Impact resistant self-resetting electric cylinder

Abstract

The present application relates to electric linear actuator and transmission technical field, especially to a kind of anti-impact self-resetting electric cylinder.The anti-impact self-resetting electric cylinder of the present application can be protected by bidirectional load barrier active protection core components, which includes cylinder barrel assembly, power input assembly, overload protection unit and piston output assembly, radial piston output assembly ball joint adaptive micro-transfer, piston rod radial load is conducted to cylinder barrel, from force flow path barrier screw rod bearing radial force and eccentric wear;Axial with pure mechanical overload protection unit structure of untwisting soft connection, ball instantaneous untwisting when impact overload, cut off impact peak to power input assembly transmission, realize mechanical overload protection, and ball untwisting structure of overload protection unit can be automatically reset quickly after impact disappears, adapt to intermittent impact continuous operation scene.

Description

Technical Field

[0001] This invention relates to the field of electric linear actuators and transmission technology, and in particular to an impact-resistant self-resetting electric cylinder. Background Technology

[0002] Electric cylinders, with their high control precision, excellent energy efficiency, clean and leak-free operation, and potential energy recovery, have been widely used in industrial automation, construction machinery, and testing equipment, gradually replacing traditional hydraulic transmission solutions. Currently, most mainstream electric cylinders employ a rigid transmission architecture driven by a motor-driven ball / roller screw pair, combined with a piston anti-rotation structure to achieve linear output, enabling stable and precise transmission under stable load conditions.

[0003] However, in complex operating conditions with intermittent impact loads and radial off-center loads, existing electric cylinder structures still have significant shortcomings: the transmission chain is a rigid direct connection, and external impact torque is directly transmitted to core precision components such as the drive motor, reduction mechanism, and lead screw and nut pair, which can easily lead to failures such as lead screw raceway wear, reducer shaft breakage, and motor overload damage; existing electronic overload protection relies on current detection response, which has lag and cannot instantly cut off the impact peak at the mechanical level, while conventional friction torque limiters have defects such as rapid wear and low reset accuracy, making them unsuitable for high-frequency impact scenarios. Furthermore, the radial load on the piston rod front end is directly transmitted to the lead screw transmission pair, causing the lead screw to bear additional bending stress and off-center load, exacerbating uneven wear of the lead screw and nut pair, and even causing lead screw instability, significantly shortening the service life of core components; existing solutions mostly use external or internal floating joints on the piston rod end, which can only compensate for installation coaxiality errors, but cannot transfer the radial load to the cylinder bearing through the force flow path, and cannot eliminate the radial force on the lead screw at its source. Summary of the Invention

[0004] The purpose of this invention is to provide an impact-resistant self-resetting electric cylinder that actively protects its core components through bidirectional load isolation. Radially, it relies on a spherical hinge for adaptive micro-rotation, transmitting the radial load of the piston rod to the cylinder barrel, thus blocking the lead screw from bearing radial force and eccentric wear along the force flow path. Axially, it uses a soft connection constructed with a purely mechanical torsion-disengagement overload protection unit. During impact overload, the ball bearings instantly disengage, cutting off the transmission of the impact peak to the power input component, thereby achieving mechanical overload protection.

[0005] This invention provides an impact-resistant self-resetting electric cylinder, comprising: Cylinder assembly, The power input assembly is mounted at the rear of the cylinder assembly; The overload protection unit includes a drive shaft connecting the lead screw inside the cylinder assembly, a drive ring axially fixed on the drive shaft and connected to the power input assembly, and balls pressed into grooves in the drive shaft and the drive ring; the balls are used to cut off the transmission path between the lead screw and the power input assembly when the transmission torque reaches the rated torque-off. The piston output assembly includes an anti-rotation nut, the inner cavity of which is connected to a lead screw drive. An anti-rotation guide is provided between the outer peripheral wall of the anti-rotation nut and the inner peripheral wall of the cylinder assembly. The anti-rotation guide is used to allow the anti-rotation nut to slide axially along the cylinder assembly and to limit the circumferential movement of the anti-rotation nut. The front and rear ends of the anti-rotation nut are respectively connected to the piston rod and the rear retaining ring via spherical hinges. The outer peripheral walls of the piston rod and the rear retaining ring are both supported by a support ring in contact with the inner wall of the cylinder assembly. The spherical hinge is used to adaptively deflect when the front end of the piston rod is subjected to a radial load and to transmit the radial force to the cylinder assembly through the support ring on the piston rod and the rear retaining ring.

