Electrically operated clutch for circuit breaker

Abstract

The application provides a kind of electric operating clutch device of circuit breaker, it relates to the field of circuit breaker structure design.The clutch device includes motor, transmission gear, drive wheel and elastic element;Transmission gear and drive wheel are all set on the output shaft of motor;Drive wheel can rotate with output shaft, also can move along the axial direction of output shaft;Transmission gear can rotate relative to output shaft;The end face of drive wheel is provided with first engagement part, and the end face towards first engagement part of transmission gear is provided with second engagement part;Elastic element is used to act on motor drive wheel, and provides continuous pressure to drive wheel towards second engagement part;When output shaft rotates along positive direction, first engagement part cooperates with second engagement part, so that transmission gear rotates synchronously;When output shaft rotates along the reverse direction opposite to positive direction, the contact surface of first engagement part and second engagement part generates axial force, and realizes the power separation between transmission gear and drive wheel.The clutch device is compact in structure, and the overall reliability is improved.

Description

Technical Field

[0001] This application relates to the field of circuit breaker structural design, and more particularly to a clutch device for electrically operated circuit breakers. Background Technology

[0002] As a critical overload and short-circuit protection component in power systems, the reliability, safety, and service life of circuit breakers directly impact the operational stability of the entire power grid. Modern circuit breakers are generally equipped with electric operating mechanisms. The core of electric operation lies in the motor driving the internal mechanical components of the circuit breaker to complete preset opening or closing actions through gear sets and other transmission mechanisms. However, during electric operation, if the motor rotates in reverse after completing the preset action, its torque may be transmitted in reverse through the transmission mechanism to the circuit breaker operating mechanism, causing malfunctions and seriously threatening equipment safety and operational reliability. Therefore, a clutch device with unidirectional transmission characteristics is needed to effectively separate the transmission gears of the transmission mechanism from the drive wheel during electric operation, so as to completely eliminate the adverse effects of motor reversal on the circuit breaker while ensuring reliable transmission.

[0003] Currently, to address the aforementioned issues, the industry commonly employs traditional clutch structures containing components such as ratchet wheels and pawls. While these solutions achieve basic anti-reverse function, they have significant limitations: First, their structures are typically complex, involving pressure plates, snap rings, riveting parts, and various screws, resulting in a large number of components, a large footprint, and requiring complex processes such as press-fitting, riveting, and multi-screw fixing during manufacturing. This demands high precision in machining and assembly, thus increasing manufacturing costs. Second, the complex structure leads to a longer transmission chain and accumulated clearances between components, resulting in a larger idle stroke of the motor. This affects the response speed and control accuracy of electric operation, hindering the rapid and accurate opening and closing of the circuit breaker. Furthermore, the increased number of components and complex assembly processes also pose challenges to the overall structural strength and long-term service life.

[0004] Therefore, there is an urgent need for a clutch device for electrically operated circuit breakers that reduces the number of parts, simplifies the assembly process, achieves a smaller motor idle stroke and a faster response speed, and has a more compact structure to save installation space. Utility Model Content

[0005] This application provides a clutch device for electrically operated circuit breakers to solve the problems of complex structure and large space occupation, and achieves the goals of greater safety and reliability, longer service life, smaller installation space and lower manufacturing cost.

[0006] In a first aspect, this application provides a clutch device for electrically operated circuit breakers, including a motor, a transmission gear, a drive wheel, and an elastic element; the drive wheel is sleeved on the output shaft of the motor, the output shaft is used for the rotation of the drive wheel, and a first meshing part is provided on the end face of the drive wheel; the drive wheel and the output shaft are correspondingly connected, so that the drive wheel can rotate with the output shaft and can also move along the axial direction of the output shaft; the transmission gear is sleeved on the output shaft and rotates with the output shaft, so that the transmission gear can rotate relative to the output shaft; a second meshing part is provided on the end face of the transmission gear; the elastic element is used to act on the drive wheel or a component linked to the drive wheel, providing the drive wheel with continuous pressure against the second meshing part; when the output shaft rotates in the forward direction, the drive wheel, under the combined action of torque and the pressure of the elastic element, engages the first meshing part and the second meshing part, and drives the transmission gear to rotate synchronously; when the output shaft rotates in the reverse direction, the contact surface of the first meshing part and the second meshing part generates an axial component force, which overcomes part or all of the pressure of the elastic element, causing the drive wheel to move away from the transmission gear axially, thereby achieving the purpose of power separation between the motor and the transmission gear.

[0007] With the above solution, the clutch device can effectively separate the transmission gear and the drive wheel when the motor reverses by only the cooperation of four key components: motor, transmission gear, drive wheel and elastic element. This greatly reduces the number of parts from the source and has a compact structure, which reduces material costs, simplifies the assembly process, reduces potential failure points and improves overall reliability.

[0008] The drive wheel and transmission gear are mounted on the motor's output shaft. All core components are arranged around and installed on the motor's output shaft, forming a compact axially integrated structure. This significantly saves radial installation space and meets the miniaturization design requirements of the circuit breaker. The drive wheel is correspondingly connected to the output shaft, allowing it to rotate with and move axially along the output shaft. The transmission gear is mounted on the output shaft and rotates relative to it, achieving complete separation of power. This ensures that when the drive wheel and transmission gear clutch are disengaged, the transmission gear and subsequent load are completely decoupled from the motor, physically eliminating any possible transmission of reverse torque and completely preventing malfunctions.

