A gantry crane with an automatic adjustment structure counterweight

Abstract

This invention discloses a single-arm gantry crane with automatic adjustment of structural counterweight, relating to the field of lifting and hoisting technology. In this design, the main counterweight can be moved both circumferentially and radially along the turntable. Moving the main counterweight circumferentially improves the precision of the crane's adjustment of its position, allowing for more precise adjustment of the counterweight's position based on the weight of the load. Moving the main counterweight radially reduces the distance it travels from the counterweight position to the unloaded position, thus shortening the time required for the counterweight to reach the unloaded position. This allows the crane to restore torque balance as quickly as possible during lifting or unloading, reducing the duration of torque imbalance on the crane during lifting or unloading, thereby extending the time before structural fatigue occurs and improving its service life.

Description

Technical Field

[0001] This invention relates to the field of lifting and hoisting technology, and in particular to a single-arm gantry crane with an automatically adjustable counterweight structure. Background Technology

[0002] Port gantry cranes typically handle cargo in two states: unloaded (the boom is not carrying any cargo) and fully loaded (the boom is carrying cargo). To ensure safe operation, gantry cranes usually have a counterweight structure on the counterweight side to balance the torque generated on the lifting side (when fully loaded, the weight of the cargo creates a torque that causes the crane to tilt forward; the counterweight structure counteracts this tendency by generating a reverse torque). As the crane continuously moves cargo, it frequently switches between unloaded and loaded states. To maintain the crane's balance, adjustments to the counterweight structure are necessary. The position of the crane needs frequent adjustments; however, when the crane boom is unloading or lifting goods, the torque on the lifting side of the crane will change instantaneously. Since the counterweight structure on the counterweight side cannot complete the adjustment of its position in a very short time, the torque on the counterweight side cannot be adjusted to be consistent with the torque on the lifting side in time. This will cause the crane as a whole to be subjected to an unbalanced torque for a short period of time. Repeated torque imbalance will cause the crane structural components to bear alternating stress, thereby accelerating structural fatigue and potentially causing cracks, deformation or other damage. Summary of the Invention

[0003] The purpose of this invention is to provide a single-arm gantry crane with automatic structural counterweight adjustment, which aims to improve the current gantry crane's inability to quickly balance the torque on the counterweight side and the lifting side, resulting in the crane repeatedly bearing unbalanced torque during lifting operations and causing damage to its structure.

[0004] To achieve the above objectives, embodiments of this application provide a single-arm gantry crane with automatically adjustable structural counterweight, comprising: The crane body has a rotatable turntable; the turntable has a lifting side and a counterweight side arranged opposite to each other; The hoisting assembly is installed on the hoisting side; and A main counterweight is disposed on the counterweight side; the main counterweight has a first track extending circumferentially along the turntable and a second track extending radially along the turntable; on the first track and the second track, the main counterweight has counterweight positions at the same location; on the first track, the main counterweight has a first unloaded position, and on the second track, the main counterweight has a second unloaded position; the distance the main counterweight moves from the counterweight position to the first unloaded position is greater than the distance the main counterweight moves from the counterweight position to the second unloaded position.

[0005] In one embodiment, the single-arm gantry crane with automatically adjusting structural counterweight further includes: An auxiliary counterweight is arranged to move radially along the turntable. The auxiliary counterweight has an initial position coaxial with the turntable, a first critical position on the hoisting side, and a second critical position on the counterweight side. The main counterweight moves along the second trajectory from the counterweight position to the second unloaded position, driving the auxiliary counterweight to move from the initial position to the first critical position, and then from the first critical position back to the initial position; The main counterweight moves along the second trajectory from the second unloaded position to the counterweight position, driving the auxiliary counterweight to move from the initial position to the second critical position, and then from the second critical position back to the initial position.

[0006] In one embodiment, the single-arm gantry crane with automatically adjusting structural counterweight further includes: A support rod is coaxially rotatably mounted on the turntable; the main counterweight is radially movable along the turntable and arranged on the support rod, so that the main counterweight has a second trajectory on the turntable; an auxiliary counterweight is radially movable along the turntable and arranged on the support rod, so that the auxiliary counterweight moves between the initial position, the first critical position, and the second critical position; and A circumferential drive member, at least partially disposed on the support rod, is used to drive the support rod to move circumferentially along the turntable so that the main counterweight has the first trajectory on the turntable.

[0007] In one embodiment, the single-arm gantry crane with automatically adjustable counterweight structure further includes a radial drive component; The radial drive unit drives the main counterweight to move from the counterweight position along the second trajectory to the second unloaded position, and simultaneously drives the auxiliary counterweight to move from the initial position to the first critical position, and then from the first critical position back to the initial position; The radial drive unit drives the main counterweight to move from the second unloaded position along the second trajectory to the counterweight position, and simultaneously drives the auxiliary counterweight to move from the initial position to the second critical position, and then from the second critical position back to the initial position; In one embodiment, the radial drive includes: A first cavity is disposed within the supporting rod. A first piston is movably disposed within the first cavity, and the first piston divides the first cavity into a first sub-cavity and a second sub-cavity. The first piston extends at least partially outward from the first cavity for connection with the main counterweight. A second cavity is provided on the bearing rod, and a second piston is movable within the second cavity, which divides the second cavity into a third sub-cavity and a fourth sub-cavity; the second piston extends at least partially outward from the second cavity for connection with the auxiliary counterweight; both the first cavity and the second cavity are filled with a liquid medium. A pump assembly for driving the liquid medium to flow between the first sub-cavity, the second sub-cavity, the third sub-cavity, and the fourth sub-cavity.

[0008] In one embodiment, the pump assembly includes: A first tube has a first end and a second end, the first end communicating with a first sub-cavity, and the second end having a first sub-end and a second sub-end communicating with a third sub-cavity and a fourth sub-cavity; and The second tube has a third end and a fourth end, the third end being connected to the second sub-cavity, and the fourth end having a third sub-end and a fourth sub-end connected to the third sub-cavity and the fourth sub-cavity; Solenoid valves are respectively located at the first sub-end, the second sub-end, the third sub-end, and the fourth sub-end; A liquid pump is provided in the first pipe and / or the second pipe.

