Multi-planet gear reinforced load bearing differential

Abstract

The present application relates to the technical field of continuously variable transmission, in particular to a multi-planet gear reinforced load differential mechanism, comprising a differential mechanism, a floating mechanism and a stability maintaining mechanism.In the present application, when the supporting shaft appears multi-angle displacement, the ball sleeve and the pipe sleeve form a spherical hinge pair, in general, the ball sleeve can be self-adaptively deflected in the pipe sleeve with the angle change of the supporting shaft, so as to avoid the jamming or additional bending moment between the supporting shaft and the pipe sleeve, ensure the sensitivity and smoothness of the floating adjustment, at the same time, the left side of the pipe sleeve is tightly pressed by the spring, the pressing frame and the pressing cylinder frame, the right side of the pipe sleeve is tightly pressed by the pressing sleeve, the spring steel and the blocking frame, this double-sided tightening structure can not only ensure that the pipe sleeve provides sufficient supporting stiffness to the supporting shaft, but also allows the ball sleeve to be self-adaptively deflected in the pipe sleeve, realize the floating supporting effect of "rigidity and flexibility", effectively alleviate the common "S" shape bending deformation and edge contact wear problems of the planet gear shaft under heavy load.

Description

Technical Field

[0001] This invention relates to the field of continuously variable transmission (CVT) technology, specifically to a multi-planetary gear reinforced load-bearing differential. Background Technology

[0002] A car differential is a mechanism that allows the left and right (or front and rear) drive wheels to rotate at different speeds. It mainly consists of left and right half-shaft gears, two planetary gears, and a gear carrier. Its function is to ensure that the left and right wheels rotate at different speeds when the car is turning or driving on uneven surfaces, thus guaranteeing pure rolling motion for both drive wheels. The differential is designed to adjust the speed difference between the left and right wheels. In four-wheel drive, all four wheels must be connected to drive them. If the four wheels are mechanically connected, the car will not rotate at the same speed when driving on curves. To ensure that the rotational speed is approximately consistent when the car is turning, a center differential is needed to adjust the speed difference between the front and rear wheels.

[0003] Under prolonged heavy-load operation, the planetary gear shaft undergoes "S"-shaped bending deformation under multi-point loads and constraints. The shaft and bore centerlines become non-parallel, resulting in edge contact. Surface pressure concentrates in narrow areas and exhibits localized peak values, leading to wear failures such as ploughing, scuffing, and plastic deformation in the planetary gear shaft and inner bore. The planetary gear bearing is subjected to combined bending and shear stresses, and its deformation directly affects the gear meshing accuracy and load-bearing capacity. Summary of the Invention

[0004] The present invention aims to solve one of the technical problems existing in the prior art or related technologies.

[0005] Therefore, the technical solution adopted in this invention is as follows: A multi-planetary gear reinforced load-bearing differential includes a differential mechanism, a floating mechanism, and a stabilizing mechanism. The differential mechanism includes a gear ring, a sun gear shaft rotatably disposed inside the gear ring, three planetary gears meshing between the gear ring and the sun gear shaft, a support shaft concentrically arranged with the planetary gears and rotatably passing through the front end of the planetary gears, two bearings rotatably connected between the planetary gears and the support shaft, an L-shaped rod movably passing through the front end of the support shaft, a core rod fixedly connected among multiple L-shaped rods, and a T-shaped opening at the front end of the support shaft suitable for the movable engagement of the L-shaped rods. The floating mechanism includes a ball sleeve fixedly sleeved to the front end of the support shaft, a tubular sleeve movably sleeved to the outside of the ball sleeve, and an interference fit... The tube sleeve consists of two pressure cylinder frames on one side, a pressure frame rotatably connected between two adjacent pressure cylinder frames, two torsion springs fixed between the pressure cylinder frame and the pressure frame, a support frame slidably sleeved on the outer end of the pressure frame and fixed to the L-rod, two springs fixed between the outer side of the pressure frame and the inner side of the support frame, a pressure sleeve with interference fit to the other side of the tube sleeve, a spring steel fixed to the inner side of the pressure sleeve, a stop frame with interference fit to the outer side of the spring steel and fixed to the outer wall of the L-rod, and a stabilizing mechanism. The stabilizing mechanism includes two traction frames movably sleeved on both ends of the spring steel, and a tension rope fixed between the pressure frame and the two traction frames. The tension rope movably passes through the stop frame and fits against the outer side of the support frame.

