WO2012132817A1 - Dispositif d'actionnement en mouvement alternatif et d'entraînement - Google Patents

Dispositif d'actionnement en mouvement alternatif et d'entraînement Download PDF

Info

Publication number
WO2012132817A1
WO2012132817A1 PCT/JP2012/055956 JP2012055956W WO2012132817A1 WO 2012132817 A1 WO2012132817 A1 WO 2012132817A1 JP 2012055956 W JP2012055956 W JP 2012055956W WO 2012132817 A1 WO2012132817 A1 WO 2012132817A1
Authority
WO
WIPO (PCT)
Prior art keywords
peripheral surface
drive
outer peripheral
axis
coil spring
Prior art date
Application number
PCT/JP2012/055956
Other languages
English (en)
Japanese (ja)
Inventor
丹羽　久信
林本　茂
Original Assignee
シーケーディ株式会社
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 シーケーディ株式会社 filed Critical シーケーディ株式会社
Priority to KR1020137000105A priority Critical patent/KR101245479B1/ko
Priority to CN2012800025332A priority patent/CN103140700A/zh
Publication of WO2012132817A1 publication Critical patent/WO2012132817A1/fr

Links

Images

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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • 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
    • F16H25/2427—Elements essential to such mechanisms, e.g. screws, nuts one of the threads being replaced by a wire or stripmetal, e.g. spring
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/025—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a friction shaft

