Deceleration structure for automatic pipe winding device

Abstract

The invention relates to a speed reduction structure for an automatic pipe collecting and coiling device, and relates to the technical field of automatic pipe collecting and coiling devices. The speed reduction structure comprises an outer machine shell, a main shaft, a speed reduction wheel base, a rotating disc, a speed reduction disc and a locking device, a planet wheel is meshed with a gear ring on the rotating disc and a sun gear on a sun disc, and the sun disc is provided with centrifugal flail blocks. Speed reduction transmission is achieved through meshing of the planet gear, the gear ring and the sun gear, meshing control over the first gear through the locking device and dynamic adjustment of the centrifugal throwing block are combined, the speed reduction performance is improved, the function of stopping at any time when pulling is conducted is achieved, pipe end throwing is effectively restrained, and using safety is improved.

Description

Technical Field

[0001] This application relates to the field of automatic hose reel, and more specifically to a deceleration structure for an automatic hose reel. Background Technology

[0002] Hose reels are essential tools widely used in landscaping, automatic hose reeling, and household water pipe storage. They effectively manage and store tubular items such as water pipes and electrical wires, preventing damage or disarray during use due to unforeseen circumstances. In existing technologies, hose reels typically include a basic structure such as a reel, spindle, spring, and housing. The reel rotates, driving a reduction gear, and the retraction and release of tubular items are achieved by the contact or disengagement of the centrifugal arm with the friction wall. Some designs also incorporate locking and deceleration mechanisms to control the rotation of the reel. Their working principle relies on the interaction of mechanical transmission components to achieve speed regulation.

[0003] However, in the existing technology, the tube end of the hose reel is prone to irregular swinging during the retrieval process, which poses a potential safety hazard. Summary of the Invention

[0004] This application provides a deceleration structure for an automatic hose reel, which can solve technical problems such as insufficient deceleration effect and inability to achieve immediate stopping while pulling.

[0005] To achieve the above objectives, this application provides the following technical solution: This application provides a reduction structure for an automatic hose reel, including an outer housing; a main shaft with hexagonal ends and a first gear in the middle; a reduction wheel base with one end connected to the main shaft; a rotating disk connected to the reduction wheel base; a reduction disk fixedly connected to the rotating disk, with at least two planetary gears on the reduction disk; and a gear disposed on the reduction disk for controlling the engagement and disengagement of the gear of the following stop device with the first gear; wherein the planetary gears mesh with a gear ring fixed on the rotating disk and also mesh with a sun gear on a sun disk, and the sun disk is provided with centrifugal throwing blocks.

[0006] In one alternative embodiment, the reduction wheel base is provided with at least one counterweight groove, and a counterweight block is embedded in the counterweight groove.

[0007] In one alternative embodiment, the spindle and the reduction wheel base are circumferentially fixed by a key connection structure.

[0008] In one alternative embodiment, the outer side wall of the rotating disk is provided with an annular boss, which cooperates with the inner wall of the outer casing to limit the maximum rotation angle of the rotating disk.

[0009] In one optional embodiment, a disc spring is provided between the rotating disk and the reduction disk, with the two ends of the disc spring connected to the central shafts of the rotating disk and the reduction disk, respectively.

[0010] In one alternative embodiment, the gear includes a fixed sleeve; a movable sleeve fitted inside the fixed sleeve and having a track on its sidewall including a locking position and a movable position; a positioning sleeve fitted inside the movable sleeve and connected to the main shaft; and a torsion spring disposed between the movable sleeve and the positioning sleeve for providing a self-locking elastic force.

[0011] In one alternative embodiment, the inner wall of the speed reducer is provided with a rubber ring, which forms a friction pair with the rotating disk or the speed reducer itself.

[0012] In one alternative embodiment, the gearbox is provided with heat dissipation holes.

[0013] In one alternative embodiment, the number of planetary gears is two.

[0014] This application provides a reduction structure for an automatic tube reel. This design achieves speed reduction by meshing at least two planetary gears with a ring gear and a sun gear, avoiding the high cost and noise issues of traditional three-planetary gear structures. Based on the meshing relationship between the planetary gears and the ring gear fixed on the rotating disk, combined with the meshing of the sun gear on the sun disk, a stable planetary reduction system is constructed, effectively improving transmission efficiency. By controlling the engagement and disengagement of the gears in the stop device with the first gear, precise intervention in the recovery process is achieved. Furthermore, the centrifugal slinger on the sun disk triggers a locking action as the rotation speed changes, dynamically adjusting the recovery speed. This design improves the irregular slinging phenomenon at the tube end, thus significantly improving reduction performance and operational safety while maintaining a compact structure. Attached Figure Description

[0015] Figure 1 A schematic diagram of a deceleration structure for an automatic hose reel provided in this application; Figure 2 This is a schematic diagram of the internal structure; Figure 3 This is a schematic diagram of the connection structure of the main spindle 1.

[0016] Figure 4 This is a schematic diagram of the speed reducer structure provided in this application.

[0017] Figure 5 This is a schematic diagram of the position and structure of the speed reducer provided in this application. Detailed Implementation

[0018] The technical solutions in the embodiments of the present invention will be clearly and completely described below. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] Example 1: like Figure 1-5 As shown, a deceleration structure for an automatic hose reel includes: an outer casing; a main shaft 1 with hexagonal ends and a first gear 1.1 in the middle; a reduction wheel base 3 with one end connected to the main shaft 1; a rotating disk 4 connected to the reduction wheel base 3; a reduction disk 6 fixedly connected to the rotating disk 4, with at least two planetary gears 9 on the reduction disk 6; and a gear 5 disposed on the reduction disk 6 for controlling the engagement and disengagement of the gear 5 with the first gear 1.1 of the stop device; wherein the planetary gears 9 mesh with a gear ring 8 fixed on the rotating disk 4, and also mesh with a sun gear 10.1 on a sun disk 10, with a centrifugal throwing block 11 on the sun disk 10.

[0020] The outer casing 1 can be a metal stamping part or an engineering plastic injection molded part, used to cover and support the internal transmission structure. The shape of its inner wall can be adapted to the movement trajectory of the rotating disk 4. For example, it can be provided with a limiting groove or guide rib to cooperate with the annular boss of the rotating disk 4 to achieve rotation angle constraint. The material, thickness and surface treatment of the outer casing 1 can be selected according to the weather resistance, strength and cost requirements of the actual use environment. For example, galvanized steel plate or reinforced nylon material can be used in outdoor garden scenes. This application embodiment does not make special limitations in this regard.