[0006] By adopting the above technical solution, when the support shaft undergoes multi-angle displacement, the ball sleeve and the tube sleeve form a spherical hinge pair. In general, the ball sleeve can adaptively deflect within the tube sleeve according to the angle change of the support shaft, thereby avoiding jamming or additional bending moment between the support shaft and the tube sleeve, ensuring the sensitivity and smoothness of floating adjustment. At the same time, the left side of the tube sleeve is firmly pressed by the spring, pressure frame, and pressure cylinder frame, while the right side of the tube sleeve is firmly pressed by the pressure sleeve, spring steel, and stop frame. This double-sided clamping structure ensures that the tube sleeve provides sufficient support rigidity to the support shaft, while allowing the ball sleeve to adaptively deflect within the tube sleeve, achieving a floating support effect that combines rigidity and flexibility. This effectively alleviates the common "S"-shaped bending deformation and edge contact wear problems of planetary gear shafts under heavy loads.

[0007] In a preferred embodiment, the present invention can be further configured such that the sun gear shaft and the gear ring are concentrically arranged, and the three planetary gears are equally spaced and arranged in a ring between the gear ring and the sun gear shaft.

[0008] In a preferred embodiment, the present invention may be further configured such that the pressure cylinder frame consists of two baffles and two rollers, with the two rollers rotatably connected between the two baffles.

[0009] In a preferred embodiment, the present invention can be further configured as follows: the pressure frame consists of an arc-shaped plate, two rotating shafts, and two T-bars. The two rotating shafts are respectively fixedly embedded in the top and bottom of the arc-shaped plate. The two pressure cylinder frames are rotatably connected to the arc-shaped plate through the two rotating shafts. The two T-bars are fixed to the outside of the arc-shaped plate. The torsion spring is movably sleeved on the outer end of the rotating shaft, and the spring is movably sleeved on the outside of the T-bar.

[0010] In a preferred embodiment, the present invention can be further configured such that the traction frame consists of a plate frame and two pressure rollers, the two pressure rollers being respectively attached to the inner and outer sides of the spring steel, and the pressure rollers being rotatably mounted on the inner side of the plate frame.

[0011] In a preferred embodiment, the present invention may be further configured such that the tension rope consists of two main ropes and a branch rope, with the two main ropes respectively fixed between the two plate frames and the branch ropes.

[0012] In a preferred embodiment, the present invention can be further configured such that a guide tube is fixedly installed on the outside of the baffle, and the tension rope movably passes through the guide tube.

[0013] In a preferred embodiment, the present invention may be further configured such that the guide tube is U-shaped and the inner wall of the guide tube is polished.

[0014] In a preferred embodiment, the present invention can be further configured such that: the support shaft is provided with two sets of anti-detachment components, the two sets of anti-detachment components are respectively located on the front and rear sides of the planetary gear, the anti-detachment component includes a retaining ring slidably sleeved on the outside of the support shaft and a pin screwed to the support shaft, the pin being attached to the outside of the retaining ring.

[0015] In a preferred embodiment, the present invention may be further configured such that a spacer ring is interference-fitted inside the planetary gear, the spacer ring being fitted between two bearings.

[0016] By adopting the above technical solution, the beneficial effects achieved by the present invention are as follows: 1. In this invention, when the support shaft undergoes multi-angle displacement, the ball sleeve and the tube sleeve form a spherical hinge pair. Generally speaking, the ball sleeve can adaptively deflect within the tube sleeve according to the angle change of the support shaft, thereby avoiding jamming or additional bending moment between the support shaft and the tube sleeve, ensuring the sensitivity and smoothness of floating adjustment. At the same time, the left side of the tube sleeve is firmly pressed by the spring, pressure frame, and pressure cylinder frame, while the right side of the tube sleeve is firmly pressed by the pressure sleeve, spring steel, and stop frame. This double-sided clamping structure ensures that the tube sleeve provides sufficient support rigidity to the support shaft while allowing the ball sleeve to adaptively deflect within the tube sleeve, achieving a "rigid and flexible" floating support effect, effectively alleviating the common "S"-shaped bending deformation and edge contact wear problems of planetary gear shafts under heavy loads.

