Anti-swing quay crane lifting appliance device for lifting large-tonnage container

Abstract

The invention relates to the technical field of cranes, in particular to an anti-swing quay crane lifting appliance device for lifting large-tonnage containers, which comprises a lifting appliance body, two damping anti-swing units are arranged at the top end of the lifting appliance body, each damping anti-swing unit comprises a damping ring and an elastic reset assembly, and the damping ring can perform translational motion at the top end of the lifting appliance body; the elastic reset assembly is provided with a pressure part, the pressure part is in contact with inner rings of the damping rings, the two damping rings are matched with each other through the two damping anti-swing units arranged at the top end of the lifting appliance body, when the lifting appliance body swings, the damping rings can move relative to the lifting appliance body, and the generated relative movement can consume swing energy of the lifting appliance body, so that the lifting appliance body can swing more stably. And the elastic reset assembly is matched with the damping ring, the damping ring is guided to reset when the lifting appliance body is static, the damping ring can continuously consume the swing energy of the lifting appliance body, and the problem that an existing container lifting appliance is prone to shaking in the lifting process is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of cranes, and in particular to an anti-swaying quay crane hoisting device for hoisting large-tonnage containers. Background Art

[0002] In modern port logistics operations, the efficient and safe lifting of large-tonnage containers is crucial for ensuring the rapid flow of cargo. As the core equipment for container loading and unloading, quay cranes (STSs) frequently experience swaying when their lifting gear is suspending containers, with significant consequences.

[0003] From an operational perspective, when a spreader lifts a container, the acceleration change at the moment the lifting mechanism activates creates inertial forces within the container, causing the spreader to sway. As the spreader moves along the dock with the gantry crane, and as the trolley operates perpendicular to the dock, the impact forces from starting, stopping, or adjusting speed are also transmitted to the spreader, exacerbating its sway. Furthermore, when the container is lowered to its designated location, the momentary impact reaction force from the container contacting the placement surface can also cause spreader sway.

[0004] External environmental factors are also a significant cause of spreader sway. Frequent wind speeds in port areas exert horizontal forces on containers and spreaders, causing them to deviate from their equilibrium position. Furthermore, the uncertainty of wind strength and direction makes spreader sway even more difficult to predict and control. In strong winds, significant spreader sway can even threaten the structural safety of the entire quay crane. Furthermore, in certain areas, such as near river estuaries or in ports with complex terrain, ground vibrations caused by water flow and tidal fluctuations can also affect the quay crane foundation, indirectly causing spreader sway during lifting operations.

[0005] Patent document publication number CN115385219B discloses a safety sling device for passenger and cargo cranes. This invention relates to the technical field of sling devices and includes a sling body, the top of which is rotatably connected to an anti-interference mechanism. The tops of the anti-interference mechanisms are fixedly connected to a protective cylinder and roller devices, respectively. Stabilization mechanisms are fixedly connected to the sides of the body. This safety sling device for passenger and cargo cranes features a roller device connected to a lifting line. The top of the container used for cargo loading has four lifting holes. The bottom of the stabilization mechanism extends into the lifting holes, thereby lifting and shifting the container.

[0006] This spreader simply rotates the container to face the wind, thus protecting it from wind forces. However, in practice, containers of varying sizes and tonnages experience significant variations in their wind load characteristics. For some large containers, simply rotating the container to the optimal windward angle makes it difficult to precisely adjust the load, significantly reducing its windproofing effectiveness. Even in strong winds, the spreader cannot effectively prevent swaying, which can lead to safety accidents. Summary of the Invention

[0007] In response to the problems existing in the existing technology, an anti-swing quay crane hoisting device for large-tonnage container lifting is provided. Two damping anti-swing units are arranged on the top of the hoisting body, so that the two damping rings cooperate with each other. When the hoisting body swings, the damping ring will move relative to the hoisting body. The relative movement generated can consume the swinging energy of the hoisting body, so that the swing amplitude is greatly reduced. At the same time, the elastic reset component cooperates with the damping ring to guide the damping ring to reset when the hoisting body is stationary, so that the damping ring can continuously consume the swinging energy of the hoisting body, solving the problem that the existing container hoist is prone to shaking during lifting.

