Compact deceleration system for frame circuit breaker

Abstract

This utility model provides a compact reduction system for a frame circuit breaker, applied within the electric operating mechanism of the frame circuit breaker. The compact reduction system includes a support frame, on which a planetary gear reduction assembly and a reversing transmission assembly are mounted. The planetary gear reduction assembly includes a multi-stage coaxially arranged planetary gear mechanism. The reversing transmission assembly includes a first bevel gear, a second bevel gear, and a rotating shaft. An output shaft is mounted on the planetary gear mechanism near the reversing transmission assembly, driving the first bevel gear to rotate. The rotating shaft is mounted on the support frame, and the second bevel gear is sleeved on the rotating shaft, meshing with the first bevel gear. The axis of the second bevel gear is perpendicular to the axis of the first bevel gear. By replacing the conventional gearbox with a planetary gear reduction assembly and using bevel gear transmission for reversing instead of conventional worm gear transmission, and by using a modular support frame, the system achieves good force transmission, a high reduction ratio, high load-bearing capacity, long service life, a compact structure, and low manufacturing cost.

Description

Technical Field

[0001] This utility model relates to the field of circuit breaker technology, specifically to a compact deceleration system 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. As a core protective electrical appliance in low-voltage power distribution systems, it is widely used in industrial, commercial and large building power distribution systems due to its ultra-high rated current carrying capacity, ultra-high short-circuit breaking capacity and integrated intelligent monitoring and communication functions.

[0003] In traditional drive and transmission systems of frame circuit breakers, gear sets and worm gears are commonly used as core components for speed reduction and force direction conversion. When a gear set in a conventional shaft-gear system is engaged, only one tooth meshes simultaneously. This single tooth must bear the entire torque output by the motor and the impact forces generated during transmission. Therefore, high-strength alloy steel or special metals are required. These materials are not only much more expensive to procure than ordinary steel, but their processing is also more complex. Furthermore, the single-tooth meshing transmission method concentrates the force on the gear, making it prone to failure problems such as tooth surface wear, pitting, and tooth root bending fatigue under long-term operation. This reduces transmission reliability and increases maintenance and replacement frequency and overall life-cycle costs. While worm gear reduction mechanisms can achieve 90° steering and high reduction ratios, the low efficiency (typically <50%) caused by sliding meshing keeps the motor under overload for extended periods: increased energy consumption and accelerated temperature rise shorten motor life and may trigger circuit breaker malfunctions due to overheating, endangering the safety of the power distribution system. Simultaneously, the complex machining process and low production efficiency of worm gears increase costs. In addition, the worm gear mechanism needs to ensure sufficient meshing depth to transmit large torque, requiring the outer diameter of the worm wheel and the length of the worm to meet a certain proportional relationship, which makes it difficult to effectively reduce its size and does not conform to the miniaturization development trend of frame circuit breakers. Summary of the Invention

[0004] The purpose of this invention is to provide a compact deceleration system for a frame circuit breaker to solve the above-mentioned problems.

[0005] The technical solution adopted in this utility model is as follows: A compact reduction system for a frame circuit breaker is applied within the electric operating mechanism of the frame circuit breaker. The compact reduction system includes a bracket, on which a planetary gear reduction assembly and a reversing transmission assembly are mounted. The planetary gear reduction assembly includes a multi-stage coaxially arranged planetary gear mechanism. The reversing transmission assembly includes a first bevel gear, a second bevel gear, and a rotating shaft. An output shaft is mounted on the planetary gear mechanism near the reversing transmission assembly. The output shaft drives the first bevel gear to rotate. The rotating shaft is mounted on the bracket. The second bevel gear is sleeved on the rotating shaft and meshes with the first bevel gear. The axis of the second bevel gear is perpendicular to the axis of the first bevel gear.

[0006] As a further improvement of the present invention, the planetary gear mechanism includes a sun gear, a planetary disk and a plurality of planetary gears. The plurality of planetary gears are evenly distributed circumferentially around the sun gear. A plurality of planetary shafts are provided on the radial surface of the planetary disk away from the reversing transmission component. The planetary gears correspond one-to-one with the planetary shafts and are sleeved on the planetary shafts. The plurality of planetary gears mesh with the sun gear and can rotate synchronously with the sun gear.

[0007] As a further improvement of this utility model, the sun gear is fixed on a planetary disk that is adjacent to it and far away from the reversing transmission assembly.

[0008] As a further improvement of this utility model, the tooth width of the sun gear is greater than the tooth width of the planet gear.

