WO2018040284A1 - 一种电动推杆 - Google Patents

一种电动推杆 Download PDF

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Publication number
WO2018040284A1
WO2018040284A1 PCT/CN2016/105224 CN2016105224W WO2018040284A1 WO 2018040284 A1 WO2018040284 A1 WO 2018040284A1 CN 2016105224 W CN2016105224 W CN 2016105224W WO 2018040284 A1 WO2018040284 A1 WO 2018040284A1
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WO
WIPO (PCT)
Prior art keywords
ball
clutch
seat
groove
push rod
Prior art date
Application number
PCT/CN2016/105224
Other languages
English (en)
French (fr)
Inventor
陆小健
胡仁昌
程云山
吴东海
Original Assignee
浙江捷昌线性驱动科技股份有限公司
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 浙江捷昌线性驱动科技股份有限公司 filed Critical 浙江捷昌线性驱动科技股份有限公司
Priority to EP16914847.5A priority Critical patent/EP3343056A4/en
Publication of WO2018040284A1 publication Critical patent/WO2018040284A1/zh
Priority to US16/286,597 priority patent/US11015686B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/02—Clutches in which the members have interengaging parts disengaged by a contact of a part mounted on the clutch with a stationarily-mounted member
    • F16D11/04—Clutches in which the members have interengaging parts disengaged by a contact of a part mounted on the clutch with a stationarily-mounted member with clutching members movable only axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H25/2454—Brakes; Rotational locks
    • 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
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • 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
    • 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
    • H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
    • H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2071—Disconnecting drive source from the actuator, e.g. using clutches for release of drive connection during manual control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/209—Arrangements for driving the actuator using worm gears

