A 360-degree rotatable heavy object angle fine-tuning hoisting device

Abstract

The present application relates to the technical field of hoist, and particularly discloses a heavy object angle fine adjustment hoisting device capable of 360-degree rotation, which comprises a shell, a partition plate, a first rolling groove, an angle adjusting mechanism and a driving mechanism, the partition plate is arranged in the middle of the inner cavity of the shell, the bottom end of the inner cavity of the shell and the bottom end of the partition plate are both provided with the first rolling groove in the circumferential direction, the angle adjusting mechanism is arranged at the bottom of the inner cavity of the shell, and the driving mechanism is arranged at the top end of the partition plate, and the driving mechanism is used for driving the angle adjusting mechanism to rotate. The device realizes the speed grading of coarse adjustment and fine adjustment through a double-input differential planetary gear train, takes into account the operation requirements of large-angle rapid rotation and precise angle fine adjustment, and realizes the independent sensing and one-time rigid locking of the stall condition under the condition of completely not relying on the electrical system through the pure mechanical centrifugal rotation speed monitoring and the rigid clamping column locking mechanism, thereby significantly improving the operation accuracy and safety and reliability of the heavy object rotation hoisting device.

Description

Technical Field

[0001] This invention relates to the field of lifting equipment technology, specifically to a lifting device for finely adjusting the angle of a heavy object that can rotate 360 ​​degrees. Background Technology

[0002] Heavy lifting equipment is an indispensable piece of equipment in industrial production, construction, logistics and warehousing and other fields. It is used to realize the vertical lifting and horizontal movement of heavy objects. Among them, lifting equipment that can drive the heavy object to rotate 360 ​​degrees has important application value in operation scenarios that require precise control of the angle of the heavy object, such as equipment installation, precision assembly, mold alignment, and warehouse stacking, because it can flexibly adjust the orientation of the object being lifted during the lifting process. In existing technologies, lifting devices used to drive the rotation of heavy objects typically employ a single electric motor or hydraulic motor as the power source, directly driving the rotating shaft of the lifting device through a reducer to achieve the rotation of the heavy object. Although this single-power-source drive scheme has a relatively simple structure, it has significant shortcomings in practical applications. First, the transmission ratio of a single drive is fixed, making it difficult to balance the conflicting requirements of rapid rotation at large angles and precise fine-tuning at small angles. If a small reduction ratio is designed to meet the needs of rapid rotation, the output speed will be too high when fine alignment is required, making it difficult for the operator to accurately adjust the heavy object to the target angle. Conversely, if a large reduction ratio is used to meet the requirements of fine-tuning accuracy, the time consumed during large-angle rotation will be too long, seriously affecting work efficiency. Although some solutions attempt to solve this problem through variable frequency speed control, the stability and responsiveness of electrical speed control at extremely low speeds still cannot meet the stringent requirements of high-precision mechanical alignment, and it also increases the complexity of the control system. Furthermore, in terms of safety protection, existing heavy object rotation hoisting devices generally rely on electrical control systems for overspeed detection and protection. When the drive motor stalls due to electrical faults, driver failure, or abnormal control signals, causing the output speed to surge unexpectedly, the protection scheme relying on electrical signals may fail to respond in time due to system malfunctions, posing a risk of protection failure. Even if some devices are equipped with mechanical brakes, their triggering often relies on electrical commands. In extreme conditions such as power outages or control system failures, it is difficult to provide reliable pure mechanical independent protection. More importantly, in the case of hoisting heavy objects, even if the absolute value of the rotational shaft speed is not high, the kinetic energy generated by abnormal rotation due to the huge inertia of the heavy object itself is still enough to cause serious safety accidents, such as the heavy object swinging and colliding with surrounding equipment or personnel, or the lifting equipment connection parts becoming loose due to abnormal loads. In summary, existing heavy object rotation hoisting devices cannot simultaneously meet the requirements of high efficiency in coarse adjustment and precision in fine adjustment in terms of speed regulation. In terms of safety protection, they lack a purely mechanical protection mechanism that is independent of the electrical system and can achieve reliable rigid locking under low speed and high inertia conditions. These shortcomings limit the application of hoisting devices in high-end operation scenarios such as precision assembly and heavy equipment installation, where both angle control accuracy and safety reliability are highly demanding. Summary of the Invention

[0003] The purpose of this invention is to provide a lifting device for adjusting the angle of a heavy object that can rotate 360 ​​degrees, so as to at least solve the problems of insufficient adjustment range of the rotation speed of the heavy object and lack of pure mechanical stall lock protection in the prior art.

[0004] To achieve the above objectives, the present invention provides the following technical solution: a 360-degree rotatable lifting device for finely adjusting the angle of a heavy object, comprising: a housing, an isolation plate, a first roller groove, an angle adjustment mechanism, and a drive mechanism. The isolation plate is disposed in the middle of the inner cavity of the housing. The bottom end of the inner cavity of the housing and the bottom end of the isolation plate are both provided with a first roller groove along the circumference. The angle adjustment mechanism is disposed at the bottom of the inner cavity of the housing. The drive mechanism is disposed at the top end of the isolation plate. The drive mechanism is used to drive the angle adjustment mechanism to rotate.

[0005] Preferably, the angle adjustment mechanism includes: a planetary carrier, a first ball groove, a second roller groove, a planetary shaft, a sliding groove, a first rotating rod, and a protective component. The planetary carrier is rotatably and appropriately inserted into the bottom of the inner cavity of the housing. The upper and lower sides of the inner cavity of the planetary carrier are provided with second roller grooves along the circumferential direction. The upper and lower sides of the planetary carrier are provided with a plurality of first ball grooves at equal intervals along the circumferential direction. The positions of the first ball grooves correspond to the positions of the first roller grooves. The planetary shaft is located at the middle of the bottom end of the planetary carrier. The bottom end of the planetary shaft extends rotatably out of the bottom end of the housing. The outer wall of the planetary shaft is provided with a plurality of sliding grooves at equal intervals from top to bottom along the circumferential direction. There are three first rotating rods. The upper and lower ends of the three first rotating rods are respectively provided at equal intervals along the circumferential direction on the upper and lower sides of the inner cavity of the planetary carrier. The protective component is located on the outer wall of the planetary shaft.