Definitions

  • the present invention relates to an apparatus for reciprocating a driven member.
  • Patent Document 1 there is a device that converts the rotational motion of a rotational drive source into a linear motion.
  • a small-diameter compression coil spring is connected coaxially to the drive shaft of the motor, and the small-diameter compression coil spring is inserted into the large-diameter compression coil spring.
  • a plurality of balls are provided between the small diameter compression coil spring and the large diameter compression coil spring so as to be in contact with the coil springs.
  • the present invention has been made in view of such circumstances, and a main object of the present invention is to increase the force for reciprocating the driven member with a simple configuration in the apparatus for reciprocating the driven member, and to increase the force to be driven in the apparatus. It is to reduce the dimension of the driving member in the axial direction.
  • the present invention employs the following means in order to solve the above problems.
  • 1st invention is a reciprocating drive device, Comprising: The motor which has a drive shaft, The drive member which has an outer peripheral surface coaxial with the said drive shaft, and rotates integrally with the said drive shaft, The outer diameter of the said drive member A driven member that has a spiral portion extending spirally while forming a gap having a wider interval, and is supported so as to be rotatable about the axis of the spiral portion and reciprocally movable in the direction of the axis; The drive member is inserted into the gap of the spiral portion, and the outer peripheral surface of the drive member is in contact with the spiral portion.
  • the drive member having an outer peripheral surface that is coaxial with the drive shaft is rotated integrally with the drive shaft.
  • the spiral portion extends spirally while forming a gap having a wider interval than the outer diameter of the drive member.
  • a drive member is inserted in the clearance gap between spiral parts, and the outer peripheral surface of a drive member is in contact with the spiral part.
  • a motor is arrange
  • the driven member is supported so as to be rotatable about the axis of the spiral portion and to be able to reciprocate in the direction of the axis. For this reason, when the drive member is rotated with the rotation of the drive shaft of the motor and a frictional force acts on the spiral portion from the outer peripheral surface of the drive member, the spiral portion is sequentially sent out. Therefore, the driven member is moved in the direction of the axis while being rotated about the axis of the spiral portion. At this time, the rotation of the drive member (drive shaft) is decelerated at a reduction ratio according to the diameter of the drive member and the diameter of the spiral portion. Therefore, the rotational torque generated in the driven member can be increased more than the rotational torque of the motor, and the force for reciprocating the driven member can be increased with a simple configuration.
  • the second invention is provided with a force applying means for applying a pressing force to the spiral portion and the outer peripheral surface of the drive member, the friction acting between the spiral portion and the outer peripheral surface of the drive member.
  • the power can be increased. Therefore, slippage between the spiral portion and the outer peripheral surface of the drive member can be suppressed, and the rotational torque of the drive member can be efficiently transmitted to the spiral portion.
  • the force applying means includes a rear portion inserted into the gap of the spiral portion on the opposite side of the drive member across a single portion of the spiral portion, It is possible to employ a configuration including a force applying portion that applies force to the rear portion so that a single portion of the spiral portion is pressed against the outer peripheral surface of the driving member. According to such a configuration, the rear portion is inserted on the opposite side of the drive member across the single portion of the spiral portion in the gap of the spiral portion. Then, a force is applied to the rear portion by the applied portion, and a single portion of the spiral portion is pressed against the outer peripheral surface of the drive member. Therefore, the frictional force acting between the spiral portion and the outer peripheral surface of the drive member can be increased.
  • the rear part has a cylindrical surface in contact with the spiral part, and is supported by the force application part so as to be rotatable about the axis of the cylindrical surface. Therefore, when the spiral portion is sequentially sent out by the driving member, the rear portion can be rotated, and the frictional resistance between the spiral portion and the rear portion can be reduced. As a result, the drive energy loss of the motor can be reduced.
  • the force applying means biases the driven member so that the spiral portion is pressed against the outer peripheral surface of the driving member. It is possible to adopt a configuration in which the urging portion is supported so as to be integrally rotatable with the driven member. According to such a configuration, the driven member is urged by the urging portion, and a single spiral portion is pressed against the outer peripheral surface of the driving member. Therefore, the frictional force acting between the spiral portion and the outer peripheral surface of the drive member can be increased. Furthermore, since the urging portion is supported so as to rotate integrally with the driven member, it is possible to prevent the urging portion from being twisted when the driven member is rotated.
  • a reciprocating member coupled to the driven member and supported so as to be capable of reciprocating in the direction of the axis of the spiral portion, and the reciprocating member is the axis of the spiral portion.
  • the driven member is rotated by a predetermined amount of rotation while maintaining a state in which the first restricting portion that restricts movement in a direction from a predetermined position and the spiral portion and the outer peripheral surface of the driving member are in contact with each other.
  • a second restricting portion that restricts rotation more than the above.
  • the reciprocating member is connected to the driven member, and the reciprocating member is supported so as to be reciprocable in the direction of the axis of the spiral portion. Then, the first restricting portion restricts the reciprocating member from moving in the axial direction of the spiral portion from a predetermined position.
  • the driven member connected to the reciprocating member is restricted from moving in the axial direction.
  • the spiral portion moves relative to the drive member, and the spiral portion and the outer peripheral surface of the drive member may be separated.
  • rotation of a drive member cannot be transmitted to a spiral part.
  • the second restricting portion restricts the driven member from rotating more than a predetermined amount of rotation while maintaining the state where the spiral portion and the outer peripheral surface of the driving member are in contact with each other.
  • the rotation of the driven member is regulated by the second regulating unit before the movement of the reciprocating member is regulated by the first regulating unit. For this reason, even if it is a case provided with the 1st control part which controls that a reciprocating member moves from a predetermined position, it can control that a spiral part and the outer peripheral surface of a drive member leave, and drive The rotational torque can be stably transmitted from the member to the spiral portion.
  • the second restricting portion extends along the spiral portion in the direction of the axis of the spiral portion and is provided so as to be integrally rotatable with the driven member.
  • the drive member and the second restricting portion are arranged so that the drive member and the second restricting portion come into contact with each other when the member rotates by the predetermined rotation amount.
  • the second restricting portion extends along the spiral portion in the direction of the axis of the spiral portion and is provided so as to be integrally rotatable with the driven member. Therefore, as the driven member is rotated, the second restricting portion is rotated integrally with the driven member.
