Electric operating mechanism of frame circuit breaker

Abstract

This utility model provides an electric operating mechanism for a frame circuit breaker, including an operating housing. A motor, a transmission device, and a main shaft are housed within the operating housing. The transmission device includes a transmission housing, within which are a planetary gear reduction assembly, a bevel gear transmission assembly, and a spur gear transmission assembly. The planetary gear reduction assembly is connected to the motor output shaft and transmits driving force to the main shaft via the bevel gear and spur gear transmission assemblies to drive the main shaft to rotate. A clutch assembly is provided between the main shaft and the spur gear transmission assembly. The transmission device has a compact structure, saving internal space in the electric operating mechanism. It features a high reduction ratio, low force transmission loss, and reduced production costs. The addition of first and second thrust bearings further improves conversion efficiency. The use of PIC control for position sampling and current detection enhances the safety performance of the electric operating mechanism.

Description

Technical Field

[0001] This utility model relates to the field of frame circuit breaker technology, and specifically to an electric operating mechanism for a frame circuit breaker. Background Technology

[0002] A frame circuit breaker is a high-performance protective electrical appliance used in low-voltage power distribution systems. With its large capacity, high segmentation capability and intelligent functions, it is widely used in power distribution systems of industry, commerce and large buildings.

[0003] In existing frame circuit breakers, series-wound motors generate surge currents several times their rated current during startup, placing high demands on power supply capacity and stability. When directly driven by DC motors or series-wound motors, the system is extremely sensitive to input voltage fluctuations. When the voltage drops, the output decreases, leading to slower drive or stall. During stall, the motor winding current remains at its peak, copper losses increase dramatically, and the winding temperature rises rapidly within a short time, potentially causing motor overheating, burnout, or even a fire. While worm gear reducers can achieve 90° steering and high reduction ratios, their low conversion efficiency results in significant energy loss in the motor. Furthermore, the complex manufacturing process and low production efficiency of worm gears increase costs. Traditional ratchet-type one-way clutches employ an internal and external ratchet engagement + spring reset structure, requiring independent housings, retaining springs, and buffer components, increasing axial dimensions. This multi-component design not only occupies a large space and is relatively complex but also demands extremely high precision, leading to a double increase in material and manufacturing costs. Summary of the Invention

[0004] The purpose of this utility model is to provide an electric operating mechanism for a frame circuit breaker to solve the above-mentioned problems.

[0005] The technical solution adopted in this utility model is as follows: An electric operating mechanism for a frame circuit breaker includes an electric operating housing. A motor, a transmission device, and a main shaft are disposed within the electric operating housing. The transmission device includes a transmission housing, within which a planetary gear reduction assembly, a bevel gear transmission assembly, and a spur gear transmission assembly are disposed. The planetary gear reduction assembly is connected to the motor output shaft and transmits driving force to the main shaft via the bevel gear transmission assembly and the spur gear transmission assembly to drive the main shaft to rotate. A clutch assembly is disposed between the main shaft and the spur gear transmission assembly.

[0006] As a further improvement of the present invention, the planetary gear reduction assembly includes several planetary gear mechanisms arranged coaxially in parallel. The planetary gear mechanism near the motor is connected to the output shaft of the motor. A transmission shaft is provided on the planetary gear mechanism near the bevel gear transmission assembly, and the transmission shaft drives the bevel gear transmission assembly to operate.

[0007] As a further improvement of the present invention, the bevel gear transmission assembly includes a first bevel gear, a second bevel gear, and a rotating shaft. The first bevel gear is sleeved on the transmission shaft and rotates synchronously with the transmission shaft. The rotating shaft is disposed on the transmission housing. The second bevel gear is sleeved on the rotating shaft. The second bevel gear meshes with the first bevel gear. The axis of the second bevel gear is perpendicular to the axis of the first bevel gear.

[0008] As a further improvement of the present invention, a first bushing is provided on the transmission shaft. The first bushing is used to limit the axial position of the first bevel gear on the transmission shaft. A first thrust bearing is provided between the first bushing and the first bevel gear.

[0009] As a further improvement of the present invention, the spur gear transmission assembly includes a first spur gear and a second spur gear. The first spur gear is sleeved on the rotating shaft and is located above the second bevel gear and rotates synchronously with the second bevel gear. A second thrust bearing is provided between the first spur gear and the rotating shaft. The second spur gear is sleeved on the upper end of the main shaft. The second spur gear meshes with the first spur gear and can drive the main shaft to rotate.