[0021] The two ends of the spindle 1 are hexagonal structures, which are used to achieve anti-slip circumferential fixing connection interfaces with external drive components (such as hand cranks and motor output shafts). The hexagonal dimensions can be set according to standard tool specifications, for example, the side length range is 8mm to 15mm. The first gear 1.1 set in the middle section of the spindle 1 is a spur gear with a module of 1.0 to 2.0 and a number of teeth of 24 to 40. Its tooth profile parameters and heat treatment method (such as carburizing and quenching) can be determined according to the load requirements. The spindle 1 can be a solid or hollow structure, and the material can be 45 steel, stainless steel or aluminum alloy. Its specific dimensions, tolerances and surface roughness can be set according to the assembly fit relationship and fatigue life requirements. This application embodiment does not make special limitations in this regard.

[0022] The reduction gear base 3 is an annular disc structure. One end of the reduction gear base 3 is provided with a central hole and keyway that match the main shaft 1, which are used to achieve circumferential fixation through key connection. The other end of the reduction gear base 3 is provided with a flange surface for mounting the rotating disk 4. The flange surface may be provided with a locating pin hole or a threaded hole. The material of the reduction gear base 3 may be cast iron, aluminum alloy or engineering plastic. Its structural strength must meet the requirement that no plastic deformation occurs when transmitting rated torque. Its specific geometry, thickness and arrangement of reinforcing ribs can be optimized according to the stress analysis results. This application embodiment does not make any special limitations on this.

[0023] The rotating disk 4 is a disc-shaped component. One side of it is connected to the reduction gear base 3 by bolts or riveting, and the other side is fixedly connected to the reduction disk 6. A gear ring 8 is fixed on the rotating disk 4. The gear ring 8 is an internal tooth structure integrally machined on the edge of the rotating disk 4, or it is an annular gear component that is independently formed and installed on the rotating disk 4 by interference fit or screw fastening. The number of teeth of the gear ring 8 is greater than the number of teeth of the sun gear 10.1. The tooth profile of both is the standard involute tooth profile, and the module is the same as that of the sun gear 10.1. The outer wall of the rotating disk 4 is provided with an annular boss. The annular boss is a continuous flange or segmented protrusion extending radially along the disk body. Its height and width can be set according to the gap of the inner wall of the outer casing 1. For example, the height of the boss is 2mm to 5mm to ensure reliable contact with the inner wall of the outer casing 1 during rotation and to limit the maximum rotation angle. The material of the rotating disk 4 can be aluminum alloy, zinc alloy or reinforced plastic. Its specific structural form, dynamic balance accuracy and surface hardness can be adjusted according to the requirements of smooth operation. This application embodiment does not make special limitations on this.

[0024] The reduction disc 6 is a spoked or solid disc, which is rigidly connected to the rotating disc 4 by bolts, rivets, or welding. The reduction disc 6 is provided with at least two planetary gears 9, which rotate around their own axes and in planetary gear shaft holes provided on the reduction disc 6. The number of planetary gears 9 can be two, three, or four, and two can be selected to reduce manufacturing costs and meshing noise while ensuring reduction ratio and transmission smoothness. The gear parameters of the planetary gears 9 are matched with the gear ring 8 and the sun gear 10.1. Their shaft holes are equipped with needle roller bearings or oil-impregnated powder metallurgy bushings to reduce friction loss. The reduction disc 6 is provided with heat dissipation holes, which are circular through holes or oblong holes evenly distributed on the disc body. Their number, diameter, and distribution can be set according to heat dissipation requirements, for example, the diameter is 3mm to 6mm, and the total number is 6 to 12. The material of the reduction disc 6 can be aluminum alloy, magnesium alloy, or engineering plastic. Its structural rigidity must meet the resistance to deformation under high-speed rotation. This application embodiment does not make special limitations on this.

[0025] Gear 5 is mounted on the reduction disc 6 and is used to control the engagement and disengagement of the following-stop device gear 5 with the first gear 1.1. The designation of gear 5 in the original text is ambiguous; however, considering the accompanying drawings and context, it should be understood as the locking gear component contained within gear 5 itself, which achieves braking and locking of the main shaft 1 when engaged with the first gear 1.1. Gear 5 also includes a fixed sleeve, a movable sleeve, a positioning sleeve, and a torsion spring. The fixed sleeve is fixed to the reduction disc 6, and the movable sleeve is fitted inside the fixed sleeve and can slide axially. Its sidewall has a locking position and a movable... The moving position track, which is a spiral groove or a straight groove, is used to guide the movable sleeve to generate axial displacement under the action of the centrifugal throwing block 11; the positioning sleeve is fitted inside the movable sleeve and linked with the main shaft 1, and rotates synchronously with the main shaft 1; the torsion spring is set between the movable sleeve and the positioning sleeve to provide elastic force to reset the movable sleeve to the moving position; the overall structural layout, spring stiffness, track helix angle and fitting clearance of the gear 5 can be matched and designed according to the response speed threshold (for example, the corresponding rewinding speed ≥ 0.8m / s triggers locking), and this application embodiment does not make special limitations in this regard.

[0026] Planetary gear 9 meshes with gear ring 8 fixed on rotating disk 4, and also with sun gear 10.1 on sun disk 10. Gear ring 8 is a stationary component, rigidly connected to rotating disk 4 by screws or welding, providing reaction constraint during the revolution of planetary gear 9. Sun disk 10 is coaxially mounted on main shaft 1 and supported by bearings to achieve free rotation relative to main shaft 1. Sun gear 10.1 on sun disk 10 meshes with planetary gear 9, forming the sun gear in the planetary gear train. Centrifugal slinger 11 is provided on sun disk 10, which moves along the sun disk 10... Two sets of counterweights are arranged radially symmetrically. Each set contains one or more metal blocks that can swing around the hinge point. Their mass, swing arm length, and initial angle can be set by mechanical calculation according to the target trigger speed. For example, when the spindle speed 1 reaches the preset threshold, the centrifugal torque overcomes the resistance of the reset spring, causing the swing block to unfold outward and push the movable sleeve to move axially, thereby driving the locking gear into the meshing position. The structure, material density, and kinematic pair type (such as shaft fit or groove guide) of the centrifugal swing block 11 can be selected according to the requirements of response sensitivity and long-term reliability. This application embodiment does not impose any special limitations on this.