[0009] In one embodiment, the single-arm gantry crane with automatic adjustable counterweight structure further includes a magnetic suction element disposed on the bearing rod; The magnetic attractor is used to apply a magnetic force to the main counterweight in the same direction as the main counterweight's movement, so as to drive the main counterweight to move.

[0010] In one embodiment, the magnetic attractor includes: A first transmission component, wherein the auxiliary counterweight moves from the initial position to the first critical position, driving the rotary switch of the first magnetic base to rotate and opening the first magnetic base; the auxiliary counterweight moves from the first critical position to the initial position, driving the rotary switch of the first magnetic base to rotate and closing the first magnetic base; and The second transmission component, wherein the auxiliary counterweight moves from the initial position to the second critical position, thereby driving the rotary switch of the second magnetic base to rotate and opening the second magnetic base; the auxiliary counterweight moves from the second critical position to the initial position, thereby driving the rotary switch of the second magnetic base to rotate and closing the second magnetic base.

[0011] In one embodiment, the single-arm gantry crane with automatically adjusting structural counterweight further includes: A first transmission component, wherein the auxiliary counterweight moves from the initial position to the second critical position, driving the rotary switch of the first magnetic base to rotate and opening the first magnetic base; the auxiliary counterweight moves from the second critical position to the initial position, driving the rotary switch of the first magnetic base to rotate and closing the first magnetic base; and The second transmission component, wherein the auxiliary counterweight moves from the initial position to the first critical position, drives the rotary switch of the second magnetic base to rotate, and opens the second magnetic base; the auxiliary counterweight moves from the first critical position to the initial position, drives the rotary switch of the second magnetic base to rotate, and closes the second magnetic base.

[0012] In one embodiment, the circumferential drive includes: The motor is mounted on one end of the support rod along its length; and The first gear is driven by the motor; The gear system is located on the inner sidewall of the turntable and is used to mesh with the first gear.

[0013] Compared with existing technologies, the beneficial effects of the automatic adjustment structural counterweight single-arm gantry crane of this invention are as follows: The main counterweight in this solution can move both circumferentially and radially along the turntable. Moving the main counterweight circumferentially improves the precision of the single-arm gantry crane's adjustment of the main counterweight's position, allowing for more precise adjustment of the main counterweight's position according to the weight of the goods to be lifted. Moving the main counterweight radially reduces the distance it travels from the counterweight position to the unloaded position, thus shortening the time it takes for the main counterweight to reach the unloaded position. This allows the single-arm gantry crane to restore torque balance as quickly as possible during lifting or unloading, reducing the duration of torque imbalance on the single-arm gantry crane during lifting or unloading, thereby extending the time before structural fatigue occurs and improving its service life. Attached Figure Description

[0014] Figure 1 This is a front view schematic diagram of the overall structure of a single-arm gantry crane according to an embodiment of the present invention; Figure 2 This is a top view schematic diagram of the overall structure of a single-arm gantry crane according to an embodiment of the present invention; Figure 3 This is a schematic diagram showing the main counterweight in the first unloaded position when the hoisting side of the present invention is unloaded; Figure 4This is a schematic diagram showing the main counterweight in its counterweight position when the object is being hoisted from the side. Figure 5 This is a schematic diagram showing the main counterweight in the second unloaded position when the hoisting side of the present invention is unloaded; Figure 6 This is a schematic diagram of the internal structure of the turntable of the present invention; Figure 7 This is a schematic diagram showing the main counterweight of the present invention in the counterweight position, the first unloaded position, and the second unloaded position. Figure 8 This is a schematic diagram showing the installation relationship of the load-bearing rod, main counterweight, and auxiliary counterweight of the present invention; Figure 9 This is a cross-sectional view of the bearing rod of the present invention. Figure 10 This is a schematic diagram showing the arrangement relationship between the first magnetic base and the second magnetic base according to another embodiment of the present invention; Figure 11 For the present invention Figure 9 Another structural diagram from a different perspective; Figure 12 This is a schematic diagram of the structure of the first transmission component and the second transmission component according to another embodiment of the present invention; Figure 13 This is a schematic diagram of the magnetic suction component of the present invention, which does not exhibit magnetic force externally; Figure 14 This is a schematic diagram showing the magnetic force state of the magnetic suction component of the present invention.

[0015] In the diagram: 1. Crane body; 11. Turntable; 111. Lifting side; 112. Counterweight side; 113. Mounting cavity; 2. Lifting components; 3. Main counterweight; 31. Counterweight position; 32. First unloaded position; 33. Second unloaded position; 4. Auxiliary counterweights; 5. Bearing rod; 6. Circumferential drive component; 61. Motor; 62. First gear; 63. Gear system; 7. Radial drive component; 71. First cavity; 711. First sub-cavity; 712. Second sub-cavity; 72. First piston; 73. Second cavity; 731. Third sub-cavity; 732. Fourth sub-cavity; 74. Second piston; 75. Pump assembly; 751. First pipe; 752. Second pipe; 753. Solenoid valve; 754. Liquid pump; 8. Magnetic suction element; 81. First magnetic base; 82. Second magnetic base; 83. Housing; 84. Magnet; 85. Non-magnetic component; 9. Transmission assembly; 91. First transmission component; 911. First transmission cylinder; 912. First transmission piston; 913. First transmission rack; 914. First transmission gear; 92. Second transmission component; 921. Second transmission cylinder; 922. Second transmission piston; 923. Second transmission rack; 924. Second transmission gear. Detailed Implementation

[0016] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0017] In the description of this invention, it should be understood that the terms "upper," "lower," "left," "right," "front," "rear," "top," and "bottom," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as blocking the invention. It should be understood that the terms "first," "second," etc., are used in this invention to describe various information, but this information should not be limited to these terms. These terms are only used to distinguish information of the same type from each other. For example, without departing from the scope of this invention, "first" information can also be referred to as "second" information, and similarly, "second" information can also be referred to as "first" information.