[0006] Optionally, the inner cavity surface of the anti-rotation nut includes a ball circulation raceway that forms a threaded ball drive engagement with the lead screw.

[0007] Optionally, the outer peripheral wall of the anti-rotation nut is provided with a mounting groove for installing an anti-rotation guide. The anti-rotation guide includes a flat key installed in the mounting groove, and the flat key forms a sliding fit with the axial guide groove on the inner peripheral wall of the cylinder assembly.

[0008] Optionally, it also includes: The spherical slider has an outer spherical body formed on both the front and rear ends of the anti-rotation nut, which forms a spherical hinge pair with the spherical slider. The spherical slider is pressed onto the outer spherical body by an axial limiting bolt between the anti-rotation nut and the piston rod or between the anti-rotation nut and the rear retaining ring.

[0009] Optionally, the drive shaft is coaxially connected to the lead screw via a spline or a flat key, and a groove for engaging with the ball is provided on the outer peripheral wall of the drive shaft near the end face of the drive ring.

[0010] Optionally, the transmission ring is connected to the output gear of the gearbox of the power input assembly via a flange, and the transmission ring is axially fixed to the transmission shaft via bearings and snap rings; a groove for engaging with a ball is provided on the side end face of the transmission ring.

[0011] Optionally, the overload protection unit further includes: Adjusting nut, fitted onto the outer circumferential wall of the drive shaft; The disc spring rests at one end against the inner side of the adjusting nut and at the other end against a movable disc that can move axially along the outer peripheral wall of the drive shaft. Rotating the adjusting nut presses the balls into the grooves of the drive shaft and drive ring via the disc spring and the movable disc. The axial clamping force of the disc spring and the rated release torque of the balls can be adjusted by adjusting the screw length of the adjusting nut. The rated release torque of the balls can also be adjusted by adjusting the number of disc spring plates.

[0012] Optionally, it also includes: A magnetic ring is attached to the moving disk. The magnetic ring is used in conjunction with a magnetic field sensor to detect the displacement of the moving disk and trigger an impact and torsion monitoring alarm when the ball disengages from the slot of the drive shaft and the drive ring.

[0013] Optionally, the cylinder assembly includes: The cylinder has a front end cover and a rear end cover at both ends; the two ends of the lead screw are respectively mounted to the central bearing seats of the front end cover and the rear end cover via support bushings or bearings.

[0014] Optionally, the power input component includes: A drive motor, the output end of which is connected to the input end of a gearbox via a reducer.

[0015] Compared to existing technologies, this invention offers the following advantages: The impact-resistant self-resetting electric cylinder of this invention can actively protect its core components through bidirectional load isolation. It includes a cylinder assembly, a power input assembly, an overload protection unit, and a piston output assembly. The overload protection unit includes a drive shaft connecting a lead screw inside the cylinder assembly, a drive ring axially fixed to the drive shaft and connected to the power input assembly, and balls pressed into grooves in the drive shaft and drive ring. The balls are used to cut off the transmission path between the lead screw and the power input assembly when the transmission torque reaches the rated torque release. This invention constructs a soft connection in the axial direction of the lead screw with a purely mechanical torque release structure in the overload protection unit. During impact overload, the balls instantly disengage, cutting off the transmission of the impact peak to the power input assembly, thus achieving mechanical overload protection. The piston output assembly of this invention includes an anti-rotation nut. The anti-rotation nut adopts an integrated spherical hinge structure of the anti-rotation piston and the drive nut, simultaneously achieving anti-rotation guidance, transmission connection, and hinged load unloading functions. The structure is compact, improving the utilization rate of cylinder space and the effective stroke ratio. The inner cavity surface of the anti-rotation nut is connected to the lead screw drive. An anti-rotation guide is provided between the outer peripheral wall of the anti-rotation nut and the inner peripheral wall of the cylinder assembly. The anti-rotation guide is used to allow the anti-rotation nut to slide axially along the cylinder assembly and to limit the circumferential movement of the anti-rotation nut. The front and rear ends of the anti-rotation nut are connected to the piston rod and the rear retaining ring respectively through a spherical hinge joint. The outer peripheral walls of the piston rod and the rear retaining ring are both supported by a support ring in contact with the inner wall of the cylinder assembly. The spherical hinge joint is used to adaptively deflect when the front end of the piston rod is subjected to radial load and to transmit the radial force to the cylinder assembly through the support ring on the piston rod and the rear retaining ring. This invention relies on the adaptive micro-rotation of the lead screw in the radial direction through the spherical hinge to transmit the radial load of the piston rod to the cylinder, thus blocking the lead screw from bearing radial force and off-center wear from the force flow path. Furthermore, the overload protection unit of the ball-bearing de-torsion structure can automatically and quickly reset after the impact disappears, adapting to continuous operation scenarios with intermittent impacts; the integrated hinge structure of the anti-rotation nut can ensure the coaxiality of the transmission and reduce the impact of assembly errors; the two work together to improve the smoothness of the electric cylinder's operation, the retention of precision, and the service life of core components under off-center load and impact conditions. Attached Figure Description