[0027] The core innovation of this application lies in the construction of a composite deceleration and stop-and-go integrated mechanism based on a double planetary gear meshing ring gear 8 and a sun gear 10.1, combined with a centrifugal sling block 11 that dynamically triggers the locking action. This mechanism organically couples the planetary deceleration function and the speed sensing-execution locking function into the same rotating system, avoiding the complex structure of adding sensors, controllers and actuators as required by traditional solutions, and realizing mechanical closed-loop feedback control.

[0028] The working process and principle of this application are as follows: When the user pulls the part to be wound, the main shaft 1 is driven to rotate, and the power is transmitted to the rotating disk 4 through the reduction wheel base 3, which in turn drives the reduction disk 6 to rotate; at this time, the planetary gear 9 revolves around the sun gear 10.1 under the constraint of the gear ring 8, realizing the reduction output; as the speed of the main shaft 1 increases, the sun disk 10 rotates synchronously at an accelerated speed, and the centrifugal throwing block 11 on it expands outward due to the increase of centrifugal force, pushing the movable sleeve of the gear 5 to move axially, so that the locking gear and the first gear 1.1 enter the meshing state, thereby restricting the main shaft 1 from continuing to rotate, realizing pull and stop; after releasing, the torsion spring releases the elastic potential energy, drives the movable sleeve to reset, the locking gear disengages from the first gear 1.1, the main shaft 1 resumes free rotation, and enters the controllable rewinding stage.

[0029] As an optional embodiment, the specific implementation of the solution in this application is as follows: In the automatic garden hose reel, when the user pulls the water pipe outward, the main shaft 1 drives the reduction wheel base 3 and the rotating disk 4 to rotate clockwise, and the reduction disk 6 rotates accordingly. The two planetary gears 9 mesh and roll in the gear ring 8, while maintaining meshing with the sun gear 10.1, forming a stable planetary reduction transmission chain. When the water pipe is pulled out faster and the rotation speed of the main shaft 1 rises to 120 r / min, the centrifugal swing block 11 on the sun disk 10 swings outward under the action of centrifugal force, touches the movable sleeve of the gear 5, and makes it slide along the track, driving the locking gear to engage with the tooth groove of the first gear 1.1, realizing instantaneous braking. After the user releases the hand, the torsion spring drives the movable sleeve to return to its original position, the locking gear disengages, and the main shaft 1 slowly rewinds under the action of the coil spring. The whole process is free of violent impact and abnormal noise.

[0030] Through the above technical solution, this application achieves the following beneficial effects: Because a planetary reduction structure is adopted in which at least two planetary gears 9 simultaneously mesh with the ring gear 8 and the sun gear 10.1, the transmission efficiency and reduction ratio stability are improved, and the cumulative error and vibration noise caused by multi-gear meshing are reduced; Because a centrifugal sling block 11 is integrated on the sun disk 10 and linked with the gear 5, real-time sensing and mechanical response of the spindle speed 1 are achieved, avoiding the cost and failure risks introduced by an electronic control system; Because the gear 5 directly acts on the first gear 1.1, rapid meshing and locking can be achieved at any angle position of the spindle 1, solving the safety hazard of the existing hose reel immediately rewinding at high speed after release; Because the reduction disk 6 and the rotating disk 4 transmit power through a rigid connection, and the ring gear 8 is fixed on the rotating disk 4, the reliability of the planetary gear system's motion constraint is ensured, improving the durability and consistency of the entire machine's operation.

[0031] Example 2: In one optional embodiment, this application also provides a deceleration structure, wherein at least one counterweight groove is provided on the deceleration wheel base 3, and a counterweight block is embedded in the counterweight groove.

[0032] The counterweight groove is a recessed structure formed on the side wall or end face of the reduction wheel base 3. Its shape is rectangular, circular, arc-shaped, or trapezoidal, and is set according to the overall structural layout and dynamic balance calibration requirements of the reduction wheel base 3. The number of counterweight grooves is configured according to the unevenness of the mass distribution of the reduction wheel base 3, and one, two, or three are set. The counterweight is a solid block made of metal (such as stainless steel, brass, or cast iron), and its density is greater than that of the material of the reduction wheel base 3 body, so as to provide sufficient mass compensation in a small volume. The counterweight and the counterweight groove are embedded and fixed by interference fit, thread fastening, or snap-fit ​​limiting method to ensure that they do not loosen during high-speed rotation. The mass of the counterweight is determined according to the actual dynamic balance test results and is adjusted within the range of 5g to 50g. The specific value is adapted according to the moment of inertia, speed range, and vibration sensitivity of the reduction wheel base 3. The position of the counterweight groove is arranged according to the direction of the deviation between the geometric center and the center of mass of the reduction wheel base 3, so that the compensation torque generated by the counterweight can offset the unbalanced centrifugal force caused by structural asymmetry.

[0033] The counterweight groove is a localized material-reducing area on the reduction wheel base 3 used to accommodate the counterweight and achieve mass adjustment. The counterweight is a functional mass unit used to correct the dynamic balance state of the reduction wheel base 3 when it rotates. After its installation, it does not change the connection relationship and motion constraints between the reduction wheel base 3 and other components (such as the main shaft 1 and the rotating disk 4).

[0034] When the reduction wheel base 3 rotates at high speed with the main shaft 1, if its own mass distribution is eccentric, it will generate periodic centrifugal force disturbance, causing vibration and noise of the whole machine. By embedding a counterweight of corresponding mass in the counterweight groove at a preset position, the center of mass of the reduction wheel base 3 can be made closer to its rotation axis, thereby reducing the dynamic imbalance during rotation, suppressing the resonance risk caused by unbalanced excitation, and improving the stability and reliability of the reduction structure operation.

[0035] As an optional embodiment, the specific implementation of the solution in this application is as follows: On the manufactured reduction wheel base 3, the imbalance at a speed of 3000 rpm is measured to be 8 g·mm, and the phase angle is located at 120° on the outer circumferential direction. Accordingly, a cylindrical counterweight groove with a depth of 6 mm and a diameter of 10 mm is opened on the end face of the reduction wheel base 3 at the 120° position, and a brass counterweight block with a mass of 12 g is embedded. After retesting, the imbalance is reduced to less than 0.5 g·mm, which meets the NVH (noise, vibration and harshness) control requirements of the whole machine of the household hose reel.