[0018] When handling cargo, port gantry cranes typically operate in two states: unloaded (the boom is not carrying any cargo) and fully loaded (the boom is carrying cargo). To ensure safe operation, gantry cranes usually have a counterweight structure on the counterweight side to balance the torque generated on the lifting side (when fully loaded, the weight of the cargo creates a torque that causes the crane to tilt forward; the counterweight structure counteracts this tendency by generating a reverse torque). As the crane continuously handles cargo, it frequently switches between unloaded and loaded states. To maintain the crane's balance, the position of the counterweight structure needs frequent adjustments. When a crane unloads cargo, the overturning moment on the lifting side will decrease to a certain extent in a very short time. After the crane finishes unloading the cargo and adjusts the angle of the turntable, it will lift the cargo again. This process will last for a certain period of time. During this period of time, an unbalanced moment will be generated between the lifting side and the counterweight side of the crane. Therefore, it is necessary to adjust the moment on the counterweight side after the crane body unloads the cargo and before lifting the new cargo, so that the counterweight side and the lifting side can maintain a balanced state as much as possible before the crane re-lifts the cargo.

[0019] However, when a crane's boom is unloading or lifting goods, the torque on the lifting side of the crane changes instantaneously. Since the counterweight structure on the counterweight side cannot adjust its position in a very short time, the torque on the counterweight side cannot be adjusted to match the torque on the lifting side in time. This causes the entire crane to be subjected to an unbalanced torque for a short period of time. Repeated torque imbalance causes the crane's structural components to be subjected to alternating stress, thereby accelerating structural fatigue and potentially causing cracks, deformation, or other damage.

[0020] Reference Figures 1-14 As shown in the figure, this application proposes a single-arm gantry crane with an automatically adjustable counterweight, including a crane body 1, a lifting assembly 2, and a main counterweight 3; wherein, the crane body 1 has a rotatable turntable 11, and a vertically extending support column on the crane body 1, the turntable 11 is coaxially rotatably mounted on the upper surface of the support column, and the support column may be equipped with a power mechanism (such as a rotary motor) for driving the turntable 11 to rotate relative to the support column; by rotating the turntable 11, the goods lifted by the lifting assembly 2 can be transferred between two points (goods stacking point and unloading point); as Figure 2 As shown, the turntable 11 has a lifting side 111 and a counterweight side 112 arranged opposite to each other, as... Figure 2 As shown, the connection between the support column and the turntable 11 forms a fulcrum, that is, one side of the fulcrum is the hoisting side 111 and the other side is the counterweight side 112. If the torque applied to the fulcrum by the hoisting side 111 and the counterweight side 112 is unbalanced, the crane body 1 may overturn towards the hoisting side and the counterweight side.

[0021] In this embodiment, the lifting assembly 2 is installed on the lifting side 111 of the turntable 11. The lifting assembly 2 includes a boom, a cable system, and a hook, etc. (a tension sensor is provided at the connection between the hook and the cable, and the tension sensor is electrically connected to the control system located in the cab to detect the weight of the lifted goods, thereby calculating the magnitude of the overturning moment generated by the lifting side 111). The weight of the goods lifted by the lifting assembly 2 acts on the lifting side 111 and applies a torque to the turntable 11. The main counterweight 3 applies an equal torque to the turntable 11, thereby balancing the forces on the turntable 11 and ensuring that the crane body 1 will not overturn. In this solution, since the installation position of the lifting assembly 2 relative to the turntable 11 is fixed, The point of application of the force exerted on the turntable 11 by the hoisted goods is fixed. The only change on the hoisting side 111 is the weight of the hoisted goods. The weight of the main counterweight 3 on the counterweight side 112 remains constant. The only variable is the vertical distance between the center of gravity of the main counterweight 3 and the fulcrum (that is, the lever arm of the main counterweight 3's own weight). By adjusting the vertical distance between the main counterweight 3 and the fulcrum (adjusting the lever arm of the main counterweight 3's own weight relative to the fulcrum), the torque applied on the counterweight side 112 is adjusted. This balances and cancels out the torque applied on the hoisting side 111 when hoisting different goods from the hoisting assembly 2, ensuring the balance and stability of the crane body 1 (preventing overturning).

[0022] In this embodiment, the greater the weight of the goods lifted by the lifting assembly 2, the greater the overturning moment generated by the lifting side 111. Therefore, it is necessary to increase the vertical distance (lever arm) between the main counterweight 3 and the fulcrum in sync to increase the balancing moment generated by the weight of the main counterweight 3 itself. This can balance the overturning moment exerted by the goods lifted by the lifting assembly 2 on the lifting side 111, and maintain the balance and stability of the turntable 11 and the crane body 1.

[0023] In this embodiment, as Figures 3-5 As shown, the main counterweight 3 can move circumferentially along the turntable 11 and form a first trajectory; the main counterweight 3 can also move radially along the turntable 11 and form a second trajectory; as shown... Figure 3 As shown, assuming that the lifting assembly 2 is not carrying any goods, the main counterweight 3 is in the following position: Figure 3 The position shown is the first unloaded position 32. At this time, the torques applied to the fulcrum by the lifting side 111 and the counterweight side 112 are kept in balance (since the lifting assembly 2 itself has a certain weight, when the crane is not lifting any goods, the center of gravity of the main counterweight 3 also needs to maintain a certain distance from the fulcrum in order to balance the overturning torque applied to the lifting side 111 by the lifting assembly 2 itself). Figure 3 As shown, the center of gravity lever arm of the main counterweight 3 is h1 at this time; as Figure 4As described above, when the crane body 1 begins to lift goods, the main counterweight 3 is driven to move along the circumference of the turntable 11 at a certain angle (i.e., the first trajectory), thereby increasing the vertical distance between the main counterweight 3 and the fulcrum (the lever arm of the center of gravity of the main counterweight 3), and the magnitude of the vertical distance between the main counterweight 3 and the fulcrum depends on the weight of the goods being lifted; such as Figure 4 As shown, at this time, the main counterweight 3 is in counterweight position 31, so that the overturning moment of the lifting side 111 and the balancing moment of the counterweight side 112 are consistent, thereby ensuring the balance and stability of the crane body 1; when the lifting assembly 2 rotates a certain angle with the turntable 11 and unloads the hoisted goods, the overturning moment of the lifting side 111 disappears. At this time, the position of the main counterweight 3 needs to be adjusted so that the moments of the lifting side 111 and the counterweight side 112 can be kept in balance, such as Figure 5 As shown, at this time, the main counterweight 3 is driven to move a certain distance along the radial direction of the turntable 11 (that is, the second trajectory), so that the lever arm of the center of gravity of the main counterweight 3 is h2. It can be understood that after the unloading of the goods is completed, if the torque of the lifting side 111 and the counterweight side 112 of the crane body 1 is balanced, then h2 and h1 should be consistent, so that the balancing torque applied by the main counterweight 3 on the counterweight side 112 is consistent with the balancing torque applied by the counterweight side 112 before the crane body 1 starts the lifting operation.