[0017] 2. In this invention, when the differential is in operation, if the load on one planetary gear is greater than that on the other two due to manufacturing errors, assembly deviations, or sudden changes in operating conditions, the small radial bias generated by the planetary gear is transmitted to the support shaft through the bearing. Since the T-shaped opening provides the L-bar with a relative space for movement relative to the support shaft, the support shaft subjected to bias can generate a micron-level radial displacement within this space. This causes the meshing state of the planetary gear with the sun gear shaft and the ring gear to be adaptively adjusted, gradually transferring the excess load to the two adjacent planetary gears. Ultimately, this achieves a dynamic load balance distribution among the three planetary gears. This process effectively avoids tooth tip contact fatigue and tooth surface pitting caused by long-term overload of a single planetary gear, and significantly improves the meshing reliability and service life of the differential under heavy load conditions.

[0018] 3. In this invention, when the radial displacement of the support shaft exceeds the reasonable range, the stabilization mechanism intervenes to limit and correct the position: the elastic deformation of the spring steel drives the movement of the traction frames at both ends, and the tension rope pulls the pressure frame to generate a reverse traction force, which is then applied to the support shaft through the pressure cylinder frame and the sleeve, forcing it to return to the center position; the guide tube constrains the direction of the tension rope to prevent centrifugal force from causing loss of transmission accuracy. This correction mechanism effectively prevents gear disengagement or aggravated uneven load, ensures the stability and safety of the dynamic adjustment of the differential system, and extends the fatigue life of the floating mechanism and the stabilization mechanism. Attached Figure Description

[0019] Figure 1 This is a perspective view of the overall structure of the present invention; Figure 2 This is a schematic diagram of the differential mechanism of the present invention; Figure 3 This is a schematic diagram showing the mounting positions of the bearing and the core rod, as well as the opening position of the T-shaped opening in this invention. Figure 4 This is a schematic diagram showing the cooperative relationship between the floating mechanism and the stabilization mechanism of the present invention; Figure 5 This is a schematic diagram of the assembly of the floating mechanism of the present invention; Figure 6 This is a schematic diagram showing the disassembled structure of the floating mechanism of the present invention; Figure 7 This is a schematic diagram showing the connection relationship between the pressure cylinder frame, the pressure frame, the torsion spring, and the spring of the present invention; Figure 8 This is a schematic diagram of the stabilization mechanism of the present invention; Figure 9 This is a schematic diagram of the specific structure of the traction frame and tension rope of the present invention.

[0020] Figure label: 100. Differential mechanism; 110. Ring gear; 120. Sun gear shaft; 130. Planetary gear; 140. Support shaft; 150. Bearing; 160. L-shaped rod; 170. Core rod; 180. T-shaped opening; 200. Floating mechanism; 210. Ball sleeve; 220. Tube sleeve; 230. Pressure cylinder frame; 231. Baffle; 232. Roller; 240. Pressure frame; 241. Arc plate; 242. Rotating shaft; 243. T-bar; 250. Torsion spring; 260. Support frame; 270. Spring; 280. Pressure sleeve; 290. Spring steel; 291. Stop frame; 300. Stabilization mechanism; 310. Traction frame; 311. Plate frame; 312. Pressure roller; 320. Tensioning rope; 321. Main rope; 322. Support rope; 500, guide tube; 600. Anti-detachment component; 610. Retaining ring; 620. Pin; 700, spacer ring. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments and accompanying drawings. It should be noted that, unless otherwise specified, the embodiments and features described herein can be combined with each other.

[0022] It should be understood that these descriptions are merely exemplary and are not intended to limit the scope of the invention.

