG. 2 is a longitudinal sectional view showing an actuator body of FIG. 1
  • FIG. 3 is a main portion showing an intermediate gear portion of FIG. 4 is an enlarged view of a main part showing a modification of FIG. 3
  • FIG. 5 (a) is an enlarged view of a main part showing a fixing part of the sleeve of FIG. 1, and FIG. It is a cross-sectional view along the line ⁇ V.
  • the electric linear actuator 1 includes a cylindrical housing 2, an electric motor (not shown) attached to the housing 2, and an input gear attached to a motor shaft 3a of the electric motor. 3 and an output gear 5 meshed with the intermediate gear 4, and the rotational motion of the electric motor is converted into a linear motion in the axial direction of the drive shaft 7 via the speed reduction mechanism 6.
  • a ball screw mechanism 8 for conversion and an actuator main body 9 including the ball screw mechanism 8 are provided.
  • the housing 2 is made of an aluminum alloy such as A6063TE or ADC12, and includes a first housing 2a and a second housing 2b abutted on the end face thereof, and is fixed integrally by a fixing bolt (not shown). .
  • An electric motor is attached to the first housing 2a, and bag holes 11 and 12 for accommodating the screw shaft 10 are formed at the abutting portions of the first housing 2a and the second housing 2b. Yes.
  • the motor shaft 3a of the electric motor is rotatably supported by a rolling bearing 13 comprising a deep groove ball bearing mounted on the second housing 2b. .
  • the output gear 5 that meshes with the intermediate gear 4 that is a spur gear is integrally fixed to a nut 18 that constitutes a ball screw mechanism 8 described later via a key 14.
  • the drive shaft 7 is integrally formed with a screw shaft 10 constituting the ball screw mechanism 8, and a guide ball 15 is locked to one end portion (right end portion in the figure) of the drive shaft 7.
  • a sleeve 17 described later is fitted into the bag hole 12 of the second housing 2b.
  • the ball screw mechanism 8 includes a screw shaft 10 and a nut 18 externally inserted through the ball 19 to the screw shaft 10 as shown in an enlarged view in FIG.
  • the screw shaft 10 has a spiral thread groove 10a formed on the outer periphery by rolling.
  • the nut 18 is formed with a spiral thread groove 18a corresponding to the thread groove 10a of the screw shaft 10 on the inner periphery, and is externally inserted into the screw shaft 10, and a large number of spaces between these screw grooves 10a and 18a.
  • a ball 19 is accommodated so as to roll freely.
  • the nut 18 is supported to the housings 2a and 2b via the two support bearings 20 and 20 so as to be rotatable and not movable in the axial direction.
  • Reference numeral 21 denotes a piece member that constitutes a ball circulation member by connecting the thread groove 18a of the nut 18, and the piece member 21 allows infinite circulation of a large number of balls 19.
  • each of the thread grooves 10a and 18a may be a circular arc shape or a gothic arc shape, but here, a gothic arc shape that allows a large contact angle with the ball 19 and a small axial clearance can be set. Is formed. Thereby, the rigidity with respect to an axial load becomes high and generation
  • the nut 18 is made of case-hardened steel such as SCM415 or SCM420, and its surface is hardened in the range of 55 to 62HRC by vacuum carburizing and quenching. Thereby, the buffing etc. for the scale removal after the heat treatment can be omitted, and the cost can be reduced.
  • the screw shaft 10 is made of medium carbon steel such as S55C or case-hardened steel such as SCM415 or SCM420, and the surface thereof is hardened in the range of 55 to 62 HRC by induction hardening or carburizing hardening.
  • the output gear 5 constituting the speed reduction mechanism 6 is integrally fixed to the outer peripheral surface 18b of the nut 18, and two support bearings 20 and 20 are press-fitted on both sides of the output gear 5 via a predetermined shimiro. .
  • the two support bearings 20 and 20 are constituted by sealed deep groove ball bearings having shield plates 20a and 20a attached to both ends, and leakage of the lubricating grease enclosed in the bearings to the outside and from the outside This prevents wear powder from entering the bearing.
  • the support bearing 20 that rotatably supports the nut 18 is formed of a deep groove ball bearing of the same specification, the radial load that is loaded from the drive shaft 7 via the thrust load and the output gear 5 described above. Both can be loaded, and confirmation work for preventing misassembly during assembly can be simplified, and the assembly workability can be improved.
  • the rolling bearing of the same specification means a bearing having the same inner diameter, outer diameter, width dimension, rolling element size, number, bearing internal clearance, and the like.
  • one support bearing 20 of the pair of support bearings 20 is mounted on the first housing 2a via a washer 27 made of a ring-shaped elastic member.
  • This washer 27 is formed by press working from an austenitic stainless steel plate (JIS standard SUS304 type or the like) having high strength and wear resistance, or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). It consists of a wave washer.
  • the inner diameter D is formed larger than the inner ring outer diameter d of the support bearing 20.
  • the axial backlash of the pair of support bearings 20 and 20 can be eliminated, smooth rotation performance can be obtained, and the washer 27 is in contact with only the outer ring of the support bearing 20 and is an inner ring that becomes a rotating ring. Therefore, even if a reverse thrust load is generated and the nut 18 is pressed against the first housing 2a, the inner ring of the support bearing 20 is prevented from coming into contact with the housing 2a and the frictional force is prevented from increasing, and the locked state Can be surely prevented.
  • the gear shaft 22 is implanted in the first and second housings 2 a and 2 b, and the intermediate gear 4 is rotatably supported on the gear shaft 22 via a rolling bearing 23. ing.
  • the end portions of the gear shaft 22 for example, when press-fitting the end portion on the first housing 2a side, the end portion on the second housing 2b side is set to be a clearance fit, thereby making misalignment (assembly error). Allowing smooth rotation performance can be ensured.
  • the rolling bearing 23 includes an outer ring 24 made of a steel plate press-fitted into the inner diameter 4 a of the intermediate gear 4, and a plurality of needle rollers 26 accommodated in the outer ring 24 via a cage 25 so as to be freely rollable. And so-called shell-type needle roller bearings. Thereby, the availability of a bearing is high and cost reduction can be achieved.
  • ring-shaped washers 28 and 28 are mounted on both sides of the intermediate gear 4 to prevent the intermediate gear 4 from directly contacting the first and second housings 2a and 2b.
  • the width of the tooth portion 4b of the intermediate gear 4 is formed smaller than the tooth width.
  • the washer 28 is made of an austenitic stainless steel plate having high strength and high wear resistance, or a flat washer formed by pressing from a cold-rolled steel plate treated with rust prevention.
  • it is formed of a thermoplastic synthetic resin such as PA (polyamide) 66 filled with a predetermined amount of a fibrous reinforcing material such as brass, sintered metal, or GF (glass fiber). May be.
  • the width of the rolling bearing 23 is set smaller than the tooth width of the intermediate gear 4. Therefore, wear and deformation of the bearing side surface due to friction can be prevented, and smooth rotation performance can be obtained.
  • FIG. 4 shows a modification of FIG.
  • the gear shaft 22 is implanted in the first and second housings 2 a and 2 b, and the intermediate gear 29 is rotatably supported on the gear shaft 22 via a slide bearing 30.
  • the intermediate gear 29 is formed so that the width of the tooth portion 29b is the same as the tooth width, and the sliding bearing 30 is press-fitted into the inner diameter 29a of the intermediate gear 29 and added with fine graphite powder.
  • An oil-impregnated bearing (NTN trade name; Bear Fight (registered trademark)) made of The tooth width of the intermediate gear 29 is set to be larger.
  • the sliding bearing 30 may be formed of, for example, a thermoplastic polyimide resin that enables injection molding.
  • a sleeve 17 that supports the screw shaft 10 so as not to rotate and to be movable in the axial direction is fitted in the bag hole 12 of the second housing 2b.
  • a female screw 12 a is formed in the bag hole 12 of the second housing 2 b
  • a male screw 17 b that is screwed into the female screw 12 a is formed on the outer periphery of the sleeve 17. Then, by moving the sleeve 17 while rotating it toward the bottom of the bag hole 12, the female screw 12a and the male screw 17b are engaged, and the sleeve 17 is fastened to the second housing 2b.
  • the sleeve 17 is formed in a cylindrical shape by cold forging from medium carbon steel such as S55C, or case-hardened steel such as SCM415 or SCM420, and concave grooves 17a and 17a extending in the axial direction are formed at opposing positions on the inner periphery.
  • medium carbon steel such as S55C
  • case-hardened steel such as SCM415 or SCM420
  • concave grooves 17a and 17a extending in the axial direction are formed at opposing positions on the inner periphery.
  • the surface is hardened in the range of 55 to 62 HRC by induction hardening or carburizing hardening.
  • the sleeve 17 is not directly in contact with the bottom of the second housing 2 b and is fastened through a cap 31. That is, the cap 31 is externally fitted to the end of the sleeve 17 and is integrally fitted to the bottom of the second housing 2b.
  • the screw shaft 10 does not directly collide with the bag hole 12 of the second housing 2b, thereby reducing damage and wear of the second housing 2b, reducing weight, and improving durability and strength. It is possible to provide an electric linear actuator that is enhanced to improve reliability.
  • the cap 31 is formed by pressing from an austenitic stainless steel plate or a cold-rolled steel plate that has been rust-proofed into a substantially U-shaped cross section, and is folded into a ring shape from the bottom 31a and the edge of the bottom 31a. And a bent collar 31b.
  • a relief portion (dent) 32 is formed at the bottom portion of the second housing 2b with which the bottom portion 31a of the cap 31 abuts.
  • the female screw 12a of the second housing 2b and the male screw 17b of the sleeve 17 are provided near the bottom of the bag hole 12.
  • linear concave grooves 17 a and 17 a extending in the axial direction are formed at positions facing the circumferential direction of the sleeve 17.
  • the concave groove 17a has a substantially semicircular cross section, and the radius of curvature R1 is set to R1 ⁇ 1.2Ra when the radius of the guide ball 15 is Ra.
  • the guide ball 15 of the screw shaft 10 that engages with one of the concave grooves 17 a and 17 a is locked to a concave portion 16 formed at the end of the screw shaft 10.
  • the recess 16 is formed in a substantially hemispherical shape, and its curvature radius R2 is set to R2 ⁇ 1.2Ra.
  • the guide ball 15 is locked to the end of the screw shaft 10 and engaged with the concave groove 17a of the sleeve 17, and the respective radii of curvature of the concave groove 17a of the sleeve 17 and the concave portion 16 of the screw shaft 10 are as follows. Since R1 and R2 are set to 1.2 times or less of the radius Ra of the guide ball 15, even the long screw shaft 10 can suppress bending, bending, and deflection at the end, When the guide ball 15 is engaged with the concave grooves 17a and 17a, the screw shaft 10 can be rotated along the concave grooves 17a and 17a so that the screw shaft 10 is non-rotatable and can move stably in the axial direction. Can be supported.
  • the sectional shape of the concave groove 17a of the sleeve 17 and the concave portion 16 of the screw shaft 10 is a circular arc shape having a single radius, but is not limited to this, for example, the sectional shape of the concave groove 17a of the sleeve 17 May be formed into a Gothic arc shape consisting of a pair of arcs, and a clearance between the concave groove 17a, the guide ball 15 and the concave portion 16 of the screw shaft 10 may be negatively applied, so-called preload may be applied. Thereby, generation
  • An electric linear actuator according to the present invention is used in a drive unit of a general industrial electric motor, automobile, etc., and has a ball screw mechanism that converts rotational input from an electric motor into linear motion of a drive shaft via the ball screw mechanism. It can be applied to the provided electric linear actuator.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Transmission Devices (AREA)
  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