[0024] In this embodiment, when the lifting assembly 2 unloads the cargo, in order to keep the balancing torque of the counterweight side 112 and the overturning torque of the lifting side 111 consistent, there are two methods: The first method: the main counterweight 3 can be moved in the opposite direction of the circumference of the turntable 11 to a position such that... Figure 3 The position shown; Alternatively, the main counterweight 3 can be moved radially along the turntable 11 to the position shown. Figure 5 The position shown; both methods can achieve torque balance between the lifting side 111 and the counterweight side 112 of the crane body 1 after the goods are unloaded; as shown Figure 7 As shown, the first method is used to make the main counterweight 3... Figure 4 The counterweight position 31 shown is moved to Figure 3 When the first unloaded position 32 is in the middle, its movement distance is S1, while the second method is used to make the main counterweight 3 move from Figure 4 The counterweight position 31 shown is moved to Figure 5 When the second empty position 33 is in the middle, its movement distance is S2; as Figure 7As shown, when the center of gravity lever arm of the main counterweight 3 is the same, the trajectory of the main counterweight 3 moving in the first method is an arc, while the trajectory of the main counterweight 3 moving in the second method is a straight line. Obviously, S1 is greater than S2. Therefore, when the main counterweight 3 moves at the same speed, the adjustment of the position of the main counterweight 3 using the second method requires less time (while the first method requires more time). It is understandable that since the unloading of the cargo by the lifting assembly 2 is completed instantaneously, the overturning moment of the lifting side 111 can be reduced instantly to the state when the crane body 1 is unloaded. However, the adjustment of the position of the main counterweight 3 on the counterweight side 112 cannot be completed instantaneously, which causes the crane body 1 to be subjected to an unbalanced moment generated between the counterweight side 112 and the lifting side 111 for a relatively short period of time. In this embodiment, the second adjustment method is adopted, which can shorten the time required for the main counterweight 3 to be adjusted to the required position as much as possible, thereby shortening the load on the crane body 1 after the lifting assembly 2 unloads the cargo. The duration of the unbalanced torque from the lifting side 111 and the counterweight side 112; when the crane body 1 frequently performs the lifting of goods, although the shortened time mentioned above is limited, the repeated execution of the above process by the crane body 1 will cause the aforementioned short time periods to accumulate and superimpose. Therefore, throughout the entire service life of the crane body 1, the duration of the unbalanced torque from the counterweight side 112 and the lifting side 111 that the crane body 1 bears during operation will be greatly reduced. This is to minimize the risk of repeated torque imbalance causing alternating stress on the crane structural components, thereby accelerating structural fatigue.

[0025] In this embodiment, the main counterweight 3 is driven only when the crane body 1 begins to perform cargo lifting (that is, when it transitions from idle to working). Figure 3 The position shown is adjusted along the first trajectory to the desired position, thereby enabling the counterweight side 112 to generate the same torque as the lifting side 111, ensuring the balance and stability of the crane body 1. During a wave of cargo lifting operations, the crane body 1 frequently performs lifting and unloading procedures. In order to shorten the duration of the unbalanced torque generated between the counterweight side 112 and the lifting side 111 when the crane body 1 is lifting and unloading cargo (to avoid structural fatigue of the crane body 1 due to unbalanced torque during repeated operations), the main counterweight 3 is driven to move radially along the turntable 11 when the crane body 1 performs frequent cargo lifting and unloading, thereby adjusting the torque of the lifting side 111 and the counterweight side 112 and keeping them balanced.

[0026] This can be understood as follows: When the crane body 1 is unloaded and the torques of the lifting side 111 and the counterweight side 112 are balanced, the main counterweight 3 is driven to move and adjust along the first trajectory, thereby adjusting the main counterweight 3 to the required position. This operation is only applicable before the crane body 1 performs a certain wave of cargo lifting (the cargo to be lifted in this wave has the same weight). This allows for more precise adjustment of the position of the main counterweight 3 based on the weight of the cargo being lifted. For example, when the crane body 1 is initially unloaded (the torques of the lifting side 111 and the counterweight side 112 are balanced), the main counterweight 3 is adjusted to the required position (i.e., the weight of the cargo being lifted) based on the weight of the cargo being lifted. When the center of gravity lever arm parameter of the main counterweight 3 is constant, and the main counterweight 3 moves at a constant speed, the adjustment range of the lever arm of the center of gravity of the main counterweight 3 is less when it moves the same distance along the first trajectory than when it moves the same distance along the second trajectory. Therefore, a more precise adjustment of the lever arm of the center of gravity of the main counterweight 3 can be achieved. This is because the adjustment process of the lever arm of the center of gravity of the main counterweight 3 along the first trajectory is more controllable than that along the second trajectory, so as to avoid the situation where the main counterweight 3 moves too fast and misses the required position, requiring readjustment.

