WO2016195104A1 - Actionneur électrique - Google Patents

Actionneur électrique Download PDF

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Publication number
WO2016195104A1
WO2016195104A1 PCT/JP2016/066692 JP2016066692W WO2016195104A1 WO 2016195104 A1 WO2016195104 A1 WO 2016195104A1 JP 2016066692 W JP2016066692 W JP 2016066692W WO 2016195104 A1 WO2016195104 A1 WO 2016195104A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
sleeve
screw shaft
shaft
electric actuator
Prior art date
Application number
PCT/JP2016/066692
Other languages
English (en)
Japanese (ja)
Inventor
辰徳 清水
寒山 工藤
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2016195104A1 publication Critical patent/WO2016195104A1/fr

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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
    • 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
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • 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
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • 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
    • 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

Definitions

  • the present invention relates to an electric actuator provided with a ball screw mechanism used in a drive unit of a general industrial electric motor or automobile, and more specifically, a rotation input from an electric motor is transmitted to a ball screw in an automobile transmission or a parking brake.
  • the present invention relates to an electric 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 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 motor supported by a housing can freely rotate a ball screw shaft constituting a ball screw, and an output member coupled to a nut by rotating the ball screw shaft. Displaceable in the axial direction. Since the ball screw mechanism has very low friction and high efficiency, the ball screw mechanism is also highly efficient against reverse input from the output side. Therefore, the reverse input is transmitted to the input side. That is, since the ball screw shaft is easily rotated by 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.
  • the electric actuator 51 is used as an electric parking brake driving device, and includes a cylindrical motor housing 51a and a housing body 51b.
  • An electric motor 52 is provided in the motor housing 51a.
  • the electric motor 52 includes a rotating shaft 52a that functions as a rotation driving unit, a stator 52b, and a rotor 52c.
  • the rotating shaft 52a is rotatably supported by the motor housing 51a via a bearing 53.
  • the rotary shaft 52a is hollow and is configured such that one axial end (the right end in the figure) has a large diameter, and the outer peripheral surface thereof is supported by the inner peripheral surface of the motor housing 51a by a bearing 54. ing.
  • the rotating shaft 52a has a plurality of claw portions 52d protruding in the axial direction from the axial end surface on the large diameter side.
  • the housing main body 51b has a shape in which a large diameter cylindrical portion and a small diameter cylindrical portion are connected in the axial direction, and the outer ring 55 cannot be rotated on the inner peripheral surface of the large diameter cylindrical portion by press fitting or the like. It is attached.
  • a roller 56 that is a locking member and a key 57 are disposed between the claw portions 52d.
  • a flange 55a is formed at one axial end (right side in the drawing) of the outer ring 55 so as to protrude radially inward. The roller 56 is prevented from moving in the axial direction by the flange 55a.
  • a rotating driven portion 59 is rotatably supported on the inner peripheral surface of the housing main body 51b via a bearing 58, and the rollers 56 are arranged so that the outer peripheral surface of the rotating driven portion 59 can roll.
  • a nut 60 is attached to the inner peripheral surface of the rotation driven portion 59 so as not to rotate relative to the rotation driven portion 59 by a set screw or the like.
  • a screw shaft 61 is provided so as to penetrate the nut 60.
  • the screw shaft 61 is arranged so that one end portion (left end portion in the figure) is inserted inside the rotation shaft 52a.
  • a screw groove (not shown) is formed at a location facing the nut 60 in the radial direction.
  • a screw groove (not shown) is formed on the inner peripheral surface of the nut 60 so as to correspond to the screw groove of the screw shaft 61.
  • a large number of balls are movably arranged in a spiral space defined by the respective thread grooves.
  • a cylindrical moving case 62 is disposed at the other end (right end in the figure) of the screw shaft 61, and via a key 62a disposed in a key groove formed at the end of the moving case 62, The screw shaft 61 is non-rotatably attached to the moving case 62.
  • One end of a wire (not shown) is connected to the axial end surface (right end surface in the figure) of the moving case 62, and the moving case 62 is connected to a parking brake device as a driven member via this wire.
  • the parking brake device When the wire moves to the left side, the parking brake device is operated to apply a braking force to a wheel (not shown), and when the wire moves to the right side, the parking brake device is released from braking.
  • the moving case 62 has a linear groove extending in the axial direction formed on the inner peripheral surface, and a pin 62b is provided so as to engage with the linear groove.