  • the driving member and the second restricting portion are arranged so that the driving member and the second restricting portion come into contact when the driven member rotates by the predetermined rotation amount. For this reason, when the driven member moves in the axial direction while rotating, and the driven member rotates by the predetermined rotation amount, the second restricting portion hits the driving member and the rotation of the driven member is restricted. Therefore, with a simple configuration, it is possible to restrict the driven member from rotating more than a predetermined amount of rotation while maintaining the state where the spiral portion and the outer peripheral surface of the driving member are in contact with each other.
  • the driving member is provided with a constricted portion, and the outer peripheral surface of the constricted portion and the single outer peripheral surface of the spiral portion are in line contact.
  • the outer peripheral surface of the drive member is provided with a plurality of teeth, and the portion of the spiral portion that contacts the outer peripheral surface of the drive member includes the teeth of the drive member.
  • a plurality of meshing teeth are provided.
  • the teeth provided on the outer peripheral surface of the driving member mesh with the teeth provided on the portion of the spiral portion that contacts the outer peripheral surface of the driving member. For this reason, the rotational torque of the drive member can be efficiently transmitted to the spiral portion. As a result, the rotational torque generated in the driven member can be further increased, and the force for reciprocating the driven member can be further increased.
  • the axis of the drive shaft that is, the axis of the outer peripheral surface of the drive member, with respect to the circumferential direction of the spiral portion. It will be orthogonal. For this reason, the direction in which the rotational torque of the drive member is transmitted can be matched with the direction in which the spiral portion is sent out. Therefore, the rotational torque of the drive member can be efficiently transmitted to the spiral portion.
  • the spiral portion is formed by a coil spring.
  • the spiral portion can be formed by an inexpensive coil spring, and when the force is applied from the driven member to the object, the elastic force of the coil spring is applied to the object. be able to. Therefore, the force for reciprocating the driven member can be increased while adopting a configuration in which an elastic force is applied from the driven member to the object.
  • the fragmentary sectional view which shows the modification of the piston apparatus of FIG. The enlarged view which shows the drive roller, the support roller, and the modification of the periphery.
  • the present invention is embodied as a piston device that is applied to a belt conveyor or the like and stops a conveyed work by reciprocating driving of the piston.
  • FIG. 1 is a partial cross-sectional view showing a piston device 10 of the present embodiment.
  • the piston device 10 includes a body 11, a stepping motor 20, a cylinder 30, a piston 40, a coil spring 50, and the like.
  • the vertical direction in FIG. 1 coincides with the vertical direction when the piston device 10 is installed, and the piston device 10 reciprocates the piston 40 in the vertical direction.
  • the body 11 is formed in a cylindrical shape with a metal material or the like.
  • an opening 12 is provided at a side near one end in the axial direction, and a cylinder 30 is attached to the other end in the axial direction.
  • a stepping motor 20 (motor) is attached to the opening 12 via a bracket 21 having an opening 21a.
  • the motor 20 has a drive shaft 22, and the motor 20 is attached to the body 11 so that the axis of the body 11 and the axis of the drive shaft 22 are perpendicular to each other.
  • the drive shaft 22 is inserted from the outside to the inside of the body 11 through the opening 21 a of the bracket 21 and the opening 12 of the body 11.
  • a driving roller 23 is attached to the tip of the driving shaft 22.
  • the drive roller 23 (drive member) is formed in a columnar shape and rotates integrally with the drive shaft 22.
  • the axis of the drive roller 23 coincides with the axis of the drive shaft 22.
  • the drive roller 23 has an outer peripheral surface that is coaxial with the drive shaft 22.
  • the cylinder 30 is formed in a cylindrical shape with a metal material or the like.
  • the axis of the cylinder 30 coincides with the axis of the body 11.
  • a cylindrical piston 40 is inserted into the cylinder 30.
  • the piston 40 (reciprocating member) is supported by the slide bearing 31 so as to be able to reciprocate in the axial direction of the body 11.
  • a flat surface portion 40 a is provided on the outer peripheral surface of the piston 40 so as to extend in the axial direction. That is, in the piston 40, the cross-sectional shape of the portion where the flat surface portion 40a is provided is a “D” shape.
  • a detent member 32 having a through hole having a cross-sectional shape of “D” is fitted to the outer periphery of the portion where the flat portion 40 a is provided.
  • the anti-rotation member 32 is fixed to the upper end of the cylinder 30. Therefore, the piston 40 can reciprocate in the axial direction in a state where the rotation about the axis is restricted.
  • a holding portion 51 of a coil spring 50 is fastened with a bolt 41 to a lower end portion of the piston 40 (an end portion closer to the motor 20) via a thrust bearing 33 and a radial bearing 34.
  • the holding part 51 is formed in a disc shape, and a guide ring 52 is provided on the outer periphery thereof.
  • the outer peripheral surface of the guide ring 52 can slide smoothly with the inner peripheral surface of the body 11. For this reason, the holding part 51 is supported by the piston 40 so as to be rotatable about the axis of the piston 40 via the guide ring 52.
  • the holding portion 51 is guided by the guide ring 52 in the axial direction of the body 11 as the piston 40 reciprocates. At that time, the axial load acting between the piston 40 and the holding portion 51 is received by the thrust bearing 33.
  • a magnet 53 for detecting the position of the holding unit 51 by a sensor or the like is provided on the outer periphery of the holding unit 51.
  • the coil spring 50 is attached to the lower part of the holding part 51 (the part opposite to the piston 40).
  • the upper end (one end) of the coil spring 50 (driven member) is fixed to the lower portion of the holding portion 51 by caulking by the holding portion 51.
  • the axis of the coil spring 50 coincides with the axis of the body 11. For this reason, the coil spring 50 is supported via the holding portion 51 so as to be rotatable about the axis of the coil and to be able to reciprocate in the direction of the axis.
  • the coil (spiral portion) of the coil spring 50 extends spirally while forming a gap having a larger interval than the outer diameter of the distal end portion of the drive roller 23. That is, the distance between the coil wire 50 a (single) and the wire 50 a (single) is larger than the outer diameter of the tip of the drive roller 23. And the front-end
  • the weight of the piston 40, the weight of the holding portion 51, the weight of the coil spring 50, and the like act downward.
  • the strand 50a of the coil spring 50 is in contact with the upper surface (outer peripheral surface) of the drive roller 23. That is, the coil spring 50 is supported by the drive roller 23. In other words, the tip of the drive roller 23 is inserted into the gap of the coil so that the outer peripheral surface of the drive roller 23 is in contact with the wire 50a of the coil spring 50. And the motor 20 is attached to the body 11 so that it may be in such a state.
  • the axis of the drive shaft 22 of the motor 20 is perpendicular to the axis of the coil spring 50.
  • FIG. 2 is an enlarged view showing the driving roller and the supporting roller and their periphery
  • FIG. 2A is a cross-sectional view taken along the line AA of FIG.
  • the drive roller 23 is made of steel or the like, and includes a tip portion 25, a cylindrical portion 24, and a flange portion 26 whose axes are aligned with each other.
  • a cylindrical tip portion 25 is provided at one end of the cylindrical cylindrical portion 24, and a flange-like flange portion 26 is provided at the other end.