[0009] As a further improvement of this utility model, a deceleration channel for accommodating the planetary gear reduction assembly is provided in the bracket, and an outer ring fixed tooth that meshes with the planetary gear in the planetary gear mechanism is provided in the deceleration channel.

[0010] As a further improvement of the present invention, a reversing channel for accommodating the reversing transmission assembly is also provided in the bracket, and a connecting channel is provided between the deceleration channel and the reversing channel, and the output shaft extends into the reversing channel through the connecting channel.

[0011] As a further improvement of this utility model, a first thrust bearing is provided between the output shaft and the first bevel gear, and a second thrust bearing is provided between the rotating shaft and the second bevel gear.

[0012] As a further improvement of the present invention, a first bushing is provided on the output shaft, the first bushing being used to limit the axial position of the first bevel gear on the output shaft.

[0013] As a further improvement of the present invention, the connecting channel is provided with a coaxial first connecting section and a second connecting section. The inner diameter of the first connecting section is smaller than the inner diameter of the second connecting section. The first bushing includes an output bushing section and a connecting bushing section. The diameter of the connecting bushing section is larger than the diameter of the output bushing section. The output bushing section is disposed between the output shaft and the first connecting section, and the connecting bushing section is disposed between the first bevel gear and the second connecting section.

[0014] As a further improvement of the present invention, a first limiting member is provided on the rotating shaft, and a second bushing is provided between the first limiting member and the second bevel gear. The second bushing is sleeved on the rotating shaft and is used to limit the axial position of the second bevel gear.

[0015] The beneficial effects of this utility model are as follows: By replacing the conventional gearbox with a planetary gear reduction assembly, better torque transmission, higher reduction ratio, better load-bearing capacity, and smaller space ratio are achieved. The use of bevel gear transmission for reversing instead of conventional worm gear transmission effectively improves force transmission efficiency, extends service life, and results in a compact structure. The modular bracket optimizes the space of the reduction system within the electric operating mechanism, facilitating assembly and reducing manufacturing costs. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the internal structure of the electric operating mechanism; Figure 2 This is a schematic diagram of a compact reduction gear system without a gearbox. Figure 3 This is a schematic diagram of the planetary gear reduction assembly; Figure 4 This is a schematic diagram of the planetary gear reduction assembly; Figure 5 This is a schematic diagram of the reversing drive assembly; Figure 6 This is a schematic diagram of the support structure; Figure 7 This is a cross-sectional view of the bracket; Figure 8 This is a cross-sectional view of a compact deceleration system.

[0017] Wherein: 1-bracket, 101-cover plate, 102-box body, 103-input hole, 104-outer ring fixed tooth, 105-reduction channel, 106-reversing channel, 1071-first connecting section, 1072-second connecting section, 2-planetary gear reduction assembly, 201-sun gear, 202-planetary disk, 203-planetary gear, 204-planetary shaft, 205-output shaft, 2051-first shaft section, 20 52-Second shaft segment, 206-Drive connection hole, 3-Reversing transmission assembly, 301-First bevel gear, 302-Second bevel gear, 303-Rotating shaft, 304-First thrust bearing, 305-Second thrust bearing, 306-First bushing, 3061-Output bushing segment, 3062-Connecting bushing segment, 307-First limiting member, 308-Second bushing, 4-Electrical control housing, 5-Motor, 6-Main shaft assembly. 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] A compact reduction gear system for a frame circuit breaker, applied within the electric operating mechanism of the frame circuit breaker, such as... Figures 1-2 As shown, the electric operating mechanism includes an electric operating housing 4, within which a motor 5, a compact reduction system, and a spindle assembly 6 are disposed. The compact reduction system includes a bracket 1, on which a planetary gear reduction assembly 2 and a reversing transmission assembly 3 are disposed. The planetary gear reduction assembly 2 includes a multi-stage coaxially arranged planetary gear mechanism. The reversing transmission assembly 3 includes a first bevel gear 301, a second bevel gear 302, and a rotating shaft 303. An output shaft 205 is disposed on the planetary gear mechanism near the reversing transmission assembly 3, driving the first bevel gear 301 to rotate. The rotating shaft 303 is disposed on the bracket 1, and the second bevel gear 302 is sleeved on the rotating shaft 303. The second bevel gear 302 meshes with the first bevel gear 301, and the axis of the second bevel gear 302 is perpendicular to the axis of the first bevel gear 301.

[0021] By setting up a multi-stage planetary gear mechanism, the reduction ratio range is expanded, enabling precise speed regulation and adapting to a wider range of motors. The bevel gear tooth surface design has excellent conjugate characteristics, allowing for smooth meshing between teeth during transmission. The reasonable distribution of the contact area results in relatively small impact forces and vibrations, effectively reducing energy loss caused by tooth surface friction and impact vibration. This has the advantage of low transmission loss, ensuring that power can be transmitted more efficiently during directional changes.