[0016] Figure 1 A cross-sectional view of an impact-resistant self-resetting electric cylinder provided in an embodiment of the present invention; Figure 2 A cross-sectional view of the piston output assembly of an impact-resistant self-resetting electric cylinder provided in an embodiment of the present invention; Figure 3 for Figure 2 Schematic diagram of the anti-rotation nut; Figure 4 This is a schematic diagram of the overload protection unit of an impact-resistant self-resetting electric cylinder provided in an embodiment of the present invention; Figure 5 for Figure 4 Schematic diagram of the transmission ring structure; Figure 6 for Figure 4 A schematic diagram of the drive shaft.

[0017] The following are the labeling elements in the diagram: 10, Cylinder assembly; 20, Power input assembly; 30, Lead screw; 40, Piston output assembly; 50, Overload protection unit; 101, Cylinder; 102, Front end cover; 103, Rear end cover; 201, Drive motor; 202, Reducer; 203, Gearbox; 401, Anti-rotation nut; 402, Piston rod; 403, Spherical slider; 404, Rear retaining ring; 405, Support ring; 406, Anti-rotation guide; 406a, Flat key; 406b, Nylon cover; 501, Drive shaft; 502, Drive ring; 503, Disc spring; 504, Moving plate; 505, Adjusting nut; 506, Ball bearing; 507, Bearing; 508, Snap ring; 509, Magnetic ring. Detailed Implementation

[0018] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are used only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more. In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0019] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0020] The inventors of this invention have discovered that existing electric cylinders have significant technical shortcomings in continuous operation scenarios involving intermittent impact and radial off-center loading. The purpose of this invention is to provide an integrated electric cylinder that combines overload protection and radial unloading functions, specifically solving the following technical problems: Firstly, it addresses the problem of insufficient impact overload protection capability of rigid transmission chains. Existing electric cylinder transmission chains are rigid direct-drive structures, where impact torque can directly act on precision core components such as the drive motor and lead screw, easily causing damage to the transmission pair and motor overload failure. Electrically controlled overload protection relies on current detection, which has a response lag and cannot instantly cut off the impact peak at the mechanical level. Conventional friction-type overload mechanisms have defects such as fast wear rate, low torque setting accuracy, and poor reset accuracy after impact, making them unsuitable for high-frequency intermittent impact scenarios and unable to meet the continuous operation requirements of overload cutoff and rapid automatic reset.

[0021] Secondly, it addresses the problem of the inability to fundamentally unload the radial load on the lead screw. In existing electric cylinders, the radial load borne by the piston rod tip is directly transmitted along the rod to the lead screw drive pair, causing the lead screw to bear additional bending stress and off-center load for a long time, exacerbating uneven wear of the lead screw and nut pair, and even inducing instability and deformation of the lead screw. Existing external or internal floating joint solutions can only compensate for installation coaxiality errors, but cannot create a bypass bearing path for the radial load to be transmitted to the cylinder. They cannot block the radial component force on the lead screw at the source of force flow transmission, and cannot fundamentally extend the service life of the lead screw drive pair.

[0022] Thirdly, it addresses the issues of low space utilization and transmission accuracy in split-type piston-nut structures. Existing anti-rotation pistons and transmission nuts use a split assembly structure, requiring additional connecting flanges, positioning mating surfaces, and other connection structures. This occupies a significant amount of axial space within the cylinder, resulting in a low ratio of total cylinder length to effective stroke and insufficient internal space utilization, making it unsuitable for compact installation scenarios. Furthermore, it easily leads to accumulated coaxiality errors during assembly, exacerbating problems such as operational stalling and accuracy drift, failing to simultaneously meet the requirements of compact structural design and high-precision, stable transmission.