  • the case 62 is attached so as to be movable in the axial direction with respect to the housing main body 51b. That is, the moving case 62 is configured to be movable in the axial direction, although it cannot be rotated relative to the housing body 51b.
  • the wire attached to the moving case 62 is always urged to the right in the drawing by a spring or the like (not shown). That is, in a state where the parking brake device is operated, the moving case 62 and the screw shaft 61 are always pulled to the right in the axial direction.
  • a key groove 59b and three cam grooves 59c are formed at equal intervals on the outer peripheral surface of the rotationally driven 59.
  • the cam surface 59a has a slope inclined to one side so as to move away from the axial center in a clockwise direction (approaching the inner peripheral surface of the outer ring 55).
  • the cam surface 59a has an inclined portion 59d and a roller 56 that can roll without the roller 56 biting between the outer ring 55 and the rotationally driven portion 59. It has an inclined portion 59e that bites into both.
  • a roller clutch 63 having a function as a one-way clutch is attached to the inner peripheral surface of the housing body 51b.
  • a sleeve 64 formed in an annular shape is fitted to the outer peripheral surface of the rotationally driven portion 59 with a slight gap.
  • the sleeve 64 is rotatably supported on the inner peripheral surface of the housing main body 51b via the roller clutch 63.
  • the sleeve 64 is hardened by, for example, bearing steel, and the outer diameter surface thereof is a rolling surface of the roller clutch 63, and one of the axial side surfaces thereof is a sliding surface with the friction material. .
  • a friction material (friction means) 65 a is arranged on the outer peripheral surface of the rotationally driven portion 59 so as to be adjacent to the sleeve 64 in the axial direction, and the friction material 65 a is configured to rotate integrally with the rotationally driven portion 59. .
  • a screw 66 is provided on the outer peripheral surface of the rotationally driven portion 59. The screw 66 presses the axial end portion of the sleeve 64 via the friction material 65b, and abuts the sleeve 64 and the friction material 65a. I am letting.
  • the screw 66 is a screw in a direction not loosened by frictional force when the rotary driven portion 59 is rotated in the biting direction of the roller clutch 63, and in this case, is a left screw.
  • the roller clutch 63 is configured to be in a locked state when the rotary driven portion 59 rotates in the direction of arrow A in FIG. 9A, and the sleeve 64 and the rotary driven portion 59 are relatively rotated. On the other hand, when rotating in the direction opposite to the arrow A direction, the unlocked state is established, and the sleeve 64 and the rotary driven portion 59 are allowed to rotate integrally.
  • the ball screw mechanism 67 is configured such that the screw shaft 61 moves to the left in the figure by rotating the rotary shaft 52a and the rotary driven portion 59 in the direction of arrow C in FIG. At this time, the state as shown in FIG. 7 is obtained, and the parking brake device, which is the driven member, is activated. Further, the ball screw mechanism is configured such that the screw shaft 61 moves to the right side of the figure by rotating the rotary shaft 52a and the rotary driven portion 59 in the direction opposite to the direction of arrow C in FIG. . At this time, the parking brake device as the driven member is in a released state.
  • FIG. 9 (a) when releasing the parking brake device which is a driven member, there is a mechanism for applying a braking force to the rotation of the rotationally driven portion 59 due to the external load. Yes.
  • the roller clutch 63 provided in the housing main body 51b has a sleeve when the rotationally driven portion 59 is about to rotate in the direction of arrow A in FIG. 64 is locked so as not to rotate integrally with the rotary driven portion 59.
  • the sleeve 64 is substantially fixed to the housing body 51b.
  • the friction material 65 a is provided so as to come into contact with the sleeve 64, and rotates integrally with the rotation driven portion 59. Then, a frictional force is generated between the sleeve 64 and the friction material 65a, and the rotational acceleration in the direction of arrow A in FIG.
  • the rotational acceleration of the rotationally driven portion 59 that receives an external load can be made smaller than the rotational acceleration of the rotational drive portion (the rotational shaft 52a). For this reason, it is possible to prevent rattling from occurring in the position holding mechanism when releasing the operation of the parking brake device (see, for example, Patent Document 1).
  • the present invention has been made in view of such problems of the prior art. Even when a system error occurs and control becomes impossible, the present invention focuses on a safety mechanism in which the screw shaft does not collide with the housing.
  • An object of the present invention is to provide an electric actuator that is lighter and more compact and that is improved in reliability by avoiding a collision of 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 rotational force of the electric motor transmitted 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.
  • the ball screw mechanism is rotatable via a support bearing mounted on the housing and cannot move in the axial direction.
  • Mated with A concave groove extending in the axial direction is formed on the inner periphery of the sleeve, and a locking pin is implanted at an end portion of the screw shaft to be engaged with the concave groove.
