Anti-roll stabilizing device for shipborne electric variable-amplitude crane

Abstract

The utility model discloses an anti-roll stabilizing device for a shipborne electric variable-amplitude crane, which comprises an anti-roll arm for connecting a crane jib of the electric variable-amplitude crane with a control tower, two ends of the anti-roll arm are respectively a hinged end hinged with the control tower and a movable end movably connected with the crane jib, and the anti-roll arm can be driven to swing along with the crane jib when the crane jib performs variable-amplitude motion; the suspension arm and the anti-tilting arm are both hinged to an inclined rod of the control tower, and the suspension arm, the anti-tilting arm and the inclined rod form a triangular connecting structure; the suspension arm and the anti-tilting arm are located on the two sides of the inclined rod respectively. Through the cooperation of hinging and moving of the anti-tilting arm, the anti-tilting capacity is enhanced while the free amplitude variation of the suspension arm is guaranteed, the impact load is reduced, the stability is improved, and the service life is prolonged.

Description

TECHNICAL FIELD

[0001] The utility model belongs to electric amplitude change crane technical field, especially relate to shipborne electric amplitude change crane anti-roll stabilizer. BACKGROUND

[0002] When shipborne electric amplitude change crane is working at sea, the boom is easy to produce lateral deviation or even overturning due to ship body shaking, wave impact and load change, which threatens the safety of work. The traditional anti-tilt device mostly adopts rigid support or hydraulic locking mechanism, which has complex structure and is easy to be impacted by dynamic load, resulting in fast component wear and high maintenance cost. Some schemes constrain the boom movement through guide rails, but the sliding friction resistance is large, which is difficult to adapt to frequent amplitude change actions. Some others adopt multi-stage hinged structure, which can relieve stress concentration, but lacks effective limitation on lateral swing. SUMMARY

[0003] The utility model discloses a shipborne electric amplitude change crane anti-roll stabilizer, which overcomes the deficiencies in the prior art. The anti-roll arm is hinged and moved cooperatively to ensure the free amplitude change of the boom, enhance the anti-roll ability and reduce the impact load.

[0004] Technical scheme: To achieve the above object, the shipborne electric amplitude change crane anti-roll stabilizer of the utility model comprises an anti-roll arm connecting the boom of the electric amplitude change crane and the tower, the two ends of the anti-roll arm are respectively a hinged end hinged with the tower and a movable end movably connected with the boom, and the anti-roll arm can be driven to swing when the boom makes amplitude change movement.

[0005] Further, the boom and the anti-roll arm are hinged on the inclined rod of the tower, and the boom, the anti-roll arm and the inclined rod constitute a triangular connection structure.

[0006] Further, the boom and the anti-roll arm are located on the two sides of the inclined rod.

[0007] Further, the hinged end of the anti-roll arm is provided with a hinge shaft, and the anti-roll arm is hinged with the inclined rod through the hinge shaft.

[0008] Further, the movable end of the anti-roll arm is provided with a movable wheel through a wheel shaft, a guide rail extending along the arm length direction is arranged on the boom, and the movable wheel is movably installed on the guide rail.

[0009] Further, the guide rail is a channel steel fixedly installed on the boom, and the groove surface of the channel steel is open for the wheel shaft of the movable wheel to extend into.

[0010] Further, the first end and the tail end of the channel steel are respectively inserted with anti-derailing pins for blocking and limiting the movable wheel.

[0011] Furthermore, the side of the movable wheel is fitted with a number of evenly distributed balls.

[0012] Furthermore, the anti-tilt boom is a telescopic rod structure with a built-in elastic component in the boom body, and the elastic component is used to buffer the impact load when the boom luffs.

[0013] Beneficial effects: This utility model, through the connection method of hinged and movable anti-roll boom, allows the boom to freely change amplitude while restricting its lateral displacement, preventing the boom from overturning laterally due to hull swaying or load changes. It simplifies the complex mechanical constraints of traditional anti-roll devices, reduces structural complexity, and improves reliability. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the overall structure of this utility model;

[0015] Figure 2 This is a three-dimensional structural diagram of the anti-tilt device;

[0016] Figure 3 This is an exploded view of the anti-tilting device. Detailed Implementation

[0017] The present invention will be further described below with reference to the accompanying drawings.

[0018] like Figure 1 , Figure 2 as well as Figure 3 As shown, the shipborne electric luffing crane anti-tilt stabilization device includes an anti-tilt arm 4 connecting the boom 2 of the electric luffing crane 1 to the tower 3. The anti-tilt arm 4 has a hinged end 4a hinged to the tower 3 and a movable end 4b movably connected to the boom 2. The anti-tilt arm 4 can be driven and swing along with the boom 2 during its luffing motion. This invention, through the combination of hinged and movable connection of the anti-tilt arm 4, allows the boom 2 to freely luff while limiting its lateral displacement, preventing lateral overturning of the boom 2 due to ship swaying or load changes. This simplifies the complex mechanical constraints of traditional anti-tilt devices, reduces structural complexity, and improves reliability.