[0006] Preferably, the angle adjustment mechanism further includes: a gear ring, second ball grooves, rolling balls, planetary gears, a second rotating rod, and a sun gear; the gear ring is rotatably fitted into the inner cavity of the planetary carrier, and several second ball grooves are equidistantly spaced along the circumference on both the upper and lower sides of the gear ring, the positions of the second ball grooves corresponding to the positions of the second rolling grooves; the number of rolling balls is several, and the rolling balls are respectively rotatably fitted into the inner cavities of several first ball grooves and several second ball grooves, and the rolling balls are respectively rotatably fitted into the inner cavities of the first rolling grooves and the second rolling grooves; the planetary gears are sleeved on the outer wall of the first rotating rod and locked by set screws; all three planetary gears mesh with the inner wall of the gear ring; the top of the outer wall of the second rotating rod is rotatably disposed at the top center of the isolation plate by bearings; the bottom end of the second rotating rod rotatably extends into the inner cavity of the gear ring; the sun gear is sleeved on the bottom of the outer wall of the second rotating rod and locked by set screws; the sun gear meshes with all three planetary gears.

[0007] Preferably, the length of the rolling ball located in the cavities of the first and second ball grooves is greater than its radius.

[0008] Preferably, the protective assembly includes: a pull ring, a brake cylinder, a wedge groove, a first extrusion groove, a slider, a speed monitoring unit, and a positioning unit. The pull ring is slidably fitted to the outer wall of the planetary shaft. The brake cylinder is disposed at the top of the pull ring. A plurality of first extrusion grooves are equidistantly formed along the circumferential direction on the outer side of the bottom end of the brake cylinder. A wedge groove is formed along the circumferential direction at the top end of the brake cylinder. There are a plurality of sliders, which are equidistantly disposed along the circumferential direction on the inner wall of the pull ring. The sliders are slidably fitted into the inner cavity of a plurality of grooves. The speed monitoring unit is disposed at the bottom end of the pull ring, and the positioning unit is disposed at the bottom end of the housing.

[0009] Preferably, the protective component further includes: a first spring and a retaining post, wherein the first spring is embedded in the inner cavity of the first extrusion groove, one end of the first spring is engaged with the inner wall of the first extrusion groove, the top end of the retaining post is slidably adapted to be inserted into the inner cavity of the first extrusion groove, the bottom end of the retaining post extends slidably out of the bottom end of the first extrusion groove, and the other end of the first spring is engaged with the top end of the retaining post.

[0010] Preferably, the speed monitoring unit includes: a rotating ring, a second spring, a first connecting rod, a second connecting rod, and a counterweight ball. The rotating ring is disposed on the outer wall of the planetary shaft. The second spring is sleeved on the outer wall of the planetary shaft. The bottom end of the second spring is engaged with the top end of the rotating ring, and the top end of the second spring is engaged with the bottom end of the pull ring. There are two first connecting rods, and the bottom ends of the two first connecting rods are rotatably disposed on the left and right sides of the rotating ring respectively via pins. There are two second connecting rods, and the top ends of the two second connecting rods are rotatably disposed on the left and right sides of the pull ring respectively via pins. The bottom ends of the two second connecting rods are rotatably disposed in the middle of the outer wall of the two first connecting rods respectively via pins. The counterweight ball is disposed on the top end of the first connecting rod.

[0011] Preferably, the positioning unit includes: a positioning cylinder, a second extrusion groove, a wedge block, a pull rod, and a third spring. The positioning cylinder is located at the bottom end of the housing. The brake cylinder is slidably and compatiblely inserted into the inner cavity of the positioning cylinder. The bottom end of the inner cavity of the positioning cylinder has several slots equidistantly spaced along the circumference. The positions of the slots correspond to and match the positions of the pins. The inner cavity of the positioning cylinder has second extrusion grooves on both the left and right sides. A portion of the wedge block is slidably and compatiblely inserted into the inner side of the second extrusion groove. The position of the wedge block corresponds to and matches the position of the wedge groove. The pull rod is located on the outer side of the wedge block and slidably extends out of the outer side of the positioning cylinder. The third spring is sleeved on the outer wall of the pull rod. One end of the third spring is engaged with the outer wall of the wedge block, and the other end of the third spring is engaged with the inner wall of the second extrusion groove.

[0012] Preferably, the distance between the bottom end of the wedge block and the bottom end of the inner cavity of the positioning cylinder is greater than 1 mm in height of the wedge groove.

[0013] Preferably, the number of teeth on the inner wall of the toothed ring is a multiple of the number of teeth on the outer wall of the sun gear.

[0014] The present invention proposes a lifting device for adjusting the angle of a heavy object that can rotate 360 ​​degrees, which has the following advantages: 1. This invention utilizes a dual-input differential planetary gear system for both the angle adjustment mechanism and the drive mechanism. When adjusting the angle of a heavy object, the first motor drives the sun gear to rotate via a first worm and worm wheel, while the second motor directly drives the ring gear to rotate via a second worm. The sun gear and ring gear serve as the two input ends of the differential gear system, each driven by an independent worm gear pair. This achieves a series connection between the first-stage worm gear reduction and the second-stage planetary differential reduction. During coarse adjustment, the ring gear drive can achieve a higher output speed to meet the requirements of large-angle rapid rotation. During fine adjustment, switching to the sun gear drive can achieve an extremely low output speed to meet the requirements of precise alignment. This effectively solves the contradiction of insufficient speed adjustment range and difficulty in balancing fast and slow speeds in traditional single power sources.

[0015] 2. This invention utilizes the cooperation between the first worm and worm wheel, and the second worm and gear ring in the drive mechanism. When both the first and second motors stop operating, the worm wheel and worm gear pairs at both ends are in a reverse self-locking state, which can mechanically lock the sun gear and gear ring at the current angular position. Then, the planetary carrier and planetary shaft are locked through the planetary gears. Power-off self-locking can be achieved without the need for an additional brake, ensuring that the heavy object can be stably stopped at any rotation angle, thus improving the safety of hoisting operations.