Definitions

  • the invention relates to an electric push rod and belongs to the field of linear drive equipment.
  • the existing electric push rod comprises a motor, a transmission component connected to the motor drive, and a sleeve assembly connected to the transmission component.
  • the sleeve assembly itself can be telescoped, and when the motor rotates, the sleeve assembly is driven by the transmission component
  • the telescopic function is realized, and in the existing electric push rod on the market, in order to quickly connect and disconnect the power between the sleeve assembly and the transmission assembly, the sleeve assembly and the transmission assembly are usually provided with a clutch device to provide a power connection.
  • the problem with the prior art is that the structure of the clutch device is relatively complicated, and the power connection and disconnection process is not smooth, and the transmission efficiency is not high.
  • the invention provides an electric push rod, which solves the problem that the electric push rod in the prior art has poor smoothness when the power is connected or disconnected.
  • the present invention adopts the following technical solutions:
  • An electric push rod includes an electric motor, a transmission assembly coupled to the electric motor, and a sleeve assembly coupled to the transmission assembly, the sleeve assembly including a main shaft, the main shaft and the transmission assembly being disposed There is a clutch for achieving a power connection or disconnection between the main shaft and the transmission assembly, the clutch device including a ball clutch.
  • the ball clutch comprises: a ball seat connected to the main shaft and a clutch seat connected to the transmission assembly, wherein the ball seat is provided with a ball, and the clutch seat is provided with a limiting groove for positioning the ball
  • the ball is accommodated in the limiting slot, and when the power is disengaged, the ball is separated from the limiting slot.
  • the circumferential side wall of the ball seat is provided with a ball groove for accommodating the ball
  • the clutch seat is sleeved on the ball seat
  • the inner peripheral wall of the clutch seat is provided with an inner convex ring on the inner convex ring.
  • the limiting slot is provided.
  • the ball groove is a wedge groove, and the ball is placed in the ball groove.
  • said electric pusher further comprises a clutch drive assembly for driving said clutch to separate or close.
  • the clutch drive assembly includes a dial ring on one side of the clutch seat axial direction.
  • the dial ring is toggled, the clutch seat is axially displaced to realize separation or docking of the limit groove and the ball.
  • the clutch drive assembly comprises a dial base, the dial ring is rotatably coupled to the dial ring, the dial ring is connected with a pull rod, the pull rod is forced to rotate the dial ring, and the clutch ring is pushed to rotate the clutch seat mobile.
  • the electric push rod further comprises a brake base, wherein the brake seat is slidably connected with a slider, and one end of the slider is connected to the pull rod, and the other end is connected with a brake cable.
  • the transmission assembly includes a worm coupled to the motor, the worm is engaged with a worm gear, the worm gear is coupled to a drive key, and the clutch seat is provided with a drive keyway that mates with the drive key.
  • the sleeve assembly comprises an inner tube and an outer tube
  • the main shaft is a screw rod
  • a nut is connected to the screw rod
  • the nut is fixedly connected with the inner tube
  • the inner tube and the outer tube are driven when the main shaft rotates. Relative movement occurs.
  • the clutch device between the main shaft and the transmission component adopts a ball clutch
  • the ball clutch is characterized in that the power connection and the disconnection are realized by the rolling of the balls, and the clutching manner of the traditional tooth docking can effectively reduce the toothing and the card.
  • the problem of the teeth, and the smoother power connection, the longer service life, for the entire electric push rod, the casing assembly will not have a large impact when the power is connected or the power is disconnected, so that the sleeve assembly More stable when stretching.
  • the ball in the ball clutch of the present invention also has a self-adjusting function, so that the clutch can realize rapid release and disengagement during normal operation or when the motor of the electric push rod is not running. That is, when the disconnection is required, the power can be quickly cut off, and when the connection is required, the quick connection can be realized, the seamless docking is achieved, and the response speed is fast.
  • FIG. 1 is a partial cross-sectional view showing a first embodiment of the present invention
  • FIG. 2 is a half cross-sectional view showing a first embodiment of the present invention
  • Embodiment 1 of the present invention is a schematic exploded view of Embodiment 1 of the present invention.
  • FIG. 4 is a schematic view showing an explosion at a clutch device according to an embodiment of the present invention.
  • FIG. 5 is a schematic structural view of a clutch seat according to Embodiment 1 of the present invention.
  • FIG. 6 is a schematic structural view of a ball seat according to Embodiment 1 of the present invention.
  • Figure 7 is a schematic view showing the assembly of the clutch drive assembly in the first embodiment of the present invention.
  • FIG. 8 is a schematic structural view of the first embodiment of the present invention after removing the upper case and the cover.
  • the embodiment is an electric push rod mainly used for medical equipment and furniture products, and is an electric accessory for providing lifting and lowering functions, for example, used in a lifting medical bed, or a lifting table and chair, etc., as shown in FIG.
  • the embodiment includes a motor 10, a transmission assembly that is drivingly coupled to the motor 10, and a sleeve assembly that is drivingly coupled to the transmission assembly.
  • the transmission assembly is mounted within the housing.
  • the housing of the present embodiment includes an upper housing 11 and a lower housing 12
  • a motor cover 13 is disposed outside the motor 10, and the motor cover 13 and the lower case 12 are fixedly mounted.
  • the motor 10 rotates, and the motor 10 transmits power to the sleeve assembly through the transmission assembly.