  • a step portion that can hold the locking pin in the axial direction is formed in the groove of the sleeve.
  • the housing, the electric motor attached to the housing, and the rotational force of the electric motor are transmitted via the motor shaft, and the rotational motion of the electric motor is converted into a linear motion in the axial direction of the drive shaft.
  • a ball screw mechanism, and the ball screw mechanism is rotatably supported via a support bearing mounted on the housing and is not axially movable, and a nut having a helical thread groove formed on the inner periphery thereof;
  • the screw shaft is inserted into the nut through a large number of balls, is integrated with the drive shaft in a coaxial manner, and includes a screw shaft having a spiral screw groove corresponding to the screw groove of the nut formed on the outer periphery.
  • a bag hole for receiving the screw shaft is formed in the housing, and a cylindrical sleeve is fitted to the bag hole in a state of being prevented from rotating, and a concave groove extending in the axial direction is formed on the inner periphery of the sleeve.
  • Screw shaft In the electric actuator in which a locking pin is implanted at the end and engaged with the groove so that the screw shaft cannot be rotated with respect to the housing and can be moved in the axial direction, the locking pin is inserted into the groove of the sleeve. Is formed so that when the reverse input from the output side is loaded, the screw shaft is rotated by this reverse input, and the locking pin moves from the groove to the step.
  • the sleeve is held at an appropriate position of the screw shaft. Even if the reverse input is constantly loaded, the screw shaft can be held at a predetermined position, so that the degree of design freedom is increased and the application range of the electric actuator is expanded.
  • a flat surface is formed on the outer periphery of the sleeve, and a flat surface is formed in the bag hole of the housing corresponding to the flat surface. If the sleeve is fitted in the bag hole in the matched state, the sleeve can be prevented from rotating with respect to the housing.
  • the locking pins are fixed at opposing positions in the circumferential direction of the screw shaft, accommodate these locking pins, and face the inner periphery of the sleeve. If the concave groove is formed, the phase alignment of the screw shaft with respect to the sleeve is simplified, and the number of assembling operations can be reduced.
  • the sleeve is made of sintered metal formed by MIM, even if it has a high workability and a complicated shape, it can be easily and accurately obtained. Can be formed into shapes and dimensions.
  • An electric actuator transmits a rotational force of a housing, an electric motor attached to the housing, and the electric motor via a motor shaft, and the rotational motion of the electric motor in the axial direction of the drive shaft.
  • a ball screw mechanism for converting into linear motion, and this 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, and has a spiral thread groove on the inner periphery.
  • a nut that is inserted into the nut through a large number of balls, is coaxially integrated with the drive shaft, and a helical thread groove corresponding to the thread groove of the nut is formed on the outer periphery.
  • the housing is formed with a bag hole for accommodating the screw shaft, and a cylindrical sleeve is fitted in the bag hole in a state in which the rotation is prevented.
  • a concave groove extending in the axial direction is formed on the inner circumference of the screw shaft, a locking pin is implanted at an end of the screw shaft and engaged with the concave groove, and the screw shaft is not rotatable with respect to the housing.
  • a step portion that can hold the locking pin in the axial direction is formed in the concave groove of the sleeve, so when a reverse input from the output side is loaded, Due to this reverse input, the screw shaft rotates, the locking pin moves from the concave groove and is locked to the stepped portion, and the rotation is blocked by the sleeve, resulting in a locked state, resulting in a system error that makes the control impossible. Even in this case, it is possible to prevent the screw shaft from colliding with the housing, and it is possible to reduce the weight and size by reducing the thickness of the housing, and to provide an electric actuator that improves the reliability by avoiding the collision of the screw shaft Rukoto can.
  • (A) is a cross-sectional view taken along line VIIIa-VIIIa of the electric parking brake drive device of FIG. 7, and (b) is a cross-sectional view taken along line VIIIb-VIIIb.
  • (A)-(c) is an expanded sectional view of the principal part which shows operation
  • An aluminum alloy housing An electric motor attached to the housing, a reduction mechanism that transmits the rotational force of the electric motor via a motor shaft, and the rotational movement of the electric motor is driven via the reduction mechanism
  • a bag hole for accommodating the screw shaft is formed in the housing, and a cylindrical sleeve is fitted to the bag hole while being prevented from rotating.
  • a concave groove extending in the axial direction is formed on the inner periphery of the sleeve, and a locking pin is implanted at the end of the screw shaft and engaged with the concave groove, so that the screw shaft cannot rotate with respect to the housing.
