Electric actuator with integrated overload protection integrated function

Abstract

The application relates to the technical field of electric actuators, and discloses an electric actuator integrated with overload protection functions, which comprises a shell, a power unit arranged on the shell, a transmission reduction unit in transmission connection with the power unit and used for driving a load, the transmission reduction unit comprising an input planet carrier and an output planet carrier, and a gear ring assembly spliced by a plurality of radially swingable arc-shaped tooth blocks and provided with first elastic members for folding the arc-shaped tooth blocks towards the center. According to the application, compared with the prior art, torque transmission, overload sensing and triggering axial displacement are simultaneously realized through an overload triggering unit, the same displacement is used for driving the input planet gear to be separated and the gear ring assembly to be radially opened, the two cutting actions required by the overload protection are integrated, an independent torque limiter or brake does not need to be additionally arranged, and the axial size and the overall volume of the actuator are obviously reduced.

Description

Technical Field

[0001] This invention relates to the technical field of electric actuators, and in particular to electric actuators with integrated overload protection. Background Technology

[0002] Electric actuators are widely used in industrial automation, valve control, aerospace, and other fields to convert the rotary motion of a power source into the driving action of a load. In practical applications, electric actuators typically need to have overload protection functions to prevent equipment damage caused by abnormal loads.

[0003] In existing technologies, overload protection often employs friction-type torque limiters or shear pin structures. However, these traditional solutions have the following shortcomings: Friction-type torque limiters require a sliding friction process when overloaded, resulting in a significant delay in action. Furthermore, the friction plates are prone to wear, causing the protection threshold to drift and requiring frequent maintenance. On the other hand, shear pin structures provide one-time protection, requiring parts replacement after overload. They cannot automatically reset and are not suitable for operating conditions with frequent start-stop cycles.

[0004] Most overload protection devices only disconnect the power input end (between the motor and the reducer), but the output end may still continue to drive the transmission mechanism due to load inertia or external reverse torque, causing secondary damage (such as gear impact or valve stem twisting).

[0005] Existing overload protection modules are usually separate from the transmission system, requiring additional installation space and connecting components, which is not conducive to the miniaturization and weight reduction of actuators.

[0006] Therefore, there is an urgent need in the field for an overload protection electric actuator that is compact, responds quickly, can simultaneously cut off power transmission at both the input and output ends, and is reusable. Summary of the Invention

[0007] The purpose of this invention is to provide an electric actuator with integrated overload protection, thereby addressing the problems in the prior art.

[0008] This invention is implemented as follows: an electric actuator integrating overload protection function, comprising: case; The power unit is mounted on the housing; A transmission reduction unit, which is connected to the power unit for driving the load, includes an input planetary carrier and an output planetary carrier. The gear ring assembly is composed of multiple radially oscillating arc-shaped gear blocks spliced ​​together, and has a first elastic element that causes each arc-shaped gear block to converge toward the center; A planetary gear set includes an input planetary gear mounted on the input planetary carrier and meshing with the ring gear assembly, and an output planetary gear mounted on the output planetary carrier and meshing with the ring gear assembly; An overload triggering unit is disposed between the input planetary carrier and the output planetary carrier, and is used to generate a triggering displacement that causes the input planetary carrier to separate axially when an overload occurs; The overload triggering unit transmits torque under normal operating conditions, and the triggering displacement generated when an overload occurs can drive: The input planetary carrier moves axially relative to the gear ring assembly, causing the input planetary gear to disengage from the gear ring assembly; and The arc-shaped tooth block is pushed to move radially outward, causing the gear ring assembly to disengage from the output planetary gear.

[0009] Preferably, the overload triggering unit includes: at least one steel ball; The mounting ring has ball sockets corresponding to the number and position of the steel balls; Drive disk and driven disk; And a second elastic element for elastically forcing the drive disc and the driven disc to press against each other.

[0010] Preferably, the drive disk is fixedly connected to the input planetary carrier and can move axially with it, and the driven disk is fixedly connected to the output planetary carrier; When overloaded, the trigger displacement caused by the steel ball detaching from the socket manifests as the axial separation of the drive plate and the driven plate. The axial separation of the drive plate and the driven plate causes the input planetary carrier to move axially relative to the output planetary carrier.