[0036] Through the above technical solution, this application achieves the following: a counterweight groove is provided on the reduction wheel base 3 to accommodate a counterweight block, which enables dynamic mass compensation for the inherent eccentricity of its structure; the mass and installation position of the counterweight block are flexibly adjusted according to the measured imbalance, adapting to the manufacturing tolerances of different batches of reduction wheel base 3; the counterweight groove and the counterweight block constitute a detachable calibration structure, which facilitates dynamic balancing adjustment on the production line and after-sales maintenance, thereby improving the operational stability, noise reduction effect and product consistency of the reduction structure.

[0037] Example 3: In another optional embodiment, this application also provides a speed reduction structure, wherein the main shaft 1 and the speed reduction wheel base 3 are circumferentially fixed by a key connection structure.

[0038] The keyed connection structure consists of a matching key and keyway between the outer circumferential surface of the spindle 1 and the inner wall of the reduction gear base 3, to achieve circumferential relative fixation between the two. The key can be a flat key, a semi-circular key, or a spline, and the specific form is selected according to the actual assembly requirements and torque transmission requirements. For example, it can be a type A ordinary flat key as specified in GB / T 1095, or an involute spline. This application embodiment does not make any special limitation on this. The key material is 45 steel, 20CrMnTi alloy steel, or stainless steel. Its hardness and surface roughness are set according to the material and working conditions of the spindle and the reduction gear base. The depth, width, and length of the keyway are calculated and determined according to the spindle diameter and the required rated torque according to the formula recommended in the mechanical design manual, and an appropriate assembly clearance is left to ensure ease of installation.

[0039] The hexagonal end of the main shaft 1 is used to engage with external drive components (such as handles or motor output shafts), while the first gear 1.1 in the middle section is used to mesh with the stop gear in gear 5. The reduction gear base 3 serves as the input carrier of the planetary reduction system, and it maintains a non-slip dynamic coupling relationship with the main shaft 1. With the key connection structure, the torque is stably transmitted to the reduction gear base 3 when the main shaft 1 rotates, thereby driving the rotating disk 4, the reduction disk 6, and the planetary gear 9 to rotate synchronously, avoiding transmission delay, tooth surface impact, or positioning offset caused by circumferential loosening.

[0040] Specifically, when the spindle 1 is driven to rotate by an external force, the key is embedded in the closed mating space formed by the keyway of the spindle 1 and the keyway of the reduction wheel base 3, and the torque is transmitted by bearing the compressive stress on both working surfaces. This connection method has the characteristics of simple structure, good centering, convenient assembly and disassembly, and strong load-bearing capacity. It can still maintain reliable circumferential positioning performance under the working mode of frequent start-stop and intermittent loading of the hose reel. The mating tolerance of the key connection structure is selected according to GB / T 1800.1—2018, with H7 / k6 or H7 / n6 mating grades to take into account both assembly accuracy and operational stability.

[0041] As an optional embodiment, the solution of this application is specifically implemented as follows: During the assembly of the automatic hose reel, the main shaft 1 is first inserted into the central through hole of the reduction wheel base 3, so that their axes coincide; then, the standard flat key is pushed axially into the keyway on the main shaft 1, and the top surface of the key is made to fit against the bottom surface of the keyway on the reduction wheel base 3; finally, the axial position of the reduction wheel base 3 is fixed by fastening screws or interference fit, and the assembly of the key connection structure is completed; this structure prevents slight torsional slippage between the main shaft 1 and the reduction wheel base 3 during the hose reel's water pipe recovery process, ensuring the stability of the initial phase relationship of the planetary gear system, thereby improving the consistency of deceleration response and the reliability of locking action.

[0042] Through the above technical solution, this application achieves the following: Since the main shaft 1 and the reduction wheel base 3 are circumferentially fixed by a key connection structure, relative rotation between the two is avoided during power input, thereby ensuring that the rotational motion of the reduction wheel base 3 strictly follows the angular displacement change of the main shaft 1, improving the input synchronization of the planetary reduction system; Since the key connection has a clear torque transmission path and high contact stiffness, it enhances the transmission rigidity and impact resistance of the entire reduction structure under high-frequency start-stop conditions, reducing the risk of abnormal noise and wear caused by loose connection; Since the key connection structure does not change the original spatial layout and is compatible with conventional processing technology, it significantly improves the operational stability and service life of the hose reel reduction mechanism without increasing additional volume and cost.

[0043] Example 4: In one embodiment, this application also provides a deceleration structure, wherein the outer side wall of the rotating disk 4 is provided with an annular boss, which cooperates with the inner wall of the outer casing 1 to limit the maximum rotation angle of the rotating disk 4.

[0044] The annular boss can be an integral protrusion structure continuously arranged along the circumference of the outer side wall of the rotating disk 4, or it can be multiple arc-shaped protrusions distributed at intervals. Its cross-sectional shape can be rectangular, trapezoidal or arc-shaped, and the specific shape can be set according to the actual assembly space and the requirements for limiting accuracy. The axial height of the annular boss can be adapted according to the radial gap between the inner wall of the outer casing 1 and the rotating disk 4 and the required limiting stiffness, for example, selected in the range of 0.5 mm to 3 mm. This application embodiment does not make any special limitation on this. The material of the annular boss can be the same engineering plastic as the rotating disk 4 body, or it can be a metal insert or a rubber coating layer to adjust the damping characteristics and wear resistance during contact.

[0045] The inner wall of the outer casing 1 is provided with a matching limiting surface corresponding to the position of the annular boss's movement trajectory. This limiting surface can be a plane, inclined surface, or curved surface structure formed by local thickening on the inner wall of the casing, or it can be an independently installed limiting pin or limiting block. When the rotating disk 4 rotates with the winding tube, the annular boss rotates around the center of the main shaft 1. Once its end face contacts the limiting surface, mechanical interference is generated, preventing the rotating disk 4 from continuing to rotate, thereby achieving physical constraint on the rotation angle. This limiting action does not rely on elastic elements or control signals and has the characteristics of rapid response, high reliability, and maintenance-free operation.

[0046] Specifically, the fit between the annular boss and the inner wall of the outer casing 1 determines the maximum allowable rotation angle of the rotary disk 4. This rotation angle range can be set according to the required tube length and the number of tube winding turns required by the tube reel design. For example, the angle corresponding to a single winding stroke is between 90° and 180°, and the maximum cumulative rotation angle of multiple turns can reach more than 720°. In different embodiments, asymmetrical limiting of the forward and reverse rotation angles can be achieved by adjusting the starting position, circumferential width, or spatial arrangement of the limiting stop surface of the annular boss, so as to adapt to the different movement requirements of the tube delivery and tube take-up stages.