[0008] In order to solve the problems of the prior art, the present invention provides an anti-swing quay crane hoisting device for lifting large-tonnage containers, comprising a hoisting body, the top of the hoisting body being provided with two damping anti-swing units arranged along its length direction, the damping anti-swing unit comprising a damping ring and an elastic reset assembly, the damping ring being able to perform translational motion at the top of the hoisting body, and during the motion, the damping ring always remains parallel to the plane where the top of the hoisting body is located; the elastic reset assembly is arranged at the top of the hoisting body and is located at the inner ring position of the damping ring, the elastic reset assembly having a pressure part, the pressure part maintaining contact with the inner ring of the damping ring, and when the damping ring is displaced relative to the hoisting body, the damping ring needs to overcome the force applied to it by the pressure part, and the force increases proportionally with the increase in the moving distance of the damping ring.

[0009] Preferably, the elastic reset assembly also includes a stand arranged at the top of the sling body, the stand extends in a direction perpendicular to the sling body, the pressure part is a pressure ring, the pressure ring is coaxially slidably arranged on the stand, the inner diameter of the damping ring is larger than the diameter of the stand, and the pressure ring forms an inclined contact fit with the inner ring of the damping ring.

[0010] Preferably, a coaxial limiting ring is provided on the stand, the limiting ring is located on the top of the pressure ring, and elastic elements distributed along the circumference of the stand are provided between the limiting ring and the pressure ring, forming elastic contact between the pressure rings.

[0011] Preferably, the pressure ring is provided with columns distributed along the circumference of the seat, and the columns slide upward and penetrate the limiting ring.

[0012] Preferably, the limiting ring is coaxially slidably arranged on the stand, the stand is hollow and an oil cylinder is arranged inside it, the output rod of the oil cylinder extends along the height direction of the stand, and a drive ring is arranged on the output rod of the oil cylinder, and the drive ring is transmission-connected to the limiting ring.

[0013] Preferably, the stand is provided with guide grooves distributed along its circumference, the limiting ring is provided with a convex ring coaxial with it, the convex ring is provided with connecting bolts distributed along its circumference, the connecting bolts extend radially along the convex ring, and one end of the connecting bolt passes through the guide groove and is connected to the drive ring.

[0014] Preferably, the inner diameter of the damping ring gradually increases from bottom to top to form a first conical surface, and the outer side of the pressure ring contacts the first conical surface to form an inclined surface fit.

[0015] Preferably, the outer diameter of the pressure ring gradually increases from bottom to top to form a second conical surface, and the inner side of the damping ring contacts the second conical surface to form an inclined surface fit.

[0016] Preferably, the inner diameter of the damping ring gradually increases from bottom to top to form a third conical surface, the outer diameter of the pressure ring gradually increases from bottom to top to form a fourth conical surface, and the third conical surface contacts the fourth conical surface to form an inclined surface fit.

[0017] Preferably, a contact surface between the damping ring and the sling body is provided with balls, and a rolling fit is formed between the damping ring and the sling body.

[0018] Compared with the prior art, the present invention has the following advantages: This application effectively suppresses spreader swing by installing two damping anti-sway units at the top of the spreader body. The damping rings in the two anti-sway damping units work together to form a coordinated anti-sway mechanism. When the spreader body swings due to factors such as lifting, braking, and wind, the damping rings move horizontally relative to the spreader body due to inertia. This relative motion gradually dissipates the energy contained in the spreader body's swing, significantly reducing the swing amplitude.