[0009] By placing the second engagement portion on the end face, the number of engagement points can be flexibly controlled, and the cooperative contact between the first and second engagement portions ensures smooth transmission and high load-bearing capacity. Simultaneously, this layout continues axially without increasing radial dimensions, maintaining structural compactness. An elastic element provides continuous pressure against the second engagement portion, effectively providing an automatic, normally closed engagement force to the drive wheel. The elastic element (such as a spring) is a low-cost, high-reliability standard component. It provides bidirectional functionality: ensuring reliable engagement between the drive wheel and transmission gear when the output shaft rotates in the forward direction; and when the output shaft rotates in the reverse direction, the constant pressure provided by the elastic element keeps the drive wheel axially away from the transmission gear without disengaging, ensuring stable and reliable clutch performance. When the output shaft rotates in the forward direction, efficient power transmission is achieved with minimal idle travel and extremely fast response, facilitating precise control of the circuit breaker and improving the performance of electric operation. When the output shaft rotates in the reverse direction, power transmission is prevented, eliminating the risk of misoperation and protecting the electric operating mechanism. Meanwhile, the separation process is mechanical and automatic, requiring no sensors or complex control logic, resulting in high reliability and low cost.

[0010] In one possible design, the motor's output shaft has a first mating shaft section and a second mating shaft section; the first mating shaft section has a circular cross-section, and the transmission gear has a circular hole at its center, which rotatably engages with the first mating shaft section, allowing the transmission gear to rotate independently of the output shaft when it is fitted onto the first mating shaft section; the second mating shaft section has an irregular cross-section, and the drive wheel has a corresponding irregularly shaped feature hole at its center, which engages with the second mating shaft section, allowing the drive wheel to rotate with the output shaft when it is fitted onto the second mating shaft section.

[0011] Through the above scheme, the motor's output shaft has a first mating shaft section and a second mating shaft section. In other words, the shaft is structurally and functionally divided into two distinct areas, allowing each shaft section to be optimally designed and manufactured for its specific function (rotational engagement or sliding transmission). This fundamentally improves overall performance and simplifies the manufacturing process. The transmission gear has a central hole that rotatably engages with the first mating shaft section. When the drive wheels reverse direction and separate, the transmission gear and the motor output shaft can achieve completely free relative rotation without torque transmission, resulting in extremely high safety and reliability.

[0012] The second mating shaft section has an irregular cross-section, providing an efficient and compact torque transmission path. Irregular cross-sections (such as D-shaped sections, splines, etc.) are the simplest solution for transmitting torque and allowing axial movement. A corresponding irregularly shaped feature hole is located at the center of the drive wheel, forming an integrated, highly efficient transmission-sliding pair. This feature hole and the irregularly shaped shaft section form a precise fit. This ensures that the motor torque can be transmitted to the drive wheel without delay or loss, with a fast response speed. While transmitting huge torque, it also ensures the flexibility of axial sliding, which is the physical basis for realizing clutch action. When the motor drives the output shaft to rotate in the forward direction, the drive wheel and the output shaft act as a single unit, ensuring that all torque is transmitted to the transmission gear to drive the circuit breaker. Therefore, the circular shaft section (the first mating shaft section) is dedicated to supporting the transmission gear and allowing the output shaft to idle, while the irregularly shaped shaft section (the second mating shaft section) is dedicated to transmitting torque and allowing the drive wheel to move axially relative to the output shaft, making the functions of each part clear and non-interfering. During assembly, the installation position and function of the transmission gear and drive wheel are immediately apparent, improving assembly accuracy and efficiency.

[0013] In one possible design, the second meshing part or the first meshing part is a one-way toothed structure; the one-way toothed structure has a working surface and a non-working surface; correspondingly, the first meshing part or the second meshing part has a mating toothed structure, the mating toothed structure having a first contact surface that mates with the working surface and a second contact surface that mates with the non-working surface; when the output shaft rotates in the forward direction, the working surface engages with the first contact surface to generate a thrust that causes the drive wheel to move toward the transmission gear, without generating an axial component force that separates the two; when the output shaft rotates in the reverse direction, the non-working surface engages with the second contact surface to generate an axial component force that causes the drive wheel to move axially away from the transmission gear.

[0014] Through the above scheme, the second meshing part and the first meshing part are mutually cooperating structures. The one-way tooth structure has a working surface that can realize torque transmission, and also a non-working surface that can realize the separation of the drive wheel shaft and the transmission gear. The complex clutch control logic is transformed into a simple and reliable mechanical structure, which successfully improves performance and reliability while simplifying the structure and reducing costs.

[0015] In one possible design, the unidirectional toothed structure is continuously or intermittently distributed around the circumference of the output shaft.

[0016] The above scheme utilizes a continuous, circular distribution to increase the number of contact points, eliminating the need to wait for a specific "alignment angle" and enabling instantaneous engagement at any circumferential position. This results in minimal motor idle travel, facilitating rapid and precise control of the circuit breaker. Because of the continuous multi-tooth simultaneous contact, the load is evenly distributed across multiple teeth, preventing stress concentration and enabling the transmission of greater torque. This leads to extremely high structural strength and reliability. Furthermore, the continuous engagement ensures smooth power transmission, reduces impact and vibration, and results in quieter operation.

[0017] In the intermittent distribution method, the unidirectional toothed structures are discretely distributed on the circumference at certain intervals. For example, they can be set as discontinuous unidirectional toothed structures, with blank areas without teeth between them. This reduces the difficulty of high-precision, continuous machining of the entire circumference, allows for larger manufacturing tolerances, and significantly reduces manufacturing costs. When the motor is idling in reverse, the drive wheel periodically passes through these intermittent unidirectional toothed structures, producing a rhythmic "click" sound. This sound serves as a clear auditory indication, telling the operator that the clutch is in disengagement protection mode, improving the user-friendliness of human-machine interaction.

[0018] In one possible design, the non-working surface is an inclined plane or curved surface that is tilted relative to the axial direction of the output shaft.