[0027] Reference Figures 3-5As shown in one embodiment of this application, the single-arm gantry crane with automatic adjustment of structural counterweight also includes an auxiliary counterweight 4. The auxiliary counterweight 4 is arranged to move radially along the turntable 11. The auxiliary counterweight 4 has an initial position coaxial with the turntable 11, a first critical position located on the lifting side 111, and a second critical position located on the counterweight side 112. When the crane body 1 is performing a lifting operation and continues to lift goods after unloading, the auxiliary counterweight 4 is in the initial position. After the lifting assembly 2 unloads the goods (the overturning moment of the lifting side 111 decreases instantaneously), it is necessary to adjust the balancing moment of the counterweight side 112. In order to make the balancing moment of the counterweight side 112 consistent with the overturning moment of the lifting side 111 in the shortest possible time, in this embodiment, the main counterweight 3 is driven to move from the counterweight position 31 to the second unloaded position 33 along the second trajectory. At the same time, the synchronous drive is in the initial position. The auxiliary counterweight 4 moves synchronously toward the lifting side 111. During this process, the main counterweight 3 moves toward the second unloaded position 33 to reduce the balancing torque applied by the counterweight side 112, and the auxiliary counterweight 4 moves toward the lifting side 111 to compensate for the overturning torque reduced by the unloading of the cargo on the lifting side 111. Thus, during the initial period after unloading the cargo, the lifting assembly 2 ensures that the overturning torque of the lifting side 111 and the torque of the counterweight side 112 do not have an excessive difference. As both the main counterweight 3 and the auxiliary counterweight 4 move toward the lifting side 111, the torques of the counterweight side 112 and the lifting side 111 can reach a balanced state in a shorter time. Compared to simply driving the main counterweight 3 toward the lifting side 111, the time required for the torques applied by the lifting side 111 and the counterweight side 112 at the fulcrum to reach a balanced state after the cargo is unloaded can be significantly shortened.

[0028] In this embodiment, when the auxiliary counterweight 4 moves radially along the turntable 11 to the first critical position, it is then driven to move in the opposite direction toward the initial position, while the main counterweight 3 continues to move toward the hoisting side 111, so that when the auxiliary counterweight 4 moves back to the initial position, the main counterweight 3 moves to the second unloaded position 33. It can be understood that the first critical position can be defined as the position when the auxiliary counterweight 4 moves to the first critical position (at which point the main counterweight 3 is in...). The first critical position in this embodiment is not a fixed point. As long as the goods are unloaded from the lifting assembly 2 and the auxiliary counterweight 4, and the balance torque of the counterweight side 112 (provided by the main counterweight 3) tends to be consistent or close, the first critical position is determined by the position of the auxiliary counterweight 4. When the goods are unloaded from the lifting assembly 2 and the main counterweight moves toward the lifting side 111 (the torque of the counterweight side 112 gradually decreases), the auxiliary counterweight 4 also moves from the initial position toward the lifting side 111 (so that the torque of the lifting side 111 gradually increases after the goods are unloaded). This can shorten the time required for the torques of the lifting side 111 and the counterweight side 112 to reach equilibrium (thereby reducing the time when the crane body 1 is subjected to unbalanced torque). As the main counterweight 3 continues to move toward the second empty position 33 (the torque of the counterweight side 112 continues to decrease), the auxiliary counterweight 4 is controlled to move toward the lifting side 111 to the farthest position. When the first critical position is reached, it is driven to rotate in the opposite direction (at this time, the torque of the lifting side 111 also begins to decrease) so that it moves back to the initial position (at this time, the overturning torque of the auxiliary counterweight 4 on the lifting side 111 is zero). When the auxiliary counterweight 4 moves back to the initial position, the main counterweight 3 moves to the second unloaded position 33. At this time, the lifting side 111 and the counterweight side 112 of the crane body 1 achieve the final balance adjustment (the torques of the lifting side 111 and the counterweight side 112 are consistent).

[0029] In this embodiment, when the turntable 11 of the crane body 1 rotates at a certain angle and begins to continue lifting goods, the overturning moment of the lifting side 111 will increase to a certain level in a very short time, while the moment of the counterweight side 112 is still at a relatively small level. This drives the main counterweight 3 to move from the second unloaded position 33 to the counterweight position 31, and simultaneously drives the auxiliary counterweight 4, which is in the initial position, to move from the initial position to the counterweight side 112. That is, both the main counterweight 3 and the auxiliary counterweight 4 move towards the counterweight side 112. During this process, the movement of the main counterweight 3 towards the counterweight side 112 is used to increase the balancing moment applied by the counterweight side 112, while the movement of the auxiliary counterweight 4... The main counterweight 3 and auxiliary counterweight 4 move towards the counterweight side 112 to supplement the torque of the counterweight side 112 together with the main counterweight 3. This ensures that during the initial period after the lifting assembly 2 lifts the goods and begins to move, the overturning torque of the lifting side 111 and the torque of the counterweight side 112 do not have an excessive difference. As both the main counterweight 3 and auxiliary counterweight 4 move towards the counterweight side 112, the torques of the counterweight side 112 and the lifting side 111 can reach a balanced state in a shorter time. Compared to simply driving the main counterweight 3 towards the counterweight position 31, this significantly shortens the time required for the torques applied to the fulcrum by the lifting side 111 and the counterweight side 112 to balance after the goods are lifted.