[0016] 3. This invention provides a rigid locking mechanism consisting of a pull ring, brake cylinder, locking pin, first spring, positioning cylinder, and locking groove. When the speed monitoring unit triggers the brake cylinder to descend under stall conditions and it is initially limited by the wedge block, once the locking pin and locking groove are aligned during the continued rotation of the planetary shaft, the first spring pushes the locking pin into the locking groove, forming a shape-locked rigid connection. This provides a positive locking method different from friction braking, fundamentally eliminating the defects of friction brakes at low speeds, such as insufficient contact pressure leading to brake force attenuation and friction pad retraction after speed drop, resulting in a vicious cycle. It achieves reliable one-time locking under low-speed, high-inertia conditions.

[0017] 4. This invention features a speed monitoring unit consisting of a first connecting rod, a second connecting rod, a counterweight ball, a rotating ring, and a second spring. The counterweight ball is fixed to the top of the first connecting rod, the bottom of the first connecting rod is hinged to the rotating ring, and the two ends of the second connecting rod are respectively hinged to the middle of the first connecting rod and the pull ring. When the planetary shaft experiences abnormal overspeed due to motor stall, the centrifugal force on the counterweight ball increases. This change in centrifugal force is converted into linear motion of the pull ring downwards along the slide groove through the connecting rod mechanism. The rotational motion is converted into an axial displacement signal through a purely mechanical means. The action response is entirely determined by the actual speed of the rotating shaft, without the need for any electrical sensors or control circuits. It can still be independently and reliably triggered under extreme conditions such as power failure, electromagnetic interference, or control system failure, providing an autonomous sensing basis for subsequent braking actions that does not rely on external energy.

[0018] 5. This invention, by setting up a preliminary limiting mechanism consisting of a wedge groove, a positioning cylinder, a wedge block, a third spring, and a pull rod, ensures that when the brake cylinder moves downward under the drive of the speed monitoring unit, the wedge groove first squeezes the wedge block outward. After the wedge groove passes through, the wedge block springs back under the action of the third spring and locks against the top of the brake cylinder. Before the locking pin and the locking groove complete the final locking, the brake cylinder is axially limited, which can effectively prevent the problem of brake cylinder rebound and locking action interruption caused by instantaneous fluctuations in centrifugal force. This provides a stable mechanical premise for the accurate alignment and reliable locking of the locking pin and the locking groove.

[0019] 6. This invention uses a pull rod and a third spring in conjunction with a wedge block to form a manually releaseable unlocking mechanism. When the fault is cleared and normal operation needs to be resumed, the operator can pull the pull rod outward to move the wedge block back and release the limit on the brake cylinder. The brake cylinder will automatically move upward and reset under the action of the second spring, and the locking pin will then exit the slot. This ensures that the locking action must be manually intervened by the operator to unlock the device, eliminating the secondary risk of the device automatically resetting and continuing to operate after the abnormal working condition is eliminated. This meets the redundant protection requirements of industrial safety for manual reset after locking.

[0020] 7. This invention forms a composite rolling support structure by setting up rolling balls in conjunction with a first ball groove, a first rolling groove, a second ball groove, and a second rolling groove. Rolling contact is achieved between the planetary carrier and the shell, and between the gear ring and the planetary carrier, through rolling balls. The rolling balls perform pure rolling motion within the ball grooves and rolling grooves, uniformly transmitting the axial and radial loads of the hoisted heavy objects through multiple rows of rolling balls. While bearing heavy loads, it significantly reduces rotational friction resistance, ensuring 360° uninterrupted continuous rotation under large inertia loads. At the same time, the length of the rolling balls within the ball groove cavity is greater than their radius, which can effectively prevent the rolling balls from radially falling off during hoisting, ensuring long-term operational reliability.

[0021] 8. This device achieves speed gradation for coarse and fine adjustment through a dual-input differential planetary gear system, taking into account the operational requirements of large-angle rapid rotation and precise angle fine adjustment. Through a purely mechanical centrifugal speed monitoring and rigid locking mechanism, it achieves autonomous detection of stall conditions and one-time rigid locking without relying on the electrical system, significantly improving the operating accuracy and safety reliability of the heavy object rotation hoisting device. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of the present invention; Figure 2 This is an exploded view of the present invention; Figure 3 This is a diagram illustrating the protective components. Figure 4 An exploded view of the angle adjustment mechanism; Figure 5 This is a diagram illustrating the speed monitoring unit; Figure 6 This is a schematic diagram of the protective component. Figure 7 for Figure 4 Enlarged view of point A; Figure 8 for Figure 4 Enlarged view of point B; Figure 9 for Figure 6 Enlarged view of point C.

[0023] In the diagram: 1. Housing; 2. Isolation plate; 3. First roller groove; 4. Angle adjustment mechanism; 41. Planetary carrier; 42. First ball groove; 43. Second roller groove; 44. Planetary shaft; 45. Slide groove; 46. First rotating rod; 47. Protective assembly; 471. Pull ring; 472. Brake cylinder; 473. Wedge groove; 474. First compression groove; 475. First spring; 476. Locking post; 477. Slider; 478. Speed ​​monitoring unit; 4781. Rotating ring; 4782. Second spring; 4783. First connecting rod. 4784. Second connecting rod; 4785. Counterweight ball; 479. Positioning unit; 4791. Positioning cylinder; 4792. Second extrusion groove; 4793. Wedge block; 4794. Pull rod; 4795. Third spring; 4796. Slot; 48. Gear ring; 49. Second ball groove; 410. Rolling ball; 411. Planetary gear; 412. Second rotating rod; 413. Sun gear; 5. Drive mechanism; 51. First motor; 52. First worm; 53. Worm wheel; 54. Second motor; 55. Second worm. Detailed Implementation

[0024] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. 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.