  • the sleeve assembly realizes the telescopic function, and one end of the sleeve assembly is fixed to the object to be lifted, thereby realizing the function of lifting and lowering the object.
  • the transmission assembly in this embodiment includes a worm 21 disposed on an output shaft of the motor 10, a worm 21 can be seen in FIG. 7, and an axial direction of the worm 21 is vertical, and the worm 21
  • the transmission meshes with a worm wheel 22, the axial direction of the worm wheel 22 is a horizontal direction, and the center of the worm wheel 22 is provided with a worm wheel center hole, and a transmission sleeve is arranged in the center hole of the worm wheel, and a transmission key is arranged on the outer peripheral wall of the transmission sleeve, and the worm wheel center hole is arranged
  • the transmission keyway matched with the transmission key is provided, and when the worm wheel 22 rotates, the transmission key is rotated to drive the transmission sleeve to rotate.
  • the transmission key and the transmission sleeve are integrated, and the two integrally form a spline.
  • the sleeve 23, and the drive key groove on the center hole of the worm wheel of the embodiment is a spline groove 221.
  • the motor 10 rotates to drive the worm 21 to rotate. After the worm 21 rotates, the worm wheel 22 rotates, and when the worm wheel 22 rotates, the spline sleeve 23 is rotated.
  • the sleeve assembly in this embodiment includes an inner tube 51 and an outer tube 52.
  • the outer tube 52 is sleeved outside the inner tube 51.
  • the inner tube 51 is provided with a main shaft.
  • the main shaft of the embodiment is a screw rod 50 and a screw rod 50.
  • a nut 53 is connected to the inner tube 51. When the screw 50 rotates, the nut 53 and the screw rod 50 are axially displaced, so that the nut 53 drives the inner tube 51 to axially displace relative to the screw rod 50.
  • the axial position of the outer tube 52 and the lead screw 50 are relatively fixed, so that the relative movement of the inner tube 51 and the outer tube 52 is finally achieved.
  • a clutch device for realizing the power connection or disconnection between the main shaft and the transmission assembly is provided, specifically, between the screw rod 50 and the spline sleeve 23 A clutch device is provided.
  • the clutch device includes a ball clutch.
  • the specific structure of the ball clutch includes a clutch seat 3 and a ball seat 4, wherein the ball seat 4 is connected with the screw rod 50, and the structure of the ball seat 4 is referred to FIG. 4 and FIG. 6. Specifically, the center of the ball seat 4 is provided with a flat shaft.
  • the hole 401, one of the screw rods 50 is a flat shaft shaft matching the shape of the flat shaft hole 401, and the flat shaft shaft penetrates into the flat shaft hole 401, and the screw rod 50 is fixedly connected with the ball seat 4, this embodiment
  • the fixed connection is achieved by an interference fit between the flat shaft and the flat shaft hole 401, so that when the ball seat 4 rotates, the screw 50 is rotated, and the cross-sectional shape of the flat shaft hole 401 in this embodiment It is not limited to the shape shown in FIGS. 4 to 6, as long as it is a non-circular hole.
  • Three ball grooves 402 are circumferentially spaced apart on the outer peripheral side wall of the ball holder 4.
  • the three ball grooves 402 are preferably evenly spaced, and each of the ball grooves 402 is provided with balls 43.
  • the three ball slots 402 are capable of achieving a minimum amount of circumferential balance, although those skilled in the art will recognize that the number is not limited in other embodiments.
  • the clutch seat 3 is connected with the spline sleeve 23, and the center of the clutch seat 3 is provided with a clutch hole 301, and the clutch The right end of the inner hole 301 is provided with a coupling keyway 302 matching the outer shape of the spline sleeve 23, that is, when the spline sleeve 23 is rotated, the clutch seat 3 is rotated.
  • the clutch inner hole 301 is provided with a limiting groove 303 for positioning the ball 43.
  • the ball 43 When the power is engaged, the ball 43 is accommodated in the limiting groove 303.
  • the groove wall of the limiting groove 303 abuts against the ball 43.
  • the ball 43 After the ball is reached, the ball 43 cannot be circumferentially free in the inner hole 301 of the clutch seat. Rotating, at this time, the ball 43 rotates together with the clutch seat 3, and when the ball 43 rotates, the ball seat 4 is rotated, so that the ball seat 4 and the clutch seat 3 rotate synchronously, and finally the synchronous driving of the screw rod 50 is realized;
  • the clutch seat 3 moves axially to the right side, and the ball 43 is disengaged from the limiting slot 303. At this time, the slot wall of the limiting slot 303 cannot contact the ball 43, and the limiting slot 303 and the ball 43 are lost.
  • the ball 43 can be freely rotated in the circumferential direction of the inner hole 301 of the clutch seat, and the clutch seat 3 is in an idling state. At this time, the screw 50 is not powered and does not rotate.
  • the specific structure of the clutch seat 3 is provided with an inner convex ring 304, and the inner convex ring 304 is provided with the limiting slot 303, and the limiting slot in this embodiment
  • the ball groove 402 in this embodiment is a wedge-shaped groove, and the wedge-shaped groove is concavely formed on the outer side wall of the ball seat 4.
  • the longitudinal direction of the wedge groove is the tangential direction of the ball seat 4, and the ball groove 402 is
  • the circumferential length is greater than the diameter of the ball 43.
  • the circumferential length of the limiting groove 303 is also larger than the diameter of the ball 43.
  • the ball 43 is moved in the ball groove 402, that is, the ball 43 is in the ball groove 402.
  • the radial and circumferential movable space is for the axial center of the ball bearing.
  • the advantage of this design is that the distance between the ball 43 and the center of the ball bearing 4 is active. Adjustable, and with the characteristics of the wedge groove, the adjustable effect is automatically adjusted, as follows:
  • the ball 43 When the ball seat 4 is in a non-rotating state, the ball 43 is not subjected to the centrifugal force. At this time, the ball 43 is automatically affected by its own weight and slides down to the center of the ball seat 4 along the slope of the wedge groove, that is, the wedge groove is the most At the inner end, at this time, the center distance between the ball 43 and the ball seat 4 is the smallest, and the roller is rolled at the position.