[0019] The elastic return assembly in this application also cooperates with the damping ring. When the spreader body stops swinging and is at rest, the elastic return assembly guides the damping ring back to its initial position. This ensures that the damping ring begins operating in the optimal initial state each time the spreader swings, thereby continuously and efficiently dissipating the swing energy of the spreader body.

[0020] Compared to existing container spreaders, this application fundamentally solves the problem of swaying during lifting. Existing spreaders often lack efficient energy consumption and reset mechanisms, making swaying difficult to effectively control in complex operating conditions. The design of two damping anti-sway units and an elastic reset assembly in this application provides a reliable and stable anti-sway solution for large-tonnage container lifting, significantly improving operational safety and efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a three-dimensional diagram of an anti-sway quay crane hoisting device for lifting large-tonnage containers according to the present invention.

[0022] Figure 2 The present invention is a cross-sectional view of a damping anti-sway unit in an anti-sway quay crane hoisting device for lifting large-tonnage containers.

[0023] Figure 3 yes Figure 2 A partial enlarged view of point A in the middle.

[0024] Figure 4 yes Figure 2 A partial enlarged view of point B in the middle.

[0025] Figure 5 It is a stereoscopic diagram of a damping ring and an elastic reset assembly in an anti-sway quay crane hoisting device for lifting large-tonnage containers according to the present invention.

[0026] Figure 6 The present invention is a three-dimensional exploded view of an elastic reset component in an anti-sway quay crane hoisting device for lifting large-tonnage containers.

[0027] Figure 7 The present invention is a three-dimensional exploded view of a stand and a cylinder in an anti-sway quay crane hoisting device for lifting large-tonnage containers.

[0028] Figure 8 The present invention is a schematic diagram of a first embodiment of a damping ring and a pressure ring in an anti-sway quay crane hoisting device for lifting large-tonnage containers.

[0029] Figure 9 It is a schematic diagram of a second embodiment of a damping ring and a pressure ring in an anti-sway quay crane hoisting device for lifting large-tonnage containers according to the present invention.

[0030] Figure 10 The present invention is a schematic diagram of a third embodiment of a damping ring and a pressure ring in an anti-sway quay crane hoisting device for lifting large-tonnage containers.

[0031] The numbers in the figure are: 1. sling body; 21. damping ring; 22. elastic reset assembly; 221. pressure part; 222. seat; 2221. guide groove; 223. limiting ring; 2231. convex ring; 224. elastic element; 225. column; 226. cylinder; 227. drive ring; 228. connecting bolt; 23. ball. DETAILED DESCRIPTION

[0032] In order to further understand the features, technical means, specific objectives and functions achieved by the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0033] like Figure 1 and Figure 2 As shown, an anti-swing quay crane hoisting device for lifting large-tonnage containers includes a hoisting body 1, and two damping anti-swing units arranged along the length direction of the hoisting body 1 are provided at the top of the hoisting body 1, and the damping anti-swing unit includes a damping ring 21 and an elastic reset component 22, and the damping ring 21 can perform translational movement at the top of the hoisting body 1, and during the movement, the damping ring 21 always remains parallel to the plane where the top of the hoisting body 1 is located; the elastic reset component 22 is arranged at the top of the hoisting body 1 and is located at the inner ring position of the damping ring 21, and the elastic reset component 22 has a pressure part 221, and the pressure part 221 maintains contact with the inner ring of the damping ring 21. When the damping ring 21 is displaced relative to the hoisting body 1, the damping ring 21 needs to overcome the force applied to it by the pressure part 221, and the force increases proportionally with the increase of the moving distance of the damping ring 21.

[0034] The lower height of a single damping anti-sway unit reduces the overall height of the spreader body 1, and its center of gravity is also lowered accordingly. During lifting and transportation, especially when encountering external disturbances such as wind and vibration, the lower center of gravity makes the spreader body 1 more stable, reduces the risk of sway and tipping, and improves operational safety.