[0023] The following describes, with reference to the accompanying drawings, some embodiments of the present invention, providing a multi-planetary gear reinforced load-bearing differential.

[0024] Example 1: Combining Figures 1-9 As shown, the present invention provides a multi-planetary gear reinforced load-bearing differential, including a differential mechanism 100, a floating mechanism 200, and a stabilizing mechanism 300. The differential mechanism 100 includes a gear ring 110, a sun gear shaft 120 rotatably disposed inside the gear ring 110, three planetary gears 130 meshing between the gear ring 110 and the sun gear shaft 120, a support shaft 140 concentrically disposed with the planetary gears 130 and rotatably passing through the front end of the planetary gears 130, two bearings 150 rotatably connected between the planetary gears 130 and the support shaft 140, an L-shaped rod 160 movably passing through the front end of the support shaft 140, a core rod 170 fixedly connected between the multiple L-shaped rods 160, and a T-shaped opening 180 opened at the front end of the support shaft 140 and adapted for the L-shaped rods 160 to be movably engaged. A floating mechanism 200 includes a ball sleeve 210 fixedly sleeved to the front end of the support shaft 140, a tube sleeve 220 movably sleeved to the outside of the ball sleeve 210, two pressure cylinder frames 230 interference-fitted to one side of the tube sleeve 220, a pressure frame 240 rotatably connected between two adjacent pressure cylinder frames 230, two torsion springs 250 fixedly connected between the pressure cylinder frame 230 and the pressure frame 240, a support frame 260 slidably sleeved to the outer end of the pressure frame 240 and fixedly connected to the L rod 160, two springs 270 fixedly connected between the outside of the pressure frame 240 and the inside of the support frame 260, a pressure sleeve 280 interference-fitted to the other side of the tube sleeve 220, a spring steel 290 fixedly sleeved to the inside of the pressure sleeve 280, and a stop frame 291 interference-fitted to the outside of the spring steel 290 and fixedly connected to the outer wall of the L rod 160. The stabilization mechanism 300 includes two traction frames 310 movably sleeved at both ends of the spring steel 290, and a tension rope 320 fixed between the pressure frame 240 and the two traction frames 310. The tension rope 320 movably passes through the baffle 291 and is attached to the outside of the support frame 260.

[0025] Furthermore, the sun gear shaft 120 and the gear ring 110 are concentrically arranged, and the three planetary gears 130 are equally spaced and arranged in a ring between the gear ring 110 and the sun gear shaft 120, so that each planetary gear 130 evenly distributes the load in the circumferential direction, reducing the inherent off-center load caused by the asymmetrical layout from the geometric source, and providing good initial symmetry conditions for the load equalization adjustment of the floating mechanism 200.

[0026] Furthermore, the pressure cylinder frame 230 is composed of two baffles 231 and two rollers 232. The two rollers 232 are rotatably connected between the two baffles 231, so that when the pressure cylinder frame 230 is in interference fit with the sleeve 220, the rollers 232 can convert sliding friction into rolling friction, which not only ensures the tightening force on the sleeve 220, but also greatly reduces the frictional resistance and wear of the contact surface, making the floating adjustment more sensitive and smooth.

[0027] Furthermore, the pressure frame 240 is composed of an arc-shaped plate 241, two rotating shafts 242, and two T-bars 243. The two rotating shafts 242 are respectively fixedly embedded in the top and bottom of the arc-shaped plate 241. The two pressure cylinder frames 230 are rotatably connected to the arc-shaped plate 241 through the two rotating shafts 242. The two T-bars 243 are fixed to the outside of the arc-shaped plate 241. The torsion spring 250 is movably sleeved on the outer end of the rotating shaft 242, and the spring 270 is movably sleeved on the outside of the T-bar 243, so that the pressure frame 240 and the pressure cylinder frame 230 form an automatically reset hinged linkage structure. The torsion spring 250 provides rotational reset torque, and the spring 270 provides axial clamping force. The two work together to ensure that the pressure cylinder frame 230 always maintains a constant and flexible clamping pressure on the sleeve 220, avoiding the attenuation of clamping force due to vibration or thermal deformation.

