Operating output module for a medium voltage load switch

Abstract

The application discloses a kind of medium voltage load switch operating output module, including shell, motor, main shaft, output assembly and at least two groups of speed reduction mechanism, motor, main shaft, output assembly, speed reduction mechanism are fixed on shell, output gear is equipped on motor, first gear is equipped on main shaft and is engaged with output gear and is linked, transmission shaft is equipped on output assembly;Speed reduction mechanism includes eccentric wheel, transmission crank and one-way bearing, eccentric wheel is sleeved on main shaft and is linked with main shaft, one-way bearing is sleeved on transmission shaft and is linked with transmission shaft, one end of transmission crank is sleeved on one-way bearing and is linked with one-way bearing, notch is equipped on the other end of transmission crank, the inner wall of the bottom surface of notch is located on the movement track of eccentric wheel;The position of the eccentric wheel of each group of speed reduction mechanism is different, all eccentric wheels are driven to rotate continuously, the invention is more stable, the structure is simpler, portable, has clutch protection effect, hand automatic integrated drive.

Description

Technical Field

[0001] This invention relates to an operating output module for a medium-voltage load switch. Background Technology

[0002] Medium-voltage load switches are a type of conventional electrical switch. They can be manual or electric. In the electric configuration, the operating output module of the medium-voltage load switch uses a motor and gearbox to achieve a deceleration output from the output shaft. The output shaft then transfers energy to its cooperating mechanism, enabling operations such as opening and closing.

[0003] However, in actual use, the gearbox requires multiple gears to mesh to achieve the deceleration effect, which increases the overall mass. Moreover, the multi-stage transmission reduces energy and lowers the transmission efficiency. Summary of the Invention

[0004] The main technical problem solved by this invention is to provide an operating output module for a medium-voltage load switch.

[0005] The technical solution adopted by this invention to solve its technical problem is: an operating output module for a medium-voltage load switch, comprising a housing, a motor, a main shaft, an output component, and at least two sets of reduction mechanisms. The motor, main shaft, output component, and reduction mechanisms are all fixed on the housing. The motor is provided with an output gear, the main shaft is provided with a first gear meshing and linked with the output gear, and the output component is provided with a transmission shaft. The reduction mechanism includes an eccentric wheel, a transmission crank arm, and a one-way bearing. The eccentric wheel is sleeved on the main shaft and linked with the main shaft. The one-way bearing is sleeved on the transmission shaft and linked with the transmission shaft. One end of the transmission crank arm is sleeved on the one-way bearing and linked with the one-way bearing. The other end of the transmission crank arm has a notch, and the inner wall of the notch, except for its bottom surface, is located on the movement trajectory of the eccentric wheel. The eccentric wheels of each set of reduction mechanisms are in different positions, and all the eccentric wheels cooperate to drive the transmission shaft to rotate continuously.

[0006] In the overall transmission process, the motor first drives the output gear to rotate, which in turn drives the first gear meshing with it. The first gear then drives the main shaft to rotate. Simultaneously, the main shaft rotates, causing the eccentric wheel to rotate. When the eccentric wheel abuts against the inner wall of the notch during its rotation, it drives the transmission crank arm. Since the transmission crank arm and the transmission shaft are connected via a one-way bearing, the transmission shaft can only rotate in one direction during the crank arm's movement. This achieves a speed reduction output effect between the output components. Compared to existing technologies, this structure is simpler, lighter, and offers higher transmission stability than a gearbox. By using two eccentric wheels with different initial positions, an alternating effect of driving the transmission shaft to rotate is created. An array distribution is preferred here. With two sets of reduction mechanisms, they can be 180° symmetrical (one forward, one backward). With three sets of reduction mechanisms, they can be positioned at the three equal divisions of the projection circle. Each set of reduction mechanisms works in conjunction to achieve continuous force transmission, ensuring the transmission shaft remains in a rotating state without interruption or jamming.

[0007] Each set of deceleration mechanisms is set up independently.

[0008] The reduction mechanisms do not affect each other; they all achieve the effect of speed reduction by rotating the main shaft and then driving the transmission shaft.

[0009] An isolation sleeve is provided between two adjacent eccentric wheels, and the isolation sleeve is fitted onto the main shaft.

[0010] The use of an isolation sleeve better isolates adjacent deceleration mechanisms, preventing them from interlocking.

[0011] Each eccentric wheel is equipped with a first bearing, and the inner wall of the notch, excluding its bottom surface, is located on the movement trajectory of the first bearing.