[0010] As a further improvement of this utility model, a limiting boss is provided at the lower end of the rotating shaft, and a second bushing is provided between the limiting boss and the second bevel gear. The second bushing is used to limit the axial position of the second bevel gear.

[0011] As a further improvement of this utility model, a cam is provided at the lower end of the main shaft. The cam can rotate synchronously with the main shaft. A radially extending annular limiting member is provided on the second bushing. The annular limiting member abuts against the upper part of the cam to limit the axial position of the cam.

[0012] As a further improvement of this utility model, a micro switch is provided inside the electric operating housing. The micro switch is located on the movement path of the cam. During the rotation of the cam, the cam can push the micro switch to close or open the micro switch. The micro switch is connected to an integrated circuit. The integrated circuit is used to sample the position and detect the current of the electric operating mechanism, and to switch the motor on and off according to the sampling and detection results.

[0013] As a further improvement of this utility model, an output shaft is provided at the bottom of the main shaft, a drive groove is provided at the top of the main shaft, and a drive hole is provided on the electric operating housing, with the drive groove located inside the drive hole.

[0014] As a further improvement of the present invention, the clutch assembly includes a slot in the radial direction of the main shaft, a spring and a locking block are provided in the slot, the spring connects the inner wall of the slot and the locking block, and at least two slots are provided on the inner circular wall of the second spur gear, each slot including an arc-shaped guide surface and a stop surface, the locking block cooperates with the slot, the locking block can abut against the arc-shaped guide surface and slide relative to the arc-shaped guide surface, and the stop surface can push the locking block to rotate.

[0015] The beneficial effects of this utility model are as follows: By setting up a transmission device composed of planetary gear reduction assembly, bevel gear transmission assembly and spur gear transmission assembly, the structure is compact, saving internal space of the electric operating mechanism, with high reduction ratio and low force transmission loss, reducing production and processing costs; the addition of first and second thrust bearings further improves conversion efficiency; the use of PIC control for position sampling and current detection improves the safety performance of the electric operating mechanism. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of the electric operating mechanism; Figure 2 This is a schematic diagram of the internal structure of the electric operating mechanism; Figure 3 This is a top view of the motor, transmission device, and main shaft; Figure 4 This is a bottom view of the motor, transmission device, and spindle; Figure 5 This is a partial explosion diagram of the transmission device; Figure 6 This is a partial explosion diagram of the transmission device from another angle; Figure 7 This is a schematic diagram showing the connection between the bevel gear transmission assembly and the spur gear transmission assembly; Figure 8 This is a schematic diagram of the internal structure of the transmission housing; Figure 9 This is a sectional view of the transmission housing; Figure 10 This is a schematic diagram of the clutch assembly.

[0017] Wherein: 1-Electric control housing, 2-Motor, 3-Transmission housing, 301-Input hole, 302-Outer ring fixed gear, 303-Reduction channel, 304-Reversing channel, 3051-First connecting section, 3052-Second connecting section, 4-Planetary gear reduction assembly, 401-Sun gear, 402-Planetary disk, 403-Planetary gear, 404-Planetary shaft, 405-Transmission shaft, 4051-First shaft section, 4052-Second shaft section, 5-Bevel gear transmission assembly, 501-First bevel gear, 502-Second bevel gear, 503-Rotating shaft, 504-First... 5041-Transmission shaft sleeve section, 5042-Connecting shaft sleeve section, 505-First thrust bearing, 506-Limiting boss, 6-Spur gear transmission assembly, 601-First spur gear, 602-Second spur gear, 603-Second thrust bearing, 604-Second shaft sleeve, 605-Annular limiting component, 7-Main shaft, 701-Output shaft, 702-Drive groove, 801-Slot, 802-Spring, 803-Card block, 804-Card slot, 8041-Arc-shaped guide surface, 8042-Stop surface, 9-Cam, 10-Micro switch, 11-Circuit board. Detailed Implementation

[0018] The present invention will now be described in detail with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments do not limit the present invention, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the protection scope of the present invention.