  • the contact area between the bead 43 and the limiting groove 303 is the smallest, which is very advantageous for the ball bearing 4 to be docked with the clutch seat 3, that is, the automatic adjustment function of the wedge groove is used to prepare the docking in advance, so that the clutch seat 3 and the ball are made.
  • the seat 4 goes smoothly from the disengaged state to the connected state.
  • the self-adjusting action of the ball is utilized, so that the clutch can achieve rapid release and disengagement during normal operation or when the motor of the electric push rod is not moved, that is, when the disconnection is required,
  • the power is quickly cut off, and when it needs to be connected, it can achieve fast connection, close to seamless docking, and fast response.
  • the ball seat 4 is split and spliced, that is, the ball seat 4 includes a ball seat body 41 and a ball retainer ring 42, which is first processed on the ball seat body 41.
  • An open ball groove is then spliced on the end surface of the ball seat body 41 with a ball seat retaining ring 42.
  • the end face of the ball retainer ring 42 serves as one of the side walls of the open ball groove, thereby forming a complete ball groove 402.
  • the structure reduces the processing difficulty and reduces the cost.
  • the ball seat 4 can also be a unitary structure.
  • the above is mainly for the specific description of the ball clutch in the embodiment.
  • the ball clutch in the embodiment has the advantages of relatively simple structure, no complicated structural features, few parts, low cost and relatively large volume. Small, in addition, the use of the rolling characteristics of the ball, so that the power is connected or disconnected, the smoothness is very good, and the characteristics of the ball rolling, so that when the power is engaged, the wear between the clutch seat 3 and the ball seat 4 is small, use The life is greatly increased.
  • the ball in this embodiment has a self-adjusting function, and in the clutching process, the function of quick connection and quick disconnection can be realized, and the response speed is fast.
  • the electric push rod further includes a clutch drive assembly for driving the ball clutch to separate or close, specifically, a clutch drive assembly that drives the clutch seat 3 to axially displace.
  • the specific structure of the clutch drive assembly includes: the outer circumference of the clutch seat 3 is provided with a dial base 61, and the dial base 61 itself is fixed on the upper shell 11 or the lower shell 12, and the dial base
  • the center of the 61 is provided with a dial inner cavity, and the clutch seat 3 is located in the inner cavity of the dial ring.
  • the dial ring 61 is rotatably connected with a dial 62.
  • the dial 62 is a U-shaped member, and the two sides of the dial 62 Rotating and connecting to the dial base 61, the end of the two sides of the dial ring 62 extends inwardly with a lever 621.
  • a convex outer ring 305 is extended radially outward.
  • the two levers 621 on the ring 62 are adjacent to the outer peripheral wall of the clutch seat 3 and are located on the left side of the outer collar 305;
  • a first return spring 24 is disposed between the right end surface of the clutch seat 3 and the left end surface of the worm wheel 22, wherein the left end surface of the worm wheel 22 is provided with a spring slot 222 for positioning the first return spring 24, and the first return spring during normal operation 24 is in an uncompressed state;
  • the outer wall of the outer tube 52 is fixedly mounted with a brake base 70.
  • the brake base 70 is provided with a sliding inner cavity 701.
  • the sliding inner cavity 701 is provided with a sliding rail 702.
  • the sliding rail 702 is slidably connected with a slider 71 and a slider.
  • the sliding direction of the 71 is parallel to the axial direction of the outer tube 52, and a second return spring 72 is disposed between the left end of the slider 71 and the left side wall of the sliding inner chamber 701, and the housing 73 is externally mounted to the sliding inner chamber 701.
  • the brake 71 is connected to the left end of the slider 71.
  • the right end of the slider 71 is connected with a pull rod 75.
  • the right end of the pull rod 75 is fixedly connected with a connecting block 76.
  • the upper shell 11 and the lower shell 12 are provided with a sliding block for the connecting block 76.
  • the connecting block 76 is provided with a card slot 761, and one end of the adjusting ring 62 away from the lever 621 is locked in the card slot 761.
  • the advantage of the clutch drive assembly in this embodiment is that the release ring 62 is rotated when the release, and the friction between the lever 621 and the outer collar 305 is small, thereby achieving the advantages of small release force and high efficiency;
  • the timely release of the rod when the load force is large, and the function that can be stopped at any time, together with the above-mentioned self-adjustable ball clutch, can realize the power connection or disconnection even when the motor is not rotating.
  • the ball clutch in the embodiment is different in structure.
  • the ball groove in this embodiment is only used to limit the ball to the ball seat.
  • the fixed position of the side wall that is, the circumferential position of the ball on the ball seat is fixed, and the rolling can only be achieved at the fixed position, similar to the sliding bearing, when the clutch is rotated in the circumferential direction during the power connection,
  • the limit groove on the clutch seat rotates to correspond to the ball position, the ball is engaged in the limit groove to realize Docking
  • the advantage of this embodiment is that the ball seat can directly adopt the ball type sliding bearing, which is advantageous for procurement and reduces cost.
  • the ball clutch in the embodiment is different in structure.
  • the ball groove is not a wedge groove, but a semicircular groove or a triangular groove.
  • the advantage of the structure is that whether the motor is forward or reverse, the ball can be smashed to the outermost end of the ball groove, that is, the motor rotates forward and reverse, and the clutch effect in this embodiment is very smooth and stable.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Transmission Devices (AREA)
  • Seats For Vehicles (AREA)
  • Braking Arrangements (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