[0011] Preferably, the driven disk has a grooved conical surface on its inner side, and the driving disk has a limiting groove on the side near the driven disk; The two sides of the steel ball are respectively abutted by the grooved conical surface and the limiting groove.

[0012] Preferably, the second elastic element is a helical compression spring, which is fitted onto the outer periphery of the mounting ring; The mounting ring is provided with an external thread, and an adjusting nut is connected to it through the external thread. One end of the second elastic element abuts against the adjusting nut, and the other end abuts against the driven plate.

[0013] Preferably, the transmission reduction unit is a double planetary gear set; The input planetary carrier is equipped with four input planetary gears, and the output planetary carrier is equipped with four output planetary gears.

[0014] Preferably, a drive shaft is provided inside the housing, a drive gear is fixed on the drive shaft, and the drive gear is connected to the power unit for transmission. An input sun gear that meshes with each input planetary gear is coaxially fixed on the drive shaft. An elastic abutment is also sleeved on the drive shaft. The elastic abutment abuts against the input planetary carrier and is used to apply an axial preload force toward the gear ring assembly to the input planetary carrier. An output end assembly plate is rotatably disposed inside the housing, and an output sun gear that meshes with each output planetary gear is coaxially fixed on the output end assembly plate.

[0015] Preferably, the gear ring assembly consists of at least two arc-shaped gear blocks, each arc-shaped gear block being hinged to the housing; The first elastic element is any one of the following: a torsion spring installed at the hinge, or a compression spring pressed against the outer edge of the arc-shaped toothed block.

[0016] Preferably, the outer periphery of the drive disk is provided with an axially extending tapered paddle; The inner side of the arc-shaped tooth block is provided with a wedge-shaped top block that matches the outer conical surface of the paddle, and a locking groove is also provided on the arc-shaped tooth block; When the overload triggering unit is in normal working condition and the drive plate and driven plate are pressed together, the edge of the paddle is engaged in the locking groove to prevent the arc-shaped tooth block from swinging outward. When the overload trigger unit is overloaded and the drive plate and driven plate are axially separated, the paddle moves axially with the drive plate, and its edge disengages from the locking groove. At the same time, the outer conical surface pushes the arc-shaped tooth block to swing radially outward through the wedge-shaped top block, causing the gear ring assembly to disengage from the output planetary gear.

[0017] Preferably, it also includes a control unit, which is electrically connected to the power unit and is used to receive external control signals and control the start, stop and steering of the power unit; And a manual handwheel, which can selectively transmit torque to the input or output end of the transmission reduction unit via a clutch mechanism for manually driving the load.

[0018] The beneficial effects of the electric actuator with integrated overload protection function disclosed in this invention are: 1. Compared with the existing technology, this solution realizes torque transmission, overload sensing and triggering axial displacement simultaneously through the overload triggering unit, and uses the same displacement to drive the input planetary gear to disengage and the gear ring assembly to open radially, thus integrating the two cutting-off actions required for overload protection into one, without the need for additional independent torque limiters or brakes, significantly reducing the axial dimension and overall volume of the actuator. 2. When an overload occurs, the trigger displacement of this device can simultaneously disengage the input planetary gear from the gear ring assembly and disengage the gear ring assembly from the output planetary gear, achieving dual power cut-off on both the input and output sides. Since the gear ring assembly opens radially during an overload, the output planetary gear and the gear ring are completely separated. Therefore, even if there is a reverse driving torque on the load side, it is impossible to reverse drive the already opened gear ring assembly through the output planetary gear, effectively avoiding secondary damage and improving the safety of the equipment and operators. 3. Under normal operating conditions, the arc-shaped toothed block remains closed under the action of the first elastic element, and the gear ring assembly maintains the complete internal gear ring structure, ensuring normal meshing transmission of the planetary gear set. When an overload occurs, the axial movement of the drive disc, through the cooperation of the paddle and the wedge-shaped top block, actively pushes the arc-shaped toothed block radially apart, achieving rapid and reliable disengagement between the gear ring and the output planetary gear. This disengagement method has no sliding friction, the action is crisp, and it can automatically reset under the action of the first elastic element after the overload disappears, without the need for manual replacement of parts. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of an electric actuator with integrated overload protection function provided in an embodiment of the present invention; Figure 2 This is another perspective schematic diagram of the electric actuator with integrated overload protection function provided in the embodiment of the present invention; Figure 3 This is a partial internal view schematic diagram of an electric actuator with integrated overload protection function provided in an embodiment of the present invention; Figure 4 This is a schematic diagram of the cross-sectional structure of an electric actuator with integrated overload protection function provided in an embodiment of the present invention; Figure 5 This is a schematic diagram of an electric actuator transmission and reduction unit with integrated overload protection function provided in an embodiment of the present invention; Figure 6 This invention provides an electric actuator with integrated overload protection. Figure 5 Another perspective, partial illustration; Figure 7 This invention provides an electric actuator with integrated overload protection. Figure 5 Schematic diagram of cross-section structure; Figure 8 This invention provides an electric actuator with integrated overload protection. Figure 5 Explosion structure diagram; Figure 9 This invention provides an electric actuator with integrated overload protection. Figure 8 Another perspective illustration.