[0019] If the description of this utility model involves directions (e.g., up, down, left, right, front, back, outside, inside, etc.), then the directions involved need to be defined. For example, "To clearly express the position and direction described in this utility model, the operator of the instrument is used as a reference, the end closer to the operator is the proximal end, and the end farther from the operator is the distal end." Or, the paper can be used as a reference. Of course, if the positional relationship between the two is defined by mutual reference in the subsequent description, then this definition is not required.

[0020] An electric operating mechanism for a frame circuit breaker, such as Figures 1-4As shown, the electric operating mechanism includes an electric operating housing 1, within which a motor 2, a transmission device, and a main shaft 7 are disposed. The transmission device includes a transmission housing 3, within which a planetary gear reduction assembly 4, a bevel gear transmission assembly 5, and a spur gear transmission assembly 6 are disposed. The planetary gear reduction assembly 4 is connected to the output shaft of the motor 2 and transmits driving force to the main shaft 7 through the bevel gear transmission assembly 5 and the spur gear transmission assembly 6 to drive the main shaft 7 to rotate. A clutch assembly is disposed between the main shaft 7 and the spur gear transmission assembly 6. A cam 9 is disposed at the lower end of the main shaft 7, and the cam 9 can rotate synchronously with the main shaft 7. A micro switch 10 and an integrated circuit connected to the micro switch 10 are also disposed within the electric operating housing 1. The micro switch 10 is disposed on the movement path of the cam 9. During the rotation of the cam 9, the cam 9 can push the micro switch 10 to close or open. The integrated circuit is integrated on a circuit board 11 and is used for position sampling and current detection of the electric operating mechanism, and for switching the power on and off of the motor 2 based on the sampling and detection results. The main shaft 7 is also rotatably mounted inside the transmission housing 3, which is integrally formed to facilitate the direct assembly of the aforementioned planetary gear reduction assembly 4, bevel gear transmission assembly 5, spur gear transmission assembly 6, and main shaft 7.

[0021] The micro switch 10 is used to display the opening and closing status of the frame circuit breaker. The integrated circuit transmits the opening and closing signals of the frame circuit breaker and the real-time position of the circuit breaker contacts. Simultaneously, the micro switch 10 is linked with the motor 2 and transmission device of the electric operating mechanism to prevent repeated or erroneous operations. During closing, the micro switch 10 cuts off the power to the motor 2 after being triggered, preventing the motor 2 from stalling. If opening is not completed, the micro switch 10 locks the closing circuit to ensure a safe operating sequence. Furthermore, the micro switch 10 can also be linked with the integrated circuit. If the cam 9 fails to trigger the micro switch 10 within a predetermined time, it is determined that the mechanism is stuck or the motor 2 is faulty, triggering an alarm or trip protection.

[0022] The electric operating mechanism is powered by a switching power supply, and the motor 2 is a low-voltage DC motor. After the external power supply is input, it is processed by the switching power supply before powering the motor 2. The design of using a switching power supply to drive the low-voltage DC motor 2 not only provides stable output and is compatible with AC and DC input, but also maintains constant output power even if the external voltage fluctuates within a large range.

[0023] The electric operating mechanism employs an integrated circuit (PIC). Position sampling determines whether to activate motor 2. In non-energy storage mode, power is supplied to motor 2 via the motor 2 drive chip. Upon reaching the energy storage position, the power to motor 2 is immediately cut off, and braking is achieved. The use of PIC control enhances the intelligence level of both the electric operating mechanism and the frame circuit breaker. Furthermore, position sampling and current monitoring provide protection—when the frame circuit breaker stalls due to a fault, current monitoring of motor 2 enables stall protection, effectively preventing product damage and mitigating the fire risk caused by motor 2 burnout.

[0024] In one embodiment of this utility model, the planetary gear reduction assembly 4 includes several planetary gear mechanisms arranged coaxially in parallel. The planetary gear mechanism closer to the motor 2 is connected to the output shaft of the motor 2, and a transmission shaft 405 is provided on the planetary gear mechanism closer to the bevel gear transmission assembly 5. The transmission shaft 405 drives the bevel gear transmission assembly 5 to rotate. Specifically, a through input hole 301 is provided on the transmission housing 3, and the output shaft of the motor 2 passes through the input hole 301 to drive the internal planetary gear mechanism to rotate.