[0030] In this embodiment, when the auxiliary counterweight 4 moves radially along the turntable 11 to the second critical position, it is then driven to move in the opposite direction toward the initial position, while the main counterweight 3 continues to move toward the counterweight position 31, so that when the auxiliary counterweight 4 moves back to the initial position, the main counterweight 3 moves to the counterweight position 31. It can be understood that the second critical position can be defined as the point at which the auxiliary counterweight 4 moves to the second critical position (at which point the main counterweight 3 is in the counterweight position 31 and the second unloaded position). At a certain point between positions 33, the overturning moment of the lifting side 111 (provided jointly by the lifting assembly 2 and the lifted cargo) and the balancing moment of the counterweight side 112 (provided jointly by the main counterweight 3 and the auxiliary counterweight 4) tend to be consistent or close; the second critical position in this embodiment is also not a fixed point, as long as when the lifting assembly 2 lifts the cargo, and the main counterweight 3 moves towards the counterweight position 31 (the moment of the counterweight side 112 gradually increases), the auxiliary counterweight 4 also moves synchronously from the initial position. By moving the counterweight side 112 (the torque on the counterweight side 112 increases faster than if only the main counterweight 3 were moved towards the counterweight position 31), the time required for the torques on the lifting side 111 and the counterweight side 112 to reach equilibrium can be shortened (thus reducing the time the crane body 1 is subjected to unbalanced torque); and as the main counterweight 3 continues to move towards the counterweight position 31 (the torque exerted by the main counterweight 3 on the counterweight side 112 continues to increase), the auxiliary counterweight 4 is controlled to move towards the counterweight side 112 to its maximum position. When at the far position (i.e. the second critical position), it is driven to rotate in the opposite direction (gradually reducing the torque of the auxiliary counterweight 4 on the counterweight side 112) until it moves back to the initial position (at this time, the torque of the auxiliary counterweight 4 on the counterweight side 112 is zero). When the auxiliary counterweight 4 moves back to the initial position, the main counterweight 3 moves to the counterweight position 31. At this time, the lifting side 111 and the counterweight side 112 of the crane body 1 achieve the final balance adjustment (the torques of the lifting side 111 and the counterweight side 112 are consistent).

[0031] In this embodiment, by setting an auxiliary counterweight 4 and moving it radially along the turntable 11, it is positioned at the center of the turntable 11, and at a first critical position on the lifting side 111 and a second critical position on the counterweight side 112. This significantly shortens the time required for the torques on the lifting side 111 and the counterweight side 112 of the crane body 1 to reach equilibrium when unloading or lifting goods. This reduces the time the crane body 1 is subjected to unbalanced torque, minimizes structural fatigue caused by unbalanced torque, and improves its service life.

[0032] Reference Figure 6As shown, in one embodiment of this application, the single-arm gantry crane with automatic adjustable structural counterweight further includes a bearing rod 5 and a circumferential drive component 6; wherein, the bearing rod 5 is coaxially rotatably mounted within the turntable 11, as shown... Figure 6 As shown, the turntable 11 has a mounting cavity 113, and the main counterweight 3, auxiliary counterweight 4, and bearing rod 5 are all located within the mounting cavity 113. For example, an annular groove can be provided on the circumferential inner wall of the mounting cavity 113, allowing the bearing rod 5 to be rotatably and slidably fitted into the groove at both ends along its length, thereby achieving coaxial rotation of the bearing rod 5 within the mounting cavity 113. Figure 6 As shown, the circumferential drive component 6 includes a motor 61 (fixedly mounted on the support rod 5), a first gear 62 coaxially fitted with the shaft of the motor 61, and a gear system 63 provided on the inner side wall of the mounting cavity 113. When the motor 61 starts, the meshing of the first gear 62 and the gear system 63 achieves the effect of driving the support rod 5 to rotate circumferentially within the turntable 11. It can be understood that the operator controls the operation of the motor 61 through the controller in the cab on the crane body 1, such as the start and stop of the motor 61 and the rotation angle of the motor 61.

[0033] In this embodiment, in order to make the torque applied to the fulcrum by the counterweight side 112 of the crane body 1 more balanced, two main counterweights 3 can be provided, such as... Figures 3-5 As shown, the two main counterweights 3 are symmetrically arranged, and consequently, there are also two auxiliary counterweights 4 and two load-bearing rods 5. This arrangement allows the two main counterweights 3 to move synchronously when the torque on the counterweight side 112 is adjusted, resulting in a more balanced torque on the crane body 1 from the counterweight side 112. It should be noted that the cooperating main counterweights 3, auxiliary counterweights 4, load-bearing rods 5, and circumferential drive components 6 form a group. When two groups of the above structures are provided, the two groups are arranged at intervals along the height direction of the crane body 1 (e.g., ...). Figure 6 As shown in the figure, this ensures that the movement of the main counterweight 3 and the auxiliary counterweight 4 in the two groups will not interfere with each other.

[0034] It is understandable that the main counterweight 3 is mounted on the support rod 5, moving radially along the turntable 11. Thus, when the support rod 5 rotates coaxially relative to the turntable 11 under the action of the circumferential drive member 6, it drives the main counterweight 3 to move along the first trajectory (i.e., the circumferential direction of the turntable 11). When the main counterweight 3 moves radially along the support rod 5, it drives the main counterweight 3 to move along the second trajectory (i.e., the radial direction of the turntable 11). For example, as... Figure 8As shown, the support rod 5 is provided with sliding holes (the sliding holes are not labeled in the figure) for sliding assembly of the main counterweight 3 and the auxiliary counterweight 4. The main counterweight 3 and the auxiliary counterweight 4 are respectively housed in the corresponding sliding holes, and the side walls of the main counterweight 3 and the auxiliary counterweight 4 are slidably assembled with the side plates of the sliding holes (the contact parts of the main counterweight 3 and the auxiliary counterweight 4 with the sliding holes are provided with sliders, and the corresponding positions of the side walls of the sliding holes are provided with sliding grooves, thereby realizing the sliding assembly of the main counterweight 3 and the auxiliary counterweight 4 on the support rod 5).

[0035] Reference Figure 8 , Figure 9 As shown in one embodiment of this application, the single-arm gantry crane with automatic adjustment of structural counterweight further includes a radial drive member 7; the radial drive member 7 is used to drive the main counterweight 3 to move from the counterweight position 31 along the second trajectory to the second unloaded position 33, and in the process of driving the main counterweight 3 to move to the second unloaded position 33, it simultaneously drives the auxiliary counterweight 4 to move from the initial position to the first critical position, and then from the first critical position to the initial position in the opposite direction; that is, while the radial drive member 7 drives the main counterweight 3 to move from the counterweight position 31 to the second unloaded position 33, it also simultaneously drives the auxiliary counterweight 4 to move back to the initial position.