  • the drive shaft 22 of the motor 20 is press-fitted inside the cylindrical portion 24 and the flange portion 26.
  • the distal end portion 25 is provided with a constricted portion 25a, and the outer diameter of the constricted portion 25a becomes smaller as it approaches the middle of the distal end portion 25 in the axial direction.
  • the radius of curvature of the constricted portion 25 a is equal to the radius of curvature of the outer peripheral surface of the wire 50 a in the coil spring 50. For this reason, the outer peripheral surface of the constricted part 25a and the outer peripheral surface of the strand 50a are in line contact.
  • a roller holder 60 is attached to the outer periphery of the driving roller 23.
  • the roller holder 60 (forced portion) is formed in an elliptical plate shape, and two through holes are formed side by side in the major axis direction. Radial bearings 61 and 62 are attached to the inner circumferences of the two through holes, respectively.
  • the drive roller 23 and the support roller 63 are inserted into the radial bearings 61 and 62, respectively. For this reason, the drive roller 23 and the support roller 63 are rotatably supported by the roller holder 60.
  • the flange portion 26 of the driving roller 23 is in contact with the end face of the radial bearing 61, and the roller holder 60 is prevented from coming off in the direction of the flange portion 26. Disengagement of the roller holder 60 in the direction of the element wire 50a of the coil spring 50 is suppressed by engagement of the constricted portion 25a of the drive roller 23 with the element wire 50a.
  • the support roller 63 (rear part) is formed in a columnar shape with steel or the like, and includes a columnar part 64 and a tip part 65 whose axes are aligned with each other.
  • the distal end portion 65 is provided with a constricted portion 65 a, and the outer diameter of the constricted portion 65 a becomes smaller as it approaches the middle in the axial direction of the distal end portion 65.
  • the radius of curvature of the constricted portion 65a is equal to the radius of curvature of the outer peripheral surface of the wire 50a in the coil spring 50. For this reason, the outer peripheral surface (cylindrical surface) of the narrow part 65a and the outer peripheral surface of the strand 50a are in line contact.
  • Two grooves are provided on the outer periphery of the cylindrical portion 64 at a distance slightly wider than the thickness of the roller holder 60 (radial bearing 62), and a retaining ring 66 is fitted in each of the grooves. Retaining rings 66 are in contact with both end faces of the radial bearing 62, and the support roller 63 is prevented from coming off the roller holder 60 in the axial direction. The engagement of the constricted portion 65a of the support roller 63 with the wire 50a of the coil spring 50 also prevents the support roller 63 from coming off from the roller holder 60 in the axial direction.
  • the diameter of the tip 65 of the support roller 63 is smaller than the diameter of the tip 25 of the drive roller 23. And the front-end
  • tip part 65 of the support roller 63 is inserted in the clearance gap between the strand 50a of a coil, and the strand 50a. That is, the support roller 63 is inserted into the gap between the coils on the opposite side of the drive roller 23 with the strand 50a (single) of the coil spring 50 interposed therebetween.
  • the axis of the drive roller 23 and the axis of the support roller 63 are parallel, and the axis of the drive roller 23 and the axis of the support roller 63 are perpendicular to the axis of the strand 50a with which these rollers 23 and 63 are in contact. Yes.
  • a notch 67 is provided between the radial bearing 61 and the radial bearing 62 in the roller holder 60.
  • the notch 67 passes through the roller holder 60 in the thickness direction of the roller holder 60.
  • the roller holder 60 is made of a metal material or the like having a relatively large elasticity, and generates an elastic force in a direction in which the width of the notch 67 is narrowed, that is, in a direction in which the radial bearings 61 and 62 are brought close to each other.
  • the outer peripheral surface of the drive roller 23 and the outer peripheral surface of the support roller 63 are It is pressed against the outer peripheral surface of the strand 50a.
  • the outer peripheral surface of the strand 50 a is pressed against the outer peripheral surface of the constricted portion 25 a of the drive roller 23.
  • the roller holder 60, the radial bearings 61 and 62, and the support roller 63 constitute a force applying unit that applies a pressing force to the element wire 50 a of the coil spring 50 and the outer peripheral surface of the drive roller 23.
  • the drive roller 23 attached to the drive shaft 22 is rotated integrally with the drive shaft 22.
  • the strand 50a of the coil spring 50 is pressed against the outer peripheral surface of the drive roller 23 by the weight of the piston 40, the weight of the holding portion 51, the own weight of the coil spring 50, and the like.
  • the strand 50 a is pushed toward the driving roller 23 by the support roller 63, and the outer circumferential surface of the strand 50 a is pushed against the outer circumferential surface of the constricted portion 25 a of the driving roller 23. It has been applied.
  • the support roller 63 is rotatably supported by the roller holder 60 via the radial bearing 62, the support roller 63 is rotated by the strand 50a, and between the strand 50a and the support roller 63. The acting frictional force is reduced.
  • the coil spring 50 is supported so that it can rotate about the axis of the coil and can reciprocate in the direction of the axis. For this reason, when the strand 50a of the coil spring 50 is sequentially sent out, the coil spring 50 is moved upward (in the direction of the cylinder 30) along the axis while being rotated about the axis of the coil. At this time, the rotation of the drive roller 23 (drive shaft 22) is decelerated at a reduction ratio according to the diameter of the tip 25 of the drive roller 23 and the diameter of the coil. For example, if the diameter of the coil is 6 times the diameter of the drive roller 23, the drive spring 23 rotates 6 times so that the coil spring 50 rotates once. In this case, the rotation reduction ratio is 6. When the coil spring 50 rotates once, the coil spring 50 is moved in the axial direction by one pitch of the coil. The amount of movement of the coil spring 50 is controlled by the number of rotation steps (rotation amount) of the motor 20.
  • the drive roller 23 having an outer peripheral surface coaxial with the drive shaft 22 is rotated integrally with the drive shaft 22.
  • the coil of the coil spring 50 extends spirally while forming a gap having a larger interval than the outer diameter of the distal end portion 25 of the drive roller 23.
  • tip part 25 of the driving roller 23 is inserted in the clearance gap between coils, and the outer peripheral surface of the driving roller 23 is in contact with the coil strand 50a.
  • the motor 20 is arranged not in the axial direction of the coil but in the radial direction, and the dimension of the coil spring 50 in the piston device 10 in the axial direction can be reduced.
  • the coil spring 50 is supported via the holding part 51 so as to be rotatable about the axis of the coil and to be able to reciprocate in the direction of the axis. For this reason, when the drive roller 23 is rotated with the rotation of the drive shaft 22 of the motor 20 and a frictional force acts on the coil from the outer peripheral surface of the drive roller 23, the coil strands 50a are sequentially sent out. Therefore, the coil spring 50 is moved in the direction of the axis while being rotated about the axis of the coil. At this time, the rotation of the drive roller 23 (drive shaft 22) is decelerated at a reduction ratio according to the diameter of the tip 25 of the drive roller 23 and the diameter of the coil. Therefore, the rotational torque generated in the coil spring 50 can be increased more than the rotational torque of the motor 20, and the force for reciprocating the coil spring 50 and consequently the piston 40 can be increased with a simple configuration.
  • the piston device 10 is provided with a force applying unit that applies a pressing force to the outer peripheral surface of the coil and the driving roller 23, so that the frictional force that acts between the coil and the outer peripheral surface of the driving roller 23 is increased. Can do. Therefore, slippage between the coil and the outer peripheral surface of the drive roller 23 can be suppressed, and the rotational torque of the drive roller 23 can be efficiently transmitted to the coil spring 50.