[0035] A single damping ring 21 has a relatively limited ability to dissipate the energy from a spreader's swing. However, two damping rings 21 working together can dissipate this energy from different directions and angles. While one damping ring 21 dissipates energy during spreader swing, the other damping ring 21 also contributes, creating a more powerful combined energy dissipation force. This effectively and rapidly reduces the spreader's swing amplitude and accelerates its return to stability.

[0036] Two anti-sway damping units provide a more balanced and stable anti-sway effect for the spreader. If only one anti-sway damping unit fails or its anti-sway effect is inadequate under certain operating conditions, the spreader's swing will be difficult to control. However, with two units working together, even if one experiences a temporary problem, the other can still maintain a certain degree of anti-sway effect, ensuring the safe continuation of the lifting operation and significantly improving the stability and reliability of the entire anti-sway system.

[0037] Each damping and anti-sway unit consists of a damping ring 21 and an elastic reset assembly 22. The damping ring 21 is capable of smooth translational motion at the top of the spreader body 1. Throughout its motion, the damping ring 21 maintains a stable position parallel to the plane of the top of the spreader body 1. When the spreader body 1 swings due to factors such as lifting, braking, and wind, the damping ring 21 moves horizontally relative to the spreader body 1 due to inertia. This relative motion gradually dissipates the energy contained in the swing of the spreader body 1, thereby significantly reducing the swing amplitude.

[0038] The elastic reset assembly 22 is mounted at the top of the spreader body 1 and positioned within the inner ring of the damping ring 21. The elastic reset assembly 22 includes a pressure portion 221, which maintains close contact with the inner ring of the damping ring 21 at all times. When the spreader body 1 swings due to various complex factors during lifting operations, such as acceleration changes during lifting, start-stop shocks during operation, and external wind interference, causing the damping ring 21 to displace relative to the spreader body 1, the damping ring 21 must overcome the force applied by the pressure portion 221. This force increases in strict proportion to the distance traveled by the damping ring 21. That is, with each additional distance traveled by the damping ring 21, the force applied by the pressure portion 221 increases according to a predetermined ratio. This allows the damping ring 21 to dissipate the spreader's swing energy with extreme efficiency and precision, effectively suppressing the spreader's swing amplitude and significantly improving the stability and safety of large-tonnage container lifting operations.

[0039] like Figure 2 and Figure 3 As shown, the elastic reset assembly 22 also includes a seat 222 arranged at the top of the sling body 1, and the seat 222 extends in a direction perpendicular to the sling body 1. The pressure portion 221 is a pressure ring, and the pressure ring is coaxially slidably arranged on the seat 222. The inner diameter of the damping ring 21 is larger than the diameter of the seat 222, and the pressure ring forms an inclined contact fit with the inner ring of the damping ring 21.

[0040] Balls 23 are provided on the contact surfaces of the damping ring 21 and the pressure ring, and a rolling fit is formed between the damping ring 21 and the pressure ring to reduce wear.

[0041] The stand 222 is mounted at the top of the sling body 1. The pressure portion 221 utilizes a pressure ring structure, coaxially mounted on the stand 222 and freely sliding along the stand 222. The inner diameter of the damping ring 21 is larger than the diameter of the stand 222, allowing ample room for the damping ring 21 to move relative to the stand 222. The pressure ring and the inner ring of the damping ring 21 engage via an inclined surface. The pressure ring transmits force to the damping ring 21 via the inclined surface. When the damping ring 21 moves relative to the sling body 1, the pressure ring increases the force applied to the damping ring 21 in a predetermined proportion based on the distance traveled by the damping ring 21, effectively consuming the swing energy of the sling and effectively suppressing the swing amplitude.

[0042] To further enhance device performance and reduce component wear, balls 23 are installed on the contact surface between damping ring 21 and the pressure ring. The presence of balls 23 transforms the traditional sliding friction between damping ring 21 and the pressure ring into a rolling fit, significantly reducing friction, minimizing component wear, extending the device's service life, and ensuring long-term, stable anti-sway performance.