[0025] Please see Figures 1-9This invention provides a 360-degree rotatable lifting device for fine-tuning the angle of heavy objects, comprising: a housing 1, an isolation plate 2, a first roller groove 3, an angle adjustment mechanism 4, and a drive mechanism 5. The housing 1 serves as the main load-bearing frame of the device, accommodating and supporting internal components such as the isolation plate 2, the angle adjustment mechanism 4, and the drive mechanism 5, and transmitting the lifting load to the crane via an external connection. The isolation plate 2 is located in the middle of the inner cavity of the housing 1. Both the bottom end of the inner cavity of the housing 1 and the bottom end of the isolation plate 2 are provided with a first roller groove 3 circumferentially. The isolation plate 2 divides the inner cavity of the housing 1 into an upper drive cavity and a lower transmission cavity, providing a mounting base for the drive mechanism 5, and participating in angle adjustment through the first roller groove 3 at its bottom end. The rolling support of the joint mechanism 4 and the angle adjustment mechanism 4 are located at the bottom of the inner cavity of the housing 1. The angle adjustment mechanism 4 is the core transmission system of the device. It adopts a dual-input differential planetary gear train structure to receive two power inputs, coarse adjustment and fine adjustment, provided by the drive mechanism 5, and transmit the power to the planetary shaft 44 to realize the 360° rotation of the weight and the fine adjustment of the angle. The drive mechanism 5 is located at the top of the isolation plate 2. The drive mechanism 5 is used to drive the angle adjustment mechanism 4 to rotate. The drive mechanism 5 is used to drive the sun gear 413 and the gear ring 48 in the angle adjustment mechanism 4 to rotate respectively. The coarse adjustment and fine adjustment functions are realized by switching between the two independent power inputs, and the transmission chain is locked by the self-locking characteristics of its own transmission pair when the machine stops.

[0026] As a preferred embodiment, the angle adjustment mechanism 4 further includes: a planetary carrier 41, a first ball groove 42, a second rolling groove 43, a planetary shaft 44, a slide 45, a first rotating rod 46, a protective component 47, a gear ring 48, a second ball groove 49, a rolling ball 410, a planetary gear 411, a second rotating rod 412, and a sun gear 413. The planetary carrier 41 is rotatably fitted into the bottom of the inner cavity of the housing 1. The upper and lower sides of the inner cavity of the planetary carrier 41 are provided with second rolling grooves 43 along the circumferential direction. The upper and lower sides of the planetary carrier 41 are provided with a plurality of first ball grooves 42 equidistantly along the circumferential direction. The positions of the first ball grooves 42 correspond to the positions of the first rolling grooves 43. The planetary carrier 41 is the output component of the planetary gear system, used to support the planetary gear 411 and the first rotating rod 413. 6. The synthesized rotational speed and torque are output through the planetary shaft 44 to drive the rotation of the heavy object. The planetary shaft 44 is located at the bottom center of the planetary carrier 41. The bottom end of the planetary shaft 44 extends rotatably out of the bottom end of the housing 1. The outer wall of the planetary shaft 44 has several grooves 45 equidistantly spaced from top to bottom along the circumferential direction. The planetary shaft 44 is the final output shaft of the device, used to connect the heavy object clamping device and transmit the rotational motion of the planetary carrier 41 to the suspended heavy object. There are three first rotating rods 46. The upper and lower ends of the three first rotating rods 46 are respectively equidistantly spaced along the circumferential direction on the upper and lower sides of the inner cavity of the planetary carrier 41. The first rotating rods 46 are used to rotatably support the planetary gear 411, provide the planetary gear 411 with a rotation axis, and transmit the planetary gear 411's revolution. The rotational speed of the planetary shaft 44 is transmitted to the planetary carrier 41. A protective component 47 is installed on the outer wall of the planetary shaft 44. The protective component 47 monitors the rotational speed of the planetary shaft 44 in real time and automatically triggers a rigid locking action through pure mechanical linkage when the speed abnormally increases due to motor stall, preventing the planetary shaft 44 from continuing to rotate. A gear ring 48 is rotatably fitted into the inner cavity of the planetary carrier 41. Several second ball grooves 49 are equidistantly spaced along the circumference on both the upper and lower sides of the gear ring 48. The positions of the second ball grooves 49 correspond to the positions of the second rolling grooves 43. The gear ring 48 is the input end of the coarse adjustment power in the dual-input differential gear train, receiving the rotational motion transmitted from the second motor 54 via the second worm gear 55. Several rolling balls 410 are rotatably fitted into several second ball grooves 410. The inner cavity of a ball groove 42 and several second ball grooves 49 has several rolling balls 410 that are adapted to each other and can roll into the inner cavity of the first rolling groove 3 and the second rolling groove 43 respectively. The length of the rolling balls 410 in the inner cavity of the first ball groove 42 and the second ball groove 49 is greater than their radius. The rolling balls 410 are used to form rolling contact between the planet carrier 41 and the housing 1, and between the gear ring 48 and the planet carrier 41, to bear the lifting load and reduce the rotational friction resistance. The planetary gears 411 are sleeved on the outer wall of the first rotating rod 46 and locked by set screws. All three planetary gears 411 mesh with the inner wall of the gear ring 48. The planetary gears 411 are used to transmit motion and torque in the differential gear train, and realize the composite motion output of the planet carrier 41 according to the input state of the sun gear 413 and the gear ring 48.The top of the outer wall of the second rotating rod 412 is rotatably mounted at the top center of the isolation plate 2 via a bearing. The bottom end of the second rotating rod 412 extends rotatably into the inner cavity of the gear ring 48. The second rotating rod 412 is used to transmit the rotational motion of the worm gear 53 to the sun gear 413, forming the input shaft for fine-tuning power. The sun gear 413 is sleeved on the bottom of the outer wall of the second rotating rod 412 and locked by a set screw. The sun gear 413 meshes with all three planetary gears 411. The number of teeth on the inner wall of the gear ring 48 is several times the number of teeth on the outer wall of the sun gear 413. The sun gear 413 is the input end for fine-tuning power in the dual-input differential gear train, receiving the rotational motion transmitted by the first motor 51 through the first worm 52 and the worm gear 53.