  • the axis of the screw shaft extends in a direction in which the groove width gradually increases in parallel with the groove from one end surface of the groove of the sleeve.
  • a plurality of spiral stepped steps are formed.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of an electric actuator according to the present invention
  • FIG. 2 is a longitudinal sectional view showing a ball screw mechanism of FIG. 1
  • FIG. 3 is a main part showing an intermediate gear portion of FIG.
  • FIG. 4 is an enlarged view of the main part showing the sleeve of FIG. 1
  • FIG. 5A is an explanatory view showing the ball screw mechanism of FIG. 1 being locked
  • FIG. FIG. 6 is a perspective view showing the sleeve and the screw shaft of FIG.
  • the electric actuator 1 includes a cylindrical housing 2, an electric motor M attached to the housing 2, and an intermediate gear meshing with an input gear 3 attached to a motor shaft 3a of the electric motor.
  • a speed reduction mechanism 6 comprising a gear 4 and an output gear 5 meshing with the intermediate gear 4, and a ball screw mechanism for converting the rotational motion of the electric motor M into the linear motion in the axial direction of the drive shaft 7 via the speed reduction mechanism 6. 8 and.
  • 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 M is attached to the first housing 2a, and a through hole 11 and a bag hole 12 for accommodating the screw shaft 10 are formed in the first housing 2a and the second housing 2b. .
  • the motor shaft 3a of the electric motor M is rotatably supported by a rolling bearing 13 composed of a deep groove ball bearing mounted on the second housing 2b. Yes.
  • 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 that will be 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 locking pin 15 is implanted at one end portion (right end portion in the figure) of the drive shaft 7.
  • a cylindrical sleeve 17 described later is fitted into the bag hole 12 of the second housing 2b. Then, a locking pin 15 of the screw shaft 10 is engaged with a concave groove 17a formed in the inner periphery of the sleeve 17 so as to extend in the axial direction, and the screw shaft 10 is supported to be non-rotatable and movable in the axial direction. Has been.
  • 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.
  • the nut 18 is extrapolated to the screw shaft 10, and a helical screw groove 18 a corresponding to the screw groove 10 a of the screw shaft 10 is formed on the inner periphery, and a large number of screws 18 a and 18 a are formed between these nuts 18.
  • a ball 19 is accommodated so as to roll freely.
  • the nut 18 is supported by the first and second housings 2a and 2b via the two support bearings 20 and 20 so as to be rotatable and non-movable in the axial direction.
  • Reference numeral 21 denotes a piece member that constitutes a circulation member by connecting the thread grooves 18a of the nut 18, and the piece member 21 allows an 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 formed in a columnar shape from medium carbon steel such as S55C or case-hardened steel such as SCM415 and SCM420, and the screw groove 10a is formed by rolling rather than machining such as turning.
  • the surface is hardened in the range of 55 to 62 HRC by induction hardening or carburizing hardening. Thereby, mass productivity improves and cost reduction can be achieved.
  • 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 composed of deep groove ball bearings having the same specifications, and thus is loaded from the drive shaft 7 through the thrust load and the output gear 5 described above. Both radial loads can be applied, and confirmation work for preventing misassembly during assembly can be simplified, and assembling workability can be improved.
  • the deep groove ball bearings having the same specifications refer to bearings having the same inner diameter, outer diameter, width dimension, rolling element size, number, bearing internal clearance, and the like.
  • one of the pair of support bearings 20, 20 (the left side in the figure) is mounted on the first housing 2a via a washer 27 made of a ring-shaped elastic member.
  • the washer 27 is formed by press working from an austenitic stainless steel sheet (JIS standard SUS304 system or the like) having high strength and wear resistance, or a cold-rolled steel sheet (JIS standard SPCC system or the like) subjected to rust prevention. 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 intermediate gear 4 constituting the speed reduction mechanism 6 is rotatably supported on a gear shaft 22 implanted in the first and second housings 2 a and 2 b via a rolling bearing 23.
  • 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, availability is high and cost reduction can be achieved.
  • the washer 28 is a flat washer formed by pressing from an austenitic stainless steel plate having high strength and high wear resistance, or a cold-rolled steel plate treated with rust prevention.
  • 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.
  • the 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.
  • flat surfaces 17b and 17b are formed at opposite phases on the outer periphery of the sleeve 17, and at the opposite phases of the bag holes 12 of the second housing 2b corresponding to these flat surfaces 17b and 17b.
  • flat surfaces 12a and 12a are formed.
  • An annular groove 29 is formed at the opening end of the bag hole 12 of the second housing 2b, and a retaining ring 30 is attached to the annular groove 29 so that the flat surfaces 17b and 12a are aligned with each other, and the sleeve 17 Is fitted toward the bottom 12b, and is positioned and fixed in the axial direction in a state in which the sleeve 17 is prevented from rotating with respect to the second housing 2b.