[0025] like Figures 5-6 As shown, the planetary gear mechanism includes a sun gear 401, a planetary disk 402, and several planetary gears 403. The planetary gears 403 are evenly distributed circumferentially around the sun gear 401. Several planetary shafts 404 are arranged on the radial surface of the planetary disk 402 away from the bevel gear transmission assembly 5. Each planetary gear 403 corresponds to and is fitted onto a planetary shaft 404. The planetary gears 403 mesh with the sun gear 401 and can rotate synchronously with the sun gear 401. The planetary disk 402, planetary shafts 404, and planetary gears 403 all rotate around the sun gear 401. The sun gear 401 is fixed to the adjacent planetary disk 402, which is located away from the bevel gear transmission assembly 5, to connect multiple planetary gear mechanisms in series and achieve rotational transmission. To achieve coaxial transmission, the sun gear 401, directly driven by the motor 2, is coaxially arranged with the transmission shaft 405.

[0026] If we define the planetary gear mechanism furthest from the bevel gear transmission assembly 5 as the first planetary gear mechanism, and the planetary gear mechanism closest to the bevel gear transmission assembly 5 as the Nth planetary gear mechanism, and so on from the first planetary gear mechanism to the Nth planetary gear mechanism as the second planetary gear mechanism... the (N-1)th planetary gear mechanism, the planetary gear mechanisms have basically the same structure. The sun gear 401 of the first planetary gear mechanism is set separately because it needs to be connected to the drive source. The Nth planetary gear mechanism needs to transmit motion to the bevel gear transmission assembly 5, so a transmission shaft 405 is set on the radial surface of the planetary disk 402 of the Nth planetary gear mechanism near the bevel gear transmission assembly 5. In order to achieve coaxial transmission, the sun gear 401 of the first planetary gear mechanism and the transmission shaft 405 of the Nth planetary gear mechanism are set coaxially.

[0027] Furthermore, the multiple sets of planetary gear mechanisms can have different numbers of planetary gears 403 to meet the requirements of reduction ratio.

[0028] Furthermore, such as Figure 8 As shown, an outer ring fixed tooth 302 is provided in the transmission housing 3 to mesh with the planetary gears 403 in the planetary gear mechanism. Since the transmission housing 3 remains stationary, as the planetary gears 403 rotate with the central sun gear 401, the planetary gears 403 mesh with the outer ring fixed tooth 302 on the inner wall of the transmission housing 3 and rotate along the outer ring fixed tooth 302.

[0029] The planetary gear reduction assembly 4 has a high transmission ratio through the meshing of the sun gear 401 and the planetary gears 403. The multi-stage planetary gear mechanism expands the reduction ratio range, enabling precise speed regulation and adapting to more motor 2 selections. At the same time, the planetary gear reduction assembly 4 has a compact structure and the planetary gears 403 are evenly distributed, achieving uniform load distribution, improving torque transmission effect, and reducing cost.

[0030] like Figures 4-7 As shown, the bevel gear transmission assembly 5 includes a first bevel gear 501, a second bevel gear 502, and a rotating shaft 503. The first bevel gear 501 is sleeved on the transmission shaft 405 and rotates synchronously with the transmission shaft 405. The rotating shaft 503 is disposed on the transmission housing 3. The second bevel gear 502 is sleeved on the rotating shaft 503. The second bevel gear 502 meshes with the first bevel gear 501. The axis of the second bevel gear 502 is perpendicular to the axis of the first bevel gear 501.

[0031] Furthermore, such as Figure 9As shown, the transmission housing 3 contains at least two regions. One region is the aforementioned reduction channel 303 for accommodating the planetary gear reduction assembly 4, in which the aforementioned outer ring fixed tooth 302 is disposed. The other region is the reversing channel 304 for accommodating the bevel gear transmission assembly 5. A connecting channel is provided between the reduction channel 303 and the reversing channel 304, through which the transmission shaft 405 extends into the reversing channel 304. Furthermore, the connecting channel is provided with a coaxial first connecting section 3051 and a second connecting section 3052. The inner diameter of the first connecting section 3051 is smaller than the inner diameter of the second connecting section 3052. The transmission shaft 405 extends into the reversing channel 304 through the first connecting section 3051 and the second connecting section 3052.