[0019] With the above scheme, when the motor rotates forward, the working surfaces of the drive wheel and the transmission gear are two parallel planes that are in close contact and pushing each other. The force between the two parallel planes is perpendicular to the contact surface. Since the contact surface is parallel to the axis, this force is a pure tangential force used to drive rotation, without generating any axial component that pushes them apart or pulls them closer. This achieves efficient and lossless power transmission. The planar contact provides the largest contact area, can withstand high surface pressure, has a large transmission torque, and high strength. When the motor rotates in reverse, the non-working surface of the drive wheel collides and is squeezed against the non-working surface (two inclined planes) of the transmission gear. The force acting on the inclined plane can be decomposed into a tangential component (attempting to rotate) and a normal component. This normal component is perpendicular to the inclined plane, and when the inclined plane is tilted, this force necessarily contains a strong axial component, the direction of which is to push the drive wheel away from the transmission gear. This axial component is spontaneous and directly triggered by the reverse action. As long as the motor torque is large enough, it can overcome the spring pressure to achieve separation, resulting in high reliability. When power transmission is required, the interaction of parallel planes achieves zero-loss, high-efficiency, and high-rigidity power engagement. When power disconnection is required, the interaction of inclined surfaces intelligently and automatically converts rotational motion into reliable axial separation motion. This design transforms complex control logic into a simple mechanical structure, ensuring that the entire device simultaneously possesses excellent characteristics such as high transmission efficiency, rapid response, high reliability, and long service life.

[0020] In one possible design, the outer side of the transmission gear has a gear structure.

[0021] With the above scheme, the gear structure set on the outside serves as the power output interface for the transmission gear, which outputs the torque from the motor or the torque from the manual operating mechanism through the gear structure. In one possible design, the drive wheel periodically contacts or disengages from the second engagement portion as the output shaft rotates in the opposite direction.

[0022] Through the above scheme, when the motor reverses, the drive wheel will not completely lock or continuously rub against the transmission gear (second meshing part), but will instead be in a cyclical dynamic process of "contact-push-re-contact-push-re-push." ​​Under spring pressure, the contact surface on the drive wheel meets and collides with the non-working surface (inclined surface) of the transmission gear meshing part. The interaction of the inclines generates a strong axial force, which overcomes the spring pressure and pushes the drive wheel backward, disengaging the two and interrupting power. After the drive wheel is pushed away, since it is still rotating, it will pass the top of the tooth or protrusion currently corresponding to the first meshing part. Simultaneously, the spring pressure immediately pushes it back to its original position. The drive wheel rotates to the position of the next tooth or protrusion, repeating the above contact-disengagement steps again. This process repeats at a very high frequency. This periodic contact and disengagement is accompanied by a clear, rhythmic "click-click" sound or similar mechanical noise, providing the operator with intuitive auditory feedback without the need for visual inspection. Once this sound is heard, it can be clearly determined that the clutch is in a "reverse idling" protection state, rather than a malfunction and jamming, which greatly improves the user-friendliness of human-machine interaction and the knowability of equipment status.

[0023] In one possible design, a limiting part is provided on the side of the drive wheel away from the second engagement part, and one end of the elastic element is inserted into the limiting part, which is used to restrict the lateral movement of the elastic element.

[0024] The above-described scheme involves machining a limiting part on the side of the drive wheel away from the engagement part (i.e., the side subjected to spring pressure). This limiting part is a groove, a raised annular wall, or a similar surrounding structure, designed to accommodate one end of the elastic element (such as a spring) and confine it within that area. During assembly, one end of the elastic element can be inserted into this limiting part. Regardless of whether the device is stationary, in forward drive, or in reverse disengagement, this limiting part always radially surrounds the end of the spring. This effectively prevents the spring from lateral bending, slipping, or shifting under pressure. It ensures that the pressure applied by the spring to the drive wheel is always along the axial direction of the output shaft, avoiding drive wheel tilting, jamming, or abnormal wear caused by lateral forces. This effectively guarantees the smoothness, consistency, and high reliability of the clutch engagement and disengagement actions.

[0025] In one possible design, a pressure plate is also included, which is fixed to the motor housing to provide axial restraint for the elastic element.

[0026] The above solution adds an independent pressure plate at the end of the elastic element (spring) away from the drive wheel. This pressure plate is fixed to the motor housing or to another nearby, stable fixed structure inside the circuit breaker using screws, clips, or other means. The pressure plate, elastic element, drive wheel, and transmission gear together form a complete force transmission chain. The pressure plate, as a fixed reference point, provides reverse support for the elastic element. The elastic element is compressed between the pressure plate and the limiting part on the drive wheel. By adjusting the fixed position of the pressure plate or using screws of different lengths, the compression of the spring can be finely adjusted, thereby precisely controlling the preload required for engagement. This ensures the consistency of the clutch engagement force, avoiding problems such as difficulty in disengagement due to excessive preload or insufficient torque transmission due to insufficient preload, significantly improving the performance consistency and reliability of the product.

[0027] In one possible design, the elastic element is a compression spring, with one end of the compression spring abutting against the pressure plate and the other end abutting against the limiting part.

[0028] The above solution demonstrates that the compression spring operates on a simple principle and possesses stable physical properties. The compression spring provides stable, smooth, and continuous axial pressure, and its cooperation with the pressure plate and limiting part ensures coaxial force, resulting in very smooth movement and engagement of the drive wheel.

[0029] The above description is merely an overview of the technical solutions of the embodiments of this application. In order to better understand the technical means of the embodiments of this application and to implement them in accordance with the contents of the specification, and to make the above and other objects, features and advantages of the embodiments of this application more obvious and understandable, specific implementation methods of this application are described below. Attached Figure Description

[0030] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0031] Figure 1 This is a cross-sectional view of a circuit breaker electrically operated clutch device provided in one embodiment of this application.

[0032] Figure 2 This is a schematic diagram of the motor rotating forward in the clutch device of the electrically operated circuit breaker provided in one embodiment of this application.

[0033] Figure 3 for Figure 2 Enlarged schematic diagram of region A in the middle.

[0034] Figure 4 This is a schematic diagram of the motor reversing in the clutch device of the electrically operated circuit breaker provided in one embodiment of this application.