  • the sleeve 17 has a plurality of spiral stepped step portions 31, 32, and 33 formed in the inner periphery from one end face of the concave groove 17 a to the axial center of the screw shaft 10.
  • step portions 31, 32, 33 are formed in a direction in which the groove width increases stepwise in parallel with the concave groove 17 a, and these step portion wall surfaces 31 a, 32 a, 33 a are connected to the screw shaft 10. It is formed along the lead angle of the screw groove 10a, and the step width surfaces 31b, 32b, 33b of the step portions 31, 32, 33 are set wider than the pitch of the screw groove 10a (see FIG. 6). .
  • the “lead” is a length that moves in the axial direction when the screw shaft 10 makes one rotation
  • the “lead angle” means a thread winding coil and one point above it.
  • An angle formed by a plane perpendicular to the passing screw axis 10 and “pitch” refer to a distance between two corresponding points of adjacent threads.
  • pitch lead
  • the screw shaft 10 is supported to the sleeve 17 so as not to rotate and to be movable in the axial direction, but a reverse input from the output side (right direction in the figure) is loaded and the torque of the electric motor is OFF At this time, by this reverse input, the screw shaft 10 rotates clockwise (clockwise direction) as indicated by an arrow in the figure, and the locking pin 15 is locked to the step portion 31. Specifically, it moves along the stepped portion width surface 31b of the stepped portion 31 to abut against the stepped portion wall surface 31a, and the locking pin 15 is fixed in the axial direction.
  • the screw shaft 10 is prevented from rotating by the sleeve 17 and is locked, and even when a system error occurs and control becomes impossible, the screw shaft 10 is prevented from colliding with the second housing 2b.
  • the screw shaft 10 is unlocked, as shown in FIG. 5B, the screw shaft 10 is moved to the left by applying a load greater than the reverse input by operating the shaft in the right direction in the figure from the input side. It rotates (counterclockwise direction), and the locking pin 15 moves upward from the step portion 31. That is, the locking pin 15 of the screw shaft 10 is disengaged from the stepped portion 31 to be unlocked, and the screw shaft 10 is supported so as to be non-rotatable and axially movable with respect to the sleeve 17. To return to the normal state.
  • a plurality of spiral stepped steps 31, 32, 33 are formed on the inner periphery of the sleeve 17, so that the screw shaft 10 can be held at an appropriate position. it can. Thereby, even if the reverse input is constantly loaded, the screw shaft 10 can be held at a predetermined position, and the degree of freedom in design is increased and the application range of the electric actuator is expanded.
  • Locking pins 15, 15 are fixed at opposing positions in the circumferential direction of the screw shaft 10, and the grooves 17 a, 17 a that house the locking pins 15, 15 and prevent the screw shaft 10 from rotating are sleeves 17. Therefore, the phase alignment of the screw shaft 10 with respect to the sleeve 17 is simplified, and the number of assembling operations can be reduced.
  • the sleeve 17 may be formed from medium carbon steel such as S55C or case-hardened steel such as SCM415 or SCM420 by forging or cold forging.
  • the sleeve 17 is made of a metal powder in a plastic form. It consists of a sintered alloy that is adjusted and molded by an injection molding machine. In this injection molding, first, metal powder and a binder made of plastic and wax are kneaded by a kneader, and the kneaded product is granulated into pellets.
  • the granulated pellets are molded by so-called MIM (Metal Injection Molding), which is supplied to a hopper of an injection molding machine and pushed into a mold in a heated and melted state.
  • MIM Metal Injection Molding
  • a sintered alloy formed by such an MIM can be easily and accurately formed into a desired shape / dimension even if it has a high workability and a complicated shape.
  • C carbon
  • Ni nickel
  • Cr chromium
  • Cu copper
  • SCM415 which is 0.04 wt%
  • Mn manganese
  • Mo molecular weight
  • Si silicon
  • Si silicon
  • the rest Fe (iron).
  • the sleeve 17 is performed by adjusting the carburizing quenching and tempering temperatures.
  • the sleeve 17 is made of a material containing 3.0 to 10.0 wt% of Ni and having excellent workability and corrosion resistance (FEN8 of Japanese Powder Metallurgy Industry Standard), or C of 0.07 wt%. %, Cr is 17 wt%, Ni is 4 wt%, Cu is 4 wt%, and the remainder is precipitation hardened stainless steel SUS630 made of Fe or the like. This SUS630 can appropriately increase the surface hardness in the range of 20 to 33 HRC by solution heat treatment, and can ensure toughness and high hardness.
  • the embodiment in the case where there is a reduction gear has been described.
  • the embodiment is not particularly limited to the case in which there is a reduction gear, and can be implemented even when there is no reduction gear.
  • An electric actuator includes a ball screw mechanism that is used in a drive unit of a general industrial electric motor, an automobile, or the like, and that converts a rotational input from an electric motor into a linear motion of a drive shaft via the ball screw mechanism. Applicable to electric actuators.