[0012] By using a first bearing, the eccentric wheel drives the rotation of the transmission crank arm through the cooperation of the first bearing, thereby further improving the stability of the overall transmission.

[0013] It also includes a first pin, and the eccentric wheel is provided with a first extension. The first pin passes through the first extension and is connected to the main shaft.

[0014] The use of the first pin allows the eccentric wheel to be better connected and fixed to the main shaft, thus creating a fixed effect between the two.

[0015] The output component is equipped with an output shaft and a clutch mechanism. The transmission shaft and the output shaft are connected by the clutch mechanism. When the motor is overloaded, the transmission shaft and the output shaft will engage and disengage.

[0016] By employing a clutch mechanism, when the load connected to the output shaft exceeds the motor's load capacity, the clutch mechanism operates, causing the output shaft to separate from the transmission shaft, thereby achieving a protective effect.

[0017] The clutch mechanism includes two friction plates and a pressure block. The drive shaft is provided with a flange that cooperates with the pressure block, and the output shaft is provided with a second extension. The pressure block is connected and fixed to the flange to form a chamber with an upper opening. The second extension is located inside the chamber. One end of the output shaft passes through the upper opening and extends out of the pressure block. The two friction plates are respectively provided on the upper and lower end faces of the second extension, and one friction plate abuts against the top surface of the chamber, and the other friction plate abuts against the bottom surface of the chamber.

[0018] By using two friction plates in combination, the linkage effect between the output shaft and the drive shaft is achieved. When the motor is overloaded, the two friction plates will not play a transmission role, causing the output shaft and the drive shaft to enter a clutch state.

[0019] The clutch mechanism also includes a gasket, which is located between the flange and the friction plate near the bottom of the chamber.

[0020] The use of shims creates a connection between the flange and the friction plate. Here, the tightness of the output shaft can be adjusted by changing the thickness of the shims.

[0021] The housing has a recessed cavity, and the motor is embedded and fixed inside the cavity.

[0022] The recessed cavity design allows for better connection and fixation of the motor to the housing.

[0023] It also includes a handle, and the main shaft is provided with a linkage part, which extends out of the housing. The handle is connected to the linkage part.

[0024] The use of a handle creates a manual / automatic integrated effect. The handle drives the spindle to rotate, thereby achieving the output effect of the output shaft. When manual operation is required, the handle is engaged and fixed with the linkage to achieve the desired transmission effect.

[0025] It also includes a second pin, with a spiral groove on the handle. The second pin passes through the linkage part, and both ends of the second pin slide into the end of the spiral groove for fixation.

[0026] The use of a second pin and a spiral groove allows the handle to be better linked and fixed with the main shaft.

[0027] The housing includes a top cover and a base. The top cover and the base are connected and fixed. The top cover is provided with a first hollow column, and a second bearing is provided inside the first hollow column. The main shaft passes through the second bearing.

[0028] The use of a first hollow column creates a guiding effect and increases the mating area between the top cover and the main shaft. Then, the use of a second bearing ensures that there is no interference between the main shaft and the top cover, thus improving the stability of the transmission.

[0029] The base has a second hollow column, inside which is a third bearing. The other end of the main shaft passes through the third bearing and connects to the first gear.

[0030] The addition of a second hollow column also increases the contact area between the base and the spindle, improving the stability of the transmission.

[0031] The height of the first bearing is greater than the depth of the notch.

[0032] This structural design allows the first bearing to better fit inside the notch, achieving a driving effect. Attached Figure Description

[0033] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention;

[0034] Figure 2 This is a cross-sectional view of Embodiment 1 of the present invention;

[0035] Figure 3 This is a cross-sectional view from another angle of Embodiment 1 of the present invention;

[0036] Figure 4 This is a partial structural schematic diagram of Embodiment 1 of the present invention;

[0037] Figure 5 This is a partial exploded view of Embodiment 1 of the present invention;

[0038] Figure 6 This is a front view of the transmission crank arm in Embodiment 1 of the present invention. Detailed Implementation

[0039] Example 1:

[0040] See attached document Figure 1-6 As shown, an operating output module for a medium-voltage load switch includes a housing 1, a motor 2, a main shaft 3, an output component, and at least two sets of reduction mechanisms.