[0027] As a preferred embodiment, the protective component 47 further includes: a pull ring 471, a brake cylinder 472, a wedge groove 473, a first compression groove 474, a first spring 475, a locking pin 476, a slider 477, a speed monitoring unit 478, and a positioning unit 479. The pull ring 471 is slidably and appropriately fitted to the outer wall of the planetary shaft 44. The pull ring 471 is used to receive the trigger action of the speed monitoring unit 478 and the brake cylinder 472, converting the centrifugal displacement of the counterweight ball 4785 into linear motion along the axial direction of the planetary shaft 44. The brake cylinder 472 is disposed at the top of the pull ring 471. Several first compression grooves 474 are equidistantly provided along the circumferential direction on the outer side of the bottom end of the brake cylinder 472. The top end of the brake cylinder 472 is equidistantly provided along the circumferential direction. A wedge-shaped groove 473 is provided. The brake cylinder 472 moves axially synchronously with the pull ring 471 and enters the positioning cylinder 4791. The wedge-shaped groove 473 at its top engages with the wedge block 4793 to achieve initial positioning. The first rigid lock is achieved by the locking pin 476 in the first extrusion groove 474 at its bottom engaging with the slot 4796. The first spring 475 is embedded in the inner cavity of the first extrusion groove 474, and one end of the first spring 475 is engaged with the inner wall of the first extrusion groove 474. The first spring 475 is a rotary spring. It undergoes elastic deformation after being compressed or stretched by external force and returns to its initial state after the external force is removed. The first spring 475 is used to spring the locking pin 476 into the slot when the locking pin 476 is aligned with the slot 4796. 4796 forms a lock. The top end of the locking post 476 is slidably fitted into the inner cavity of the first extrusion groove 474, and the bottom end of the locking post 476 slidably extends out of the bottom end of the first extrusion groove 474. The other end of the first spring 475 is fitted into the top end of the locking post 476. The locking post 476 is used to embed into the locking groove 4796 when the brake cylinder 472 rotates to align with the locking groove 4796, forming a shape-locked rigid brake. There are several sliders 477, which are equidistantly arranged on the inner wall of the pull ring 471 along the circumference. The sliders 477 are slidably fitted into the inner cavities of several sliding grooves 45. The sliders 477 are used to guide the pull ring 471 to slide axially along the planetary axis 44. The relative rotation between the pull ring 471 and the planetary shaft 44 is restricted to ensure that the brake cylinder 472 rotates synchronously with the planetary shaft 44. The speed monitoring unit 478 is located at the bottom of the pull ring 471. The speed monitoring unit 478 is used to convert the speed change of the planetary shaft 44 into the axial displacement of the pull ring 471 through the centrifugal pendulum mechanism composed of the counterweight ball 4785, the first connecting rod 4783 and the second connecting rod 4784, so as to realize the purely mechanical autonomous sensing of abnormal overspeed. The positioning unit 479 is located at the bottom of the housing 1. The positioning unit 479 is used to receive and lock the brake cylinder 472 after it has descended. The axial initial limit is achieved by the wedge block 4793, and the circumferential rigid locking is achieved by the cooperation of the slot 4796 and the pin 476.

[0028] As a preferred embodiment, the speed monitoring unit 478 further includes: a rotating ring 4781, a second spring 4782, a first connecting rod 4783, a second connecting rod 4784, and a counterweight ball 4785. The rotating ring 4781 is disposed on the outer wall of the planetary shaft 44, serving as the hinge base for the first connecting rod 4783 and the bottom support for the second spring 4782, transmitting the rotational motion of the planetary shaft 44 to the centrifugal pendulum mechanism. The second spring 4782 is sleeved on the outer wall of the planetary shaft 44, and the bottom of the second spring 4782... The first end is engaged with the top end of the rotating ring 4781, and the top end of the second spring 4782 is engaged with the bottom end of the pull ring 471. The second spring 4782 is a rotating spring that undergoes elastic deformation after being compressed or stretched by external force, and returns to its initial state after the external force is removed. The second spring 4782 is used to provide elastic support force to keep the pull ring 471 and brake cylinder 472 in the initial high position under normal speed, and is overcome and compressed by the centrifugal force of the counterweight ball 4785 under stall conditions, providing a restoring elastic force for the pull ring 471. The first connecting rod 4783 has several... There are two first connecting rods 4783. The bottom ends of the two first connecting rods 4783 are rotatably mounted on the left and right sides of the rotating ring 4781 via pins. The first connecting rods 4783 are used to cause the counterweight ball 4785 to swing outward around the bottom pin under the action of centrifugal force when the planetary shaft 44 rotates, converting the magnitude of the centrifugal force into an angular displacement signal. There are also two second connecting rods 4784. The top ends of the two second connecting rods 4784 are rotatably mounted on the left and right sides of the pull ring 471 via pins, and the bottom ends of the two second connecting rods 4784 are respectively mounted on pins. The first link 4783 is rotatably mounted in the middle of the outer wall of the two first links 4783. The second link 4784 is used to convert the angular displacement of the first link 4783 into the linear displacement of the pull ring 471 along the planetary axis 44. The counterweight ball 4785 is mounted at the top of the first link 4783. The counterweight ball 4785 is used to generate centrifugal force when the planetary axis 44 rotates. When the speed increases abnormally, the centrifugal force increases sharply, overcoming the elastic force of the second spring 4782 to drive the first link 4783 to swing outward, providing triggering power for the speed monitoring unit 478.