[0019] Both the boom 2 and the anti-tilt arm 4 are hinged to the diagonal brace 30 of the tower 3, forming a triangular connection structure. Utilizing the stability of the triangular structure, the luffing motion of the boom 2 is converted into the coordinated swinging of the anti-tilt arm 4, dispersing the lateral load and reducing local stress concentration on the tower. Simultaneously, the diagonal brace 30 acts as a fulcrum, enhancing overall rigidity and preventing deformation of the tower 3 when the boom 2 swings significantly.

[0020] The boom 2 and anti-tilt boom 4 are located on both sides of the diagonal bar 30, balancing the forces on both sides of the diagonal bar 30, preventing excessive force on one side from causing structural fatigue or fracture, while improving symmetry and reducing vibration and noise caused by eccentric loading.

[0021] The hinge end 4a of the anti-tilt arm 4 is provided with a hinge shaft 5. The anti-tilt arm 4 is hinged to the diagonal bar 30 through the hinge shaft 5. The hinge shaft 5 provides a low-friction rotation fulcrum to ensure that the anti-tilt arm 4 swings smoothly and adapts to the dynamic angle changes of the boom 2.

[0022] The movable end 4b of the anti-tilt arm 4 is equipped with a movable wheel 7 via a wheel axle 6. Correspondingly, a guide rail 8 extending along the arm length direction is provided on the boom 2. The movable wheel 7 is movably mounted on the guide rail 8. The guide rail 8 guides the path of the movable wheel 7, precisely limiting the movement direction of the anti-tilt arm 4, preventing deviation or jamming. The wheel-rail contact reduces sliding friction, improves energy transfer efficiency, and reduces power loss caused by friction.

[0023] The guide rail 8 is a channel steel fixedly installed on the boom 2. Anti-derailment pins 10 are inserted into the first and last ends of the channel steel to prevent and limit the movement of the wheels 7. The opening in the channel steel allows the wheel axle 6 of the wheels 7 to extend into it. The high strength of the channel steel enhances the bending and torsional resistance of the guide rail 8, adapting to the high-frequency vibrations of the shipboard environment. The design of the channel opening enclosing the wheel axle 6 prevents derailment and ensures safety under extreme working conditions.

[0024] In addition to the wheel surface contacting the inner wall of the channel steel, the wheel side may also contact the side wall of the channel steel. Therefore, the wheel side of the movable wheel 7 is fitted with a number of evenly distributed balls 9. The balls 9 convert sliding friction into rolling friction, further reducing resistance.

[0025] The anti-tilt arm 4 is a telescopic rod structure with an internal elastic component 42 on the boom body 41. The elastic component 42 is used to buffer the impact load when the boom 2 changes luffing angle. The elastic component 42 adopts a spring or hydraulic damper to absorb the impact energy during the luffing process, avoid damage to the components caused by rigid collisions, and dynamically adjust the length of the anti-tilt arm 4 to adapt to the force changes of the boom 2 at different luffing angles, thereby improving the system's compliance.

[0026] The above description is only a preferred embodiment of the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A roll stabilisation device for a ship-borne electric luffing crane, characterised in that: The anti-tipping arm (4) is connected between the tower (3) and the boom (2) of the electric luffing crane (1), and has a hinged end (4a) hinged to the tower (3) and a movable end (4b) movably connected to the boom (2), and the anti-tipping arm (4) can be driven to swing when the boom (2) performs luffing movement.

2. A shipboard electrodynamic luffing stability device according to claim 1, characterized in that: The boom (2) and the anti-tipping arm (4) are hinged to the diagonal rod (30) of the tower (3), and the boom (2), the anti-tipping arm (4) and the diagonal rod (30) form a triangular connection structure.

3. A shipboard electrodynamic luffing stability device according to claim 2, characterized in that: The boom (2) and the anti-tipping arm (4) are located on two sides of the diagonal rod (30).

4. The anti-roll stabilizer system for a ship-mounted electro-hoist according to claim 2, characterized in that: The hinged end (4a) of the anti-tipping arm (4) is provided with a hinged shaft (5) in correspondence, and the anti-tipping arm (4) is hinged to the diagonal rod (30) through the hinged shaft (5).

5. The anti-roll stabilizer system for a ship-mounted electro-hoist according to claim 2, characterized in that: The movable end (4b) of the anti-tipping arm (4) is provided with a movable wheel (7) through an axle (6), and a guide rail (8) extending along the length of the boom (2) is provided in correspondence, and the movable wheel (7) is movably installed on the guide rail (8).

6. A shipboard electrodynamic luffing stability device according to claim 5, characterized in that: The guide rail (8) is a channel steel fixedly installed on the boom (2), and the groove surface of the channel steel is open for the axle (6) of the movable wheel (7) to extend into.

7. A shipboard electrodynamic luffing stability device according to claim 6, characterized in that: The first end and the tail end of the channel steel are respectively inserted with anti-derailing pins (10) for blocking and limiting the movable wheel (7).

8. A shipboard electrodynamic luffing stability device according to claim 6, characterized in that: The wheel side surface of the movable wheel (7) is embedded with a plurality of uniformly distributed balls (9).

9. A shipboard electrodynamic luffing crane anti-roll stabilizer according to any one of claims 1 to 8, characterized in that: The anti-tipping arm (4) is a telescopic rod structure with an elastic component (42) embedded in an arm body (41), and the elastic component (42) is used to buffer the impact load when the boom (2) performs luffing movement.

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