[0035] Figure 5 for Figure 4 A magnified view of region B in the middle.

[0036] Figure 6 This is a schematic diagram of a motor structure provided in one embodiment of this application.

[0037] Figure 7 This is a schematic diagram of the drive wheel provided in one embodiment of this application from one perspective.

[0038] Figure 8 This is a schematic diagram of the drive wheel provided in one embodiment of this application from another perspective.

[0039] Figure 9 This is a schematic diagram of the transmission gear provided in one embodiment of this application.

[0040] Explanation of reference numerals in the attached figures: 100. Motor; 101. Motor mounting hole; 110. First mating shaft section; 120. Second mating shaft section; 200. Drive wheel; 210. First meshing part; 211. Non-working surface of drive wheel; 212. Working surface of drive wheel; 220. Feature hole; 230. Limiting part; 300. Transmission gear; 310. Second meshing part; 311. Non-working surface of transmission gear; 312. Working surface of transmission gear; 320. Circular hole; 330. Gear structure; 400. Elastic element; 500. Pressure plate. Detailed Implementation To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0041] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used herein in the specification of the application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms “comprising” and “having”, and any variations thereof, in the specification, claims and drawings of this application are intended to cover non-exclusive inclusion.

[0042] The term "embodiment" as used herein means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of the phrase "embodiment" in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0043] In this article, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can mean: A exists, A and B exist simultaneously, or B exists. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0044] The directional terms appearing in the following description refer to the directions shown in the figures and are not intended to limit the specific structure of this application. For example, in the description of this application, the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the figures. They are only for the convenience of describing this application 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, they should not be construed as limitations on this application.

[0045] Furthermore, the terms "first," "second," etc., in the specification and claims of this application or in the aforementioned drawings are used to distinguish different objects rather than to describe a specific order, and may explicitly or implicitly include one or more of the features.

[0046] In the description of this application, unless otherwise stated, "multiple" means two or more (including two), and similarly, "multiple groups" means two or more (including two groups).

[0047] In the description of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, "connection" or "joining" in mechanical structures can refer to a physical connection, such as a fixed connection, for example, a connection fixed by a partition, such as a connection fixed by screws, bolts, or other partitions; a physical connection can also be a detachable connection, such as a snap-fit ​​or interlocking connection; a physical connection can also be an integral connection, such as a connection formed by welding, bonding, or integral molding. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0048] As the background technology shows, in a clutch device, the forward rotation of the motor, which is designed to drive the motor, drives the circuit breaker to complete the preset opening or closing action through the transmission gears and their connected gear sets. However, when the motor rotates in reverse, a clutch setting is required to prevent the motor from driving the transmission gears and their connected gear sets. In related technologies, traditional clutch structures containing ratchet wheels and pawls are commonly used. While this approach can achieve basic anti-reverse function, it has significant limitations: First, its structure is usually quite complex, involving pressure plates, snap rings, riveting components, and various screws, resulting in a large number of parts, a large space requirement, and reliance on complex processes such as press-fitting, riveting, and multi-screw fixing during manufacturing. This demands high precision in machining and assembly, thus increasing manufacturing costs. Second, the complex structure also leads to a longer transmission chain and accumulated clearances between parts, resulting in a larger idle stroke of the motor. This affects the response speed and control accuracy of electric operation, hindering the rapid and accurate opening and closing of the circuit breaker. Furthermore, the increased number of parts and complex assembly processes also pose challenges to its overall structural strength and long-term service life. In view of this, this application provides a clutch device for electrically operated circuit breakers, including a motor, a transmission gear, a drive wheel, and an elastic element; both the transmission gear and the drive wheel are mounted on the output shaft of the motor; the drive wheel can rotate with the output shaft and can also move axially along the output shaft; the transmission gear can rotate relative to the output shaft; a first meshing portion is provided on the end face of the drive wheel, and a second meshing portion is provided on the end face of the transmission gear facing the first meshing portion; the elastic element acts on the drive wheel or a component linked to the drive wheel, providing continuous pressure to the drive wheel against the second meshing portion; when the motor drives the output shaft to rotate in the forward direction, the drive wheel, under the combined action of torque and the pressure of the elastic element, engages with the first meshing portion and the second meshing portion, driving the transmission gear to rotate synchronously; when the motor drives the output shaft to rotate in the opposite direction, the contact surface of the first meshing portion and the second meshing portion generates an axial component force, overcoming part or all of the pressure of the elastic element, causing the drive wheel to move axially away from the transmission gear, thereby achieving the purpose of power separation between the motor and the transmission gear. The number of parts has been significantly reduced, material costs have been lowered, assembly processes have been simplified, potential failure points have been reduced, and overall reliability has been improved. To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings.

[0049] Figure 1 This is a cross-sectional view of the electrically operated clutch device for a circuit breaker provided in this embodiment. Figure 2 This is a schematic diagram of the motor rotating forward in the electrically operated clutch device of the circuit breaker provided in this embodiment. Figure 3 for Figure 2 Enlarged schematic diagram of region A in the middle. Figure 4 This is a schematic diagram of the motor reversing in the electrically operated clutch device of the circuit breaker provided in this embodiment. Figure 5 for Figure 4 A magnified view of region B in the middle. Please refer to this diagram. Figures 1 to 5 This application provides a clutch device for electrically operated circuit breakers, including a motor 100, a transmission gear 300, a drive wheel 200, and an elastic element 400.

[0050] Both the transmission gear 300 and the drive wheel 200 are mounted on the output shaft of the motor 100; the drive wheel 200 can rotate with the output shaft and can also move along the axial direction of the output shaft; the transmission gear 300 can rotate relative to the output shaft. The output shaft on the motor 100 is used to output torque, and the drive wheel 200 and the transmission gear 300 are mounted on the output shaft of the motor 100.