[0032] A first bushing 504 is provided on the transmission shaft 405. The first bushing 504 is used to limit the axial position of the first bevel gear 501 on the transmission shaft 405 and reduce hard friction. A first thrust bearing 505 is provided between the first bushing 504 and the first bevel gear 501. Specifically, the cross-section of the mating surface between the transmission shaft 405 and the first bevel gear 501 can be a non-circular cross-section to achieve synchronous rotation. The transmission shaft 405 includes a first shaft segment 4051 and a second shaft segment 4052. The diameter of the first shaft segment 4051 is larger than the maximum radial segment length of the second shaft segment 4052. The first bevel gear 501 is sleeved on the second shaft segment 4052. The first bushing 504 is sleeved on the first shaft segment 4051 and mates with the first shaft segment 4051. The first bushing 504 is located between the first bevel gear 501 and the planetary disk 402 of the Nth planetary gear mechanism. The first thrust bearing 505 is located inside the first bushing 504. Specifically, the first bushing 504 includes a drive bushing section 5041 and a connecting bushing section 5042, wherein the diameter of the connecting bushing section 5042 is larger than the diameter of the drive bushing section 5041, such as... Figure 9 As shown, the transmission shaft sleeve 5041 is disposed between the transmission shaft 405 and the first connecting section 3051. The transmission shaft sleeve 5041 cooperates with the first connecting section 3051 to reduce hard friction between the first shaft section 4051 and the first connecting section 3051. The connecting shaft sleeve 5042 is sleeved on the first bevel gear 501. The second shaft section 4052 is disposed inside the second connecting section 3052. The connecting shaft sleeve 5042 is disposed between the first bevel gear 501 and the second connecting section 3052. The connecting shaft sleeve 5042 cooperates with the second connecting section 3052 to reduce hard friction between the first bevel gear 501 and the second connecting section 3052.

[0033] The tooth surface design of bevel gears has good conjugate characteristics. During transmission, the teeth can mesh smoothly and the contact area is reasonably distributed, resulting in relatively small impact force and vibration. This effectively reduces energy loss caused by tooth surface friction and impact vibration, and has the advantage of low transmission loss, ensuring that power can be transmitted more efficiently during directional changes.

[0034] like Figures 5-7 As shown, the spur gear transmission assembly 6 includes a first spur gear 601 and a second spur gear 602. The first spur gear 601 is sleeved on the rotating shaft 503 and is positioned above the second bevel gear 502, rotating synchronously with it. A second thrust bearing 603 is provided between the first spur gear 601 and the rotating shaft 503. The second spur gear 602 is sleeved on the upper end of the main shaft 7, and meshes with the first spur gear 601 for transmission. The second spur gear 602 can drive the main shaft 7 to rotate. Specifically, the first spur gear 601 can be coaxially and fixedly connected to the second bevel gear 502, forming a single piece.

[0035] In actual transmission processes, when gears mesh to transmit power, axial forces are inevitably generated. This can lead to slight displacement in the axial direction, resulting in poor tooth surface contact, increased frictional losses, and potentially affecting the service life of the gears and the stability of the transmission. By adding a thrust bearing, the thrust bearing can accurately withstand this axial force, limit unnecessary movement of the gears in the axial direction, ensure that the gears are always in the correct meshing position, reduce additional losses caused by axial displacement, and thus further improve the conversion efficiency of the entire transmission system.

[0036] A limiting boss 506 is provided at the lower end of the rotating shaft 503, and a second bushing 604 is provided between the limiting boss 506 and the second bevel gear 502. The second bushing 604 is used to limit the axial position of the second bevel gear 502.

[0037] The cam 9 is located at the lower end of the main shaft 7 and can rotate synchronously with the main shaft 7. A radially extending annular limiting member 605 is provided on the second bushing 604. The annular limiting member 605 abuts against the upper part of the cam 9 to limit the axial position of the cam 9 and prevent the cam 9 from moving upward. Specifically, the annular limiting member 605 is integrally formed with the second bushing 604. The micro switch 10 is located on the movement path of the cam 9. During the rotation of the cam 9, the cam 9 can push the lever of the micro switch 10 to close the micro switch 10 or move away from the micro switch 10 to open the micro switch 10.

[0038] An output shaft 701 is provided at the bottom of the main shaft 7, and the output shaft 701 is used to link with the internal structure of the frame circuit breaker. A drive groove 702 is provided at the top of the main shaft 7, and the drive groove 702 facilitates the application of external force to the main shaft 7. A drive hole is provided on the electric operating housing 1, and the top end of the main shaft 7 is located in the drive hole. The drive groove 702 is located in the drive hole, so that the main shaft 7 can be manually driven to rotate by applying external force to the drive groove 702 in the drive hole.