[0036] It is understandable that when the radial drive 7 drives the main counterweight 3 to move from the second unloaded position 33 to the counterweight position 31, it simultaneously drives the auxiliary counterweight 4 to move from the initial position to the second critical position, so that when the main counterweight 3 moves to the counterweight position 31, the radial drive 7 drives the auxiliary counterweight 4 to move back to the initial position.

[0037] Reference Figure 9 As shown, in one embodiment of this application, the radial drive member 7 includes a first cavity 71, a second cavity 73, and a pumping assembly 75; wherein, the first cavity 71 and the second cavity 73 are both disposed on the support rod 5, that is, both are integrated into the interior of the support rod 5 (e.g., Figure 9As shown), a first piston 72 is movable within a first cavity 71, dividing the first cavity 71 into a first sub-cavity 711 and a second sub-cavity 712. The first piston 72 includes a piston part and a piston rod, with one end of the piston rod extending outward from the first cavity 71 for fixed connection with the main counterweight 3, thereby achieving synchronous movement between the first piston 72 and the main counterweight 3. A second piston 74 is provided within a second cavity 73, dividing the second cavity 73 into a third sub-cavity 731 and a fourth sub-cavity 732. The second piston 74 includes... The piston part and piston rod have one end of the piston rod extending outward into the second cavity 73 for fixed connection with the auxiliary counterweight 4, thereby achieving synchronous movement between the second piston 74 and the auxiliary counterweight 4; both the first cavity 71 and the second cavity 73 are filled with a liquid medium, which can be hydraulic oil, for example; the pump assembly 75 is used to drive the liquid medium to flow between the first sub-cavity 711, the second sub-cavity 712, the third sub-cavity 731 and the fourth sub-cavity 732, thereby achieving the effect of synchronously driving the main counterweight 3 and the auxiliary counterweight 4 to move.

[0038] In this embodiment, as Figure 9 As shown, when the main counterweight 3 moves from the counterweight position 31 to the second unloaded position 33, the pumping assembly 75 drives the liquid medium in the third sub-cavity 731 to move into the second sub-cavity 712, and the liquid medium in the first sub-cavity 711 to move into the fourth sub-cavity 732. This achieves the effect that the first piston 72 (main counterweight 3) and the second piston 74 (auxiliary counterweight 4) move synchronously toward the hoisting side 111. When the auxiliary counterweight 4 moves to the first critical position, the pumping assembly 75 drives the liquid medium in the fourth sub-cavity 732 to move into the second sub-cavity 712, and the liquid in the first sub-cavity 711 to move into the third sub-cavity 731. This achieves the effect that while driving the main counterweight 3 to continue moving toward the second unloaded position 33, the auxiliary counterweight 4 moves from the first critical position to the initial position. When the main counterweight 3 moves from the second unloaded position 33 to the counterweight position 31, and the auxiliary counterweight 4 moves from the initial position to the second critical position, the pumping assembly 75 drives the liquid medium to flow from the liquid medium in the fourth sub-cavity 732 to the first sub-cavity 711, and the liquid medium in the second sub-cavity 712 to the third sub-cavity 731; when the auxiliary counterweight 4 moves to the second critical position, the pumping assembly 75 drives the liquid medium in the second sub-cavity 712 to the fourth sub-cavity 732, and the liquid medium in the third sub-cavity 731 to the first sub-cavity 711, thereby achieving the effect of driving the auxiliary counterweight 4 to move from the second critical position to the initial position while driving the main counterweight 3 to continue moving to the counterweight position 31.

[0039] It should be noted that: due to the different weights of the hoisted goods, the position 31 of the main counterweight 3 is different in each wave of hoisting operations performed by the crane body 1 (that is, the lever arm length of the center of the main counterweight 3 is different). Therefore, the distance the main counterweight 3 travels from its position 31 along the second trajectory to the corresponding second unloaded position 33 is also different. To ensure that when the main counterweight 3 moves from its position 31 to the second unloaded position 33, the auxiliary counterweight 4 can first move from its initial position to the first critical position and then from the first critical position back to the initial position; and to ensure that when the main counterweight 3 moves from the second unloaded position 33 to the counterweight 31, the auxiliary counterweight 4 can first move from its initial position to the second critical position and then from the second critical position back to the initial position; the distance the main counterweight 3 travels from its position 31 along the second trajectory to the second unloaded position 33 can be calculated by the control system (e.g., ...). Figure 7 As shown in the figure, S2 can be calculated based on the mass of the cargo lifted each time. Since the weight of the lifting assembly 2 (including the cargo), the lever arm of the lifting assembly 2, and the weight of the main counterweight 3 are all known, the length of the lever arm of the main counterweight 3 can be calculated. For example, as shown in the figure... Figure 7 As shown, after calculating the lever arm length of the center of gravity of the main counterweight 3 when it is in counterweight position 31 (the vertical distance from counterweight position 31 to the center line), the difference in lever arm length between the two can be obtained by subtracting the lever arm length of the center of gravity of the main counterweight 3 when it is in the second unloaded position 33 (the vertical distance from the second unloaded position 33 to the center line, which is the same as the vertical distance from the first unloaded position 32 to the center line and is known and fixed). Combined with the rotation angle of the bearing rod 5 at this time (an angle sensor can be installed on the bearing rod 5 and communicated with the control system in the cockpit to detect the rotation angle of the bearing rod 5), the distance the main counterweight 3 moves from counterweight position 31 to the second unloaded position 33 can be calculated. Figure 7 The size of S2 in the middle; In this embodiment, when the pumping assembly 75 drives the main counterweight 3 to move from the counterweight position 31 to the second unloaded position 33 by half the distance of S2 (at which time the auxiliary counterweight 4 moves to the first critical position), the pumping assembly 75 controls the flow direction of the liquid medium to adjust so that while driving the main counterweight 3 to continue moving to the second unloaded position 33, it drives the auxiliary counterweight 4 to move from the first critical position to the initial position, so that when the main counterweight 3 moves to the second unloaded position 33, the auxiliary counterweight 4 moves to the initial position synchronously. It is understandable that when the main counterweight 3 moves from the second unloaded position 33 to the counterweight position 31, after the main counterweight 3 moves halfway through S2, the pump liquid assembly 75 is controlled to adjust the flow direction of the liquid medium. This is so that while driving the main counterweight 3 to continue moving towards the counterweight position 31, the auxiliary counterweight 4 is driven to move from the second critical position to the initial position. As a result, when the main counterweight 3 moves to the counterweight position 31, the auxiliary counterweight 4 moves to the initial position synchronously.