[0051] It is understood that the output shaft is the medium through which the motor 100 outputs torque. Therefore, in this embodiment, the forward rotation of the motor 100 means that the motor 100 drives the output shaft to rotate in the forward direction, and the reverse rotation of the motor 100 means that the motor 100 drives the output shaft to rotate in the reverse direction.

[0052] In this embodiment, the transmission gear 300 is sleeved below the drive wheel 200.

[0053] In some embodiments, the drive wheel 200 is mounted below the transmission gear 300.

[0054] A first meshing part 210 is provided on the end face of the drive wheel 200.

[0055] In this embodiment, a second meshing portion 310 is provided on the end face of the transmission gear 300 facing the first meshing portion 210.

[0056] In this embodiment, the outer side of the transmission gear 300 also has a gear structure 330. The gear structure 330 is the power output interface of the transmission gear 300. The transmission gear 300 outputs the torque from the motor 100 or the torque from the manual operating mechanism to the load connected to the gear structure 330 through the gear structure 330.

[0057] The elastic element 400 is used to act on the drive wheel 200 or a component linked to the drive wheel 200 to provide the drive wheel 200 with continuous pressure against the second engagement part 310.

[0058] When the motor 100 drives the output shaft to rotate in the forward direction, the drive wheel 200, under the combined action of torque and pressure from the elastic element 400, engages with the first meshing part 210 and the second meshing part 310, and drives the transmission gear 300 to rotate synchronously.

[0059] When the output shaft of the motor 100 rotates in the opposite direction to the forward direction, the contact surface of the first meshing part 210 and the second meshing part 310 generates an axial component force, which overcomes part or all of the pressure of the elastic element 400, causing the drive wheel 200 to move away from the transmission gear 300 axially, thereby achieving the purpose of power separation between the motor 100 and the transmission gear 300.

[0060] The elastic element 400 is used to provide a continuous force for the drive wheel 200 and the transmission gear 300 to cooperate. Therefore, the force of the elastic element 400 can be a continuous pressure on the drive wheel 200, or it can act on the drive wheel 200 by pressing on the component linked with the drive wheel 200, so that the first meshing part 210 always presses against the second meshing part 310.

[0061] In this embodiment, "positive" means clockwise and "negative" means counterclockwise.

[0062] In some other embodiments, the forward direction can be counterclockwise, and the reverse direction can be clockwise.

[0063] The solution in this embodiment enables the clutch device to effectively separate the transmission gear 300 from the drive wheel 200 when the motor 100 reverses, using only the cooperation of four key components: motor 100, transmission gear 300, drive wheel 200, and elastic element 400. This significantly reduces the number of parts from the source and results in a compact structure, which reduces material costs, simplifies the assembly process, reduces potential failure points, and improves overall reliability.

[0064] The drive wheel 200 and transmission gear 300 are mounted on the output shaft of the motor 100. All core components are arranged around and mounted on the output shaft of the motor 100, forming a compact axially integrated structure. This greatly saves radial installation space and meets the design requirements for miniaturization of the circuit breaker. The drive wheel 200 is correspondingly connected to the output shaft, allowing it to rotate with the output shaft and move axially along it. The transmission gear 300 is mounted on the output shaft and rotates with it, allowing it to rotate relative to the output shaft. This achieves complete separation of power and ensures that when the clutch of the drive wheel 200 and transmission gear 300 is disengaged, the transmission gear 300 and its connected load are completely decoupled from the motor 100. This physically eliminates any possible transmission of reverse torque from the motor 100, completely preventing malfunctions.

[0065] The second engagement portion 310 is positioned on the end face, allowing for flexible control of the number of engagement points. The mating contact between the first engagement portion 210 and the second engagement portion 310 ensures smooth transmission and high load-bearing capacity. Simultaneously, this layout continues axially without increasing radial dimensions, maintaining structural compactness. The elastic element 400 provides continuous pressure against the second engagement portion 310, effectively providing an automatic, normally closed engagement force to the drive wheel 200. The elastic element 400 (such as a spring) is a low-cost, high-reliability standard component. It provides bidirectional functionality: ensuring reliable engagement between the drive wheel 200 and the transmission gear 300 when the output shaft rotates in the forward direction; and providing constant pressure when the output shaft rotates in the reverse direction, keeping the drive wheel 200 axially away from the transmission gear 300 without disengaging, thus ensuring stable and reliable clutch performance. When the output shaft rotates in the forward direction, efficient, slip-free power transmission is achieved, with minimal free travel and extremely fast response, facilitating precise control of the circuit breaker and improving the performance of electric operation. When the output shaft rotates in the opposite direction, power transmission is prevented, eliminating the risk of misoperation and protecting the electric operating mechanism. Simultaneously, the separation process is mechanical and automatic, requiring no sensors or complex control logic, resulting in high reliability and low cost.

[0066] Figure 6This is a schematic diagram of the structure of the motor 100 provided in this embodiment. Figure 7 This is a schematic diagram of the drive wheel 200 provided in this embodiment from one perspective. Figure 8 This is a structural schematic diagram of the drive wheel 200 provided in this embodiment from another perspective. Figure 9 This is a schematic diagram of the transmission gear 300 provided in this embodiment. Please refer to it. Figures 6 to 9 In this embodiment, the output shaft of the motor 100 has a first mating shaft section 110 and a second mating shaft section 120. The cross-section of the first mating shaft section 110 is circular, and the center of the transmission gear 300 is provided with a circular hole 320. The circular hole 320 is rotatably engaged with the first mating shaft section 110, so that the transmission gear 300 can rotate independently of the output shaft when it is fitted onto the first mating shaft section 110. The cross-section of the second mating shaft section 120 is irregular, and the center of the drive wheel 200 is provided with a corresponding irregularly shaped feature hole 220. The feature hole 220 is engaged with the second mating shaft section 120, so that the drive wheel 200 can rotate with the rotation of the output shaft when it is fitted onto the second mating shaft section 120.