[0041] The housing 1 includes an upper cover 10 and a base 11. The base 11 and the upper cover 10 are not perfectly matched in a 1:1 ratio; the size of the base 11 is larger than that of the upper cover 10 because the base 11 also needs to fix the external motor 2. The base 11 and the upper cover 10 cooperate to form a receiving chamber 4, in which the reduction mechanism and the main shaft 3 are fixed. The portion of the base 11 that extends beyond the upper cover 10 has a recess 111, which is used to cooperate with the motor 2 to achieve the effect of fixing the motor 2. The recess 111 extends laterally, and the opening of the recess 111 faces upward. The size of the recess 111 can be adapted to the motor 2 to achieve a positioning and fixing effect, or it can be larger than the size of the motor 2, with bolts inserted from the other side of the recess 111 to cooperate with the motor 2 to achieve the effect of fixing the motor 2. It should also be noted that the output gear of the motor 2 passes through the recess 111 and extends out of the recess 111.

[0042] The receiving chamber 4 serves a fixing effect. In this embodiment, the upper cover 10 and the base 11 are connected by bolts. Furthermore, in this embodiment, the upper cover 10 has a first hollow column 101 and a third hollow column 102 on its upward-facing side. The first hollow column 101 is connected to the receiving chamber 4. A second bearing 62 is installed inside the first hollow column 101. The second bearing 62 cooperates with the main shaft 3, preventing interference between the main shaft 3 and the upper cover 10 and improving transmission stability. Here, the second bearing 62 is adapted to the main shaft 3, meaning the main shaft 3 can drive the second bearing 62 to rotate. The first hollow column 101 provides a guiding effect and increases the mating area between the upper cover 10 and the main shaft 3. The third hollow column 102 has the same structure as the first hollow column 101, and is also hollow. The third hollow column 102 is provided with a fourth bearing 64, which is used to cooperate with the transmission shaft to realize the effect of the transmission shaft passing through the third hollow column 102 and cooperating with the output shaft. Here, the transmission shaft can also drive the fourth bearing 64 to rotate.

[0043] A second hollow column 112 is provided on the side of the base 11 facing the receiving chamber 4. The second hollow column 112 is also hollow and connects the receiving chamber 4 to the outside. A third bearing 63 is provided inside the second hollow column 112. The third bearing 63 cooperates with the lower end of the main shaft 3, so that the lower end of the main shaft 3 extends out of the housing 1. The main shaft 3 and the third bearing 63 cooperate here. The setting of the second hollow column 112 also increases the cooperation area between the base 11 and the main shaft 3, improving the stability of the transmission. A first through hole 113 is provided on the bottom surface of the base 11. A fifth bearing 65 is fixed in the first through hole 113. The lower end of the transmission shaft passes through the fifth bearing 65 and extends out of the housing 1.

[0044] Motor 2 can be a conventional motor 2, and users can choose motor 2 with different power according to actual needs. However, in this embodiment, in order to cooperate with the manual rotation of the handle and prevent the manual operation from being too strenuous, it is preferable to use a motor 2 with an internal clutch function. That is, when manually operated, when the first gear 71 meshes with the output gear 21, the reverse rotation is effortless. Motor 2 is fixed in the cavity 111, which can be said to be externally fixed to the base 11, thus making maintenance or replacement more convenient.

[0045] The main shaft 3 is a circular shaft, so all parts of the shaft are coaxial. The upper end of the main shaft 3 passes through the second bearing 62, and a linkage part 31 is provided on this end. The linkage part 31 is used to cooperate with the handle 8 to achieve a linkage effect. Specifically, the handle 8 achieves the linkage effect through the second pin 82. It should be noted that the linkage part 31 is located above the upper cover 10, that is, the linkage part 31 is located outside the housing 1.

[0046] The lower end of the main shaft 3 extends beyond the base 11 and is connected and fixed to the lower end of the main shaft 3 via a third pin 72 passing through the first gear 71, thus achieving the effect of the first gear 71 driving the main shaft 3 to rotate. The first gear 71 meshes with the output gear 21, thereby achieving the linkage effect between the motor 2 and the main shaft 3. The transmission ratio between the first gear 71 and the output gear 21 can be adjusted according to actual needs, which will not be described in detail in this embodiment. However, it should be noted that since the whole structure is a reduction gear, the diameter of the first gear 71 is larger than the diameter of the output gear 21.

[0047] The output assembly includes a drive shaft 41, an output shaft 42, and a clutch mechanism. The drive shaft 41 and the main shaft 3 are arranged parallel to each other and are both located within the receiving chamber 4. The upper end of the drive shaft 41 passes through the fourth bearing 64 and extends out of the housing 1. A flange 411 is provided at this end of the drive shaft 41. The flange 411 has a disc-shaped structure and has several circumferentially arranged fixing holes 412. Bolts pass through the fixing holes 412 and are connected and fixed to the pressure block, thereby realizing the connection and fixation between the drive shaft 41 and the pressure block. At the same time, a linkage effect is formed between the drive shaft 41 and the pressure block.