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

Abstract

L'invention concerne un actionneur électrique pour lequel un poids réduit et une taille plus compacte sont obtenus par la réduction de l'épaisseur d'un carter, et pour lequel une collision de l'arbre fileté avec le carter est évitée, ce qui permet d'améliorer la fiabilité. Dans cet actionneur électrique, un trou borgne 12 destiné à loger un arbre fileté 10 est formé dans un carter, un manchon cylindrique 17 est ajusté dans celui-ci de manière à ne pas pouvoir tourner, des rainures concaves 17a s'étendant dans la direction axiale sont formées dans le manchon 17, des broches de verrouillage 15 sont implantées dans une partie d'extrémité de l'arbre fileté 10 et entrent en prise dans les rainures concaves 17a, et l'arbre fileté 10 est supporté de manière à ne pas pouvoir tourner par rapport au carter, tout en étant mobile dans la direction axiale. De multiples parties étagées en forme de palier en spirale 31, 32, 33 sont formées à partir d'une première surface d'extrémité des rainures concaves 17a du manchon 17, parallèlement aux rainures concaves 17a et dans la direction dans laquelle la largeur de rainure augmente de manière progressive. Par conséquent, lorsqu'une entrée inverse est appliquée depuis le côté sortie, l'arbre fileté 10 tourne, les broches de verrouillage 15 sont verrouillées dans la partie étagée 31 et la rotation est évitée, entraînant un état verrouillé.
PCT/JP2016/066692 2015-06-04 2016-06-03 Actionneur électrique WO2016195104A1 (fr)

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JP2015113733A JP6039748B1 (ja) 2015-06-04 2015-06-04 電動アクチュエータ
JP2015-113733 2015-06-04

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WO2016195104A1 true WO2016195104A1 (fr) 2016-12-08

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Cited By (1)

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CN111828272A (zh) * 2020-08-11 2020-10-27 何景安 单向旋转装置滚珠往复旋转器

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Publication number Priority date Publication date Assignee Title
IT201800020782A1 (it) * 2018-12-21 2020-06-21 Danieli Off Mecc Pressa per l’estrusione diretta di materiale metallico
US11193565B2 (en) * 2019-05-09 2021-12-07 Westcoast Cylinders Inc. Anti-rotation system having replaceable keyway
KR102323132B1 (ko) * 2020-02-19 2021-11-10 박준웅 신발 장식용 원단 및 신발 장식용 원단의 제조 방법

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JP2007333046A (ja) * 2006-06-14 2007-12-27 Ntn Corp 電動アクチュエータ
JP2014037854A (ja) * 2012-08-14 2014-02-27 Ntn Corp 電動リニアアクチュエータ
JP2014080994A (ja) * 2012-10-12 2014-05-08 Ntn Corp 電動リニアアクチュエータ

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JP2007333046A (ja) * 2006-06-14 2007-12-27 Ntn Corp 電動アクチュエータ
JP2014037854A (ja) * 2012-08-14 2014-02-27 Ntn Corp 電動リニアアクチュエータ
JP2014080994A (ja) * 2012-10-12 2014-05-08 Ntn Corp 電動リニアアクチュエータ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111828272A (zh) * 2020-08-11 2020-10-27 何景安 单向旋转装置滚珠往复旋转器

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