一种电动推杆，包括电机（10）、与所述电机（10）传动连接的传动组件和与所述传动组件传动连接的套管组件，所述套管组件包括主轴，所述主轴与所述传动组件之间设有用于实现主轴与传动组件两者之间动力衔接或断开的离合装置，所述离合装置包括滚珠离合器，解决了现有技术中电动推杆在动力衔接或断开时平顺度不佳的问题，而且传动效率更高、寿命更长。

Description

一种电动推杆 【技术领域】
本发明涉及一种电动推杆，属于线性驱动设备领域。
【背景技术】
现有的电动推杆，包括电机、与所述电机传动连接的传动组件和与所述传动组件传动连接的套管组件，套管组件自身能伸缩，电机转动时，通过传动组件带动套管组件实现伸缩功能，而现有市面上的电动推杆，为了实现套管组件与传动组件之间的动力快速衔接与断开，套管组件与传动组件通常设置一个离合装置，起到一个动力衔接的纽带，而现有技术中存在的问题是，离合装置结构较为复杂，而且动力衔接和断开过程中不够平顺，传动效率不高。
【发明内容】
本发明提供一种电动推杆，解决现有技术中电动推杆在动力衔接或断开时平顺度不佳的问题。
解决上述技术问题，本发明采用如下技术方案：
一种电动推杆，包括电机、与所述电机传动连接的传动组件和与所述传动组件传动连接的套管组件，所述套管组件包括主轴，所述主轴与所述传动组件之间设有用于实现主轴与传动组件两者之间动力衔接或断开的离合装置，所述离合装置包括滚珠离合器。
作为优选，所述滚珠离合器包括：与所述主轴连接的滚珠座和与所述传动组件连接的离合座，滚珠座上设有滚珠，所述离合座上设有定位所述滚珠的限位槽，动力衔接时，滚珠容置在限位槽内，动力脱离时，滚珠脱离所述限位槽。
作为优选，所述滚珠座的周侧壁上设有容置所述滚珠的滚珠槽，所述离合座外套在滚珠座上，离合座的内周壁设有内凸环，所述内凸环上设有所述限位槽。
作为优选，所述滚珠槽为楔形槽，所述滚珠活动置于所述滚珠槽内。
作为优选，所述电动推杆还包括用于驱动所述离合装置分离或闭合用的离合驱动组件。
作为优选，所述离合驱动组件包括位于所述离合座轴向一侧的拨环，拨环被拨动时，推动所述离合座轴向位移，以实现限位槽与滚珠分离或对接。
作为优选，所述离合驱动组件包括拨环座，所述拨环转动连接在拨环座上，所述拨环连接有拉杆，拉杆受力带动拨环转动，拨环转动时推动所述离合座移动。
作为优选，所述电动推杆还包括刹车座，所述刹车座内滑动连接有滑块，所述滑块一端与所述拉杆连接，另一端连接有刹车拉线。
作为优选，所述传动组件包括与所述电机连接的蜗杆，所述蜗杆啮合有蜗轮，所述蜗轮传动连接有传动键，所述离合座上设有与所述传动键匹配的传动键槽。
作为优选，所述套管组件包括内管和外管，所述主轴为丝杆，丝杆上连接有螺母，所述螺母与内管固定连接，主轴转动时，驱动所述内管与外管发生相对移动。
采用本发明的有益效果：
本发明中主轴与传动组件之间的离合装置采用滚珠离合器，滚珠离合器的特点在于动力衔接和断开是通过滚珠滚动来实现，相对于传统的齿对接的离合方式，能有效减少打齿、卡齿的问题，而且动力衔接时更平顺，使用寿命较长，对于整个电动推杆来说，让套管组件在动力接入或动力断开时，不会产生较大的冲击，使得套管组件在伸缩时更加稳定。
另外，作为其中优选方案，本发明中的滚珠离合器中的滚珠还具备自调节作用，使得电动推杆在正常运行时或者电动推杆的电机不运行时，该离合器均能实现快速释放的离合作用，即在需要断开时，能实现动力快速切断，在需要衔接时，能实现快速衔接，接近于无缝对接，响应速度快。
本发明的这些特点和优点将会在下面的具体实施方式、附图中详细的揭露。
【附图说明】
下面结合附图对本发明做进一步的说明：
图1为本发明实施例一的局部剖视示意图；
图2为本发明实施例一的半剖示意图；
图3为本发明实施例一的爆炸示意图；
图4为本发明实施例一在离合装置处的爆炸示意图；
图5为本发明实施例一中离合座的结构示意图；
图6为本发明实施例一中滚珠座的结构示意图；
图7为本发明实施例一中离合驱动组件的装配示意图；
图8为本发明实施例一中去除上壳和罩壳后的结构示意图。
【具体实施方式】
下面结合本发明实施例的附图对本发明实施例的技术方案进行解释和说明，但下述实施例仅为本发明的优选实施例，并非全部。基于实施方式中的实施例，本领域技术人员在没有做出创造性劳动的前提下所获得其他实施例，都属于本发明的保护范围。
为了方便下文进行描述，以下出现的“左”、“右”、“上”、“下”均以图1中展示的方位为参照而定义。
实施例1
本实施例为一种电动推杆，主要用于医疗设备、家具产品上，是一种提供升降作用的电动配件，比如用在升降医疗床上，或者升降桌椅等等，如图1所示，本实施例包括电机10、与所述电机10传动连接的传动组件和与所述传动组件传动连接的套管组件，传动组件安装在外壳内，本实施例的外壳包括上壳11和下壳12，电机10外设有电机罩13，电机罩13与下壳12固定安装。运作时，电机10转动，电机10转动时通过传动组件将动力传输到套管组件上，套管组件实现伸缩功能，套管组件的一端与被升降对象固定，从而实现该对象升降的功能。
如图1至图3，具体而言，本实施例中的传动组件：包括设在电机10的输出轴上的蜗杆21，蜗杆21可参见图7，蜗杆21轴向方向为竖向，蜗杆21传动啮合有蜗轮22，蜗轮22的轴向方向为左右水平方向，蜗轮22的轴线中心设有蜗轮中心孔，蜗轮中心孔内设有传动套，传动套外周壁设有传动键，蜗轮中心孔上设有与所述传动键匹配的传动键槽，蜗轮22转动时，带动传动键转动，从而带动传动套转动，在本实施例中传动键与传动套为一体结构，整体上两者形成一个花键套23，而本实施例蜗轮中心孔上的传动键槽为花键槽221。
正常工作时，电机10转动，带动蜗杆21转动，蜗杆21转动后带动蜗轮22转动，蜗轮22转动时带动花键套23转动。
本实施例中的套管组件：包括内管51和外管52，外管52套设在内管51外，内管51内设有主轴，本实施例的主轴为丝杆50，丝杆50上连接有螺母53，所述螺母53与内管51固定连接，丝杆50转动时，螺母53与丝杆50发生轴向位移，从而螺母53带动内管51相对于丝杆50发生轴向位移，外管52与丝杆50的轴向位置相对固定，从而最终实现内管51与外管52发生相对移动。
本实施例中所述主轴与所述传动组件之间设有用于实现主轴与传动组件两者之间动力衔接或断开的离合装置，具体而言，是丝杆50与花键套23之间设有离合装置，本实施例中离合装置包括滚珠离合器。
滚珠离合器的具体结构：包括离合座3和滚珠座4，其中滚珠座4与丝杆50连接，滚珠座4的结构参照图4和图6，具体的说，滚珠座4中心设有扁位轴孔401，所述丝杆50上其中一段为与扁位轴孔401形状匹配的扁位轴，扁位轴穿入扁位轴孔401，丝杆50与滚珠座4是固定连接，本实施例中该固定连接是通过扁位轴与扁位轴孔401的过盈配合来实现，使得滚珠座4在转动时，会带动丝杆50转动，本实施例中的扁位轴孔401的截面形状并不局限于图4至6中展示的形状，只要是非圆形孔即可。
滚珠座4的外周侧壁上周向间隔设有三个滚珠槽402，本实施例中三个滚珠槽402优选为均匀间隔分布，每个滚珠槽402内容置有滚珠43。三个滚珠槽402能达到最小数量的周向平衡，当然本领域技术人员应知晓在其他实施例中并不局限于该数量。