[0023] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0024] Combination Figure 1This embodiment provides an impact-resistant self-resetting electric cylinder, which includes a cylinder assembly 10, a power input assembly 20, a lead screw 30, a piston output assembly 40, and an overload protection unit 50. The power input assembly 20 is fixedly installed at the tail of the cylinder assembly 10, and its output end is coaxially connected to the input end of the lead screw 30 through the overload protection unit 50. The lead screw 30 is arranged axially inside the cylinder assembly 10 and is in transmission cooperation with the piston output assembly 40. The piston output assembly 40 is slidably assembled in the inner cavity of the cylinder assembly 10, and its front end is connected to the piston rod 402. The piston output assembly 40 can drive the piston rod 402 to perform linear reciprocating motion along the cylinder axis.

[0025] The cylinder assembly 10 includes a cylinder 101, a front cover 102, and a rear cover 103. The two ends of the lead screw 30 are respectively mounted on the central bearing seats of the front cover 102 and the rear cover 103 via support bushings or bearings. The power input assembly 20 includes a drive motor 201, a reducer 202, and a gearbox 203. The housing of the gearbox 203 is fixedly connected to the rear cover 103, and the output gear of the gearbox 203 is connected to the input end of the overload protection unit 50.

[0026] Combination Figure 2 and Figure 3 In this embodiment, the piston output assembly 40 adopts an integrated spherical hinge structure of anti-rotation piston and transmission nut, including an anti-rotation nut 401 (the integrated structure of anti-rotation piston and transmission nut is collectively referred to as such), a piston rod 402, a spherical slider 403, a rear retaining ring 404, a support ring 405, and an anti-rotation guide 406. The inner surface of the anti-rotation nut 401 is a ball bearing raceway, forming a threaded ball bearing transmission fit with the lead screw 30. The outer peripheral wall has a mounting groove for the anti-rotation guide 406, and the front and rear end faces are spherical structures with several through holes evenly distributed axially. The anti-rotation guide 406 includes a flat key 406a and a nylon cover 406b covering the outside of the flat key 406a, fixed in the keyway of the outer peripheral wall of the anti-rotation nut 401, and forming a sliding fit with the axial guide groove opened in the inner wall of the cylinder 101, thus realizing the circumferential anti-rotation and axial movement guidance of the anti-rotation nut 401. The inner surface of the spherical slider 403 is also an inner spherical structure, with the same radius as the outer spherical body of the anti-rotation nut 401. It forms a spherical hinge joint with the anti-rotation nut 401, allowing for adaptive circumferential micro-rotation in response to radial loads. Existing anti-rotation pistons and transmission nuts often employ separate assembly structures, requiring additional connecting flanges and positioning mating surfaces. This not only increases accumulated assembly errors but also occupies a significant amount of axial space within the cylinder, resulting in a low ratio of total cylinder length to effective stroke and insufficient space utilization, making it difficult to meet the needs of compact installation scenarios. This embodiment adopts an integrated spherical hinge structure for the anti-rotation piston and transmission nut, simultaneously achieving anti-rotation guidance, transmission connection, and hinged load unloading functions. The structure is compact, improving cylinder space utilization and the effective stroke ratio.

[0027] The piston rod 402 and the rear retaining ring 404 are embedded one after the other into the spherical slider 403, and are fixed by several long bolts serving as axial fixing bolts. The two spherical sliders 403 are pressed tightly onto the spherical body of the anti-rotation nut 401. The long bolts pass through several through holes in the anti-rotation nut 401 without contact, thereby achieving axial limitation. The support ring 405 is made of a strip-shaped soft material and is installed in the groove on the outer peripheral wall of the piston rod 402 and the rear retaining ring 404, contacting and supporting the inner wall of the cylinder 101. This integrated structure eliminates redundant structures such as connecting flanges and positioning mating surfaces between the separate piston and nut, directly compressing the axial size occupied by the transmission end and increasing the effective working stroke ratio under the same total cylinder length. When the front end of the piston rod 402 bears a radial load, the spherical hinge joint deflects adaptively with the load, transmitting the radial force through the piston rod 402, the rear retaining ring 404 and the support ring 405 to the cylinder body 101. This completely blocks the transmission of radial force and additional bending stress to the lead screw 30 from the force flow transmission path, avoiding off-center wear and instability of the lead screw and nut pair.