[0020] Marker explanation: 1. Housing; 2. Control unit; 3. Power unit; 4. Manual handwheel; 11. Drive shaft; 12. Transmission reduction unit; 13. Overload triggering unit; 111. Drive gear; 112. Input sun gear; 121. Arc-shaped toothed block; 122. Input planetary carrier; 123. Output planetary carrier; 124. Elastic bearing plate; 125. Output end mounting plate; 1211, Locking groove; 1212, Wedge-shaped top block; 1213, Hinge; 1214, First elastic element; 1221, Input planetary gear; 1231, Output planetary gear; 1251. Output sun gear; 131. Mounting ring; 132. Second elastic element; 133. Adjusting nut; 134. Driven disc; 135. Drive disc; 1311, Steel ball; 1312, Ball socket; 1341, Grooved conical surface; 1351, Paddle; 1352, Limiting groove. Detailed Implementation

[0021] 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. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0022] In the accompanying drawings of this embodiment, the same or similar reference numerals correspond to the same or similar components. In the description of this invention, it should be understood that if terms such as "upper," "lower," "left," and "right" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this 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. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this invention. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0023] The implementation of the present invention will be described in detail below with reference to specific embodiments.

[0024] In this embodiment: Reference Figures 1-4 The diagram shows a preferred embodiment of the present invention.

[0025] The electric actuator with integrated overload protection function in this embodiment includes: housing 1; The power unit 3, mounted on the housing 1, is used to provide rotational driving force; The transmission reduction unit 12 is connected to the power unit 3 and is used to drive the load. It includes an input planetary carrier 122 and an output planetary carrier 123. The gear ring assembly is composed of multiple radially oscillating arc-shaped tooth blocks 121 spliced ​​together to form a complete annular inner gear ring structure; the gear ring assembly is also provided with a first elastic element 1214, which is used to apply an elastic restoring force toward the center to each arc-shaped tooth block 121. The planetary gear set includes an input planetary gear 1221 mounted on the input planetary carrier 122 and meshing with the ring gear assembly, and an output planetary gear 1231 mounted on the output planetary carrier 123 and meshing with the ring gear assembly; An overload triggering unit 13 is disposed between the input planetary carrier 122 and the output planetary carrier 123, and is used to generate a trigger displacement under overload conditions, which drives the input planetary carrier 122 to separate relative to the output planetary carrier 123 along the axial direction. The overload triggering unit 13 transmits torque under normal operating conditions, and the triggering displacement generated when an overload occurs can drive: On the one hand, the input planetary carrier 122 is driven to move axially relative to the gear ring assembly, so that the input planetary gear 1221 disengages from the gear ring assembly; On the other hand, the arc-shaped tooth block 121 is pushed to move radially outward, causing the gear ring assembly to disengage from the output planetary gear 1231.

[0026] The two actions mentioned above are executed concurrently under the same trigger displacement, forming a dual safety protection mechanism of active disengagement at the input end and passive disengagement at the output end. This reliably eliminates the overload torque transmission path, avoids the gear system from bearing continuous stress under overload conditions, and thus significantly reduces the risk of tooth surface wear and fatigue failure.