而离合座3是与花键套23连接，离合座3中心设有离合座内孔301，离合 座内孔301的右端设有与所述花键套23外形匹配的联轴键槽302，即花键套23在转动时，会带动离合座3转动。而离合座内孔301上除了联轴键槽302外，还设有定位所述滚珠43的限位槽303。
动力衔接时，滚珠43容置在限位槽303内，即离合座3转动时，限位槽303的槽壁与滚珠43相抵，相抵后滚珠43无法实现在离合座内孔301内周向自由转动，此时滚珠43跟随离合座3一起转动，滚珠43转动时，带动滚珠座4转动，从而实现滚珠座4与离合座3同步转动，最终实现带动丝杆50同步转动；
而动力脱离时，即离合座3往右侧轴向移动，滚珠43脱离所述限位槽303，此时限位槽303的槽壁无法与滚珠43接触，限位槽303与滚珠43之间失去作用力，滚珠43可在离合座内孔301内周向自由转动，离合座3处于空转状态，此时丝杆50无动力接入，不发生转动。
参见图5，离合座3的具体结构：离合座内孔301的内周壁设有内凸环304，所述内凸环304上设有所述限位槽303，本实施例中的限位槽303有三个，沿内凸环304周向间隔均匀而设，而上述联轴键槽302刚好位于内凸环304的右侧，可作为对滚珠的轴向限位用。
作为进一步的优选，本实施例中的滚珠槽402为楔形槽，该楔形槽为滚珠座4外侧壁内凹形成，该楔形槽的长度方向为滚珠座4的切线方向，所述滚珠槽402的周向长度大于滚珠43的直径，所述限位槽303的周向长度同样大于所述滚珠43的直径，所述滚珠43活动置于所述滚珠槽402内，即滚珠43在滚珠槽402内具备径向、周向的活动空间，该径向、周向的活动空间是针对于滚珠座4轴心而言，这样设计的优点在于，滚珠43与滚珠座4的中心之间的距离是活动可调式的，而且利用楔形槽的特征，该可调效果是自动调节的，具体如下：
当滚珠座4与离合座3刚对接时，滚珠座4刚启动转动时，滚珠43受离心力作用，自动会被甩到离滚珠座4中心最远处，即楔形槽最外端，此时滚珠43与滚珠座4的中心间距为最大，在该位置状态下滚珠43与限位槽303的槽壁接触面积是最大的，咬合紧密好；
当滚珠座4处于不转动的状态下时，滚珠43不受离心力作用，此时的滚珠43受其自重影响会沿楔形槽的斜面作用自动下滑到最靠近滚珠座4中心处，即楔形槽最内端，此时滚珠43与滚珠座4的中心间距为最小，在该位置状态下滚 珠43与限位槽303的槽壁接触面积是最小的，非常利于滚珠座4与离合座3对接，即利用楔形槽的自动调整功能，预先自动做好对接的准备，使得离合座3与滚珠座4从顺利从脱离状态进入到衔接状态。
采用这种优选方案，利用滚珠的自调节作用，使得电动推杆在正常运行时或者电动推杆的电机不动时，该离合器均能实现快速释放的离合作用，即在需要断开时，能实现动力快速切断，在需要衔接时，能实现快速衔接，接近于无缝对接，响应速度快。
在本实施例中，出于加工难度的考虑，对滚珠座4采用分体加工拼接的方式，即滚珠座4包括滚珠座本体41和滚珠座挡圈42，先在滚珠座本体41上加工出敞开式的滚珠槽，然后在滚珠座本体41端面拼接一个滚珠座挡圈42，滚珠座挡圈42的端面作为敞开式滚珠槽的其中一个侧壁，从而形成一个完整的滚珠槽402，这种结构降低了加工难度，降低成本。当然本领域技术人员应知晓，滚珠座4也可以是一体结构。
以上主要是针对于本实施例中滚珠离合器的具体阐述，本实施例中的滚珠离合器，其优点在于结构上相对简单，没有复杂的结构特征，而且零部件很少，成本低，体积也相对较小，另外，利用滚珠的滚动特性，使得动力衔接或者断开时，平顺度非常好，而且滚珠滚动的特征，使得动力在衔接时，离合座3与滚珠座4之间的磨损很小，使用寿命大大增加，最关键是，本实施例中的滚珠带有自调节作用，在离合过程中，能实现快速衔接、快速断开的作用，响应速度快。
另外，本实施例中，所述电动推杆还包括用于驱动所述滚珠离合器分离或闭合用的离合驱动组件，具体而言是驱动离合座3发生轴向位移的离合驱动组件。
结合图2和图7来看，离合驱动组件的具体结构包括：所述离合座3的外周设有拨环座61，拨环座61自身固定在上壳11或下壳12上，拨环座61中心设有拨环座内腔，离合座3位于拨环座内腔中，拨环座61上转动连接有拨环62，拨环62为一U形件，所述拨环62的两侧翼转动连接在拨环座61上，拨环62两侧翼的端部朝内延伸有拨杆621，本实施例中的离合座3的外周壁上设有径向往外延伸有外凸环305，拨环62上的两个拨杆621贴近离合座3的外周壁上并位于外凸环305的左侧；
离合座3的右端面与蜗轮22的左端面之间设有第一复位弹簧24，其中蜗轮22的左端面上设有定位第一复位弹簧24的弹簧槽222，正常工作时，第一复位弹簧24处于未压缩状态；
外管52的外壁上固定安装有刹车座70，刹车座70内设有滑动内腔701，滑动内腔701上设有滑轨702，所述滑轨702上滑动连接有滑块71，滑块71的滑动方向与外管52的轴向方向平行，滑块71的左侧端与滑动内腔701的左侧壁之间设有第二复位弹簧72，滑动内腔701外部安装有罩壳73，滑块71的左端连接有刹车拉线74，滑块71的右端连接有拉杆75，拉杆75的右端固定连接有连接块76，所述上壳11和下壳12上设有供连接块76滑动的滑道，连接块76上设有卡槽761，所述拨环62远离拨杆621的一端卡装在所述卡槽761内。
当刹车拉线74往左侧拉动时，所述滑块71从原始位置相应往左侧移动，此时带动拉杆75往左侧移动，拉杆75往左侧移动时，连接块76相应往左移动，此时连接块76利用卡槽761拨动拨环62转动，拨环62转动时，拨环62上的拨杆621与离合座3上的外凸环305相抵，推动离合座3往右侧移动，第一复位弹簧24被压缩，离合座3往右侧移动时，滚珠座4上的滚珠43脱离离合座3上的限位槽303，从而实现动力断开；
而当松开刹车拉线74时，借助第一复位弹簧24弹力作用，离合座3受到第一复位弹簧24向左的推力，重新实现离合座3与滚珠座4动力衔接，而滑块71也借助第二复位弹簧72的作用恢复到原始位置。
本实施例中离合驱动组件的优点在于：释放时拨环62是转动的，拨杆621与外凸环305之间摩擦力小，从而达到释放力小，效率高的优点；而且可实现电动推杆负载力大时的及时释放，以及中途可随时停止的功能，配合上述可自调节的滚珠离合器，即便是电机在不转动时，也可以实现动力衔接或断开。
实施例2
本实施例与实施例1的区别在于，本实施例中的滚珠离合在结构上有所不同，本实施例中的滚珠离合器，本实施例中的滚珠槽仅仅用于将滚珠限位在滚珠座侧壁的固定位置上，即滚珠在滚珠座上的周向位置为固定的，只能在该固定位置上实现滚动，类似于滑动轴承，在动力衔接时，离合座在周向转动的时候，离合座上的限位槽转动到与滚珠位置对应时，滚珠卡入所述限位槽内实现 对接，本实施例的优点在于，滚珠座可直接采用滚珠式的滑动轴承，利于采购，降低成本。
实施例3
本实施例与实施例1的区别在于，本实施例中的滚珠离合在结构上有所不同，本实施例中的滚珠离合器，其滚珠槽不是楔形槽，而是半圆槽，或者三角形槽，这种结构的优点在于，无论电机是正转还是反转，滚珠都能被甩至滚珠槽的最外端，即电机正转反转，本实施例中的离合效果都非常平顺、稳定。
以上所述，仅为本发明的具体实施方式，但本发明的保护范围并不局限于此，熟悉该本领域的技术人员应该明白本发明包括但不限于附图和上面具体实施方式中描述的内容。任何不偏离本发明的功能和结构原理的修改都将包括在权利要求书的范围中。