  • the force applying means includes a support roller 63 inserted in a coil gap on the opposite side of the drive roller 23 across the coil wire 50a, and the coil wire 50a on the outer peripheral surface of the drive roller 23.
  • a roller holder 60 that applies force to the support roller 63 so as to be pressed against the roller is provided. According to such a configuration, a force is applied to the support roller 63 by the roller holder 60, and the coil wire 50 a is pressed against the outer peripheral surface of the drive roller 23.
  • the support roller 63 has a constricted portion 65a (cylindrical surface) in contact with the coil wire 50a, and is supported by the roller holder 60 and the radial bearing 62 so as to be rotatable about the axis of the constricted portion 65a. Yes. Therefore, the support roller 63 can be rotated when the coil wire 50a is sequentially sent out by the drive roller 23, and the frictional resistance between the coil wire 50a and the support roller 63 can be reduced. As a result, the drive energy loss of the motor 20 can be reduced. Furthermore, since the outer peripheral surface of the constricted portion 65a and the outer peripheral surface of the strand 50a are in line contact, the contact pressure can be reduced, and a larger force is applied from the support roller 63 to the strand 50a. Is possible.
  • the axis of the drive shaft 22 Since the axis of the coil spring 50 and the axis of the drive shaft 22 are orthogonal, the axis of the drive shaft 22, that is, the axis of the outer peripheral surface of the drive roller 23 is orthogonal to the circumferential direction of the coil. For this reason, the direction in which the rotational torque of the drive roller 23 is transmitted and the direction in which the coil wire 50a is sent out can be matched. Therefore, the rotational torque of the drive roller 23 can be efficiently transmitted to the coil spring 50.
  • a coil spring 50 is employed as a spiral portion that is sequentially sent out by the drive roller 23.
  • the spiral portion can be formed by the inexpensive coil spring 50, and when the force is applied from the coil spring 50 to the object, the elastic force of the coil spring 50 is applied to the object. Can be. Therefore, the force for reciprocating the coil spring 50 can be increased while adopting a configuration in which an elastic force is applied from the coil spring 50 to the object.
  • FIG. 3 is a partial cross-sectional view showing a modification of the piston device 10 of FIG.
  • a flange portion 142 is provided at the upper end of the piston 140 (the end opposite to the coil spring 50).
  • the flange portion 142 comes into contact with the rotation preventing member 32.
  • the rotation prevention member 32 and the flange portion 142 restrict the piston 140 from moving downward from the initial position.
  • the holding portion 51 is provided with a pin 154 (second restricting portion) extending along the inner circumference of the coil spring 50 in the axial direction of the coil spring 50 so as to be able to rotate integrally with the coil spring 50.
  • the drive roller 123 is formed longer than the drive roller 23 of FIG.
  • the drive roller 123 and the pin 154 are arranged so that the drive roller 123 and the pin 154 come into contact when the coil spring 50 is lowered from above to the initial position (when the coil spring 50 is rotated by a predetermined rotation amount).
  • the coil spring 50 coupled to the piston 140 moves in the axial direction.
  • the strand 50a of the coil spring 50 moves with respect to the drive roller 123, and there is a possibility that the strand 50a and the outer peripheral surface of the drive roller 123 are separated.
  • rotation of the drive roller 123 cannot be transmitted to the strand 50a.
  • the pin 154 restricts the coil spring 50 from rotating from the initial position while maintaining the state in which the wire 50a and the outer peripheral surface of the driving roller 123 are in contact with each other. That is, the rotation of the coil spring 50 is restricted by the pin 154 before the movement of the piston 140 is restricted by the rotation preventing member 32 and the flange portion 142. For this reason, even if it is a case where the rotation prevention member 32 and the flange part 142 which control that the piston 140 moves from an initial position are provided, the strand 50a of the coil spring 50 and the outer peripheral surface of the drive roller 123 leave
  • FIG. 4 is an enlarged view showing a modified example of the driving roller 223 and the supporting roller 265 and their surroundings.
  • the force applying means for applying the pressing force to the outer peripheral surface of the coil and the driving roller 223 can be configured as follows.
  • the force applying means is such that the support roller 63 inserted in the coil gap on the opposite side of the drive roller 223 across the coil strand 50a and the coil strand 50a are pressed against the outer peripheral surface of the drive roller 223.
  • the roller holder 260 for applying a force to the support roller 63 and the torsion spring 268 are provided.
  • the driving roller 223 and the supporting roller 265 are rotatably supported by a roller holder 260.
  • the torsion spring 268 is provided on the outer periphery of the drive roller 223. One end of the torsion spring 268 is inserted into a hole 269 provided in the roller holder 260, and the other end is applied to the opening 21 a of the bracket 21.
  • the torsion spring 268 applies a rotational force to the roller holder 260 so as to rotate the roller holder 260 clockwise around the drive roller 223. Also with such a configuration, a force is applied to the support roller 63 by the roller holder 260 and the torsion spring 268, and the coil wire 50 a is pressed against the outer peripheral surface of the drive roller 223.
  • FIG. 5 is an enlarged view showing another modified example of the driving roller 23 and the supporting roller 63 and their surroundings.
  • a plurality of support rollers 63 may be inserted into the gap between the coils on the opposite side of the drive roller 23 across the coil wire 50a.
  • two support rollers 63 are provided at intervals. Even in this case, by adopting a configuration according to the force applying means shown in FIG. 2 or a structure according to the force applying means shown in FIG. It can be pressed against the surface.
  • a sliding member that slides with the coil wire 50a may be provided.
  • FIG. 6 is a partial cross-sectional view showing another modification of the piston device 10 of FIG.
  • the coil spring 50 is moved downward (in the direction opposite to the cylinder 30) so that the wire 50a of the coil spring 50 is pressed against the outer peripheral surface of the drive roller 23.
  • a tension spring 360 biases the coil spring 50 is supported, and the tension spring 360 is supported so as to rotate integrally with the coil spring 50.
  • Both ends of the rotating pin 361 are slidably engaged with an annular groove 362 provided on the inner peripheral surface of the lower end of the body 11 (the end opposite to the cylinder 30). For this reason, the rotation pin 361 is supported rotatably about the axis of the coil spring 50 in a state where movement of the coil spring 50 in the axial direction is restricted.
  • One end of the tension spring 360 is fixed to the holding portion 51 via a bolt 341, and the other end is centered on the axis of the tension spring 360 (the axis of the coil spring 50) by the body 11 via the rotation pin 361. It is rotatably supported.
  • the coil spring 50 is biased downward by the tension spring 360, and the element wire 50 a (single) of the coil spring 50 is pressed against the outer peripheral surface of the drive roller 23. Therefore, the frictional force acting between the strand 50a and the outer peripheral surface of the drive roller 23 can be increased. Further, since the tension spring 360 is supported by the body 11 via the rotation pin 361 so as to be integrally rotatable with the coil spring 50, the coil spring 50 is twisted when the coil spring 50 is rotated. Can be suppressed. Instead of the tension spring 360, a tension rubber formed of elastic rubber or the like can be used.
  • the drive roller 23 can be formed of a magnet so that the coil wire 50a can be pressed against the outer peripheral surface of the drive roller 23.