[0039] like Figure 10 As shown, the clutch assembly includes a slot 801 or blind hole (described here as slot 801) disposed in the radial direction of the main shaft 7. A spring 802 and a locking block 803 are disposed in the slot 801. The spring 802 connects the inner wall of the slot 801 and the locking block 803. One end of the spring 802 is fixedly connected to the inner wall of the slot 801, and the other end of the spring 802 is connected to the locking block 803. The locking block 803 can extend out of or retract into the slot 801, within the inner circle of the second spur gear 602. At least two slots 804 are provided on the wall. Each slot 804 includes an arc-shaped guide surface 8041 and a stop surface 8042. The closer to the stop surface 8042, the greater the distance between the arc-shaped guide surface 8041 and the axis of the main shaft 7. The locking block 803 has an arc-shaped inclined surface that cooperates with the slot 804. The arc-shaped inclined surface can be locked into the slot 804. The locking block 803 can abut against the arc-shaped guide surface 8041 and slide relative to the arc-shaped guide surface 8041. The stop surface 8042 can push the locking block 803 to rotate. During the rotation of the second spur gear 602, the locking block 803 extends out of the slot 801, and the arc-shaped guide surface 8041 abuts against the locking block 803. Relative sliding occurs between the locking block 803 and the arc-shaped guide surface 8041 until the locking block 803 contacts the stop surface 8042. The stop surface 8042 pushes the locking block 803 to rotate, thereby causing the locking block 803 to drive the main shaft 7 to rotate. When the second spur gear 602 rotates in the opposite direction, the stop surface 8042 moves away from the locking block 803. The locking block 803 slides relative to the arc-shaped guide surface 8041. As the distance between the contact point between the locking block 803 and the arc-shaped guide surface 8041 and the locking block 803 gradually decreases, the spring 802 is compressed, and the locking block 803 gradually retracts into the slot 801 until it reaches the next stop surface 8042. The spring 802 then drives the locking block 803 to return to its original position and extend out of the slot 801. The locking block 803 then abuts against the arc-shaped guide surface 8041 of the next slot 804 again, repeating the above cycle. The clutch assembly has a simple and compact structure and low cost.

[0040] A foolproof protrusion extending toward the cam 9 is provided on the radial surface of the second spur gear 602 facing the cam 9. The foolproof protrusion is used to prevent the installation direction of the second spur gear 602 from being reversed during installation. The foolproof protrusion is arc-shaped and cooperates with the main shaft 7.

[0041] Furthermore, most of the components in the electric operating mechanism of the frame circuit breaker provided by this utility model can be made of injection molded parts, including but not limited to the electric operating housing, transmission housing, planetary gear reduction assembly (except for the planetary disk, planetary shaft and output shaft in the Nth planetary gear mechanism near the bevel gear transmission assembly), cam, and second bushing. Compared with metal parts, they are not only cheaper and more efficient in production, but also generate less noise during operation.

[0042] The electric operating mechanism of the frame circuit breaker provided by this utility model has a compact structure by setting a transmission device composed of a planetary gear reduction assembly 4, a bevel gear transmission assembly 5 and a spur gear transmission assembly 6, which saves internal space of the electric operating mechanism, has a high reduction ratio, low force transmission loss and reduces production and processing costs; the addition of first and second thrust bearings 603 further improves the conversion efficiency; and the use of PIC control for position sampling and current detection improves the safety performance of the electric operating mechanism.

[0043] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0044] The detailed descriptions listed above are merely specific descriptions of feasible implementation methods of this utility model, and are not intended to limit the scope of protection of this utility model. All equivalent implementation methods or modifications made without departing from the spirit of this utility model should be included within the scope of protection of this utility model.

Claims

1. An electrically operated mechanism for a frame circuit breaker, characterized in that: The device includes an electric control housing (1), in which a motor (2), a transmission device and a main shaft (7) are provided. The transmission device includes a transmission housing (3), in which a planetary gear reduction assembly (4), a bevel gear transmission assembly (5) and a spur gear transmission assembly (6) are provided. The planetary gear reduction assembly (4) is connected to the output shaft of the motor (2) and transmits driving force to the main shaft (7) through the bevel gear transmission assembly (5) and the spur gear transmission assembly (6) to drive the main shaft (7) to rotate. A clutch assembly (8) is provided between the main shaft (7) and the spur gear transmission assembly (6).