[0027] Furthermore, such as Figures 5-9 As shown, the overload triggering unit 13 includes: at least one steel ball 1311; a mounting ring 131 having a socket 1312 corresponding to the number and position of the steel balls 1311, wherein the steel balls 1311 are partially embedded in the socket 1312; a drive disk 135 and a driven disk 134, which are coaxially arranged opposite each other; and a second elastic member 132 for elastically forcing the drive disk 135 and the driven disk 134 to press against each other, so as to set an overload triggering threshold.

[0028] The drive disk 135 is fixedly connected to the input planetary carrier 122 and can move axially with it; the driven disk 134 is fixedly connected to the output planetary carrier 123. When an overload occurs, the trigger displacement generated by the steel ball 1311 dislodging from the ball socket 1312 manifests as the axial separation of the drive disk 135 and the driven disk 134. The axial separation of the drive disk 135 and the driven disk 134 causes the input planetary carrier 122 to move axially relative to the output planetary carrier 123.

[0029] It is worth noting that the inner side of the driven disk 134 is provided with a grooved conical surface 1341, and the side of the drive disk 135 near the driven disk 134 is provided with a limiting groove 1352; the two sides of the steel ball 1311 are respectively abutted by the grooved conical surface 1341 and the limiting groove 1352.

[0030] Under normal operating conditions, the steel ball 1311 is simultaneously confined in contact with and limited by the ball socket 1312, the limiting groove 1352 and the grooved conical surface 1341, thereby achieving torque transmission; Under overload, the steel ball 1311 rolls along the grooved conical surface 1341 and moves radially, forcing the drive disk 135 to separate from the driven disk 134. The double-sided contact ensures that the steel ball 1311 will not accidentally dislodge due to vibration during normal operation, improving vibration resistance. Simultaneously, the inclination angle of the grooved conical surface 1341 determines the relationship between the disengagement torque and the axial thrust; by optimizing the cone angle, ideal triggering sensitivity can be obtained.

[0031] The second elastic element 132 is a helical compression spring, which is fitted onto the outer circumference of the mounting ring 131. The mounting ring 131 is provided with an external thread, and an adjusting nut 133 is connected to the external thread. One end of the second elastic element 132 abuts against the adjusting nut 133, and the other end abuts against the driven plate 134. By rotating the adjusting nut 133, the compression amount of the second elastic element 132 can be adjusted, thereby setting the trigger torque threshold for overload protection. This adjustment structure enables the actuator to adapt to the overload protection requirements of different loads.

[0032] The transmission reduction unit 12 is a double planetary gear set; four input planetary gears 1221 are mounted on the input planetary carrier 122, and four output planetary gears 1231 are mounted on the output planetary carrier 123; a drive shaft 11 is provided inside the housing 1, and drive gears 111 are fixed on the drive shaft 11, which are connected to the power unit 3; an input sun gear 112 is also coaxially fixed on the drive shaft 11, and the input sun gear 112 meshes with each input planetary gear 1221; an elastic abutment is also sleeved on the drive shaft 11. 124, the elastic abutment 124 abuts against the input planetary carrier 122, and is used to apply an axial preload force toward the gear ring assembly to the input planetary carrier 122 to maintain normal meshing. The elastic abutment 124 can be compressed by the input planetary carrier 122 when overloaded, without hindering its axial movement. The housing 1 is also provided with an output end mounting plate 125. An output sun gear 1251 is coaxially fixed on the output end mounting plate 125. The output sun gear 1251 meshes with each output planetary gear 1231 to output the reduced torque to the load.

[0033] The gear ring assembly consists of at least two arc-shaped gear blocks 121, each arc-shaped gear block 121 being hinged to the housing 1 via a hinge 1213, allowing it to swing radially around the hinge 1213; the first elastic element 1214 is any one of the following: a torsion spring mounted at the hinge 1213, or a compression spring pressed against the outer edge of the arc-shaped gear block 121; the first elastic element 1214 is used to keep each arc-shaped gear block 121 in a state of closing towards the center under normal operating conditions; The hinge 1213 serves only to constrain the radial position, allowing the arc-shaped toothed block 121 to open radially when overloaded. The opening range only needs to disengage from the surface teeth of the input planetary gear 1221 and the output planetary gear 1231, so as not to interfere with the radial movement of the planetary gear with the drive wheel 135.