[0028] Combination Figure 4 , Figure 5 and Figure 6 The overload protection unit 50 adopts a purely mechanical ball torque limiting structure and is connected in series between the output shaft of the power input component 20 and the input end of the lead screw 30. The overload protection unit 50 includes a drive shaft 501, a drive ring 502, a disc spring 503, a moving plate 504, an adjusting nut 505, balls 506, bearings 507, snap rings 508, and a magnetic ring 509. The drive shaft 501 is the output end, which is coaxially fixedly connected to the lead screw 30 via a spline or flat key, and a groove for the balls 506 is opened at a suitable position on its outer peripheral wall. The drive ring 502 is the input end, which is connected to the output gear of the gearbox 203 via a flange, and is axially fixed to the drive shaft 501 via bearings 507 and snap rings 508, and a groove for the balls 506 is opened on its side end face. The ball bearing 506 is disposed in the slot between the drive shaft 501 and the drive ring 502, and is pressed by the disc spring 503, the moving plate 504, and the adjusting nut 505 to achieve torque transmission. The adjusting nut 505 can be screwed in to adjust the axial clamping force of the disc spring 503 and set the rated torque value. The rated torque value of the disc spring 503 can be increased / decreased by increasing / decreasing the number of discs. The magnetic ring 509 is attracted to the moving plate 504 and can move axially with the moving plate 504. In conjunction with the magnetic field sensor installed on the outside of the gearbox 203, the displacement of the moving plate 504 can be detected to perform impact torque detection and alarm.

[0029] This embodiment actively protects the core components through bidirectional load isolation. Radially, relying on the adaptive micro-rotation of the spherical hinge, the radial load of the piston rod 402 is transmitted to the cylinder 101, blocking the lead screw from bearing radial force and off-center wear from the force flow path; axially, a soft connection is constructed with a purely mechanical torsion-free structure, which instantly disengages from the torsion during impact overload, cutting off the transmission of the impact peak to the drive component, thus achieving mechanical overload protection.

[0030] Under normal transmission conditions, the balls 506 inside the overload protection unit 50 remain in a pressed and engaged state, the transmission chain is rigidly connected, and the power is smoothly transmitted to the lead screw drive pair after deceleration. When the transmission system encounters an impact load and the peak transmission torque exceeds the rated disengagement torque, the balls 506 instantly disengage from the slots of the transmission shaft 501 and the transmission ring 502, the transmission chain instantly disengages, directly cutting off the transmission path of the impact torque from the lead screw drive pair to the power input component 20, and issuing an impact disengagement alarm to avoid damage to precision components. After the impact load subsides, the balls 506 automatically engage in the next slot under the combined action of the clamping force of the disc spring 503 and the continuous output torque of the drive motor 201, and the transmission chain quickly restores rigid transmission. There is no need to stop the machine or manually adjust it, which is equivalent to realizing the function of cylinder overload unloading protection and resumption of operation after load removal, providing a possibility for replacing the traditional hydraulic transmission solution.

[0031] The ball-bearing unwinding structure in this embodiment can automatically and quickly reset after the impact disappears, adapting to continuous operation scenarios with intermittent impact; the integrated hinge structure can ensure the coaxiality of the transmission and reduce the impact of assembly errors; the two work together to improve the smoothness of operation, accuracy retention and service life of the electric cylinder under off-center load and impact conditions.

[0032] Rated torsion torque value Reset torque value It can be calculated using the following formula:

[0033]

[0034]

[0035] Automatic reset conditions: .

[0036] in,

[0037] This indicates the rated de-torque value, and the limit torque for overload slippage;

[0038] This indicates the reset torque value, which is the torque value at which the balls re-engage in the slot after the overload is eliminated. It is always less than the rated release torque.

[0039] Indicates the contact angle, the angle between the generatrix of the conical recess in the slot and the flange end face;

[0040] Indicates the angle of friction. ( (The static friction coefficient between the ball and the groove contact surface).

[0041] This indicates the total axial preload of the disc spring;

[0042] This indicates the radius of the ball's center pitch circle.

[0043] This electric cylinder achieves three major technical effects simultaneously: radial load cylinder unloading, impact torque mechanical cutoff, and compact high stroke utilization through the coordinated configuration of an integrated spherical hinge structure and a pure mechanical ball bearing torque limiting structure. It can stably adapt to complex continuous working conditions with intermittent impact and radial off-center load.