[0067] The cross-sectional shape of the feature hole 220 is an irregular shape corresponding to the cross-section of the second mating shaft segment 120.

[0068] like Figure 6 As shown, in this embodiment, the irregular shape is set as a cylindrical output shaft with some material removed from both sides.

[0069] In some embodiments, a portion of the material may be removed from one side of the output shaft, or other keyway mating mechanisms may be used, such as D-shaped cuts, splines, etc. Since the feature hole 220 is connected to the irregular shape, when the output shaft rotates, it can drive the drive wheel 200 to rotate.

[0070] Through the above embodiments, the output shaft of the motor 100 is divided into a first mating shaft section 110 and a second mating shaft section 120. In other words, a shaft is divided into two distinct areas in terms of structure and function, so that each shaft section can be optimally designed and processed for its specific function (rotational mating or sliding transmission), thereby fundamentally improving the overall performance and simplifying the process.

[0071] like Figure 9 As shown, in this embodiment, the transmission gear 300 has a central hole 320, which rotates with the first mating shaft section 110. When the drive wheel 200 separates in the opposite direction, there is no connection between the transmission gear 300 and the output shaft of the motor 100, allowing for completely free rotation and absolutely preventing the transmission of any reverse torque, resulting in extremely high safety and reliability. This structure allows the manual operating mechanism to directly drive the transmission gear 300 without being restricted by the motor 100, achieving perfect compatibility between electric and manual modes.

[0072] In this embodiment, any cross-section of the circular hole 320 is circular.

[0073] like Figure 7 and Figure 8 The second mating shaft segment 120 has an irregular cross-section, providing an efficient and compact torque transmission path. An irregular cross-section is the simplest solution for transmitting torque and allowing axial movement. The drive wheel 200 has a corresponding irregularly shaped feature hole 220 at its center, forming an integrated, high-efficiency transmission-sliding pair. This feature hole 220 forms a precise fit with the irregular shaft segment. This ensures that the torque of the motor 100 can be transmitted to the drive wheel 200 without delay or loss, with a fast response speed. While transmitting huge torque, it also ensures the flexibility of axial sliding, which is the physical basis for realizing clutch action. When the motor 100 drives the output shaft to rotate in the forward direction, the drive wheel 200 and the output shaft act as a single unit, ensuring that all torque can be transmitted to the transmission gear 300 to drive the circuit breaker. Therefore, the circular shaft segment (first mating shaft segment 110) is dedicated to supporting the transmission gear 300 and allowing the output shaft to idle, while the irregularly shaped shaft segment (second mating shaft segment 120) is dedicated to transmitting torque and allowing the drive wheel 200 to move axially relative to the output shaft, making the functions of each part clear and non-interfering. During assembly, the installation position and function of the transmission gear 300 and the drive wheel 200 are immediately apparent, improving assembly accuracy and efficiency.

[0074] It is understood that the second engagement part 310 and the first engagement part 210 can be toothed structures or protrusions. The toothed structures and protrusions are continuously distributed around or spaced apart along the circumference of the output shaft. The second engagement part 310 and the first engagement part 210 can cooperate with each other to achieve the clutch function.

[0075] In this embodiment, the second meshing part 310 or the first meshing part 210 is a unidirectional tooth structure; the unidirectional tooth structure has a working surface and a non-working surface.

[0076] It is understandable that the first engaging part 210 and the second engaging part 310 are two mating end faces of the parts. Therefore, the design of the first engaging part 210 and the second engaging part 310 can be flexibly designed and adjusted, as long as the engagement and disengagement effect between the first engaging part 210 and the second engaging part 310 can be achieved.

[0077] When the first meshing part 210 and the second meshing part 310 are configured, the following three schemes can be set up according to the situation: For example, when the first meshing part 210 is a unidirectional toothed structure, the second meshing part 310 can be a mating toothed structure.

[0078] For example, when the second meshing part 310 is a unidirectional toothed structure, the first meshing part 210 can be a mating toothed structure.

[0079] The toothed structure has a first contact surface that mates with the working surface and a second contact surface that mates with the non-working surface. When the output shaft rotates in the forward direction, the working surface engages with the first contact surface to generate a thrust toward the transmission gear 300 without generating an axial component force that separates the two. When the output shaft rotates in the reverse direction, the non-working surface engages with the second contact surface to generate an axial component force that moves the drive wheel 200 axially away from the transmission gear 300.

[0080] Understandably, the purpose of a mating tooth structure is to match a unidirectional tooth structure in order to transmit torque or to axially separate the drive wheel and the transmission gear. Therefore, a mating tooth structure can be the same as or different from a unidirectional tooth structure.

[0081] For example, in cases where the tooth profile and unidirectional tooth profile are the same: please refer to section 3 and... Figure 5 Both the first meshing part 210 and the second meshing part 310 are complementary unidirectional toothed structures.

[0082] When the mating tooth structure and the unidirectional tooth structure are different, the mating tooth structure can be a discontinuous protrusion design. The first contact surface can be a plane or arc surface that can contact the working surface, and the second contact surface can be a plane or arc surface that contacts the non-working surface.

[0083] In this embodiment, when the motor 100 rotates forward, since the working surface is designed not to generate axial force, the rotational torque of the motor 100 can be efficiently and almost losslessly converted into the driving force of the transmission gear 300, resulting in fast response and high transmission efficiency. When the motor 100 rotates in reverse, the non-working surfaces (inclined or curved surfaces) of the first meshing part 210 and the second meshing part 310 come into contact. When the drive wheel 200 attempts to push the transmission gear 300, this force is decomposed into tangential and axial components on the inclined surface. The tangential component attempts to drive the transmission gear 300 but is offset by load resistance. The axial component pushes the drive wheel 200 away from the transmission gear 300. When this axial component is greater than the preload provided by the elastic element 400, the drive wheel 200 is forced to move axially backward, compressing the spring. Once axial clearance is generated, the mechanical engagement between the two is released, the torque transmission path is cut off, power separation is achieved, and the motor 100 enters an idling state. Through the mechanical design of this scheme, the complex clutch control logic is transformed into a simple and reliable mechanical structure, which successfully improves performance and reliability while simplifying the structure and reducing costs.