[0048] The output shaft 42 is connected to an external mechanism. Through the transmission of the entire output module, the force generated by the operation of the motor 2 is decelerated and transmitted, thereby achieving an overall deceleration output effect. The output shaft 42 is provided with a second extension 421, which is located in the chamber 43. One end of the output shaft 42 passes through the pressure block 92 and is connected to the external mechanism to achieve the force transmission effect.

[0049] The clutch mechanism includes two friction plates 91, a pressure block 92, and a gasket 93. The pressure block 92 is connected and fixed to the flange 411, forming a chamber 43 with an upper opening. The other end of the output shaft 42 extends through the upper opening to the outside of the pressure block 92. The two friction plates 91, the second extension 421, and the gasket 93 are all located inside the chamber 43. In this embodiment, the two friction plates 91 are respectively disposed on the upper and lower sides of the second extension 421. One side of the upper friction plate 91 abuts against the second extension 421, and the other side abuts against the top surface of the chamber 43. One side of the lower friction plate 91 abuts against the second extension 421, and the other side abuts against the gasket 93. The gasket 93 is located between the flange 411 and the lower friction plate 91. The gasket 93 forms a connection between the flange 411 and the friction plates 91. Here, the tightness of the output shaft 42 can be adjusted by changing the thickness of the gasket 93. By using two friction plates 91 in cooperation, the linkage effect between the output shaft 42 and the transmission shaft 41 is achieved. When the load connected to the output shaft 42 exceeds the load of the motor 2, the two friction plates 91 will not provide a transmission effect, causing the output shaft 42 and the transmission shaft 41 to enter a disengaged state, thereby achieving a protective effect. Here, the friction plate 91 refers to an assembly composed of a chip and a friction liner or friction material layer.

[0050] Furthermore, a positioning protrusion 422 can be provided on the output shaft 42, which extends into the positioning groove 413 of the flange portion 411 to achieve a certain positioning effect.

[0051] The number of reduction mechanisms is at least two. In this embodiment, the number of reduction mechanisms is described using two sets as an example. The two sets of reduction mechanisms are set independently of each other. One end of each set is connected to the main shaft 3, and the other end is connected to the transmission shaft 41, thereby achieving the effect of force reduction and transmission.

[0052] In this embodiment, in order to better describe the deceleration structure, the two deceleration mechanisms are respectively designated as the first deceleration mechanism 51 and the second deceleration mechanism 52.

[0053] The first reduction mechanism 51 includes an eccentric wheel 53, a transmission crank arm 54, a one-way bearing 55, and a first bearing 56. The eccentric wheel 53 is sleeved on the main shaft 3 and achieves a linkage effect with the main shaft 3. In this embodiment, the eccentric wheel 53 is provided with a first extension 531, which extends beyond the first bearing 56. A first pin 74 passes through the first extension 531 and is connected to the main shaft 3. Here, the first extension 531 extends beyond the first bearing 56, specifically meaning that the first extension 531 is located above the eccentric wheel 53, the bottom surface of the eccentric wheel 53 is coplanar with the bottom surface of the first bearing 56, and the top surface of the first extension 531 is higher than the top surface of the first bearing 56, thus creating the effect of extending beyond. The arrangement of the first pin 74 allows the eccentric wheel 53 to be better connected and fixed to the main shaft 3, thereby forming a fixed effect between the two. It should be noted that, as the name suggests, the axis of the eccentric wheel 53 is not the same point as the axis of the main shaft 3. It should also be noted that the first extension 531 extends upwards.

[0054] The first bearing 56 is mounted on the eccentric wheel 53, and the first bearing 56 and the eccentric wheel 53 are coaxially aligned. However, the first bearing 56 and the main shaft 3 are also eccentrically aligned. The first bearing 56 engages with the notch 541 on the transmission crank arm 54 to achieve the movement of the transmission crank arm 54. By using the first bearing 56, the eccentric wheel 53 drives the rotation of the transmission crank arm 54 through the engagement of the first bearing 56, further improving the overall stability of the transmission.

[0055] A one-way bearing 55 is sleeved on and linked to the drive shaft 41. In this embodiment, the one-way bearing 55 can only rotate in one direction. The one-way bearing 55 is existing technology and therefore will not be described in detail in this embodiment. In this embodiment, the one-way bearing 55 is preferably a one-way needle roller bearing.