[0034] Unlike traditional one-piece gear rings, this invention uses arc-shaped tooth blocks 121 connected by hinges 1213 to form a radially opening gear ring assembly. This is the core structure for realizing the active disengagement of the gear ring from the planetary gears. This structure allows the disengagement process to completely break the meshing without axially moving the entire reducer. Only a small radial displacement is needed, which greatly reduces the energy and stroke required for triggering. This makes it possible to directly drive the gear ring 111 to open by using the small displacement generated by the disengagement of the steel ball 1311.

[0035] The outer periphery of the drive disk 135 is provided with an axially extending tapered paddle 1351; The inner side of the arc-shaped tooth block 121 is provided with a wedge-shaped top block 1212 that cooperates with the outer conical surface of the paddle 1351, and a locking groove 1211 is also provided on the arc-shaped tooth block 121. Under normal operating conditions, the overload triggering unit 13 is in torque transmission state, and the drive disk 135 and the driven disk 134 are pressed together. At this time, the edge of the paddle 1351 is inserted into the locking groove 1211, thereby restricting the arc-shaped tooth block 121 from swinging outward, keeping the gear ring assembly in a closed and locked state, locking the arc-shaped tooth block 121, keeping the gear ring assembly in a closed state, and preventing it from accidentally opening during normal operation. When an overload occurs, the drive disc 135 separates axially from the driven disc 134, and the paddle 1351 moves axially along with the drive disc 135, with its edge disengaging from the locking groove 1211. At the same time, the outer conical surface of the paddle 1351 interacts with the inclined surface of the wedge-shaped top block 1212, pushing the arc-shaped tooth block 121 to overcome the elastic force of the first elastic element 1214 and swing radially outward, thereby disengaging the gear ring assembly from the output planetary gear 1231 and realizing the overload protection function.

[0036] The above-mentioned linkage structure between the locking groove 1211 and the lever 1351: During normal operation, the edge of the paddle 1351 engages with the locking groove 1211, mechanically locking the arc-shaped toothed block 121 to form a rigid self-locking toothed ring, which can withstand a large reverse driving torque and does not require an electromagnetic brake. When overloaded, the paddle 1351 moves axially with the drive disc 135, simultaneously completing the unlocking and pushing actions. It exits the lock groove to release the constraint and actively pushes the arc-shaped toothed block 121 open through the cooperation of the conical surface and the wedge-shaped top block 1212.

[0037] The electric actuator with integrated overload protection described in this embodiment is particularly suitable for applications requiring high reliability and safety, such as valve automation, industrial robot joints, and lifting mechanisms. It is especially suitable for long-term operation in environments without power or in explosion-proof environments. Furthermore, under normal operating conditions, the toothed ring assembly remains closed and locked by the engagement of the paddle 1351 and the locking groove 1211, achieving a mechanical self-locking function without the need for additional brakes or electromagnetic components. This self-locking function and the overload protection function share the same mechanical linkage mechanism, achieving integrated protection lock and working lock, resulting in a compact structure and high reliability.

[0038] It is worth noting that the overload protection mechanism of the present invention can keep the output shaft position unchanged when an overload occurs due to load jamming, because the jamming of the load itself can provide position holding; if the overload is caused by other reasons and power disconnection is required to maintain position, a braking device can be additionally configured (not an essential feature of the present invention).

[0039] In addition, the electric actuator also includes a control unit 2, which is electrically connected to the power unit 3 and is used to receive external control signals and control the start, stop, steering and speed of the power unit 3; and a manual handwheel 4, which is used to selectively transmit torque to the input or output end of the transmission reduction unit 12 through a clutch mechanism (this mechanism is a well-known prior art and will not be described in detail in this solution), for manually driving the load in the power-off or debugging state. The control unit 2 and the manual handwheel 4 are only peripheral auxiliary components and do not affect the core protection scope of the present invention.

[0040] Compared with the existing technology, this solution simultaneously realizes torque transmission, overload sensing and triggering axial displacement through the overload triggering unit 13, and uses the same displacement to drive the input planetary gear 1221 to disengage and the gear ring assembly (composed of arc-shaped tooth blocks 121) to open radially, thereby integrating overload protection and gear ring structure self-locking into one, without the need for additional independent torque limiters or brakes, significantly reducing the axial dimension and overall volume of the actuator.