[0022] As one embodiment of this utility model, such as Figures 3-4 As shown, the planetary gear mechanism includes a sun gear 201, a planetary disk 202, and a plurality of planetary gears 203. The plurality of planetary gears 203 are evenly distributed circumferentially around the sun gear 201. A plurality of planetary shafts 204 are provided on the radial surface of the planetary disk 202 away from the reversing transmission component 3. The planetary gears 203 correspond one-to-one with the planetary shafts 204 and are sleeved on the planetary shafts 204. The plurality of planetary gears 203 mesh with the sun gear 201. The plurality of planetary gears 203 can rotate synchronously with the sun gear 201. The planetary disk 202, planetary shafts 204, and planetary gears 203 all rotate around the sun gear 201.

[0023] The planetary gear reduction assembly 2 has a high transmission ratio through the meshing of the sun gear 201 and planet gears 203. Specifically, the sun gear 201 is fixed on a planetary disk 202 located adjacent to it and away from the reversing transmission assembly 3. Furthermore, multiple sets of the planetary gear mechanism can have different numbers of planet gears 203 to meet the requirements of the reduction ratio.

[0024] If we define the planetary gear mechanism furthest from the reversing transmission assembly 3 as the first planetary gear mechanism, and the planetary gear mechanism closest to the reversing transmission assembly 3 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. Among them, the sun gear 201 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 reversing transmission assembly 3, so an output shaft 205 is set on the radial surface of the planetary disk 202 of the Nth planetary gear mechanism near the reversing transmission assembly 3; in order to achieve coaxial transmission, the sun gear 201 of the first planetary gear mechanism and the output shaft 205 of the Nth planetary gear mechanism are set coaxially.

[0025] The planetary gear reduction assembly 2 uses coaxial transmission, has a compact structure, and is easy to install and design in a limited space; the planetary gears 203 are evenly distributed, achieving uniform load distribution. Under the same volume and weight, the planetary gear reduction assembly 2 has better torque transmission effect than ordinary gearboxes, runs more smoothly, and reduces costs; by connecting multiple planetary gear mechanisms in series, a larger reduction ratio can be obtained without significantly increasing the volume.

[0026] As one embodiment of this utility model, such as Figures 6-8 As shown, the bracket 1 is a plug-in type bracket, which includes a cover plate 101 and a housing 102. The cover plate 101 and the housing 102 are plugged together. The motor 5 can be fixed on the cover plate 101. An input hole 103 is provided on the cover plate 101. The drive shaft of the motor 5 passes through the input hole 103 to drive the planetary gear reduction assembly 2 to rotate. A drive connection hole 206 is provided on the sun gear 201, which is farthest from the reversing transmission assembly 3. The drive connection hole 206 is an irregularly shaped hole. The drive connection hole 206 cooperates with the drive shaft of the motor 5, so that the drive shaft of the motor 5 can drive the adjacent sun gear 201 to rotate.

[0027] As an embodiment of this utility model, an outer ring fixed tooth 104 is provided on the bracket 1 to mesh with the planetary gears 203 in the planetary gear mechanism. Since the bracket 1 remains stationary, as the planetary gears 203 rotate with the central sun gear 201, the planetary gears 203 mesh with the outer ring fixed tooth 104 on the inner wall of the bracket 1 and rotate along the outer ring fixed tooth 104, providing a "fixed track" for the planetary gears 203. This not only limits the movement trajectory of the planetary gears 203, but also forces the planetary gears 203 to revolve around the sun gear 201 while rotating on their own axis, thus completing the "planetary" motion. This structure integrates the conventional outer ring gear frame with the bracket 1 into one unit, saving the internal space of the bracket 1.

[0028] In one embodiment of this utility model, the tooth width of the sun gear 201 is greater than that of the planet gear 203. Since the sun gear 201 is the power input end, it must be disassembled and replaced if damaged, resulting in high maintenance costs. In contrast, the planet gears 203 are numerous, small in size, easy to disassemble and assemble, and have low material costs. Therefore, setting the tooth width of the sun gear 201 to be higher can provide higher bending strength and contact strength. This not only reduces the risk of undercutting of the sun gear 201 and improves the single-tooth load-bearing capacity, but also "transfers" the failure risks such as fatigue and wear to the planet gears 203. In this way, even if the planet gears 203 fail first, they can be quickly replaced, reducing the downtime and maintenance costs of the entire machine. The entire planetary gear mechanism can transmit greater torque in a more compact space.