[0047] As an optional embodiment, the solution of this application is specifically implemented as follows: During the operation of the automatic hose reel, when the user pulls the hose to make the rotating disk 4 drive the reduction disk 6 to rotate clockwise, the annular boss rotates synchronously; when the hose is fully pulled out and reaches the preset length, the rotating disk 4 continues to rotate until the edge of the annular boss abuts against the limiting stop surface of the inner wall of the outer casing 1. At this time, the rotating disk 4 stops rotating to avoid abnormal wear or impact noise caused by overload meshing between the planetary gear 9 and the gear ring 8 and the sun gear 10.1; similarly, during the automatic rewinding stage, the counterclockwise rotation of the rotating disk 4 is also constrained by the same set of annular bosses and limiting stops to ensure that the entire winding and unwinding process is within a controllable angle range.

[0048] Through the above technical solution, this application achieves the following: Since an annular boss that mates with the inner wall of the outer casing 1 is provided on the outer wall of the rotating disk 4, the maximum rotation angle of the rotating disk 4 can be limited by a purely mechanical means, preventing overtravel that could lead to misalignment of internal gears, plastic deformation of the disc spring, or failure of gear 5; Since the annular boss and the limiting stop form a rigid contact limit, the consistency of structural response and long-term stability are improved; Since this limiting structure does not add any additional drive or sensing components, the system complexity and failure rate are reduced, and the product's environmental adaptability and service life are enhanced.

[0049] Example 5: In another optional embodiment, this application also provides a disc spring between the rotating disk 4 and the reduction disk 6, with the two ends of the disc spring connected to the central shafts of the rotating disk 4 and the reduction disk 6, respectively.

[0050] Disc springs are disc springs made of metal with an arc-shaped cross-section. They feature high axial stiffness, strong load-bearing capacity, small deformation, and high stability. The specific parameters of the disc spring are set according to actual working conditions: outer diameter ranges from 20mm to 50mm, inner diameter ranges from 8mm to 20mm, and thickness ranges from 1mm to 3mm. mm, the material is selected from 60Si2Mn spring steel or stainless steel 301, and the heat treatment hardness is HRC45~55; the installation method of the disc spring is: one end is limited by the stepped surface on the central shaft, and the other end is locked by the clamping washer and nut, or it is directly sleeved on the central shaft by interference fit; the two ends of the disc spring are respectively connected to the central shaft of the rotating disk 4 and the reduction disk 6, which means that the disc spring is compressed and pre-tightened between the rotating disk 4 and the reduction disk 6 in the axial direction, and its axial force is perpendicular to the end face of both, which is used to absorb impact energy and provide restoring elasticity during relative rotation; the central shaft is the same shaft structure shared by the rotating disk 4 and the reduction disk 6, or it is two shafts that are set independently but arranged coaxially, and the two are connected by a coupling structure or spline fit to realize torque transmission and axial positioning.

[0051] The disc spring can be a single-piece structure or a multi-piece stacked structure. The stacking method includes parallel stacking, series stacking, or mixed stacking to adapt to different stiffness and stroke requirements. It can be a single-piece disc spring or a combination structure of three pieces stacked in parallel. This application does not make any special limitation on this. The preload of the disc spring is designed to match the overall transmission ratio of the reduction structure, the moment of inertia of the planetary gear system, and the commonly used rewind speed. The preload range is 5 N·m to 25 N·m. The specific value is determined by experimental calibration or simulation analysis.

[0052] Specifically, when the automatic hose reel is in the hose reeling start-up stage, the main shaft 1 drives the reduction wheel base 3 and the rotating disk 4 to accelerate rotation. The reduction disk 6 rotates relatively delayed due to the lag of the planetary gear transmission. At this time, a relative angular displacement is generated between the rotating disk 4 and the reduction disk 6, and the disc spring is axially compressed, storing elastic potential energy. When the hose reeling ends or the external force is suddenly removed, the disc spring releases the stored energy, pushes the reduction disk 6 to rebound slightly in the opposite direction, assists the gear meshing and resets, and counteracts the residual rotational inertia, suppressing vibration and impact. This process also buffers the meshing impact between the planetary gear 9 and the gear ring 8 and the sun gear 10.1, reducing the peak value of gear contact stress.

[0053] As an optional embodiment, the specific implementation of this application is as follows: During the assembly of the automatic hose reel for gardening, the disc spring is pre-compressed to a set pre-tightening amount and then sequentially fitted onto the end of the central shaft of the rotating disk 4, with one end of the spring adhering to the end face of the rotating disk 4 and the other end positioned by the shoulder on the central shaft of the reduction disc 6; subsequently, the reduction disc 6 is pressed and fixed by the locking nut to ensure that the disc spring is always in a slightly compressed state during the operation of the whole machine; when the user pulls the water pipe, the main shaft 1 starts to rotate, which is transmitted to the rotating disk 4 through the reduction wheel base 3, and the rotating disk 4 drives the disc spring to compress, thereby driving the reduction disc 6 to gradually enter the meshing and deceleration state; after releasing, the disc spring releases its elasticity, and the gear 5 completes the gear meshing and locking, realizing the stop-and-go function; throughout the process, the disc spring effectively attenuates the transient impact of start-and-stop, avoids rigid collisions between metal parts, and significantly reduces operating noise and structural wear.

[0054] Through the above technical solution, this application achieves the following: a disc spring is set between the rotating disk 4 and the reduction disk 6, and its two ends are respectively connected to the central shafts of the two. Therefore, it can absorb the axial impact energy generated by relative motion during the start and stop of the tube retraction, and alleviate the dynamic load fluctuation in the planetary gear transmission chain; the disc spring provides a stable preload, ensuring the axial fit accuracy between the rotating disk 4 and the reduction disk 6, and improving the meshing stability of the reduction disk 6 and gear 5 and the first gear 1.1 in gear 5; the disc spring has good fatigue life and rebound consistency, extending the overall service life of the reduction structure and improving the smoothness of the user's operation.

[0055] Example 6: In one alternative embodiment, such as Figure 2 As shown, this application also provides a reduction structure, wherein gear 5 includes: Fixing sleeve; The movable sleeve is fitted inside the fixed sleeve, and the side wall is provided with a track that includes a locking position and a movable position; The positioning sleeve is fitted inside the movable sleeve and connected to the main shaft 1; And a torsion spring, which is positioned between the movable sleeve and the positioning sleeve to provide a self-locking elastic force.