[0056] One end of the transmission crank arm 54 is fitted onto the one-way bearing 55, thereby achieving a linkage effect between the transmission crank arm 54 and the one-way bearing 55. That is, the movement of the transmission crank arm 54, through the one-way bearing 55, achieves the unidirectional rotation effect of the transmission shaft 41. The other end of the transmission crank arm 54 has a notch 541 facing the main shaft 3. The inner wall of the notch 541, except for its bottom surface, is located on the movement trajectory of the eccentric wheel 53. Specifically, the notch 541 is a transverse U-shaped structure. The bottom surface of the U-shape is the end closest to the transmission shaft 41. This bottom surface forms a clearance design, so that the first bearing 56 will not interfere with each other during rotation, that is, the first bearing 56 will not abut against the bottom surface of the notch 541. The front and rear inner walls of the notch 541 are located on the movement trajectory of the first bearing 56. The first bearing 56 abuts against the inner wall of the notch 541, creating a back-and-forth swinging effect. However, due to the limitation of the one-way bearing 55, the transmission shaft 41 can only rotate in one direction. It should also be noted that the height of the first bearing 56 is greater than the depth of the notch 541. This structural arrangement allows the first bearing 56 to better fit inside the notch 541, achieving a driving effect. In this embodiment, the back-and-forth swing of the transmission crank arm 54 creates a deceleration transmission effect. The preferred swing amplitude of the transmission crank arm 54 is ±15°, but this swing amplitude can also be adjusted according to actual needs.

[0057] The first reduction mechanism 51 is located above the second reduction mechanism 52, and an isolation sleeve 57 is provided between the first reduction mechanism 51 and the second reduction mechanism 52 near the end of the main shaft 3. An isolation sleeve 57 is also provided between two adjacent eccentric wheels 53, and the isolation sleeve 57 is fitted onto the main shaft 3. The use of the isolation sleeve 57 better achieves the isolation effect between the two adjacent sets of reduction mechanisms and prevents linkage.

[0058] The difference between the first reduction mechanism 51 and the second reduction mechanism 52 is that the first extension 531 of the eccentric wheel 53 on the second reduction mechanism 52 extends downward. Furthermore, the initial positions of the two eccentric wheels 53 are different; according to axial projection, the two eccentric wheels 53 are arranged 180° opposite each other, meaning they are symmetrically arranged after projection. Simply put, the eccentric wheel 53 in the first reduction mechanism 51 abuts against the front inner wall of the notch 541 of the corresponding transmission crank arm 54, while the eccentric wheel 53 in the second reduction mechanism 52 abuts against the rear inner wall of the notch 541 of the corresponding transmission crank arm 54.

[0059] Furthermore, it should be noted that the one-way bearing 55 on the second reduction mechanism 52 and the one-way bearing 55 on the first reduction mechanism 51 are in the same direction, thus ensuring that the transmission shaft 41 can only rotate in one direction. When there are two sets of reduction mechanisms, the two eccentric wheels 53 rotate alternately, thereby achieving the unidirectional rotation effect of the transmission shaft 41, thus forming an overall reduction transmission effect. As for the actual reduction ratio, those skilled in the art can adjust it according to the eccentric angle and eccentric distance of the eccentric wheels 53 and calculate a suitable value. When the number of reduction mechanisms increases, the actual reduction ratio can also be obtained through calculation. The transmission crank arm 54 on the second reduction mechanism 52 and the transmission crank arm 54 on the first reduction mechanism 51 are arranged parallel to each other. This structural arrangement ensures uninterrupted transmission during use and prevents jamming during transmission.

[0060] In addition, when there are three sets of reduction mechanisms, each eccentric wheel 53 can be located at any position on the circumference after projection, as long as the force is continuously output. Simply put, during the normal rotation of the main shaft 3, it always drives the transmission shaft 41 to rotate without stopping.

[0061] When there are four sets of reduction mechanisms, they can also be arranged in pairs, with two sets of reduction mechanisms in the same position and the other two sets of reduction mechanisms symmetrically positioned at 180°. Those skilled in the art can increase the number of reduction mechanisms according to the cavity size of the housing 1, so this embodiment will not be described in detail.