[0043] like Figure 3 、 Figure 5 、 Figure 6 and Figure 7 As shown, a coaxial limiting ring 223 is provided on the stand 222, and the limiting ring 223 is located on the top of the pressure ring. An elastic element 224 distributed circumferentially along the stand 222 is provided between the limiting ring 223 and the pressure ring, and elastic contact is formed between the pressure rings.

[0044] Between the retaining ring 223 and the pressure ring are elastic elements 224 evenly distributed along the circumference of the stand 222. The elastic elements 224, such as springs, possess excellent elastic deformation capabilities. When installed, one end of the elastic element 224 is tightly connected to the retaining ring 223, while the other end is connected to the pressure ring, creating elastic contact between the pressure ring and the retaining ring 223. When the damping ring 21 moves relative to the sling body 1, causing the pressure ring to slide on the stand 222, the elastic elements 224 undergo corresponding compression or tension deformation. The force generated by this elastic deformation acts on the pressure ring, ensuring more stable and adjustable contact with the inner bevel of the damping ring 21. This precisely applies a force that increases proportionally with the movement of the damping ring 21, effectively dissipating the swing energy of the sling body 1. When the sling body 1 is stationary, the elastic elements 224 assist in resetting the pressure ring and damping ring 21, allowing them to continue their anti-sway function during the next swing.

[0045] like Figure 3 and Figure 6 As shown, the pressure ring is provided with columns 225 distributed along the circumference of the seat 222 , and the columns 225 slide upward and pass through the limiting ring 223 .

[0046] The column 225 is fixedly connected to the pressure ring and slides upward to pass through the limit ring 223. The sliding fit between the column 225 and the limit ring 223 provides a precise guide for the up and down movement of the pressure ring, ensuring that the pressure ring slides smoothly and steadily on the seat 222, preventing the pressure ring from tilting or shaking during movement. This ensures that the pressure ring can continuously and stably maintain good inclined contact with the inner ring of the damping ring 21, enhancing the working stability and reliability of the entire damping anti-sway unit.

[0047] like Figure 3 、 Figure 6 and Figure 7 As shown, the limiting ring 223 is coaxially slidably arranged on the stand 222. The stand 222 is hollow and has a cylinder 226 arranged therein. The output rod of the cylinder 226 extends along the height direction of the stand 222. A driving ring 227 is arranged on the output rod of the cylinder 226. The driving ring 227 is transmission-connected to the limiting ring 223.

[0048] By driving the sliding of the limit ring 223 by the oil cylinder 226, the initial compression of the elastic element 224 can be further adjusted, and the initial force of the pressure ring on the damping ring 21 can be flexibly adjusted to meet the requirements of the anti-swing performance of the sling under different lifting conditions.

[0049] In actual use, the spreader body 1 may encounter a variety of different operating conditions and loads. By adjusting the movement resistance of the damping ring 21 (i.e., the pressure exerted by the pressure ring on the damping ring 21), the anti-sway effect can be optimized according to the specific operating conditions. For example, when the spreader body 1 is lifting a lighter container, the movement resistance is appropriately reduced. Specifically, the cylinder 226 drives the drive ring 227 and the limit ring 223 upward, thereby stretching the elastic element 224. This allows the damping ring 21 to respond more sensitively to the swing of the spreader body 1 and better exert its damping effect. Conversely, when lifting a heavier container, the movement resistance is increased. Specifically, the cylinder 226 drives the drive ring 227 and the limit ring 223 downward, thereby compressing the elastic element 224. This ensures that the damping ring 21 can withstand greater impact and inertial forces, effectively suppressing the spreader's swing.

[0050] like Figure 7 As shown, the stand 222 is provided with a guide groove 2221 distributed along its circumference, the limiting ring 223 is provided with a convex ring 2231 coaxial therewith, and the convex ring 2231 is provided with a connecting bolt 228 distributed along its circumference. The connecting bolt 228 extends radially along the convex ring 2231, and one end of the connecting bolt 228 passes through the guide groove 2221 and is connected to the driving ring 227.