[0044] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. An impact-resistant self-resetting electric cylinder, characterized in that, include: Cylinder assembly (10) The power input assembly (20) is mounted at the rear of the cylinder assembly (10); The overload protection unit (50) includes a drive shaft (501) connecting the lead screw (30) inside the cylinder assembly (10), a drive ring (502) axially fixed on the drive shaft (501) and connected to the power input assembly (20), and balls (506) pressed into grooves in the drive shaft (501) and the drive ring (502); the balls (506) are used to cut off the transmission path between the lead screw (30) and the power input assembly (20) when the transmission torque reaches the rated torque. The piston output assembly (40) includes an anti-rotation nut (401), the inner cavity surface of which is connected to the lead screw (30) for transmission. An anti-rotation guide (406) is provided between the outer peripheral wall of the anti-rotation nut (401) and the inner peripheral wall of the cylinder assembly (10). The anti-rotation guide (406) is used to enable the anti-rotation nut (401) to slide along the axial direction of the cylinder assembly (10) and to limit the anti-rotation nut (401) circumferentially. The front end and rear end of the anti-rotation nut (401) are respectively connected to the piston rod (402) and the rear retaining ring (404) through a spherical hinge pair. The outer peripheral walls of the piston rod (402) and the rear retainer ring (404) are both supported by the inner wall of the cylinder assembly (10) through the support ring (405). The spherical hinge is used to adaptively deflect when the front end of the piston rod (402) is subjected to radial load and transmit the radial force to the cylinder assembly (10) through the support ring (405) on the piston rod (402) and the rear retainer ring (404).

2. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The inner cavity surface of the anti-rotation nut (401) includes a ball circulation raceway that forms a threaded ball drive engagement with the lead screw (30).

3. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The anti-rotation nut (401) has an installation groove on its outer peripheral wall for installing the anti-rotation guide (406). The anti-rotation guide (406) includes a flat key (406a) installed in the installation groove. The flat key (406a) forms a sliding fit with the axial guide groove on the inner peripheral wall of the cylinder assembly (10).

4. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, Also includes: The spherical slider (403) has an outer spherical body formed on both the front and rear ends of the anti-rotation nut (401) to form a spherical hinge pair with the spherical slider (403); the spherical slider (403) is pressed onto the outer spherical body by an axial limiting bolt between the anti-rotation nut (401) and the piston rod (402) or between the anti-rotation nut (401) and the rear retaining ring (404).

5. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The drive shaft (501) is coaxially connected to the lead screw (30) via a spline or flat key. A groove for engaging with the ball (506) is provided on the outer peripheral wall of the drive shaft (501) near the end face of the drive ring (502).

6. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The transmission ring (502) is connected to the output gear of the gearbox (203) of the power input assembly (20) via a flange. The transmission ring (502) is axially fixed to the transmission shaft (501) via a bearing (507) and a snap ring (508). A groove for engaging with a ball (506) is provided on the side end face of the transmission ring (502).

7. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The overload protection unit (50) further includes: Adjusting nut (505) is sleeved on the outer peripheral wall of drive shaft (501); The disc spring (503) rests on the inner side of the adjusting nut (505) at one end and on the moving plate (504) which can move axially along the outer peripheral wall of the drive shaft (501) at the other end. Rotating the adjusting nut (505) can press the ball (506) into the groove of the drive shaft (501) and the drive ring (502) through the disc spring (503) and the moving plate (504). The axial clamping force of the disc spring (503) and the rated torque of the ball (506) can be adjusted by adjusting the screw length of the adjusting nut (505). The rated torque of the ball (506) can also be adjusted by adjusting the number of discs of the disc spring (503).

8. The impact-resistant self-resetting electric cylinder according to claim 7, characterized in that, Also includes: A magnetic ring (509) is attached to the moving disk (504). The magnetic ring (509) is used to cooperate with the magnetic field sensor to detect the displacement of the moving disk (504) to trigger an impact and torsion monitoring alarm when the ball (506) disengages from the slot of the drive shaft (501) and the drive ring (502).

9. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The cylinder assembly (10) includes: The cylinder (101) has a front end cover (102) and a rear end cover (103) at both ends; the two ends of the lead screw (30) are respectively mounted on the central bearing seats of the front end cover (102) and the rear end cover (103) through support bushings or bearings.

10. The impact-resistant self-resetting electric cylinder according to claim 1, characterized in that, The power input assembly (20) includes: A drive motor (201) is provided, the output end of which is connected to the input end of a gearbox (203) via a reducer (202).

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