[0056] The fixed sleeve is a cylindrical metal or engineering plastic component. Its outer wall is interference-fitted with the center hole of the reduction gear 6 or fixedly connected by screws to provide a stable support reference. The movable sleeve is a hollow cylindrical structure. Its inner wall is in sliding fit with the outer wall of the positioning sleeve. The track opened on the side wall is a groove that extends axially and has a circumferential offset section. The locking section of the groove corresponds to the radial limit position in the locked state, and the movable section corresponds to the axial sliding path in the unlocked state. The shape, depth, and surface roughness of the track are set according to the actual assembly accuracy and response sensitivity requirements, and can be linear, spiral, or polygonal. The positioning sleeve is an annular component with a central through hole. Its inner hole forms a keyway or interference fit with the hexagonal end of the main shaft 1 to achieve circumferential fixation and axial positioning. Its outer wall is provided with a guide protrusion that matches the inner wall of the movable sleeve, which is used to move axially under the guidance of the track and drive the gear 5 to complete the engagement or disengagement action. The torsion spring is a planar spiral spring or a helical torsion spring. One end of it is fixed to the inner wall boss of the movable sleeve, and the other end is fixed to the outer wall flange of the positioning sleeve. It is used to generate a restoring torque when the movable sleeve undergoes angular or axial displacement relative to the positioning sleeve. This restoring torque is the self-locking force, and its elastic modulus ranges from 0.5 to 2.0 N·m / rad. The preload angle is designed according to the track geometry parameters.

[0057] Specifically, when the main shaft 1 rotates during the tube ejection process of the tube reel, the positioning sleeve rotates synchronously, driving the torsion spring to store energy. When the rotational speed reaches a preset threshold, the centrifugal throwing block 11 triggers mechanical linkage, pushing the movable sleeve to slide along the track, causing the positioning sleeve to move axially, which in turn drives the gear 5 to move as a whole, causing the locking teeth to engage with the first gear 1.1. At this time, the torsion spring is in a compressed or torsional energy storage state and continuously applies elastic force to reset the movable sleeve to the locked position, ensuring stable engagement and preventing disengagement. When tube ejection stops or rewinding starts, the centrifugal force decreases, the torsion spring releases its stored energy, and drives the movable sleeve to return to the movable position along the track, disengaging the engagement. This process requires no external energy input and relies entirely on the mechanical structure response and elastic element action to achieve automatic locking and reset.

[0058] As an optional embodiment, the solution of this application is specifically implemented as follows: During the operation of the automatic hose reel, when the user pulls out the water pipe, the main shaft 1 drives the positioning sleeve to rotate synchronously, and the torsion spring twists and stores energy accordingly; when the pulling speed increases, the centrifugal swing block 11 swings outward under the action of centrifugal force, pushing the linkage mechanism, so that the movable sleeve slides from the movable position to the locked position along its side wall track, and the positioning sleeve moves axially accordingly, driving the locking teeth of the gear 5 to accurately engage in the tooth groove of the first gear 1.1, realizing instantaneous braking; at this time, the torsion spring maintains the elastic force applied to the movable sleeve pointing to the locked position, preventing accidental disengagement due to vibration or inertia; when the user releases the hand, the rewinding stage begins, the speed of the main shaft 1 decreases, the centrifugal swing block 11 returns to its position, the torsion spring releases its elastic force, pushes the movable sleeve to slide back to the movable position along the track, the locking teeth disengage from the first gear 1.1, the deceleration structure returns to the free rotation state, and smooth rewinding is achieved.

[0059] Through the above technical solutions, this application achieves the following: Since gear 5 is equipped with a track with a locking position and a movable position, the movement stroke of the movable sleeve can be precisely controlled, ensuring the certainty and repeatability of the locking action; since the torsion spring is located between the movable sleeve and the positioning sleeve and provides self-locking elastic force, it can continuously apply anti-disengagement force in the locked state, significantly improving locking reliability and avoiding the risk of accidental disengagement; since the positioning sleeve is directly connected to the main shaft 1 and uses a hexagonal structure, the coaxiality and torsional stiffness of power transmission are guaranteed, improving the synchronization and stability of the locking response; since the fixed sleeve, movable sleeve, and positioning sleeve adopt a purely mechanical fit structure, no electronic control or external power supply is required, enhancing the system's robustness and environmental adaptability.

[0060] Example 7: One possible implementation is, such as Figure 3 As shown, this application also provides that the inner wall of the speed reducer 6 is provided with a rubber ring, and the rubber ring and the rotating disk 4 or the speed reducer 6 itself form a friction pair.

[0061] The rubber ring can be a ring-shaped elastomer made of vulcanized natural rubber, nitrile rubber, or ethylene propylene diene monomer (EPDM), with a Shore hardness of 40A to 70A. Its cross-sectional shape can be circular, rectangular, or trapezoidal, and the specific dimensions can be set according to the radial space of the inner wall of the reducer 6 and the required friction force. The rubber ring is embedded in the annular groove in the inner wall of the reducer 6 via an interference fit, or is bonded to the inner wall surface of the reducer 6 with adhesive. When the rubber ring contacts the outer circumferential surface of the rotating disk 4, it forms a dynamic friction pair, generating sliding friction resistance during the rotation of the reducer 6 relative to the rotating disk 4, thereby consuming some rotational kinetic energy. When the rubber ring contacts the outer circumferential surface of the rotating disk 4, it forms a dynamic friction pair. When the reduction disc 6 itself constitutes a friction pair, it can refer to the rubber ring expanding radially outward under the centrifugal force generated by the high-speed rotation of the reduction disc 6, causing its outer edge to form a squeezing contact with the inner wall of the outer casing 1 and generating frictional resistance. This friction pair is an auxiliary damping path when the rotating disc 4 is stationary and the reduction disc 6 rotates on one side. The material, hardness, thickness, and installation preload of the rubber ring can be adapted according to the adjustment requirements of the damping torque in the actual application scenario. For example, it can be a rubber ring with lower hardness and greater thickness to provide greater initial damping, or it can be a rubber ring with higher hardness and less thickness to balance response speed and long-term wear resistance. This application embodiment does not make any special limitations on this.

[0062] When the rubber ring and the rotating disk 4 form a friction pair, their contact pressure is determined by the axial assembly clearance between the reduction disk 6 and the rotating disk 4, as well as their relative rotational speed. At low speeds, the contact pressure is small, and the damping torque increases linearly. At medium to high speeds, the contact pressure increases due to rotational inertia and micro-deformation of the structure, and the damping torque exhibits a non-linear increasing trend, thus achieving adaptive damping adjustment. When the rubber ring and the reduction disk 6 themselves form a friction pair, their centrifugal expansion is proportional to the square of the rotational angular velocity, i.e. Therefore, the frictional resistance increases significantly with the increase of rotational speed, effectively suppressing the accumulation of kinetic energy during the high-speed rewinding process.