[0051] When the drive ring 227 is driven by an external power source (e.g., the output rod of the oil cylinder 226 disposed within the hollow structure of the stand 222), the drive ring 227 drives the limit ring 223 via the connecting bolt 228. Since the connecting bolt 228 slides within the guide groove 2221, the guide groove 2221 precisely guides and constrains the relative movement between the stand 222 and the limit ring 223, ensuring that the limit ring 223 can only slide smoothly and coaxially along the circumferential direction of the stand 222, following the trajectory defined by the guide groove 2221.

[0052] like Figure 8 As shown, the inner diameter of the damping ring 21 gradually increases from bottom to top to form a first conical surface, and the outer side of the pressure ring contacts the first conical surface to form an inclined surface fit.

[0053] As a first embodiment of the damping ring 21 and the pressure ring, the inner diameter of the damping ring 21 gradually increases from bottom to top, thereby forming a first conical surface. The outer side of the pressure ring contacts the first conical surface of the damping ring 21, and the two fit together to form an inclined surface. When the sling body 1 swings and causes the damping ring 21 to move relative to it, the pressure ring will produce a corresponding force change according to the movement of the damping ring 21 due to the inclined surface fit. As the movement distance of the damping ring 21 increases, the force exerted by the pressure ring on the damping ring 21 increases proportionally, thereby efficiently consuming the energy generated by the swing of the sling and effectively suppressing the swing amplitude of the sling.

[0054] like Figure 9 As shown, the outer diameter of the pressure ring gradually increases from bottom to top to form a second conical surface, and the inner side of the damping ring 21 contacts the second conical surface to form an inclined surface fit.

[0055] As a second embodiment of the damping ring 21 and the pressure ring, the outer diameter of the pressure ring gradually increases from bottom to top, thereby forming a second conical surface. The inner side of the damping ring 21 contacts the second conical surface of the pressure ring, and the two form an inclined surface fit. When the sling body 1 swings and causes the damping ring 21 to move relative to it, based on the characteristics of the inclined surface fit, the pressure ring will produce a corresponding force change according to the movement of the damping ring 21. As the movement distance of the damping ring 21 increases, the force exerted by the pressure ring on the damping ring 21 increases proportionally, thereby efficiently consuming the energy generated by the swing of the sling and effectively suppressing the swing amplitude of the sling.

[0056] like Figure 10 As shown, the inner diameter of the damping ring 21 gradually increases from bottom to top to form a third conical surface, and the outer diameter of the pressure ring gradually increases from bottom to top to form a fourth conical surface. The third conical surface contacts the fourth conical surface to form an inclined surface fit.

[0057] As a third embodiment of the damping ring 21 and the pressure ring, the inner diameter of the damping ring 21 gradually increases from bottom to top to form a third conical surface. The outer diameter of the pressure ring also follows a pattern of gradually increasing from bottom to top to form a fourth conical surface. When the damping ring 21 is in its initial position, the third conical surface of the damping ring 21 is precisely docked with the fourth conical surface of the pressure ring, achieving a tight bevel fit between the surfaces. This matching method not only provides a larger contact area for force transmission between the damping ring 21 and the pressure ring, ensuring uniform and stable force application, but also, during the subsequent swinging process of the sling body 1, as the damping ring 21 undergoes relative displacement, based on the geometric characteristics of the conical surface, the pressure ring can accurately and efficiently output a force that increases proportionally with the movement distance of the damping ring 21, so that the damping ring 21 moves relative to the sling body 1 under the action of this force, thereby effectively suppressing the swinging of the sling body 1.

[0058] like Figure 4 As shown, the contact surface between the damping ring 21 and the sling body 1 is provided with balls 23 , and a rolling fit is formed between the damping ring 21 and the sling body 1 .