[0028] Furthermore, the traction frame 310 is composed of a plate frame 311 and two pressure rollers 312. The two pressure rollers 312 are respectively attached to the inner and outer sides of the spring steel 290. The pressure rollers 312 are rotatably mounted on the inner side of the plate frame 311, so that the traction frame 310 can clamp the spring steel 290 from both the inner and outer sides. The sliding friction is converted into rolling friction through the rolling contact of the pressure rollers 312, which not only ensures the reliable clamping and traction of the spring steel 290 by the traction frame 310, but also avoids scratching damage to the surface of the spring steel 290, ensuring the stability and reliability of the stabilization mechanism 300 in long-term reciprocating motion.

[0029] Furthermore, the tension rope 320 consists of two main ropes 321 and a branch rope 322. The two main ropes 321 are respectively fixed between the two plate frames 311 and the branch rope 322, so that the displacement of the pressure frame 240 can be synchronously transmitted to the two main ropes 321 through the branch rope 322, thereby simultaneously pulling the two traction frames 310 to apply symmetrical traction force to both ends of the spring steel 290, ensuring that the spring steel 290 is subjected to balanced force at both ends when deforming, and preventing structural tilting or jamming caused by unilateral traction.

[0030] Furthermore, the planetary gear 130 is internally interference-fitted with a spacer ring 700, which fits between the two bearings 150, so that the two bearings 150 always maintain a precise axial distance on the support shaft 140, preventing the bearings 150 from axially moving under heavy load or vibration conditions. At the same time, the spacer ring 700 can also share the axial load, improving the overall rigidity and life of the bearing 150 assembly.

[0031] Example 2: Combination Figure 1 , 4 8 and Figure 9As shown, based on Embodiment 1, a guide tube 500 is fixedly installed on the outer side of the baffle 291, and the tension rope 320 moves through the guide tube 500, so that the direction of the tension rope 320 is precisely constrained, avoiding interference or entanglement between the tension rope 320 and other components due to centrifugal force when the differential rotates at high speed, and ensuring that the transmission path of the stability signal is stable and reliable.

[0032] Furthermore, the guide tube 500 is U-shaped, and the inner wall of the guide tube 500 is polished to minimize the frictional resistance when the tension rope 320 slides in the guide tube 500. At the same time, the U-shaped design can effectively buffer the impact load of the tension rope 320 in reciprocating motion, reduce rope fatigue wear, and extend the service life of the tension rope 320.

[0033] Example 3: Combination Figure 1-2 As shown, in the above embodiment, the support shaft 140 is provided with two sets of anti-disengagement components 600. The two sets of anti-disengagement components 600 are respectively located on the front and rear sides of the planetary gear 130. The anti-disengagement component 600 includes a retaining ring 610 that is slidably sleeved on the outside of the support shaft 140 and a pin 620 that is screwed to the support shaft 140. The pin 620 fits against the outside of the retaining ring 610, so that the axial position of the planetary gear 130 on the support shaft 140 is doubly locked. The retaining ring 610 provides a large area of ​​axial limit, and the pin 620 prevents the retaining ring 610 from loosening. The two work together to effectively eliminate the risk of the planetary gear 130 moving or disengaging along the axial direction of the support shaft 140 under high speed and high vibration conditions, and ensure that the gear meshing width is always within the design range.