  • FIG. 7 is a partial cross-sectional view showing the hand device 410 of the present embodiment.
  • the hand device 410 includes a body 411, a stepping motor 420, a rod 440, a coil spring 450, a grip piece 444A, and the like.
  • the vertical direction in FIG. 7 coincides with the vertical direction when the hand device 410 is attached in the basic posture of the robot. In this state, the hand device 410 reciprocates the rod 440 in the horizontal direction.
  • the body 411 is made of a metal material or the like and has a bottomed cylindrical shape.
  • An opening 412 is provided on the side of the body 411, and a gripping mechanism 470 is attached to one end of the body 411 in the axial direction.
  • a stepping motor 420 (motor) is attached to the opening 412 via a bracket 421 having an opening 421a.
  • the motor 420 has a drive shaft 422, and the motor 420 is attached to the body 411 so that the axis of the body 411 and the axis of the drive shaft 422 are perpendicular to each other.
  • the drive shaft 422 is inserted from the outside to the inside of the body 411 through the opening 421a of the bracket 421 and the opening 412 of the body 411.
  • a driving roller 423 is attached to the tip of the driving shaft 422.
  • the drive roller 423 (drive member) is formed in a columnar shape and rotates integrally with the drive shaft 422.
  • the axis of the drive roller 423 coincides with the axis of the drive shaft 422.
  • the drive roller 423 has an outer peripheral surface that is coaxial with the drive shaft 422.
  • a through hole 414 is provided at the center of one end of the body 411 in the axial direction.
  • the center of the through hole 414 coincides with the axis of the body 411.
  • a cylindrical actuating member 441 is inserted into the through hole 414.
  • the operating member 441 (reciprocating member) is supported by the body 411 via the sliding bearing 435 so as to be reciprocable in the axial direction of the body 411.
  • the axis of the operating member 441 coincides with the axis of the body 411.
  • a key groove 441a is provided on the outer peripheral surface of the operating member 441 so as to extend in the axial direction thereof.
  • the tip of a pin 432 is inserted into the key groove 441a through a through hole provided in the body 411. Therefore, the actuating member 441 can reciprocate in the axial direction in a state where rotation about the axis is restricted.
  • a rod 440 is fixed to the end of the operating member 441 on the motor 420 side.
  • the rod 440 is formed in a columnar shape, and annular metal bushes 433 and 434 are provided on the outer circumferences of both ends thereof.
  • a flange 440a is provided at the end of the rod 440 where the metal bush 434 is provided. The flange 440a is in contact with the side surface of the metal bush 434, and the flange 440a prevents the metal bush 434 from coming off from the rod 440.
  • a holding portion 451 of a coil spring 450 is provided between the metal bushes 433 and 434 on the outer periphery of the rod 440.
  • the holding portion 451 is formed in a cylindrical shape with a metal material or the like, and a flange portion 451a is provided at one end thereof.
  • a slight gap (clearance) is provided between the outer peripheral surface of the rod 440 and the inner peripheral surface of the holding portion 451.
  • the outer peripheral surface of the flange portion 451a is slidably in contact with the inner peripheral surface of the body 411.
  • Both end portions in the axial direction of the holding portion 451 are rotatably supported by the rod 440 via the metal bushes 433 and 434.
  • the axis of the holding portion 451 and the axis of the rod 440 coincide with the axis of the body 411 and the axis of the operating member 441. Further, part of both end faces in the axial direction of the holding portion 451 is in contact with the end faces of the metal bushes 433 and 434, respectively. For this reason, the axial load acting between the rod 440 and the holding portion 451 is received by the metal bushes 433 and 434.
  • the coil spring 450 is attached to the flange portion 451a of the holding portion 451.
  • One end of the coil spring 450 (driven member) is fixed to the end portion of the holding portion 451 by caulking one end by the flange portion 451a.
  • the axis of the coil spring 450 coincides with the axis of the body 411.
  • the coil spring 450 is supported by the rod 440 via the holding portion 451 so as to be rotatable about the axis of the coil spring 450.
  • the coil spring 450 is supported by the body 411 through the rod 440, the actuating member 441, and the sliding bearing 435 so as to be reciprocally movable in the axial direction.
  • the flange portion 451 a of the holding portion 451 is guided in the axial direction by the inner peripheral surface of the body 411.
  • the coil (spiral portion) of the coil spring 450 extends spirally while forming a gap having a wider interval than the outer diameter of the tip end portion 425 of the drive roller 423. That is, the distance between the coil wire 450 a (single) and the wire 450 a (single) is wider than the outer diameter of the tip 425 of the drive roller 423. And the front-end
  • the element wire 450a of the coil spring 450 is in contact with the right side surface (outer peripheral surface) of the drive roller 423 in FIG. That is, the tip end portion 425 of the drive roller 423 is inserted into the gap of the coil so that the outer peripheral surface of the drive roller 423 is in contact with the element wire 450a of the coil spring 450.
  • the motor 420 is attached to the body 411 so that it may be in such a state.
  • the axis of the drive shaft 422 of the motor 420 is perpendicular to the axis of the coil spring 450.
  • FIG. 8 is a partial cross-sectional view of the gripping mechanism 470 as viewed from above.
  • the gripping mechanism 470 includes cam members 443A and 443B, a torsion spring 446, gripping pieces 444A and 444B, and the like.
  • the operating member 441 is inserted into the gripping mechanism 470.
  • the body 411 is provided with a pair of support pins 447 symmetrically across the operating member 441.
  • the body 411 is provided with a pair of detent pins 445 symmetrically with the operation member 441 interposed therebetween.
  • the axis of the support pin 447 and the axis of the detent pin 445 are perpendicular to the axis of the actuating member 441.
  • the axis of the support pin 447 and the axis of the detent pin 445 are parallel to each other.
  • the gripping pieces 444A and 444B are supported by the body 411 so as to be slidable in a direction perpendicular to both the axis of the operating member 441 and the axis of the detent pin 445 (support pin 447). That is, the gripping pieces 444A and 444B slide so as to approach and separate from each other.
  • the gripping mechanism 470 grips the workpiece by sandwiching the workpiece between the gripping piece 444A and the gripping piece 444B.
  • the gripping pieces 444A and 444B are provided with action pins 448 in parallel with the support pins 447 and the rotation prevention pins 445, respectively.
  • the cam members 443A and 443B are rotatably supported by the support pins 447, respectively.
  • the actuating member 441 is provided with a coupling pin 442 in parallel with the support pin 447, the detent pin 445, and the action pin 448.
  • the cam members 443A and 443B are also rotatably supported by the coupling pins 442, respectively.
  • the cam members 443A and 443B are provided with notches 449, respectively.
  • An action pin 448 is slidably engaged with the notch 449.
  • a torsion spring 446 is attached to each support pin 447. One end of the torsion spring 446 is in contact with the detent pin 445, and the other end is in contact with the action pin 448. Each torsion spring 446 generates a force that rotates the action pin 448 around the support pin 447. Accordingly, the grip pieces 444A and 444B are urged by the respective torsion springs 446 in a direction away from each other. At this time, a force that moves the operating member 441 in the direction of the gripping pieces 444A and 444B acts on the operating member 441.
  • a force applying means for applying a pressing force to each other is configured on the outer peripheral surfaces of the wire 450 a and the driving roller 423.
  • FIG. 9 is an enlarged view showing the drive roller 423 and the rotation stopper 454 and the periphery thereof.
  • FIG. 4A is a view of the coil spring 450 and the holding portion 451 viewed from the axial direction