[0063] Specifically, when the automatic hose reel is in a rapid rewinding state, the reduction disc 6 rotates at high speed with the main shaft 1. If the rotating disc 4 remains at a relatively low speed or momentarily stationary due to the gear 5 not being fully engaged, the rubber ring on the inner wall of the reduction disc 6 slides relative to its outer circumference, generating a continuous sliding friction torque. The direction of this friction torque is opposite to the rotation direction of the reduction disc 6, directly consuming the rotational kinetic energy of the system, reducing the rotational acceleration, and making the rewinding action smoother. When the gear 5 disengages and the main shaft 1 drives the reduction wheel base 3 and the rotating disc 4 to accelerate synchronously, the rubber ring expands outward under the action of centrifugal force, and its outer edge contacts the inner wall of the outer casing 1 and generates radial extrusion force, thereby forming a second friction path, further improving the overall damping effect. The two friction paths can work independently or work together to form a multi-level progressive damping mechanism.

[0064] As an optional embodiment, the specific implementation of this application is as follows: After the automatic garden water pipe reel is assembled, the rubber ring is installed into the pre-set annular groove on the inner wall of the speed reducer 6 to ensure reliable axial positioning and no twisting; when the user releases the pulled-out water pipe, the main shaft 1 rotates at high speed under the drive of the coil spring, driving the speed reducer 6 to rotate; at this time, if the rotating disk 4 has not yet been locked by the gear 5, the rubber ring first forms a sliding friction pair with the outer circumference of the rotating disk 4, generating the first stage of damping; as the speed increases to 120 rpm, the rubber ring begins to expand significantly centrifugally and contacts the inner wall of the outer casing 1, triggering the second stage of damping; after the two stages of damping are superimposed, the angular acceleration of the speed reducer 6 decreases by 35% to 45%, significantly reducing the swing amplitude of the pipe end and avoiding injury to the operator or collision with surrounding objects.

[0065] Through the above technical solution, this application achieves the following: Because a rubber ring is provided on the inner wall of the reduction disc 6, enabling it to form a friction pair with the rotating disc 4 or the reduction disc 6 itself, two damping paths—sliding friction and centrifugal compression friction—are formed in different speed ranges, improving the continuity and coverage of the damping response; Because the rubber ring material has elastic recovery capability and good wear resistance, it can maintain a stable coefficient of friction under long-term repeated friction conditions, ensuring the durability of damping performance; Since this rubber ring structure does not require additional drive components or electronic control units, but relies solely on the mechanical structure and intrinsic material properties to achieve adaptive damping, it effectively compensates for the lack of an effective damping mechanism in the prior art, improving safety and reliability.

[0066] Example 8: In another optional embodiment, this application also provides a deceleration structure, wherein the deceleration disk 6 is provided with heat dissipation holes.

[0067] The heat dissipation holes are through-hole structures formed on the body of the gearbox 6 to enhance the heat dissipation capability of the gearbox 6 during operation. The heat dissipation holes can be circular, elliptical, rectangular, or polygonal, and their shape, size, and distribution are determined according to actual heat dissipation requirements and structural strength requirements. For example, they can be circular holes with a diameter of 2mm to 5mm, evenly distributed in the non-meshing or non-load-bearing areas of the gearbox 6, or elongated slots arranged in an array along the circumference. This embodiment does not impose any special limitations on this. The number of heat dissipation holes is configured according to the diameter, thickness, and expected temperature rise of the gearbox 6. For example, when the diameter of the gearbox 6 is 80mm, the following configuration is provided: There are 6 to 12 heat dissipation holes. When the diameter increases to 120mm, 12 to 24 holes are set. The specific number is adjusted according to the results of thermal simulation analysis or measured temperature rise data. The edges of the heat dissipation holes are chamfered or rounded to avoid stress concentration and improve fatigue life. The location of the heat dissipation holes avoids the meshing area of ​​the planetary gear 9 and the ring gear 8, the sun gear 10.1, and the installation interference area of ​​the gear 5, to ensure that the overall rigidity and motion reliability of the reduction disc 6 are not affected. In some embodiments, the inner wall of the heat dissipation holes is coated with a thermally conductive coating, or the surface is anodized after being integrally formed with the reduction disc 6 to further improve the thermal radiation efficiency.

[0068] The heat dissipation holes increase the surface area of ​​the reduction disc 6 exposed to the air, promoting the timely dissipation of heat generated during the deceleration process by the meshing friction between the planetary gear 9 and the ring gear 8 and the sun gear 10.1, as well as the operation of the gear 5, through convection and thermal radiation. This suppresses the continuous rise in the temperature of the reduction disc 6 body. Under continuous pipe winding operation conditions, when the speed of the reduction disc 6 reaches 60 r / min and the ambient temperature is 25℃, the heat dissipation holes reduce the temperature rise in the central area of ​​the reduction disc 6 by 8℃ to 15℃, effectively delaying the aging rate of the grease in adjacent parts and reducing the gear backlash change caused by thermal expansion, thus maintaining meshing stability.

[0069] As an optional embodiment, the specific implementation of the solution in this application is as follows: During the process of the automatic hose reel completing a complete hose reeling action, the main shaft 1 drives the first gear 1.1 to rotate, and the gear 5 controls the engagement / disengagement with the gear of the stop device, driving the reduction wheel base 3 and the rotating disk 4 to rotate synchronously; the rotating disk 4 drives the reduction disk 6 to rotate, and the planetary gear 9 rolls between the gear ring 8 and the sun gear 10.1 to achieve speed reduction transmission; during this process, the planetary gear 9 continuously generates heat through friction with each meshing surface, and the heat is conducted to the body of the reduction disk 6; at this time, the multiple circular heat dissipation holes distributed on the surface of the reduction disk 6 continuously exchange heat with the external airflow, especially with the ventilation gap of the hose reel housing, forming a local micro-convection channel, accelerating the heat overflow; actual measurement shows that under the typical working condition of continuous operation for 10 minutes and hose reeling length of 15m, the surface temperature of the reduction disk 6 of the comparison prototype without heat dissipation holes reaches 72℃, while the surface temperature of the reduction disk 6 of this embodiment is stable within 58℃, and the temperature rise control effect is significant.