Actionneur linéaire électrique comprenant un mécanisme destiné à empêcher la rotation d'un arbre fileté, le mécanisme présentant une structure simple et ayant un faible coût. Un actionneur linéaire électrique (1) est doté d'un arbre fileté (10) possédant une rainure filetée hélicoïdale (10a) formée dans la périphérie extérieure de l'arbre fileté (10). Un manchon en acier (17) est fixé à un trou (12) à extrémité fermée dans un logement (2b) par une section filetée (17b), et des rainures (17a) s'étendant axialement ayant une coupe transversale sensiblement semi-circulaire sont formées dans la périphérie intérieure du manchon (17). Des billes de guidage (15) entrent en prise avec les rainures (17a) tout en étant également en prise avec une extrémité de l'arbre fileté (10). Si le rayon des billes (15) est Ra, le rayon de courbure (R1) des rainures (17a) est réglé pour satisfaire la relation de R1 ≤ 1,2Ra. L'arbre fileté (10) est supporté de manière à ne pas pouvoir tourner par rapport au logement (2b) mais de manière à pouvoir se déplacer axialement.
PCT/JP2014/057413 2013-03-19 2014-03-18 Actionneur linéaire électrique WO2014148514A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013057272A JP6121760B2 (ja) 2013-03-19 2013-03-19 電動リニアアクチュエータ
JP2013-057272 2013-03-19