[0029] As a preferred embodiment, the positioning unit 479 further includes: a positioning cylinder 4791, a second pressing groove 4792, a wedge block 4793, a pull rod 4794, and a third spring 4795. The positioning cylinder 4791 is disposed at the bottom end of the housing 1. The brake cylinder 472 is slidably and compatiblely inserted into the inner cavity of the positioning cylinder 4791. A plurality of slots 4796 are equidistantly provided along the circumferential direction at the bottom end of the inner cavity of the positioning cylinder 4791. The positions of the plurality of slots 4796 correspond to and match the positions of the plurality of locking posts 476. The positioning cylinder 4791 has a second pressing groove 4792 on both the left and right sides of the inner cavity. The second extrusion groove 4792 and the positioning cylinder 4791 are used to accommodate the insertion of the brake cylinder 472 and provide it with an axial and circumferential locking base. The slot 4796 opened at the bottom of the inner cavity cooperates with the locking post 476 to form a rigid locking pair. The second extrusion groove 4792 opened on the left and right sides of the inner cavity provides radial sliding space for the wedge block 4793. A part of the wedge block 4793 is slidably adapted to be inserted into the inner side of the inner cavity of the second extrusion groove 4792. The position of the wedge block 4793 corresponds to the position of the wedge groove 473 and matches it. The bottom end of the wedge block 4793 extends into the inner cavity of the positioning cylinder 4791. The distance between the bottom ends is 1mm greater than the height of the wedge groove 473. The wedge block 4793 is used to cooperate with the wedge groove 473 to complete the initial axial limit when the brake cylinder 472 moves downward. Its bottom end blocks the top of the brake cylinder 472 to prevent the brake cylinder 472 from rebounding. The pull rod 4794 is located on the outside of the wedge block 4793. The pull rod 4794 extends slidably out of the outside of the positioning cylinder 4791. The pull rod 4794 is used by the operator to pull it outward after troubleshooting, causing the wedge block 4793 to retract and release the limit on the brake cylinder 472, realizing manual unlocking and reset. The third spring 4 795 is sleeved on the outer wall of the pull rod 4794. One end of the third spring 4795 is engaged with the outer wall of the wedge block 4793, and the other end of the third spring 4795 is engaged with the inner wall of the second compression groove 4792. The third spring 4795 is a rotary spring. After being compressed or stretched by external force, it undergoes elastic deformation and returns to its initial state after the external force is removed. The third spring 4795 is used to push the wedge block 4793 to reset inward after passing through the wedge block 4793 in the wedge groove 473 of the brake cylinder 472, so that it is engaged in the top of the brake cylinder 472 to achieve the limit, and to provide the reset elastic force when unlocking.

[0030] As a preferred embodiment, the drive mechanism 5 further includes: a first motor 51, a first worm 52, a worm wheel 53, a second motor 54, and a second worm 55. The first motor 51 is screwed to the top of the isolation plate 2. The first motor 51 is existing technology and will not be described in detail here. The first motor 51 is used to start in fine-tuning mode and drive the sun gear 413 to rotate through the first worm 52 and the worm wheel 53, thereby achieving high-precision fine-tuning of the load angle. The first worm 52 is locked to the output end of the first motor 51 by a coupling. The first worm 52 is used to transmit the rotational motion of the first motor 51 to the worm wheel 53 and cooperates with the worm wheel 53 to form a first-stage reduction and self-locking pair. When the machine stops, the sun gear 413 is locked. The worm wheel 53 is sleeved on the top of the outer wall of the second rotating rod 412 and locked by a set screw. The worm gear 53 meshes with the first worm 52. The worm gear 53 receives the power transmitted by the first worm 52 and drives the second rotating rod 412 to rotate. At the same time, it cooperates with the first worm 52 to achieve self-locking of the sun gear 413 transmission chain when the machine stops. The second motor 54 is screwed into the inner cavity of the housing 1. The second motor 54 is existing technology and will not be described in detail here. The second motor 54 is used to start in coarse adjustment mode and directly drive the gear ring 48 to rotate through the second worm 55 to achieve large-angle rapid rotation of the heavy object. The second worm 55 is locked to the output end of the second motor 54 through a coupling. The second worm 55 meshes with the gear ring 48. The second worm 55 is used to transmit the rotational motion of the second motor 54 to the gear ring 48 and lock the gear ring 48 transmission chain when the machine stops by utilizing the self-locking characteristic between it and the gear ring 48.

[0031] Its detailed connection method is a well-known technology in this field. The following mainly introduces the working principle and process, and the specific work is as follows.