[0084] Please continue to refer to this. Figure 3 and Figure 5In this embodiment, the non-working surface is an inclined plane or curved surface that is axially inclined relative to the output shaft, and the working surface is a plane that is perpendicular to the end face of the transmission gear 300. The cross-section of the one-way tooth structure is a right-angled triangle.

[0085] With the above scheme, when the motor 100 rotates forward, the working surface 212 of the drive wheel and the working surface 312 of the transmission gear are two parallel planes that are in close contact and pushing each other. The force between the two parallel planes is perpendicular to the contact surface. Since the contact surface is parallel to the axis, this force is a purely tangential force used to drive rotation, without generating any axial component that pushes them apart or pulls them closer. This achieves efficient and lossless power transmission. The planar contact provides the largest contact area, can withstand high surface pressure, has a large transmission torque, and high strength.

[0086] When motor 100 reverses, the non-working surface 211 of the drive wheel collides and is pressed against the non-working surface 311 of the transmission gear (two inclined planes). The force acting on the inclined planes can be decomposed into a tangential component (attempting to rotate) and a normal component. This normal component is perpendicular to the inclined planes, and when the inclined planes are tilted, this force necessarily includes a strong axial component (axial direction refers to the direction parallel to the drive shaft). The direction of this component is to push the drive wheel 200 away from the transmission gear 300. This axial component is spontaneous and directly triggered by the reversing action. As long as the torque of motor 100 is large enough, it can definitely overcome the spring pressure to achieve separation, resulting in high reliability.

[0087] In this embodiment, the unidirectional toothed structure is continuously distributed around or spaced along the circumference of the output shaft.

[0088] The continuous, circular distribution results in a large number of contact points, eliminating the need to wait for a specific "alignment angle" and enabling instantaneous engagement at any circumferential position. The motor's idle travel is minimal, facilitating rapid and precise control of the circuit breaker. Because of the continuous multi-tooth simultaneous contact, the load is evenly distributed across multiple teeth, avoiding stress concentration and enabling the transmission of greater torque. This results in extremely high structural strength and reliability. Furthermore, the continuous engagement ensures smooth power transmission, reduces impact and vibration, and makes operation quieter.

[0089] In the case of intermittent distribution, the unidirectional toothed structures are discretely distributed on the circumference at certain intervals. For example, they can be set as discontinuous unidirectional toothed structures, with blank areas without teeth between them. This reduces the difficulty of high-precision, continuous machining of the entire circumference, allows for larger manufacturing tolerances, and significantly reduces manufacturing costs. When the motor 100 rotates in reverse, the drive wheel 200 periodically passes through these intermittent unidirectional toothed structures, producing a rhythmic "clicking" sound. This sound serves as a clear auditory indication, telling the operator that the clutch is in disengagement protection mode, thus improving the user-friendliness of human-machine interaction.

[0090] In this embodiment, when the motor 100 rotates in the opposite direction, the drive wheel 200 periodically contacts or disengages from the second engagement part 310.

[0091] Understandably, when the motor 100 reverses, the drive wheel 200 does not completely lock or continuously rub against the transmission gear 300 (second meshing part 310), but rather is in a cyclical dynamic process of "contact-push-re-contact-push-re-push." ​​Under spring pressure, the contact surface on the drive wheel 200 meets and collides with the non-working surface (inclined surface) of the meshing part of the transmission gear 300. The interaction of the inclined surfaces generates a strong axial force, which overcomes the spring pressure and pushes the drive wheel 200 backward, disengaging the two and interrupting power. After the drive wheel 200 is pushed away, since it is still rotating, it will pass the top of the tooth or protrusion currently corresponding to the first meshing part 210. Simultaneously, the spring pressure immediately pushes it back to its original position. The drive wheel 200 rotates to the position of the next tooth or protrusion, repeating the above contact-disengagement steps again. This process repeats itself at a very high frequency. This periodic engagement and disengagement is accompanied by a clear, rhythmic "clicking" sound or similar mechanical noise. This provides operators with intuitive auditory feedback without the need for visual inspection. Upon hearing this sound, it is immediately clear that the clutch is in a "reverse idling" protection state, rather than malfunctioning and stuck, greatly improving the user-friendliness of the human-machine interface and the visibility of the equipment's status.

[0092] In this embodiment, the elastic element 400 can be a tension spring or a compression spring.

[0093] One end of the tension spring can be fixed to the drive wheel 200, and the other end can be fixed to the side away from the drive wheel 200. The tension of the tension spring should be able to always pull the drive wheel 200 toward the transmission gear 300.

[0094] In this embodiment, the elastic element 400 is set as a compression spring, with one end of the compression spring abutting against the drive wheel and the other end abutting against the side away from the drive wheel 200, so that the pressure of the compression spring can always press the drive wheel 200 against the transmission gear 300.

[0095] Please refer to Figure 8 In this embodiment, a limiting part 230 is provided on the side of the drive wheel 200 away from the second engagement part 310, and one end of the elastic element 400 is inserted into the limiting part 230. The limiting part 230 is used to restrict the lateral movement of the elastic element 400.

[0096] The limiting part 230 can be designed as a continuous or discontinuous protrusion along the outer periphery of the elastic element 400.

[0097] For example, in this embodiment, the outer periphery of the elastic element 400 is circular, and the limiting part 230 is a circular protrusion.