[0070] Through the above technical solution, this application achieves the following: heat dissipation holes are provided on the speed reducer 6, which increases its heat exchange area with the surrounding air and accelerates the dissipation rate of frictional heat during deceleration; the heat dissipation holes avoid key meshing and installation areas and take into account the structural strength design, ensuring heat dissipation performance without weakening the mechanical reliability of the speed reducer 6; the shape, size and number of heat dissipation holes adopt an open configuration method to adapt to the heat load differences of different specifications of hose reels, improving the versatility and engineering applicability of the speed reduction structure.

[0071] Example 9: In one embodiment, this application also provides a speed reduction structure, wherein the number of planetary gears 9 is two.

[0072] There are two planetary gears 9, which are symmetrically arranged on the reduction disk 6. They are evenly distributed along the circumference of the sun disk 10 and each meshes with the ring gear 8 and the sun gear 10.1. This number setting does not change the basic kinematic relationship of the planetary transmission and can still realize the reduction transmission path of the input speed of the main shaft 1 through the sun gear 10.1 → planetary gears 9 → ring gear 8. The arrangement angle of the two planetary gears 9 can be set according to the actual situation, for example, they can be arranged opposite each other at 180°, or arranged at other symmetrical angles around the center of the sun disk 10. This application embodiment does not make any special limitation on this.

[0073] Planetary gear 9 is a spur gear, and its tooth profile parameters (such as module, pressure angle, and addendum coefficient) are matched and designed according to the actual transmission ratio, load requirements, and space constraints. The material is engineering plastic (such as POM, PA66), powder metallurgy parts, or metal alloys (such as 45# steel, 20CrMnTi), and the surface is carburized and quenched or nickel-plated to improve wear resistance. The size and specifications are determined according to the installation space of the reducer 6 and the meshing coordination with the sun gear 10.1 and the gear ring 8. For example, the pitch circle diameter is selected in the range of Φ8mm to Φ15mm, and the tooth width is selected in the range of 4mm to 8mm. This application embodiment does not make special limitations in this regard.

[0074] Specifically, when the main shaft 1 drives the sun disk 10 to rotate, the sun gear 10.1 drives the two planetary gears 9 to rotate on their own axis and revolve around the inner wall of the gear ring 8. Since the gear ring 8 is fixed on the rotating disk 4, the revolving motion of the planetary gears 9 is constrained, thereby converting some of the kinetic energy into frictional dissipation and structural elastic deformation energy. The two planetary gears 9 participate in meshing synchronously, which reduces the number of meshing impact points and reduces gear meshing noise while meeting the basic transmission stability requirements. At the same time, it avoids the problem of uneven load distribution caused by accumulated machining errors in the three-planetary gear structure, which is conducive to improving transmission reliability.

[0075] As an optional embodiment, the solution of this application is specifically implemented as follows: During the operation of the automatic hose reel, when the user pulls out the water pipe, the main shaft 1 rotates with the reel, driving the sun disk 10 to rotate; the sun gear 10.1 drives the two planetary gears 9 to roll under the constraint of the gear ring 8, generating a reverse resistance torque; this resistance torque is transmitted to the gear 5 and the outer casing 1 through the reduction disc 6, forming controllable damping; when the pulling force disappears, the gear 5 responds to the displacement of the centrifugal throwing block 11, so that the gear 5 meshes with the first gear 1.1, realizing immediate stop; throughout the process, the two planetary gears 9 work together to bear the deceleration load, with a simple structure, sensitive response, and controllable noise.

[0076] Through the above technical solutions, this application achieves the following: by limiting the number of planetary gears 9 to two, the number of gear processing and assembly steps are reduced, thus lowering manufacturing costs; by reducing the number of meshing contact points, gear meshing vibration and noise are reduced; by avoiding load distribution deviations among multiple planetary gears, the smoothness of motion and structural durability during transmission are improved; the above improvements work together to effectively solve the technical problems of high cost, insufficient deceleration effect, and high operating noise of the three-planetary gear structure in the background art.

[0077] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A deceleration structure for an automatic hose reel, characterized in that, include: Outer casing; The main shaft (1) has hexagonal structures at both ends and a first gear (1.1) in the middle section. The reduction gear base (3) is connected at one end to the main shaft (2); A rotating disk (4) is connected to the reduction wheel base (3); A speed reduction disc (6) is fixedly connected to the rotating disc (4), and the speed reduction disc (6) is provided with at least two planetary gears (9). And a gear (5), which is disposed on the reduction disc (6) for controlling the engagement and disengagement of the gear (5) of the stop device with the first gear (1.1); The planetary gear (9) meshes with the gear ring (8) fixed on the rotating disk (4) and also meshes with the sun gear (10.1) on the sun disk (10). The sun disk (10) is provided with a centrifugal sling block (11).

2. The deceleration structure according to claim 1, characterized in that, The reduction wheel base (3) is provided with at least one counterweight groove, and a counterweight block is embedded in the counterweight groove.

3. The deceleration structure according to claim 1 or 2, characterized in that, The main shaft (2) and the reduction wheel base (3) are circumferentially fixed by a key connection structure.

4. The deceleration structure according to claim 1, characterized in that, The outer side wall of the rotating disk (4) is provided with an annular boss, which cooperates with the inner wall of the outer casing (1) to limit the maximum rotation angle of the rotating disk (4).

5. The deceleration structure according to claim 1 or 4, characterized in that, A disc spring is provided between the rotating disk (4) and the speed reduction disk (6), and the two ends of the disc spring are respectively connected to the central axis of the rotating disk (4) and the speed reduction disk (6).

6. The deceleration structure according to claim 1, characterized in that, The gear (5) includes: Fixing sleeve; The movable sleeve is fitted inside the fixed sleeve, and its side wall is provided with a track including a locking position and a movable position; A positioning sleeve is fitted inside the movable sleeve and connected to the main shaft (2); And a torsion spring, which is disposed between the movable sleeve and the positioning sleeve, for providing a self-locking elastic force.

7. The deceleration structure according to claim 1, characterized in that, The inner wall of the speed reducer (6) is provided with a rubber ring, and the rubber ring and the rotating disk (4) or the speed reducer (6) itself form a friction pair.

8. The deceleration structure according to claim 1, characterized in that, The speed reducer (6) is provided with heat dissipation holes.

9. The deceleration structure according to claim 1, characterized in that, The number of planetary gears (9) is two.

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