[0029] In one embodiment of this utility model, the number of teeth of the sun gear 201 is generally less than the number of teeth of the planet gear 203 in order to obtain a larger reduction ratio.

[0030] Furthermore, apart from the planetary disk 202, planetary shaft 204 and output shaft 205 in the Nth planetary gear mechanism near the reversing transmission assembly 3, all other parts in the planetary gear reduction assembly 2 can be injection molded parts, and the bracket 1 and the electric control housing 4 can also be injection molded parts. Compared with metal parts, they are not only cheaper and more efficient in production, but also generate less noise during operation.

[0031] As one embodiment of this utility model, such as Figure 2 , Figure 5 As shown, a first thrust bearing 304 is provided between the output shaft 205 and the first bevel gear 301, and a second thrust bearing 305 is provided between the rotating shaft 303 and the second bevel gear 302. In actual transmission, when the bevel gears mesh to transmit power, axial force is inevitably generated, which may cause slight displacement in the axial direction. This leads to poor tooth surface contact, increased frictional losses, and may even affect the service life of the bevel gears and the stability of the transmission. By adding thrust bearings, these bearings can accurately withstand this axial force, limiting unnecessary movement of the bevel gears in the axial direction, ensuring that the bevel gears are always in the correct meshing position, reducing additional losses caused by axial displacement, and thus further improving the conversion efficiency of the entire transmission system.

[0032] As an embodiment of the present invention, a first bushing 306 is provided on the output shaft 205. The first bushing 306 is used to limit the axial position of the first bevel gear 301 on the output shaft 205 and reduce the hard friction between the output shaft 205 and the first bevel gear 301, thereby improving the service life.

[0033] Furthermore, such as Figure 7As shown, the housing 102 of the bracket 1 contains at least two areas. One area is the aforementioned reduction channel 105 for accommodating the planetary gear reduction assembly 2, in which the aforementioned outer ring fixed tooth 104 is provided. The other area is the reversing channel 106 for accommodating the reversing transmission assembly 3. A connecting channel is provided between the reduction channel 105 and the reversing channel 106, through which the output shaft 205 extends into the reversing channel 106. Furthermore, the connecting channel is provided with a coaxial first connecting section 1071 and a second connecting section 1072. The inner diameter of the first connecting section 1071 is smaller than the inner diameter of the second connecting section 1072. The output shaft 205 extends into the reversing channel 106 through the first connecting section 1071 and the second connecting section 1072. Furthermore, as needed, a spindle channel for accommodating the spindle assembly 6 can be provided inside the housing 102. This spindle channel can be connected to the reversing channel 106. The integrated structure can effectively improve the fitting accuracy and make the structure more compact, thereby facilitating the assembly of the overall structure.

[0034] Furthermore, the mating surface of the output shaft 205 and the first bevel gear 301 can be a non-circular cross-section to achieve synchronous rotation. The output shaft 205 includes a first shaft segment 2051 and a second shaft segment 2052. The diameter of the first shaft segment 2051 is greater than the maximum radial segment length of the second shaft segment 2052. The first bevel gear 301 is sleeved on the second shaft segment 2052. The first bushing 306 includes an output shaft sleeve segment 3061 and a connecting shaft sleeve segment 3062. The diameter of the connecting shaft sleeve segment 3062 is greater than the diameter of the output shaft sleeve segment 3061. The output shaft sleeve segment 3061 is sleeved on the first shaft segment 2051. The first shaft segment 2051 is disposed within the first connecting segment 1071. The output shaft sleeve segment 3061 is disposed between the output shaft 205 and the first connecting segment 1071. The output shaft sleeve segment 3061 mates with the first connecting segment 1071 to achieve synchronous rotation. To reduce hard friction between the first shaft segment 2051 and the first connecting segment 1071, the connecting shaft sleeve segment 3062 is sleeved on the first bevel gear 301, the second shaft segment 2052 is disposed inside the second connecting segment 1072, and the connecting shaft sleeve segment 3062 is disposed between the first bevel gear 301 and the second connecting segment 1072. The connecting shaft sleeve segment 3062 cooperates with the second connecting segment 1072 to reduce hard friction between the first bevel gear 301 and the second connecting segment 1072.

[0035] As one embodiment of this utility model, such as Figure 2As shown, a first limiting member 307 is provided on the rotating shaft 303, and a second bushing 308 is provided between the first limiting member 307 and the second bevel gear 302. The second bushing 308 is sleeved on the rotating shaft 303 and is used to limit the axial position of the second bevel gear 302. Specifically, the first limiting member 307 is an annular boss coaxially arranged with the rotating shaft 303. Specifically, the second bushing 308 can also be made of plastic.