[0041] It is worth noting that the ends of the teeth of the input planetary gear 1221 have chamfers and inclinations, which is a common self-aligning characteristic of planetary gear systems and does not rely on precise phase alignment.

[0042] When an overload occurs, the trigger displacement of the device can simultaneously disengage the input planetary gear 1221 from the gear ring assembly and the gear ring assembly from the output planetary gear 1231, achieving dual power cut-off on both the input and output sides. Since the gear ring assembly opens radially during an overload, the output planetary gear 1231 completely separates from the gear ring. Therefore, even if there is a reverse driving torque on the load side, it is impossible to reverse drive the opened gear ring assembly through the output planetary gear 1231, effectively avoiding secondary damage and improving the safety of the equipment and operators.

[0043] Under normal operating conditions, the edge of the paddle 1351 on the outer periphery of the drive disc 135 engages in the locking groove 1211 of the arc-shaped toothed block 121, forcing the gear ring assembly to remain in a closed and locked state, preventing the arc-shaped toothed block 121 from swinging outward. This self-locking mechanism is purely mechanical and does not rely on friction, electromagnetic or external control signals, reliably preventing the gear ring from accidentally opening radially under normal operating conditions.

[0044] This design uses a steel ball 1311 and a socket 1312 as an overload sensing element. When an overload occurs, the steel ball 1311 instantly disengages from the socket 1312, resulting in an axial trigger stroke without slippage lag. The drive disc 135 and the driven disc 134 quickly separate, thus triggering two disengagement actions simultaneously. Compared to friction-type torque limiters, the response time is significantly shortened, and the protection action is more precise.

[0045] It is worth noting that the reset mechanism of steel ball 1311 is a conventional function of steel ball torque limiters known in the art, and the specific process is as follows: When overloaded, the steel ball 1311 overcomes the pressure of the second elastic element 132 and is squeezed out of the ball socket 1312, rolling up along the grooved conical surface 1341, causing the drive disk 135 to separate axially from the driven disk 134. When the overload torque disappears, the axial pressure of the second elastic element 132 forces the steel ball 1311 to automatically roll back to the lowest point of the ball socket 1312 along the original ejection path (grooved conical surface 1341), and the drive disk 135 and the driven disk 134 are pressed together again to restore normal torque transmission.

[0046] Furthermore, the second elastic element 132 is a helical compression spring, and with the adjusting nut 133, the preload can be easily adjusted, thereby setting the trigger torque threshold for overload protection online. It can adapt to different operating conditions without disassembling or replacing parts, significantly reducing debugging and maintenance costs.

[0047] The overload triggering unit 13 transmits torque within the normal torque range through the rigid fit between the steel ball 1311 and the ball socket 1312, without slippage loss; at the same time, the locking effect of the paddle 1351 and the locking groove 1211 does not affect the integrity of the gear ring assembly, the planetary gear set maintains full tooth meshing, and the transmission efficiency is comparable to that of a common planetary reducer.

[0048] In summary, this invention achieves overload protection while also ensuring structural compactness, operational reliability, response speed, and ease of adjustment, demonstrating outstanding substantive features and significant progress.