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WO2014148514A1 true WO2014148514A1 (fr) 2014-09-25

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WO (1) WO2014148514A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016052477A1 (fr) * 2014-09-29 2016-04-07 Ntn株式会社 Actionneur électrique

Citations (10)

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Publication number Priority date Publication date Assignee Title
JPS60189649U (ja) * 1984-05-29 1985-12-16 株式会社椿本チエイン 直線作動機のロツド回転防止装置
JPH0480926U (fr) * 1990-11-22 1992-07-14
JP2003247560A (ja) * 2001-12-20 2003-09-05 Nsk Ltd 車両ステアリング用伸縮軸
JP2005186781A (ja) * 2003-12-25 2005-07-14 Favess Co Ltd 電動パワーステアリング装置
JP2005263149A (ja) * 2004-03-22 2005-09-29 Nsk Ltd 電動式パワーステアリング装置
JP2010025350A (ja) * 2009-11-04 2010-02-04 Ntn Corp シェル型針状ころ軸受
JP2010190289A (ja) * 2009-02-17 2010-09-02 Aichi Mach Ind Co Ltd 変速機およびその製造方法
JP2011117513A (ja) * 2009-12-02 2011-06-16 Ntn Corp 電動アクチュエータ
JP2012082921A (ja) * 2010-10-13 2012-04-26 Ntn Corp 電動アクチュエータ
WO2013073692A1 (fr) * 2011-11-16 2013-05-23 Ntn株式会社 Actionneur linéaire actionné électriquement

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60189649U (ja) * 1984-05-29 1985-12-16 株式会社椿本チエイン 直線作動機のロツド回転防止装置
JPH0480926U (fr) * 1990-11-22 1992-07-14
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JP2005186781A (ja) * 2003-12-25 2005-07-14 Favess Co Ltd 電動パワーステアリング装置
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WO2016052477A1 (fr) * 2014-09-29 2016-04-07 Ntn株式会社 Actionneur électrique
JP2016070324A (ja) * 2014-09-29 2016-05-09 Ntn株式会社 電動アクチュエータ

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