[0036] The compact reduction system provided by this utility model replaces the conventional gearbox with a planetary gear reduction assembly 2, achieving better torque transmission, higher reduction ratio, better load-bearing capacity, and smaller space ratio. It adopts bevel gear transmission for reversing instead of conventional worm gear transmission, effectively improving force transmission efficiency, extending service life, and resulting in a compact structure. The modular bracket 1 optimizes the space of the reduction system inside the electric operating mechanism, facilitating assembly and reducing manufacturing costs.

[0037] 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.

[0038] 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. A compact deceleration system for a frame circuit breaker, applied within the electric operating mechanism of the frame circuit breaker, characterized in that: The compact reduction system includes a bracket (1), on which a planetary gear reduction assembly (2) and a reversing transmission assembly (3) are arranged. The planetary gear reduction assembly (2) includes a multi-stage coaxially arranged planetary gear mechanism. The reversing transmission assembly (3) includes a first bevel gear (301), a second bevel gear (302), and a rotating shaft (303). An output shaft (205) is arranged on the planetary gear mechanism near the reversing transmission assembly (3). The output shaft (205) drives the first bevel gear (301) to rotate. The rotating shaft (303) is arranged on the bracket (1). The second bevel gear (302) is sleeved on the rotating shaft (303). The second bevel gear (302) meshes with the first bevel gear (301). The axis of the second bevel gear (302) is perpendicular to the axis of the first bevel gear (301).

2. The compact deceleration system for the frame circuit breaker according to claim 1, characterized in that: The planetary gear mechanism includes a sun gear (201), a planetary disk (202), and a plurality of planet gears (203). The plurality of planet gears (203) are evenly distributed circumferentially around the sun gear (201). A plurality of planet shafts (204) are provided on the radial surface of the planetary disk (202) away from the reversing transmission assembly (3). The planet gears (203) correspond one-to-one with the planet shafts (204) and are sleeved on the planet shafts (204). The plurality of planet gears (203) mesh with the sun gear (201), and the plurality of planet gears (203) can rotate synchronously with the sun gear (201).

3. The compact deceleration system for the frame circuit breaker according to claim 2, characterized in that: The sun gear (201) is fixed to a planetary disk (202) located adjacent to and away from the reversing drive assembly (3).

4. The compact deceleration system for the frame circuit breaker according to claim 2, characterized in that: The tooth width of the sun gear (201) is greater than that of the planet gear (203).

5. The compact deceleration system for the frame circuit breaker according to claim 2, characterized in that: A reduction channel (105) for accommodating the planetary gear reduction assembly (2) is provided in the bracket (1), and an outer ring fixed tooth (104) for meshing with the planetary gear (203) in the planetary gear mechanism is provided in the reduction channel (105).

6. The compact deceleration system for the frame circuit breaker according to claim 5, characterized in that: The bracket (1) is also provided with a reversing channel (106) for accommodating the reversing transmission assembly (3). A connecting channel is provided between the deceleration channel (105) and the reversing channel (106). The output shaft (205) extends into the reversing channel (106) through the connecting channel.

7. The compact deceleration system for the frame circuit breaker according to claim 1, characterized in that: A first thrust bearing (304) is provided between the output shaft (205) and the first bevel gear (301), and a second thrust bearing (305) is provided between the rotating shaft (303) and the second bevel gear (302).

8. The compact deceleration system for the frame circuit breaker according to claim 6, characterized in that: A first bushing (306) is provided on the output shaft (205), and the first bushing (306) is used to limit the axial position of the first bevel gear (301) on the output shaft (205).

9. The compact deceleration system for the frame circuit breaker according to claim 8, characterized in that: The connecting channel is provided with a coaxial first connecting section (1071) and a second connecting section (1072). The inner diameter of the first connecting section (1071) is smaller than the inner diameter of the second connecting section (1072). The first bushing (306) includes an output bushing section (3061) and a connecting bushing section (3062). The diameter of the connecting bushing section (3062) is larger than the diameter of the output bushing section (3061). The output bushing section (3061) is located between the output shaft (205) and the first connecting section (1071). The connecting bushing section (3062) is located between the first bevel gear (301) and the second connecting section (1072).

10. The compact deceleration system for the frame circuit breaker according to claim 1, characterized in that: A first limiting member (307) is provided on the rotating shaft (303), and a second bushing (308) is provided between the first limiting member (307) and the second bevel gear (302). The second bushing (308) is sleeved on the rotating shaft (303) and is used to limit the axial position of the second bevel gear (302).

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