Claims (10)

  1. 一种电动推杆，包括电机、与所述电机传动连接的传动组件和与所述传动组件传动连接的套管组件，其特征在于，所述套管组件包括主轴，所述主轴与所述传动组件之间设有用于实现主轴与传动组件两者之间动力衔接或断开的离合装置，所述离合装置包括滚珠离合器。
  2. 如权利要求1所述电动推杆，其特征在于，所述滚珠离合器包括：与所述主轴连接的滚珠座和与所述传动组件连接的离合座，滚珠座上设有滚珠，所述离合座上设有定位所述滚珠的限位槽，动力衔接时，滚珠容置在限位槽内，动力脱离时，滚珠脱离所述限位槽。
  3. 如权利要求2所述电动推杆，其特征在于，所述滚珠座的周侧壁上设有容置所述滚珠的滚珠槽，所述离合座外套在滚珠座上，离合座的内周壁设有内凸环，所述内凸环上设有所述限位槽。
  4. 如权利要求3所述电动推杆，其特征在于，所述滚珠槽为楔形槽，所述滚珠活动置于所述滚珠槽内。
  5. 如权利要求2所述电动推杆，其特征在于，所述电动推杆还包括用于驱动所述离合装置分离或闭合用的离合驱动组件。
  6. 如权利要求5所述电动推杆，其特征在于，所述离合驱动组件包括位于所述离合座轴向一侧的拨环，拨环被拨动时，推动所述离合座轴向位移，以实现限位槽与滚珠分离或对接。
  7. 如权利要求6所述电动推杆，其特征在于，所述离合驱动组件还包括拨环座，所述拨环转动连接在拨环座上，所述拨环连接有拉杆，拉杆受力带动拨环转动，拨环转动时推动所述离合座移动。
  8. 如权利要求7所述电动推杆，其特征在于，所述电动推杆还包括刹车座，所述刹车座内滑动连接有滑块，所述滑块一端与所述拉杆连接，另一端连接有刹车拉线。
  9. 如权利要求2至8之一所述电动推杆，其特征在于，所述传动组件包括与所述电机连接的蜗杆，所述蜗杆啮合有蜗轮，所述蜗轮传动连接有传动键，所述离合座上设有与所述传动键匹配的传动键槽。
  10. 如权利要求1至8之一所述电动推杆，其特征在于，所述套管组件包括内管和外管，所述主轴为丝杆，丝杆上连接有螺母，所述螺母与内管固定连接，主轴转动时，驱动所述内管与外管发生相对移动。
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2023026308A (ja) * 2021-08-11 2023-02-24 第一傳動科技股▲ふん▼有限公司 電動シリンダ及びその遠心式安全装置
US11788611B1 (en) * 2022-12-15 2023-10-17 Timotion Technology Co., Ltd. Actuator with worm gear positioning mechanism

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107314090A (zh) * 2017-07-04 2017-11-03 浙江捷昌线性驱动科技股份有限公司 一种可双向自锁的电动推杆
CN107387701A (zh) * 2017-07-26 2017-11-24 上海舜拓电机有限公司 电动推杆及其快速释放装置
CN108594069A (zh) * 2018-04-08 2018-09-28 苏州银蕨电力科技有限公司 一种改进的智能电网传感装置
CN108518466B (zh) * 2018-04-19 2023-09-26 宁波海仕凯驱动科技有限公司 一种结构紧凑的线性致动器
CN109759271B (zh) * 2019-02-01 2024-03-15 浙江普莱得电器股份有限公司 一种滚涂机的切换结构及滚涂机
DE202019103356U1 (de) * 2019-06-14 2020-09-15 Dewertokin Gmbh Entstörter Linearantrieb
CN111600432A (zh) * 2020-04-29 2020-08-28 浙江捷昌线性驱动科技股份有限公司 一种离合顺畅的线性致动器
CN111466812B (zh) * 2020-05-11 2021-08-17 新疆华庭工贸有限公司 一种吸排一体式环保厕所系统
CN111810603A (zh) * 2020-06-09 2020-10-23 浙江捷昌线性驱动科技股份有限公司 一种单向驱动的线性致动器
CN112769283A (zh) * 2020-12-31 2021-05-07 无锡灵德自动化科技有限公司 一种集成式电动执行器
TWM614035U (zh) * 2021-03-09 2021-07-01 第一傳動科技股份有限公司 具有可限位快速釋放結構的線性致動器
CN113633183B (zh) * 2021-09-15 2023-03-31 广东格匠实业有限公司 一种升降式防撞锅盖
US11987371B2 (en) * 2021-09-16 2024-05-21 Hamilton Sundstrand Corporation Drive-through friction clutch as a tensile load disconnect