[0062] The handle 8 has a spiral groove 81, and the second pin 82 passes through the linkage part 31. Both ends of the second pin 82 slide into the end of the spiral groove 81 and are fixed, thus connecting the handle 8 to the linkage part 31. This handle 8 configuration creates a manual / automatic integrated effect. The handle 8 drives the main shaft 3 to rotate, thereby achieving the output effect of the output shaft 42. The cooperation between the second pin 82 and the spiral groove 81 allows for a better linkage and fixation between the handle 8 and the main shaft 3. In this embodiment, the length of the spiral groove 81 can be adjusted according to actual needs. This structure creates a detachable structure between the handle 8 and the main shaft 3. Under normal conditions, the handle 8 is not required; the normal state is motor-driven. When manual operation is required, simply install the handle 8, causing the second pin 82 to rotate into the spiral groove 81 to achieve the linkage effect. After manual operation is complete, rotating the handle 8 allows for disassembly.

[0063] In the overall transmission process, the motor 2 first drives the output gear 21 to rotate, which in turn drives the first gear 71 that meshes with it. The first gear 71 then drives the main shaft 3 to rotate. As the main shaft 3 rotates, it also drives the two eccentric wheels 53 to rotate. When the eccentric wheels 53 come into contact with the inner wall of the notch 541 during their rotation, they drive the transmission crank arm 54 to move. Since the transmission crank arm 54 and the transmission shaft 41 are connected by a one-way bearing 55, the transmission shaft 41 can only rotate in one direction during the movement of the transmission crank arm 54. This achieves the deceleration output effect between the output components. Compared with the existing technology, this structure is simpler and lighter than the gearbox structure, has higher transmission stability, and also has clutch protection and manual / automatic integrated drive.

Claims

1. An operating output module for a medium-voltage load switch, characterized in that: The device includes a housing, a motor, a main shaft, an output assembly, and at least two sets of reduction mechanisms. The motor, main shaft, output assembly, and reduction mechanisms are all fixed to the housing. The motor has an output gear, the main shaft has a first gear that meshes with the output gear, and the output assembly has a drive shaft. The reduction mechanism includes an eccentric wheel, a transmission crank arm, and a one-way bearing. The eccentric wheel is sleeved on the main shaft and is linked to it. The one-way bearing is sleeved on the drive shaft and is linked to it. One end of the transmission crank arm is sleeved on the one-way bearing and is linked to it. The other end of the transmission crank arm has a notch, and the inner wall of the notch, except for its bottom surface, is located on the movement trajectory of the eccentric wheel. The eccentric wheels of each reduction mechanism are in different positions, and all the eccentric wheels work together to drive the drive shaft to rotate continuously.

2. The operating output module of a medium-voltage load switch as described in claim 1, characterized in that: Each set of deceleration mechanisms is set up independently.

3. The operating output module of a medium-voltage load switch as described in claim 2, characterized in that: An isolation sleeve is provided between two adjacent eccentric wheels, and the isolation sleeve is fitted on the main shaft.

4. The operating output module of a medium-voltage load switch as described in claim 1, 2, or 3, characterized in that: Each eccentric wheel is equipped with a first bearing, and the inner wall of the notch, excluding its bottom surface, is located on the movement trajectory of the first bearing.

5. The operating output module of a medium-voltage load switch as described in claim 4, characterized in that: The height of the first bearing is greater than the depth of the notch.

6. The operating output module of a medium-voltage load switch as described in claim 1, characterized in that: It also includes a first pin, and the eccentric wheel has a first extension, through which the first pin passes and is connected to the main shaft.

7. The operating output module of a medium-voltage load switch as described in claim 1, characterized in that: The output assembly is equipped with an output shaft and a clutch mechanism. The drive shaft and the output shaft are connected by the clutch mechanism. When the motor is overloaded, the drive shaft and the output shaft will engage and disengage.

8. The operating output module of a medium-voltage load switch as described in claim 7, characterized in that: The clutch mechanism includes two friction plates and a pressure block. The drive shaft is provided with a flange that mates with the pressure block, and the output shaft is provided with a second extension. The pressure block is connected and fixed to the flange to form a chamber with an upper opening. The second extension is located inside the chamber. One end of the output shaft passes through the upper opening and extends out of the pressure block. The two friction plates are respectively provided on the upper and lower end faces of the second extension, with one friction plate abutting against the top surface of the chamber and the other friction plate abutting against the bottom surface of the chamber.

9. The operating output module of a medium-voltage load switch as described in claim 8, characterized in that: The clutch mechanism also includes a gasket located between the flange and the friction plate near the bottom of the chamber.

10. The operating output module of a medium-voltage load switch as described in claim 1, characterized in that: The housing has a recessed cavity, and the motor part is embedded in the recessed cavity for fixation.

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