[0032] Step 1: Install the top of the shell 1 below the heavy-duty crane, and install the heavy-duty clamping device at the bottom of the planetary shaft 44. When lifting heavy objects, use the heavy-duty clamping device at the bottom of the planetary shaft 44 to clamp and fix the heavy objects, and use the heavy-duty crane to pull the shell 1 to lift the heavy objects until they are lifted to a suitable height. Step 2: When the angle of the weight needs to be adjusted, first start the second motor 54. The output end of the second motor 54 drives the second worm 55 to rotate, thereby driving the gear ring 48 to rotate. At this time, the sun gear 413 is fixed in the cooperation of the worm gear 53 and the first worm 52. Then, the rotation of the gear ring 48, in cooperation with the sun gear 413 and the planetary gear 411, drives the planet carrier 41 to rotate. Thus, the planet carrier 41 drives the weight to rotate through the planet shaft 44, thereby allowing the angle of the weight to be coarsely adjusted. Step 3: After the coarse adjustment, when fine adjustment of the weight is required, turn off the second motor 54, fix the gear ring 48 using the second worm 55, start the first motor 51, and use the output end of the first motor 51 to drive the first worm 52 to rotate. The cooperation between the first worm 52 and the worm wheel 53 drives the second rotating rod 412 to rotate. At this time, the cooperation between the first worm 52 and the worm wheel 53 can perform primary deceleration rotation. The rotation of the second rotating rod 412 drives the sun gear 413 to rotate. The rotation of the sun gear 413, in cooperation with the gear ring 48 and the planetary gear 411, drives the planet carrier 41 to rotate. Then, a secondary deceleration rotation is performed, which causes the planet carrier 41 to decelerate and rotate, thereby achieving fine adjustment of the weight until the weight is adjusted to a suitable angle. Step 4: When the planetary carrier 41 rotates, the first ball grooves 42 on its upper and lower sides correspond to the first rolling grooves 3 of the shell 1 and the isolation plate 2, and the second ball grooves 49 on its upper and lower sides correspond to the second rolling grooves 43 of the planetary carrier 41. The rolling balls 410 roll and adapt to the inner cavities of the first ball groove 42, the first rolling groove 3, the second ball groove 49 and the second rolling groove 43 respectively. With the rotation of the planetary carrier 41 and the gear ring 48, they make pure rolling motion, reducing rotational friction resistance, while supporting the hoisting load, and realizing 360° continuous rotation without jamming or dead angle. When the rolling balls 410 roll in the ball grooves and rolling grooves, their length in the inner cavity of the first ball groove 42 and the second ball groove 49 is greater than their own radius. They are always limited inside the groove and will not fall off radially, ensuring the connection stability between the planetary carrier 41, the gear ring 48 and the shell 1, and bearing the axial and radial loads of the heavy load hoisting. Step 5: When the planetary shaft 44 rotates at normal speed, the speed monitoring unit 478 of the protective component 47 is in standby mode, the second spring 4782 is in a naturally extended state, pushing the pull ring 471 and brake cylinder 472 to remain in their initial positions, the centrifugal force on the counterweight ball 4785 is small, the first connecting rod 4783 and the second connecting rod 4784 remain in a retracted state, the brake cylinder 472 has not moved to the bottom of the inner cavity of the positioning cylinder 4791, and the locking pin 476 and the locking groove 4796 are not in contact. If the first motor 51 or the second motor 54 experiences a stall due to electrical faults or other reasons, the first motor 51 or the second motor 54 will rotate at maximum power, thereby driving the planetary shaft. 44 rotates rapidly. At this time, the centrifugal force on the counterweight ball 4785 of the speed monitoring unit 478 increases sharply, overcoming the elastic force of the second spring 4782 and swinging outward, causing the first connecting rod 4783 to swing downward around the pin shaft. The first connecting rod 4783 pulls the second connecting rod 4784 downward through the pin shaft. The second connecting rod 4784 pulls the pull ring 471 to slide downward along the slide groove 45 on the outer wall of the planetary shaft 44. When the pull ring 471 slides downward, it drives the slider 477 on the inner wall to slide synchronously in the slide groove 45 and squeezes the second spring 4782 to undergo elastic deformation, ensuring that the pull ring 471 moves coaxially with the planetary shaft 44 without deviation. At the same time, the brake cylinder 472 at the top of the pull ring 471 moves downward accordingly. Step Six: During the downward movement of the brake cylinder 472, the wedge-shaped groove 473 on its outer wall contacts and engages with the wedge-shaped block 4793 inside the positioning cylinder 4791. The wedge-shaped groove 473 compresses the wedge-shaped block 4793 to move outward. The outward movement of the wedge-shaped block 4793 compresses the third spring 4795, causing elastic deformation, until the wedge-shaped groove 473 disengages from the outer wall of the wedge-shaped block 4793. At this point, under the elastic force of the third spring 4795, the wedge-shaped block 4793 is pushed inward. Thus, the engagement between the bottom end of the wedge-shaped block 4793 and the top end of the brake cylinder 472 initially limits the position of the brake cylinder 472, preventing it from moving up and down. Step 7: At this time, since the planetary shaft 44 is still driving the brake cylinder 472 to rotate, it is impossible to guarantee that the positions of the several locking pins 476 correspond to the positions of the several locking slots 4796. Therefore, the bottom of the inner cavity of the positioning cylinder 4791 is used to squeeze the locking pins 476 into the inner cavity of the first squeezing groove 474, and squeeze the first spring 475 to undergo elastic deformation until the brake cylinder 472 rotates to the point where the positions of the several locking pins 476 correspond one-to-one with the positions of the several locking slots 4796. At this time, under the elastic force of the first spring 475, the locking pins 476 can be pushed into the inner cavity of the locking slot 4796 corresponding to their current position, thereby braking and fixing the brake cylinder 472. After the brake cylinder 472 is locked, the planetary shaft 44 is restricted from continuing to rotate through the cooperation of the pull ring 471, the slider 477 and the sliding groove 45, so as to realize the timely mechanical braking and locking of the planetary shaft 44, avoid overspeeding and causing the heavy object to swing or fall, and complete the hoisting safety protection. Step 8: When the device stops, the first motor 51 and the second motor 54 of the drive mechanism stop running. The self-locking characteristic of the worm gear structure immediately locks the second rotating rod 412 and the sun gear 413. The planetary gear system stops transmission, and the planetary shaft 44 remains at its current angle. In conjunction with the standby state of the protective components, the stability of the hoisting posture of the heavy object is ensured. After the fault is cleared, the pull rod 4794 is pulled outward to drive the wedge block 4793 to move outward and squeeze the third spring 4795 to undergo elastic deformation until the wedge block 4793 and the brake cylinder 472 separate. Then, under the elastic force of the second spring 4782, the pull ring 471 is pushed upward until it returns to the initial position, and then it moves in the opposite direction to the above.

[0033] This device achieves speed gradation for coarse and fine adjustment through a dual-input differential planetary gear system, taking into account both the operational requirements of large-angle rapid rotation and precise angle fine adjustment. Through a purely mechanical centrifugal speed monitoring and rigid locking mechanism, it achieves autonomous detection of stall conditions and one-time rigid locking without relying on the electrical system, significantly improving the operational accuracy and safety reliability of the heavy object rotation hoisting device.

[0034] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art 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 appended claims and their equivalents.