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2081012U (zh) * 1990-08-30 1991-07-17 张锦权 电动推杆
CN2315706Y (zh) * 1998-01-22 1999-04-21 张锦民 电动推杆
CN201651205U (zh) * 2010-04-13 2010-11-24 模帝科电子科技股份有限公司 电动推杆的可调速释放装置
EP2444695A1 (en) * 2010-10-25 2012-04-25 Moteck Electric Corp. Linear actuator driven by electric motor with quick release mechanism
CN202381584U (zh) * 2011-11-25 2012-08-15 浙江捷昌线性驱动科技股份有限公司 电动推杆用超越离合器
US20160146317A1 (en) * 2014-11-21 2016-05-26 Moteck Electric Corp. Structure of linear actuator
CN206054568U (zh) * 2016-08-31 2017-03-29 浙江捷昌线性驱动科技股份有限公司 一种电动推杆的离合装置
CN206145016U (zh) * 2016-08-31 2017-05-03 浙江捷昌线性驱动科技股份有限公司 一种电动推杆

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB614410A (en) * 1945-10-29 1948-12-15 Goesta Thure Harry Enquist Improvements in or relating to coupling devices
DE4437184A1 (de) * 1994-10-18 1996-04-25 Roemheld A Gmbh & Co Kg Spindelantrieb mit Schnellentriegelung
DE60027380T2 (de) * 1999-10-07 2007-05-10 ITT Mfg. Enterprises, Inc., Wilmington Automatische Abschaltvorrichtung
ITMI20032000A1 (it) * 2003-10-16 2005-04-17 Univer Spa Cilindro elettrico
US20050160846A1 (en) * 2004-01-20 2005-07-28 Yi-Chung Chiang Linear actuator
TWM296325U (en) * 2005-12-27 2006-08-21 Jaeger Ind Co Ltd Linear transmission device with quick-release function
ITTO20060110A1 (it) * 2006-02-16 2007-08-17 Skf Ab Attuatore elettromeccanico lineare per un freno di stazionamento.
DE202007001797U1 (de) * 2007-02-07 2007-04-05 T-MOTION Technology Co., Ltd., Xindian City Schnelllösevorrichtung für eine Stelleinrichtung
TW201106585A (en) * 2009-08-11 2011-02-16 Hiwin Mikrosystem Corp Quick-release mechanism of an actuator
US9267547B2 (en) * 2011-03-29 2016-02-23 New Gencoat, Inc. Tool-less quick-disconnect power transmission coupling assembly
CN102494051B (zh) * 2011-11-25 2013-07-17 浙江捷昌线性驱动科技股份有限公司 电动推杆用超越离合器
CN104179913B (zh) * 2013-05-21 2018-05-11 模帝科电子科技股份有限公司 电动推杆的释放装置
DE102015110089A1 (de) * 2014-06-27 2015-12-31 Magna Closures Inc. Elektromechanische Strebe mit integrierter Flexkupplung und Schlupfvorrichtung und zugehörige Kupplungs-/Kopplungs-Anordnung
CN104828757B (zh) * 2015-05-20 2018-07-13 浙江捷昌线性驱动科技股份有限公司 一种手动、电动两用型推杆
CN204628463U (zh) * 2015-05-20 2015-09-09 浙江捷昌线性驱动科技股份有限公司 一种离合装置
CN204633523U (zh) * 2015-05-20 2015-09-09 浙江捷昌线性驱动科技股份有限公司 一种电动推杆
CN105864318B (zh) * 2016-05-03 2018-05-29 成都劲德致动科技有限公司 一种电动推杆刹车系统

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2081012U (zh) * 1990-08-30 1991-07-17 张锦权 电动推杆
CN2315706Y (zh) * 1998-01-22 1999-04-21 张锦民 电动推杆
CN201651205U (zh) * 2010-04-13 2010-11-24 模帝科电子科技股份有限公司 电动推杆的可调速释放装置
EP2444695A1 (en) * 2010-10-25 2012-04-25 Moteck Electric Corp. Linear actuator driven by electric motor with quick release mechanism
CN202381584U (zh) * 2011-11-25 2012-08-15 浙江捷昌线性驱动科技股份有限公司 电动推杆用超越离合器
US20160146317A1 (en) * 2014-11-21 2016-05-26 Moteck Electric Corp. Structure of linear actuator
CN206054568U (zh) * 2016-08-31 2017-03-29 浙江捷昌线性驱动科技股份有限公司 一种电动推杆的离合装置
CN206145016U (zh) * 2016-08-31 2017-05-03 浙江捷昌线性驱动科技股份有限公司 一种电动推杆

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3343056A4 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2023026308A (ja) * 2021-08-11 2023-02-24 第一傳動科技股▲ふん▼有限公司 電動シリンダ及びその遠心式安全装置
JP7457054B2 (ja) 2021-08-11 2024-03-27 第一傳動科技股▲ふん▼有限公司 電動シリンダ及びその遠心式安全装置
US11788611B1 (en) * 2022-12-15 2023-10-17 Timotion Technology Co., Ltd. Actuator with worm gear positioning mechanism

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