[0049] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. An electric actuator with integrated overload protection function, characterized in that, include: Shell (1); The power unit (3) is mounted on the housing (1); The transmission reduction unit (12) is connected to the power unit (3) for driving the load, and includes an input planetary carrier (122) and an output planetary carrier (123). The gear ring assembly is composed of multiple radially oscillating arc-shaped gear blocks (121) spliced ​​together, and has a first elastic element (1214) that causes each arc-shaped gear block (121) to converge toward the center. The planetary gear set includes an input planetary gear (1221) mounted on the input planetary carrier (122) and meshing with the ring gear assembly, and an output planetary gear (1231) mounted on the output planetary carrier (123) and meshing with the ring gear assembly. An overload triggering unit (13) is disposed between the input planetary carrier (122) and the output planetary carrier (123) and is used to generate a trigger displacement that causes the input planetary carrier (122) to separate axially when overloaded; The overload triggering unit (13) transmits torque under normal operating conditions, and the triggering displacement generated when an overload occurs can drive: The input planetary carrier (122) moves axially relative to the gear ring assembly, causing the input planetary gear (1221) to disengage from the gear ring assembly; as well as The arc-shaped tooth block (121) is pushed to move radially outward, causing the gear ring assembly to disengage from the output planetary gear (1231); The overload triggering unit (13) includes: at least one steel ball (1311); Mounting ring (131), which has ball sockets (1312) corresponding to the number and position of steel balls (1311). Drive disk (135) and driven disk (134); And a second elastic element (132) for elastically forcing the drive disk (135) and the driven disk (134) to press against each other. The drive disk (135) is fixedly connected to the input planetary carrier (122) and can move axially with it; the driven disk (134) is fixedly connected to the output planetary carrier (123). When overloaded, the trigger displacement caused by the steel ball (1311) dislodging from the ball socket (1312) manifests as the axial separation of the drive disk (135) and the driven disk (134). The axial separation of the drive disk (135) and the driven disk (134) causes the input planetary carrier (122) to move axially relative to the output planetary carrier (123). The driven disk (134) has a grooved conical surface (1341) on its inner side, and the driving disk (135) has a limiting groove (1352) on the side near the driven disk (134). The two sides of the steel ball (1311) are respectively abutted by the grooved conical surface (1341) and the limiting groove (1352); The outer periphery of the drive disk (135) is provided with an axially extending tapered paddle (1351). The inner side of the arc-shaped tooth block (121) is provided with a wedge-shaped top block (1212) that matches the outer conical surface of the paddle (1351), and a locking groove (1211) is also provided on the arc-shaped tooth block (121). When the overload triggering unit (13) is in normal working condition and the drive disk (135) and the driven disk (134) are pressed together, the edge of the paddle (1351) is inserted into the locking groove (1211) to prevent the arc-shaped tooth block (121) from swinging outward. When the overload trigger unit (13) is overloaded and the drive disk (135) and driven disk (134) are axially separated, the paddle (1351) moves axially with the drive disk (135), and its edge disengages from the locking groove (1211). At the same time, the outer conical surface pushes the arc-shaped tooth block (121) to swing radially outward through the wedge-shaped top block (1212), so that the gear ring assembly disengages from the output planetary gear (1231).

2. The electric actuator with integrated overload protection function as described in claim 1, characterized in that, The second elastic element (132) is a helical compression spring, which is fitted around the outer periphery of the mounting ring (131); The mounting ring (131) is provided with an external thread, and an adjusting nut (133) is connected through the external thread. One end of the second elastic member (132) abuts against the adjusting nut (133), and the other end abuts against the driven plate (134).

3. The electric actuator with integrated overload protection function as described in claim 1, characterized in that, The transmission reduction unit (12) is a double planetary gear set; The input planetary carrier (122) is equipped with four input planetary gears (1221), and the output planetary carrier (123) is equipped with four output planetary gears (1231).

4. The electric actuator with integrated overload protection function as described in claim 3, characterized in that, The housing (1) is provided with a drive shaft (11), and a drive gear (111) is fixed on the drive shaft (11). The drive gear (111) is connected by the power unit (3). An input sun gear (112) that meshes with each input planetary gear (1221) is coaxially fixed on the drive shaft (11). An elastic abutment (124) is also sleeved on the drive shaft (11). The elastic abutment (124) abuts against the input planetary carrier (122) and is used to apply an axial preload force toward the gear ring assembly to the input planetary carrier (122). An output end assembly plate (125) is rotatably provided inside the housing (1), and an output sun gear (1251) that meshes with each output planetary gear (1231) is coaxially fixed on the output end assembly plate (125).

5. The electric actuator with integrated overload protection function as described in claim 1, characterized in that, The gear ring assembly consists of at least two arc-shaped gear blocks (121), each arc-shaped gear block (121) being hinged to the housing (1) via a hinge (1213); The first elastic element (1214) is any one of the following: a torsion spring installed at the hinge (1213), or a compression spring pressed against the outer edge of the arc-shaped tooth block (121).

6. The electric actuator with integrated overload protection function as described in claim 1, characterized in that, It also includes a control unit (2), which is electrically connected to the power unit (3) and is used to receive external control signals and control the start, stop and steering of the power unit (3); And a manual handwheel (4), which can selectively transmit torque to the input or output end of the transmission reduction unit (12) through a clutch mechanism for manually driving the load.

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