Claims

1. A lifting device for adjusting the angle of a heavy object that can rotate 360 ​​degrees, characterized in that, include: Shell (1); The isolation plate (2) is located in the middle of the inner cavity of the housing (1). The bottom of the inner cavity of the housing (1) and the bottom of the isolation plate (2) are both provided with a first rolling groove (3) along the circumferential direction. An angle adjustment mechanism (4) is provided at the bottom of the inner cavity of the housing (1); A drive mechanism (5) is located at the top of the isolation plate (2) and is used to drive the angle adjustment mechanism (4) to rotate. The angle adjustment mechanism (4) includes: Planetary carrier (41), which is rotatably adapted to be inserted into the bottom of the inner cavity of the housing (1), and the upper and lower sides of the inner cavity of the planetary carrier (41) are provided with second rolling grooves (43) along the circumferential direction. The upper and lower sides of the planetary carrier (41) are provided with a plurality of first ball grooves (42) at equal intervals along the circumferential direction. The positions of the first ball grooves (42) correspond to the positions of the first rolling grooves (3). Planetary shaft (44) is located at the bottom center of planet carrier (41). The bottom end of planetary shaft (44) extends rotatably out of the bottom end of housing (1). The outer wall of planetary shaft (44) is provided with several grooves (45) equidistantly from top to bottom along the circumferential direction. The first rotating rod (46) has three parts, and the upper and lower ends of the three first rotating rods (46) are respectively arranged equidistantly along the circumferential direction on the upper and lower sides of the inner cavity of the planet carrier (41); A protective component (47) is disposed on the outer wall of the planetary shaft (44); A toothed ring (48) is rotatably fitted into the inner cavity of the planetary carrier (41). The upper and lower sides of the toothed ring (48) are provided with a plurality of second ball grooves (49) at equal intervals along the circumference. The positions of the second ball grooves (49) correspond to the positions of the second rolling grooves (43). The number of the rolling balls (410) is several, and the several rolling balls (410) are respectively rotatably adapted to be inserted into the inner cavity of several first ball grooves (42) and several second ball grooves (49), and the several rolling balls (410) are respectively rotatably adapted to extend into the inner cavity of the first rolling groove (3) and the second rolling groove (43); Planetary gears (411) are sleeved on the outer wall of the first rotating rod (46) and locked by set screws. All three planetary gears (411) mesh with the inner wall of the gear ring (48). The second rotating rod (412) is rotatably mounted on the top center of the top of the isolation plate (2) via a bearing at the top of the outer wall of the second rotating rod (412), and the bottom end of the second rotating rod (412) extends rotatably into the inner cavity of the toothed ring (48). The sun gear (413) is sleeved on the bottom of the outer wall of the second rotating rod (412) and locked by a set screw. The sun gear (413) meshes with three planetary gears (411).

2. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 1, characterized in that, The length of the ball (410) located in the inner cavity of the first ball groove (42) and the second ball groove (49) is greater than its radius.

3. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 2, characterized in that, The protective component (47) includes: Pull ring (471), which is slidably fitted to the outer wall of the planetary shaft (44); Brake cylinder (472), the brake cylinder (472) is disposed at the top of pull ring (471), the bottom outer side of the brake cylinder (472) is provided with a plurality of first extrusion grooves (474) at equal intervals along the circumference, and the top of the brake cylinder (472) is provided with a wedge-shaped groove (473) along the circumference. The slider (477) is a plurality of sliders (477), and the plurality of sliders (477) are respectively arranged equidistantly along the circumferential direction on the inner wall of the pull ring (471), and the plurality of sliders (477) are respectively slidably adapted to be inserted into the inner cavity of the plurality of sliding grooves (45); A speed monitoring unit (478) is disposed at the bottom end of the pull ring (471); Positioning unit (479) is disposed at the bottom end of housing (1).

4. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 3, characterized in that, The protective component (47) also includes: The first spring (475) is embedded in the inner cavity of the first extrusion groove (474), and one end of the first spring (475) is engaged with the inner wall of the first extrusion groove (474). The top end of the locking post (476) is slidably fitted into the inner cavity of the first extrusion groove (474), and the bottom end of the locking post (476) extends slidably out of the bottom end of the first extrusion groove (474). The other end of the first spring (475) is engaged with the top end of the locking post (476).

5. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 4, characterized in that, The speed monitoring unit (478) includes: A rotating ring (4781) is disposed on the outer wall of the planetary shaft (44); The second spring (4782) is sleeved on the outer wall of the planetary shaft (44), the bottom end of the second spring (4782) is engaged with the top end of the rotating ring (4781), and the top end of the second spring (4782) is engaged with the bottom end of the pull ring (471). The first link (4783) has two components, and the bottom ends of the two first links (4783) are rotatably mounted on the left and right sides of the rotating ring (4781) by means of pins. The second link (4784) has two parts. The top ends of the two second links (4784) are rotatably mounted on the left and right sides of the pull ring (471) by means of pins. The bottom ends of the two second links (4784) are rotatably mounted on the middle of the outer wall of the two first links (4783) by means of pins. A counterweight ball (4785) is disposed at the top of the first link (4783).

6. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 5, characterized in that, The positioning unit (479) includes: Positioning cylinder (4791) is located at the bottom end of housing (1). Braking cylinder (472) is slidably and compatiblely inserted into the inner cavity of positioning cylinder (4791). Several slots (4796) are equidistantly provided at the bottom end of the inner cavity of positioning cylinder (4791) along the circumferential direction. The positions of several slots (4796) correspond to and match the positions of several pins (476). Second extrusion grooves (4792) are provided on both the left and right sides of the inner cavity of positioning cylinder (4791). A wedge block (4793), a portion of which is slidably adapted to be inserted into the inner side of the cavity of the second extrusion groove (4792), the position of the wedge block (4793) and the position of the wedge groove (473) correspond to and match each other; A pull rod (4794) is disposed on the outside of the wedge block (4793) and the pull rod (4794) extends slidably out of the outside of the positioning cylinder (4791); The third spring (4795) is sleeved on the outer wall of the pull rod (4794), one end of the third spring (4795) is engaged with the outer wall of the wedge block (4793), and the other end of the third spring (4795) is engaged with the inner wall of the second extrusion groove (4792).

7. A 360-degree rotatable, fine-adjustable lifting device for heavy objects, as described in claim 6, is characterized in that... The distance between the bottom end of the wedge block (4793) and the bottom end of the inner cavity of the positioning cylinder (4791) is greater than the height of the wedge groove (473) by 1 mm.

8. The 360-degree rotatable, fine-adjustable lifting device for heavy objects according to claim 7, characterized in that, The number of teeth on the inner wall of the toothed ring (48) is several times the number of teeth on the outer wall of the sun gear (413).

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