[0034] Working principle and usage process of this invention: Before use, this device is installed entirely inside the gearbox housing. When this device is put into actual use, the core rod 170 is movably engaged with the T-shaped opening 180 at the front end of the support shaft 140 through the L rod 160, so that the three support shafts 140 are connected in series in the circumferential direction by the core rod 170, thereby providing a stable radial support foundation for the three planetary gears 130. At the same time, the bearing 150 is rotatably connected between the planetary gear 130 and the support shaft 140, ensuring that the planetary gear 130 can rotate smoothly around the support shaft 140. During differential operation, if a certain planetary gear 130 bears a greater load than the other two due to manufacturing errors, assembly deviations, or sudden changes in operating conditions, the planetary gear 130 will generate a small radial bias. This bias is transmitted to the support shaft 140 through the bearing 150. Since the T-shaped opening 180 provides the L-bar 160 with a relative space to the support shaft 140, the support shaft 140 subjected to bias can generate a micron-level radial displacement within this space. This allows the meshing state of the planetary gear 130 with the sun gear shaft 120 and the ring gear 110 to be adaptively adjusted, gradually transferring the excess load to the two adjacent planetary gears 130, and finally achieving a dynamic load balance distribution among the three planetary gears 130. During the process of the support shaft 140 completing the above-mentioned radial displacement, the floating mechanism 200 plays a key supporting and guiding role. Specifically, the ball sleeve 210 fixedly sleeved at the front end of the support shaft 140 and the tube sleeve 220 movably sleeved on the outside of the ball sleeve 210 form a spherical hinge pair. When the support shaft 140 rotates at a small angle due to force, the ball sleeve 210 can adaptively deflect within the tube sleeve 220 according to the angle change of the support shaft 140, thereby avoiding jamming or additional bending moment between the support shaft 140 and the tube sleeve 220. Meanwhile, both sides of the sleeve 220 are stably tightened: on the left side, two pressure cylinder frames 230 provide clamping force through springs 270 inside the pressure frame 240 and support frame 260, and a torsion spring 250 provides rotational reset torque between the pressure cylinder frame 230 and the pressure frame 240, ensuring that the pressure cylinder frame 230 always fits against the outer wall of the left side of the sleeve 220 with flexible and constant pressure; on the right side, the stop frame 291, spring steel 290 and pressure sleeve 280 are sequentially interference-fitted to tighten the outer wall of the right side of the sleeve 220. This double-sided tightening structure ensures that the sleeve 220 provides sufficient support rigidity to the support shaft 140, while allowing the ball sleeve 210 to make adaptive angle deflection within the sleeve 220, achieving a floating support effect that combines rigidity and flexibility. When the radial displacement of the support shaft 140 exceeds the reasonable range, the stabilization mechanism 300 intervenes to limit and correct the displacement. That is, when the spring steel 290 is subjected to the radial force transmitted by the pressure sleeve 280, it will undergo elastic deformation. The two traction frames 310, which are movably sleeved at both ends of the spring steel 290 (clamping the spring steel 290 from the inside and outside sides through the plate frame 311 and the pressure roller 312), move synchronously with the deformation of the spring steel 290. The movement of the traction frames 310 is transmitted to the pressure frame 240 through the tension rope 320—one end of the support rope 322 is fixed to the pressure frame 240. Two main ropes 321 are respectively fixed between the plate frame 311 and the support rope 322 of the two traction frames 310. When the support shaft 140 is displaced too much, the tension rope 320 is tightened, thereby generating a reverse traction force on the pressure frame 240. This traction force is reacted on the support shaft 140 through the pressure frame 240, the pressure cylinder frame 230 and the sleeve 220, forcing the support shaft 140 to return to the center position. At the same time, the guide tube 500 precisely limits and guides the direction of the tension rope 320 to prevent the tension rope 320 from losing transmission accuracy due to centrifugal force swing. In summary, the T-shaped opening 180 of the differential mechanism 100, in conjunction with the L-bar 160, provides displacement space; the ball sleeve 210 of the floating mechanism 200, in conjunction with the tube sleeve 220, provides adaptive angle compensation; the pressure cylinder frame 230 and the pressure sleeve 280 provide double-sided tension support; and the spring steel 290 of the stabilizing mechanism 300, in conjunction with the tension rope 320, provides displacement limiting and return-to-center traction. These three mechanisms work together to achieve dynamic adaptive load sharing, bending resistance, and stable operation of the multi-planetary gear differential under heavy load conditions. This significantly reduces the risk of tooth surface contact fatigue, shaft hole edge wear, and gear eccentricity failure, and extends the overall service life of the differential.