[0098] Through the above-described scheme, a limiting part 230 is machined on the side of the drive wheel 200 away from the engagement part (i.e., the side subjected to spring pressure). This limiting part 230 is a groove, a raised annular wall, or a similar surrounding structure, which serves to accommodate one end of the elastic element 400 (such as a spring) and confine it within this area. During assembly, one end of the elastic element 400 can be inserted into this limiting part 230. Regardless of whether the device is stationary, in forward drive, or in reverse disengagement, the limiting part 230 always radially surrounds the end of the spring. This effectively prevents the spring from bending laterally, slipping, or shifting under pressure. It ensures that the pressure applied by the spring to the drive wheel 200 is always along the axial direction of the output shaft, avoiding tilting, jamming, or abnormal wear of the drive wheel 200 caused by lateral forces. This effectively ensures the smoothness, consistency, and high reliability of the clutch engagement and disengagement actions.

[0099] Please continue to refer to this. Figure 1 In this embodiment, a pressure plate 500 is also included. The pressure plate 500 is fixed to the housing of the motor 100 or an adjacent fixed structure and is used to provide axial limiting for the elastic element 400.

[0100] In this embodiment, an independent pressure plate 500 is added at the other end of the elastic element 400 (spring) away from the drive wheel 200.

[0101] The pressure plate 500 can be fixed to the housing of the motor 100 by means of screws, clips, etc., or fixed to other adjacent and stable fixed structures inside the circuit breaker.

[0102] In this embodiment, the motor 100 is provided with a motor fixing hole 101, through which the pressure plate 500 can be fixed to the motor 100.

[0103] In some other embodiments, the pressure plate 500 may also be fixed to the circuit breaker or to other adjacent, stable fixing structures in the circuit breaker, as long as it can serve to fix the pressure plate 500, with the purpose of providing axial limiting for the elastic element 400.

[0104] The pressure plate 500, elastic element 400, drive wheel 200, and transmission gear 300 together form a complete force transmission chain. The pressure plate 500, as a fixed reference point, provides support for the elastic element 400. The elastic element 400 is compressed between the pressure plate 500 and the limiting part 230 on the drive wheel 200. By adjusting the fixed position of the pressure plate 500 or using screws of different lengths, the compression of the spring can be finely adjusted, thereby precisely controlling the preload required for engagement. This ensures the consistency of the clutch engagement force, avoiding problems such as difficulty in disengagement due to excessive preload or insufficient torque transmission due to insufficient preload, significantly improving the product's performance consistency and reliability.

[0105] In this embodiment, one end of the compression spring abuts against the pressure plate 500, and the other end abuts against the limiting part 230.

[0106] The above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application.

Claims

1. A clutch device for electrically operated circuit breakers, characterized in that, include: Motor, transmission gears, drive wheel, and elastic elements; Both the transmission gear and the drive wheel are mounted on the output shaft of the motor; the drive wheel can rotate with the output shaft and can also move along the axial direction of the output shaft; the transmission gear can rotate relative to the output shaft. The drive wheel has a first meshing part on its end face, and the transmission gear has a second meshing part on its end face facing the first meshing part. The elastic element acts on the motor drive wheel to provide a continuous pressure to the drive wheel against the second engagement part. When the motor drives the output shaft to rotate in the positive direction, the first meshing part and the second meshing part engage under the combined action of torque and pressure of the elastic element, and drive the transmission gear to rotate synchronously. When the motor drives the output shaft to rotate in the opposite direction to the forward direction, the contact surface between the first meshing part and the second meshing part generates an axial component force, which overcomes part or all of the pressure of the elastic element, causing the drive wheel to move away from the transmission gear axially, thereby achieving the purpose of power separation between the motor and the transmission gear.

2. The clutch device according to claim 1, characterized in that, The output shaft of the motor has a first mating shaft section and a second mating shaft section; The first mating shaft section has a circular cross-section, and the transmission gear has a circular hole at its center. The circular hole is rotatably fitted with the first mating shaft section, so that the transmission gear can rotate relative to the output shaft. The cross-section of the second mating shaft section is irregular, and the center of the drive wheel is provided with a feature hole corresponding to the irregular shape. The feature hole is fitted with the second mating shaft section, so that the drive wheel can rotate with the rotation of the output shaft.

3. The clutch device according to claim 1, characterized in that, The second meshing part or the first meshing part is a unidirectional toothed structure; the unidirectional toothed structure has a working surface and a non-working surface; Correspondingly, The first or second meshing part has a mating tooth structure, which has a first contact surface that mates with the working surface and a second contact surface that mates with the non-working surface; When the output shaft rotates in the positive direction, the working surface engages with the first contact surface to generate a thrust that causes the drive wheel to move toward the transmission gear, without generating an axial component force that would separate the two. When the output shaft rotates in the opposite direction, the non-working surface engages with the second contact surface to generate an axial force that causes the drive wheel to move axially away from the transmission gear.

4. The clutch device according to claim 3, characterized in that, The unidirectional toothed structure is continuously distributed around or spaced along the circumference of the output shaft.

5. The clutch device according to claim 3, characterized in that, The non-working surface is an inclined plane or curved surface that is tilted relative to the axial direction of the output shaft.

6. The clutch device according to any one of claims 1-5, characterized in that, The outer side of the transmission gear has a gear structure.

7. The clutch device according to any one of claims 1-5, characterized in that, When the output shaft rotates in the opposite direction, the first engagement part and the second engagement part periodically come into contact or disengage.

8. The clutch device according to any one of claims 1-5, characterized in that, A limiting part is provided on the end face of the drive wheel away from the second meshing part, and one end of the elastic element can be inserted into the limiting part. The limiting part is used to restrict the lateral movement of the elastic element.

9. The clutch device according to claim 8, characterized in that, It also includes a pressure plate, which is fixed to the housing of the motor and is used to provide axial restraint for the elastic element.

10. The clutch device according to claim 9, characterized in that, The elastic element is a compression spring, which is sleeved on the output shaft, with one end abutting against the pressure plate and the other end abutting against the limiting part.

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