  • FIG. 4B is a view of the coil spring 450 and the holding portion 451 viewed from the axial direction of the drive roller 423. is there.
  • the flange portion 451a of the holding portion 451 is provided with a rotation preventing portion 454 (second restricting portion) extending along the outer periphery of the coil spring 450 in the axial direction of the coil spring 450 so as to be integrally rotatable with the coil spring 450. .
  • the front end 425 of the drive roller 423 protrudes to the inner periphery of the coil spring 450. Then, when the coil spring 450 is moved from the right side in FIG. 9 to the initial position (when the coil spring 450 is rotated by a predetermined rotation amount), the drive roller 423 and the anti-rotation portion are arranged so that the drive roller 423 and the anti-rotation portion 454 come into contact 454 is arranged.
  • FIG. 7 shows a state where the coil spring 450 is in the initial position.
  • the coil spring 450 may rotate around the axis after stopping the movement from right to left in FIG.
  • the wire 450a of the coil spring 450 moves relative to the drive roller 423, and there is a possibility that the wire 450a and the outer peripheral surface of the tip end portion 425 of the drive roller 423 are separated.
  • the rotational torque of the drive roller 423 cannot be transmitted to the strand 450a.
  • the rotation preventing portion 454 restricts the coil spring 450 from rotating from the initial position while maintaining the state in which the wire 450a and the outer peripheral surface of the driving roller 423 are in contact with each other. For this reason, it can suppress that the strand 450a of the coil spring 450 and the outer peripheral surface of the drive roller 423 can separate, and can transmit rotational torque from the drive roller 423 to the strand 450a stably.
  • the drive roller 423 attached to the drive shaft 422 is rotated integrally with the drive shaft 422.
  • the outer peripheral surface of the wire 450 a of the coil spring 450 is pressed against the outer peripheral surface of the tip end portion 425 of the drive roller 423. Therefore, a relatively large frictional force acts between the drive roller 423 and the wire 450a of the coil spring 450, and the wire 450a of the coil spring 450 is sequentially sent out by the drive roller 423.
  • the coil spring 450 is supported so that it can rotate about the axis of the coil and can reciprocate in the direction of the axis. For this reason, when the wire 450a of the coil spring 450 is sequentially sent out, the coil spring 450 is rotated about the axis of the coil and moved to the opposite side of the gripping mechanism 470 along the axis. At this time, the rotation of the drive roller 423 (drive shaft 422) is decelerated at a reduction ratio according to the diameter of the tip end portion 425 of the drive roller 423 and the diameter of the coil. When the coil spring 450 rotates once, the coil spring 450 is moved in the axial direction by one pitch of the coil. The amount of movement of the coil spring 450 is controlled by the number of rotation steps (rotation amount) of the motor 420.
  • the operation member 441 When the coil spring 450 is moved to the side opposite to the gripping mechanism 470, the operating member 441 connected to the coil spring 450 via the holding portion 451 and the rod 440 is moved to the motor 420 side. At this time, since the rotation of the actuating member 441 is restricted by the key groove 441 a and the pin 432, the coil spring 450 and the holding portion 451 rotate with respect to the actuating member 441 and the rod 440. Then, the operation member 441 is moved to the side away from the gripping mechanism 470 as shown in FIG. 10 in a state where the rotation around the axis is restricted.
  • the cam members 443A and 443B are rotated about the support pins 447, respectively, and the gripping pieces 444A and 444B are slid in the approaching direction via the action pins 448. Accordingly, the work is sandwiched between the gripping piece 444A and the gripping piece 444B, and the work is gripped by the gripping mechanism 470.
  • the motor 420 is rotated in the opposite direction to that when the workpiece is gripped.
  • the strand 450a of the coil spring 450 is sequentially sent out in the reverse direction to the time of holding
  • the coil spring 450 is moved toward the gripping mechanism 470 along the axis while being rotated about the axis of the coil. As a result, as shown in FIG. 7, the coil spring 450 is moved to the initial position.
  • the motor 420 is disposed not in the coil axial direction but in the radial direction with respect to the coil spring 450, and the axial dimension of the coil spring 450 in the hand device 410 can be reduced. For this reason, when the hand device 410 is attached to the wrist of the articulated robot, the rotational moment due to the weight of the hand device 410 acting on the wrist of the robot can be reduced.
  • the hand device 410 includes a force applying unit that exerts a pressing force on the outer peripheral surface of the coil and the driving roller 423, the friction force acting between the coil and the outer peripheral surface of the driving roller 423 is increased. Can do. Therefore, slippage between the coil and the outer peripheral surface of the drive roller 423 can be suppressed, and the rotational torque of the drive roller 423 can be efficiently transmitted to the coil spring 450.
  • the force applying means is configured by adding a torsion spring 446 and a detent pin 445 to the gripping mechanism 470. For this reason, the change location of the gripping mechanism 470 can be reduced, and the configuration in the vicinity of the drive roller 423 can be simplified as compared with the first embodiment.
  • a coil spring 450 is adopted as the spiral portion sequentially fed by the drive roller 423. According to such a configuration, the spiral portion can be formed by the inexpensive coil spring 450. Furthermore, when the workpiece is gripped by the gripping mechanism 470, the state in which the elastic force of the coil spring 450 is applied to the workpiece can be maintained. Therefore, it is possible to increase the force for reciprocating the coil spring 450 while adopting a configuration capable of elastically gripping the workpiece.
  • the second embodiment can be implemented with the following modifications.
  • an anti-rotation pin 554 can be employed. That is, the flange portion 451a of the holding portion 451 is provided with a detent pin 554 (second restricting portion) that extends along the outer periphery of the coil spring 450 in the axial direction of the coil spring 450 so as to be integrally rotatable with the coil spring 450. ing. Even in such a configuration, the rotation of the coil spring 450 from the initial position is restricted by the non-rotating pin 554 while maintaining the state where the element wire 450a of the coil spring 450 and the outer peripheral surface of the drive roller 423 are in contact with each other. Can do.
  • the present invention is not limited to the first and second embodiments, and can be implemented as follows, for example.
  • the spiral member 650 can be formed of a metal material, resin, or the like.
  • the teeth 623a provided on the outer peripheral surface of the drive gear 623 are meshed with the teeth 651a provided on the portion of the spiral portion 651 that is in contact with the outer peripheral surface of the drive gear 623. For this reason, the rotational torque of the drive gear 623 can be efficiently transmitted to the spiral portion 651. As a result, the rotational torque generated in the spiral member 650 (driven member) can be further increased, and the force for reciprocating the spiral member 650 can be further increased.
  • a plurality of teeth 651 a that mesh with the teeth 623 a of the drive gear 623 can also be provided in portions of the coil springs 50 and 450 that are in contact with the outer peripheral surface of the drive gear 623. At this time, a plurality of teeth that mesh with the teeth 623 a of the drive gear 623 can be provided on the entire circumference of the strands 50 a and 450 a of the coil springs 50 and 450.
  • the axes of the drive shafts 22 and 422 of the motors 20 and 420 are perpendicular to the axis of the coil springs 50 and 450.
  • the drive shafts 22 and 422 of the motors 20 and 420 are used. Can be inclined with respect to the axis of the coil springs 50 and 450.
  • Asynchronous motors may be employed in place of the stepping motors 20 and 420 (synchronous motors).