[0035] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A multi-planetary gear reinforced load-bearing differential, characterized in that, include: A differential mechanism (100) includes a gear ring (110), a sun gear shaft (120) rotatably disposed inside the gear ring (110), three planetary gears (130) meshing between the gear ring (110) and the sun gear shaft (120), a support shaft (140) concentrically disposed with the planetary gears (130) and rotatably passing through the front end of the planetary gears (130), two bearings (150) rotatably connected between the planetary gears (130) and the support shaft (140), an L-shaped rod (160) movably passing through the front end of the support shaft (140), a core rod (170) fixed between the multiple L-shaped rods (160), and a T-shaped opening (180) opened at the front end of the support shaft (140) and adapted for the L-shaped rod (160) to be movably engaged. A floating mechanism (200) includes a ball sleeve (210) fixedly sleeved to the front end of the support shaft (140), a tube sleeve (220) movably sleeved to the outside of the ball sleeve (210), two pressure cylinder frames (230) interference-fitted to one side of the tube sleeve (220), a pressure frame (240) rotatably connected between two adjacent pressure cylinder frames (230), two torsion springs (250) fixedly connected between the pressure cylinder frame (230) and the pressure frame (240), and a sliding sleeve. A support frame (260) is attached to the outer end of the pressure frame (240) and fixed to the L rod (160); two springs (270) are fixed between the outer side of the pressure frame (240) and the inner side of the support frame (260); a pressure sleeve (280) is interference-fitted to the other side of the sleeve (220); a spring steel (290) is fixed to the inner side of the pressure sleeve (280); and a stop (291) is interference-fitted to the outer side of the spring steel (290) and fixed to the outer wall of the L rod (160). The stabilization mechanism (300) includes two traction frames (310) movably sleeved at both ends of the spring steel (290) and a tension rope (320) fixed between the pressure frame (240) and the two traction frames (310). The tension rope (320) movably passes through the baffle (291) and fits against the outside of the support frame (260).

2. The multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The sun gear shaft (120) and the gear ring (110) are concentrically arranged, and three planetary gears (130) are equally spaced and arranged in a ring between the gear ring (110) and the sun gear shaft (120).

3. The multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The pressure cylinder frame (230) consists of two baffles (231) and two rollers (232), with the two rollers (232) rotatably connected between the two baffles (231).

4. The multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The pressure frame (240) is composed of an arc plate (241), two rotating shafts (242), and two T rods (243). The two rotating shafts (242) are fixedly embedded in the top and bottom of the arc plate (241), and the two pressure cylinder frames (230) are rotatably connected to the arc plate (241) through the two rotating shafts (242). The two T rods (243) are fixed to the outside of the arc plate (241). The torsion spring (250) is movably sleeved on the outer end of the rotating shaft (242), and the spring (270) is movably sleeved on the outside of the T rod (243).

5. A multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The traction frame (310) consists of a plate frame (311) and two pressure rollers (312). The two pressure rollers (312) are respectively attached to the inner and outer sides of the spring steel (290). The pressure rollers (312) are rotatably installed on the inner side of the plate frame (311).

6. A multi-planetary gear reinforced load-bearing differential according to claim 5, characterized in that, The tension rope (320) consists of two main ropes (321) and a branch rope (322), with the two main ropes (321) fixed between the two plate frames (311) and the branch rope (322).

7. A multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, A guide tube (500) is fixedly installed on the outside of the baffle (291), and the elastic rope (320) moves through the guide tube (500).

8. A multi-planetary gear reinforced load-bearing differential according to claim 7, characterized in that, The guide tube (500) is U-shaped, and the inner wall of the guide tube (500) is polished.

9. A multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The support shaft (140) is provided with two sets of anti-detachment components (600). The two sets of anti-detachment components (600) are located on the front and rear sides of the planetary gear (130) respectively. The anti-detachment component (600) includes a retaining ring (610) that is slidably sleeved on the outside of the support shaft (140) and a pin (620) that is screwed to the support shaft (140). The pin (620) is attached to the outside of the retaining ring (610).

10. A multi-planetary gear reinforced load-bearing differential according to claim 1, characterized in that, The planetary gear (130) is internally interference-fitted with a spacer ring (700), which fits between two bearings (150).

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