2. The electrically operated mechanism of the frame circuit breaker according to claim 1, characterized in that: The planetary gear reduction assembly (4) includes several planetary gear mechanisms arranged coaxially in parallel. The planetary gear mechanism near the motor (2) is connected to the output shaft of the motor (2). A transmission shaft (405) is provided on the planetary gear mechanism near the bevel gear transmission assembly (5). The transmission shaft (405) drives the bevel gear transmission assembly (5) to operate.

3. The electrically operated mechanism of the frame circuit breaker according to claim 2, characterized in that: The bevel gear transmission assembly (5) includes a first bevel gear (501), a second bevel gear (502), and a rotating shaft (503). The first bevel gear (501) is sleeved on the transmission shaft (405) and rotates synchronously with the transmission shaft (405). The rotating shaft (503) is disposed on the transmission housing (3). The second bevel gear (502) is sleeved on the rotating shaft (503). The second bevel gear (502) meshes with the first bevel gear (501). The axis of the second bevel gear (502) is perpendicular to the axis of the first bevel gear (501).

4. The electrically operated mechanism of the frame circuit breaker according to claim 3, characterized in that: A first bushing (504) is provided on the transmission shaft (405). The first bushing (504) is used to limit the axial position of the first bevel gear (501) on the transmission shaft (405). A first thrust bearing (505) is provided between the first bushing (504) and the first bevel gear (501).

5. The electrically operated mechanism of the frame circuit breaker according to claim 3, characterized in that: The spur gear transmission assembly (6) includes a first spur gear (601) and a second spur gear (602). The first spur gear (601) is sleeved on the rotating shaft (503). The first spur gear (601) is located above the second bevel gear (502) and rotates synchronously with the second bevel gear (502). A second thrust bearing (603) is provided between the first spur gear (601) and the rotating shaft (503). The second spur gear (602) is sleeved on the upper end of the main shaft (7). The second spur gear (602) meshes with the first spur gear (601) for transmission. The second spur gear (602) can drive the main shaft (7) to rotate.

6. The electrically operated mechanism of the frame circuit breaker according to claim 5, characterized in that: A limiting boss (506) is provided at the lower end of the rotating shaft (503), and a second bushing (604) is provided between the limiting boss (506) and the second bevel gear (502). The second bushing (604) is used to limit the axial position of the second bevel gear (502).

7. The electrically operated mechanism of the frame circuit breaker according to claim 6, characterized in that: A cam (9) is provided at the lower end of the main shaft (7). The cam (9) can rotate synchronously with the main shaft (7). A radially extending annular limiting member (605) is provided on the second bushing (604). The annular limiting member (605) abuts against the upper part of the cam (9) to limit the axial position of the cam (9).

8. The electrically operated mechanism of the frame circuit breaker according to claim 7, characterized in that: A micro switch (10) is provided inside the electric operating housing (1). The micro switch (10) is located on the movement path of the cam (9). During the rotation of the cam (9), the cam (9) can push the micro switch (10) to close or make the micro switch (10) open. The micro switch (10) is connected to an integrated circuit. The integrated circuit is used to sample the position and detect the current of the electric operating mechanism, and to turn the motor (2) on and off according to the sampling and detection results.

9. The electrically operated mechanism of the frame circuit breaker according to claim 1, characterized in that: An output shaft (701) is provided at the bottom of the main shaft (7), a drive groove (702) is provided at the top of the main shaft (7), and a drive hole is provided on the electric operating housing (1). The drive groove (702) is located inside the drive hole.

10. The electrically operated mechanism of the frame circuit breaker according to claim 5, characterized in that: The clutch assembly (8) includes a slot (801) disposed in the radial direction of the main shaft (7). A spring (802) and a locking block (803) are disposed in the slot (801). The spring (802) connects the inner wall of the slot (801) and the locking block (803). At least two slots (804) are disposed on the inner circular wall of the second spur gear (602). The slots (804) include an arc-shaped guide surface (8041) and a stop surface (8042). The locking block (803) cooperates with the slots (804). The locking block (803) can abut against the arc-shaped guide surface (8041) and slide relative to the arc-shaped guide surface (8041). The stop surface (8042) can push the locking block (803) to rotate.

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