Landscapes

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

Abstract

L'invention concerne un dispositif pour actionner d'un mouvement alternatif et entraîner un élément à faire fonctionner qui est configuré de telle manière qu'on augmente une force pour actionner d'un mouvement alternatif et entraîner un élément à faire fonctionner par une configuration simple et que la dimension de l'élément à faire fonctionner, qui est prévue dans le dispositif, mesurée dans la direction axiale, est réduite. Un dispositif à piston (10) est pourvu d'un moteur électrique (20) qui comporte un arbre d'entraînement (22) et un rouleau d'entraînement (23) qui comporte une surface périphérique extérieure coaxiale avec l'arbre d'entraînement (22) et qui tourne d'une seule pièce avec l'arbre d'entraînement (22). Le dispositif à piston (10) est pourvu d'un ressort hélicoïdal (50) soutenu de telle sorte que ce ressort hélicoïdal (50) peut tourner autour de l'axe de la spirale et peut avoir un mouvement de va-et-vient dans la direction de l'axe. La spirale du ressort hélicoïdal (50) s'étend en hélice en laissant un espace supérieur au diamètre extérieur de la section terminale avant du rouleau d'entraînement (23). Le rouleau d'entraînement (23) est introduit dans l'espace laissé par la spirale et la surface périphérique extérieure du rouleau d'entraînement (23) est en contact avec le fil (50a) de la spirale.
PCT/JP2012/055956 2011-03-25 2012-03-08 Dispositif d'actionnement en mouvement alternatif et d'entraînement WO2012132817A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020137000105A KR101245479B1 (ko) 2011-03-25 2012-03-08 왕복구동장치
CN2012800025332A CN103140700A (zh) 2011-03-25 2012-03-08 往复驱动装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011067440A JP2012202477A (ja) 2011-03-25 2011-03-25 往復駆動装置
JP2011-067440 2011-03-25

Publications (1)

Publication Number Publication Date
WO2012132817A1 true WO2012132817A1 (fr) 2012-10-04

Family

ID=46930558

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/055956 WO2012132817A1 (fr) 2011-03-25 2012-03-08 Dispositif d'actionnement en mouvement alternatif et d'entraînement

Country Status (5)

Country Link
JP (1) JP2012202477A (fr)
KR (1) KR101245479B1 (fr)
CN (1) CN103140700A (fr)
TW (1) TW201243187A (fr)
WO (1) WO2012132817A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014128302A1 (fr) * 2013-02-22 2014-08-28 Joachim Uhing Gmbh & Co. Kg Mécanisme d'inversion pour entraînement de bague de roulement

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105864381A (zh) * 2016-06-29 2016-08-17 北京邮电大学 一种改进的软轴螺旋传动装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH108799A (ja) * 1996-06-24 1998-01-13 Miwa Lock Co Ltd 作動装置
JP2004211725A (ja) * 2002-12-26 2004-07-29 Ckd Corp アクチュエータ
JP2009174713A (ja) * 2007-12-27 2009-08-06 Takehiro Otsubo 送りねじ装置及びウォーム歯車装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZW7888A1 (en) * 1987-06-15 1989-01-25 Dartnall Eng & Innovat A rotary/reciprocatory motion converter
CN2895888Y (zh) * 2006-02-28 2007-05-02 周立 稳定静音往复驱动机构
AT508241B1 (de) * 2009-05-05 2021-04-15 Engel Austria Gmbh Vorrichtung zur umsetzung einer drehbewegung in eine linearbewegung
CN101865266A (zh) * 2010-05-26 2010-10-20 广州中国科学院工业技术研究院 一种往复运动机构及将旋转运动转换为往复运动的方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH108799A (ja) * 1996-06-24 1998-01-13 Miwa Lock Co Ltd 作動装置
JP2004211725A (ja) * 2002-12-26 2004-07-29 Ckd Corp アクチュエータ
JP2009174713A (ja) * 2007-12-27 2009-08-06 Takehiro Otsubo 送りねじ装置及びウォーム歯車装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014128302A1 (fr) * 2013-02-22 2014-08-28 Joachim Uhing Gmbh & Co. Kg Mécanisme d'inversion pour entraînement de bague de roulement
US10197136B2 (en) 2013-02-22 2019-02-05 Joachim Uhing Gmbh & Co. Kg Reversal mechanism for a rolling ring drive

Also Published As

Publication number Publication date
KR101245479B1 (ko) 2013-03-25
TW201243187A (en) 2012-11-01
CN103140700A (zh) 2013-06-05
JP2012202477A (ja) 2012-10-22
KR20130018977A (ko) 2013-02-25

Similar Documents

Publication Publication Date Title
JP5340640B2 (ja) 電動リニアアクチュエータ
CN103946587B (zh) 电动线性致动器
JP5562795B2 (ja) 電動アクチュエータ
CN107054445B (zh) 转向装置
WO2014034648A1 (fr) Actionneur à action directe électrique et dispositif de frein à disque électrique
KR20060049819A (ko) 전동 액추에이터
JP2013104525A5 (fr)
EP3104040A1 (fr) Dispositif de conversion de mouvement et actionneur d'embrayage
WO2012132817A1 (fr) Dispositif d'actionnement en mouvement alternatif et d'entraînement
TWI391584B (zh) 致動器
US9523398B2 (en) Clutch device
US20230383822A1 (en) Helical drive mechanism and handle mechanism for wheelchair with helical drive
US8839935B2 (en) Transmission device
EP3022473B1 (fr) Ensemble d'actionnement de soupape comprenant un actionneur de compensation
JP4930771B2 (ja) 電動パワーステアリング装置
WO2015057111A1 (fr) Unité d'entraînement électromécanique avec dispositif d'amortissement
WO2016017437A1 (fr) Actionneur pour transmission à variation continue et transmission à variation continue
JP2020023968A5 (fr)
JP6348306B2 (ja) 電動アクチュエータ
JP2015007462A (ja) Ｖベルト式無段変速機
JPH11108143A (ja) 電動シリンダ
WO2016078687A1 (fr) Ensemble de vis et d'écrou
BG66396B1 (bg) Устройство за ротационно електрозадвижване

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201280002533.2

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12763991

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 20137000105

Country of ref document: KR

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12763991

Country of ref document: EP

Kind code of ref document: A1