[0059] Compared to traditional sliding contact, rolling contact significantly reduces friction between the damping ring 21 and the spreader body 1. This not only makes the damping ring 21's translational motion on the top of the spreader body 1 smoother, enabling it to respond more quickly to the spreader's swing and promptly play its anti-sway role, but also reduces wear between components and extends the service life of the device.

[0060] The above embodiments merely represent one or more embodiments of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of protection of the present invention. It should be noted that a person of ordinary skill in the art may make various modifications and improvements without departing from the spirit of the present invention, and such modifications and improvements fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be subject to the appended claims.

Claims

1. An anti-sway quay crane spreader device for lifting large-tonnage containers, comprising a spreader body, characterized in that: The top of the sling body is provided with two damping and anti-sway units arranged along its length direction, and the damping and anti-sway units include a damping ring and an elastic reset assembly, the damping ring can perform translational movement at the top of the sling body, and during the movement, the damping ring always remains parallel to the plane where the top of the sling body is located; the elastic reset assembly is arranged at the top of the sling body and is located at the inner ring position of the damping ring, the elastic reset assembly has a pressure part, and the pressure part maintains a contact state with the inner ring of the damping ring. When the damping ring is displaced relative to the sling body, the damping ring needs to overcome the force applied to it by the pressure part, and the force increases proportionally with the increase of the movement distance of the damping ring; the elastic reset assembly also includes a stand provided at the top of the sling body, the stand extends in a direction perpendicular to the sling body, the pressure part is a pressure ring, and the pressure ring is coaxially slidably arranged on the stand, the inner diameter of the damping ring is larger than the diameter of the stand, and the pressure ring forms an inclined contact fit with the inner ring of the damping ring.

2. The anti-sway quay crane hoisting device for large-tonnage container lifting according to claim 1, characterized in that: A coaxial limiting ring is provided on the stand, and the limiting ring is located on the top of the pressure ring. Elastic elements distributed along the circumference of the stand are provided between the limiting ring and the pressure ring, and elastic contact is formed between the pressure rings.

3. The anti-sway quay crane hoisting device for large-tonnage container lifting according to claim 2, characterized in that: The pressure ring is provided with columns distributed along the circumference of the seat, and the columns slide upward and pass through the limiting ring.

4. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to claim 2 or 3, characterized in that: The limiting ring is coaxially slidably arranged on the stand. The stand is hollow and has an oil cylinder arranged therein. The output rod of the oil cylinder extends along the height direction of the stand. A driving ring is arranged on the output rod of the oil cylinder. The driving ring is transmission-connected to the limiting ring.

5. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to claim 4, characterized in that: The stand is provided with guide grooves distributed along its circumference, the limiting ring is provided with a convex ring coaxial with it, the convex ring is provided with connecting bolts distributed along its circumference, the connecting bolts extend radially along the convex ring, and one end of the connecting bolt passes through the guide groove and is connected to the drive ring.

6. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to any one of claims 1 to 3, characterized in that: The inner diameter of the damping ring gradually increases from bottom to top to form a first conical surface, and the outer side of the pressure ring contacts the first conical surface to form an inclined surface fit.

7. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to any one of claims 1 to 3, characterized in that: The outer diameter of the pressure ring gradually increases from bottom to top to form a second conical surface, and the inner side of the damping ring contacts the second conical surface to form an inclined surface fit.

8. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to any one of claims 1 to 3, characterized in that: The inner diameter of the damping ring gradually increases from bottom to top to form a third conical surface, the outer diameter of the pressure ring gradually increases from bottom to top to form a fourth conical surface, and the third conical surface contacts the fourth conical surface to form an inclined surface fit.

9. The anti-sway quay crane hoisting device for large-tonnage container hoisting according to any one of claims 1 to 3, characterized in that: The contact surface between the damping ring and the sling body is provided with balls, and a rolling fit is formed between the damping ring and the sling body.

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