[0040] Reference Figures 8-10 As shown, in one embodiment of this application, the pump assembly 75 includes a first pipe 751, a second pipe 752, a solenoid valve 753, and a liquid pump 754; wherein the first pipe 751 has a first end and a second end along its length, as shown in the figure. Figure 9 As shown, the first end is connected to the first sub-cavity 711, and the second end includes a first sub-end and a second sub-end, wherein the first sub-end is connected to the third sub-cavity 731 and the second sub-end is connected to the fourth sub-cavity 732; the second tube 752 has a third end and a fourth end along its length direction, the third end is connected to the second sub-cavity 712, and the fourth end includes a third sub-end and a fourth sub-end, wherein the third sub-end is connected to the third sub-cavity 731 and the fourth sub-end is connected to the fourth sub-cavity 732; the solenoid valves 753 are respectively provided at the connection points of the first tube 751, the second tube 752 and the corresponding sub-cavities, and the solenoid valves 753 are connected to the control system and used to control whether each sub-cavity is connected to the corresponding sub-end; The liquid pump 754 can be installed on the first pipe 751, or on the second pipe 752, or on both the first pipe 751 and the second pipe 752. When the liquid pump 754 is installed on both the first pipe 751 and the second pipe 752, there are two liquid pumps 754. The two liquid pumps 754 can improve the driving effect on the liquid medium, thereby improving the response speed of driving the main counterweight 3 and the auxiliary counterweight 4 to move and enabling the main counterweight 3 and the auxiliary counterweight 4 to move at a faster speed. This shortens the duration of the unbalanced torque applied to the crane body 1 by the lifting side 111 and the counterweight side 112.

[0041] In this embodiment, the movement of the main counterweight 3 from the counterweight position 31 to the second unloaded position 33 is described as an example. When the main counterweight 3 moves from the counterweight position 31 to the second unloaded position 33, the control system controls the solenoid valve 753 located at the second sub-end to open (so that the second end of the first pipe 751 is connected to the fourth sub-cavity 732) and controls the solenoid valve 753 located at the third sub-end to open (so that the second end of the second pipe 752 is connected to the third sub-cavity 731). At this time, the liquid pump 754 drives the liquid medium in the first sub-cavity 711 to flow into the fourth sub-cavity 732, and also causes the liquid medium in the third sub-cavity 731 to flow into the fourth sub-cavity 732. The second sub-cavity 712 enables the first piston 72 and the second piston 74 to move synchronously toward the hoisting side 111. When the main counterweight 3 moves to half position S2, the control system controls the solenoid valve 753 located at the first sub-end to open (so that the second end of the first pipe 751 is connected to the third sub-cavity 731) and controls the solenoid valve 753 located at the fourth sub-end to open (so that the second end of the second pipe 752 is connected to the fourth sub-cavity 732). The liquid pump continues to work, thereby driving the auxiliary counterweight 4 to move in the opposite direction toward the initial position while controlling the main counterweight 3 to continue moving toward the second unloaded position 33.

[0042] Understandably, when the main counterweight 3 is in the second unloaded position 33 or in the counterweight position 31, and when the auxiliary counterweight 4 is in the initial position, the control system should control all solenoid valves 753 to be in the closed state, thereby ensuring that the liquid medium in the first chamber 71 and the second chamber 73 no longer flows, thereby achieving the positioning of the main counterweight 3 and the auxiliary counterweight 4 (to prevent them from shaking).

[0043] Reference Figure 10-12 As shown in one embodiment of this application, the single-arm gantry crane with automatic adjustment of structural counterweight also includes a magnetic attractor 8 disposed on the bearing rod 5; during the process of the main counterweight 3 moving from the counterweight position 31 to the second unloaded position 33, the magnetic attractor 8 is controlled to apply a magnetic attraction force to the main counterweight 3 in the same direction of movement, thereby improving the sensitivity of the main counterweight 3 during movement and increasing the movement speed of the main counterweight 3 to a certain extent (because at this time the main counterweight 3 is driven by the radial drive 7 and the magnetic drive together); thereby further shortening the duration of the unbalanced torque generated by the lifting side 111 and the counterweight side 112 when the crane body 1 is unloading goods.

[0044] In this embodiment, when the main counterweight 3 moves from the second unloaded position 33 to the counterweight position 31, the magnetic suction component 8 is controlled to apply a magnetic suction force to the main counterweight 3 in the same direction as its movement. This can improve the sensitivity of the main counterweight 3 during movement and increase the movement speed of the main counterweight 3 to a certain extent (because at this time, the main counterweight 3 is driven by the radial drive component 7 and the magnetic drive). This can further shorten the duration of the unbalanced torque generated by the lifting side 111 and the counterweight side 112 when the crane body 1 lifts the goods.

[0045] It is understandable that the main counterweight 3 in this solution can be made of iron or concrete. When it is made of concrete, the concrete needs to be poured into an iron box. On the one hand, it is used to hold the concrete, and on the other hand, during later use, the iron box is attracted by the magnetic component 8 to achieve the effect of assisting in driving the main counterweight 3 to move.

[0046] Reference Figure 10-12As shown, in one embodiment of this application, the magnetic attractor 8 includes a first magnetic base 81 and a second magnetic base 82; wherein, the first magnetic base 81 is disposed on the side of the second empty position 33 away from the counterweight position 31, the main counterweight 3 moves from the counterweight position 31 to the second empty position 33, controlling the first magnetic base 81 to open and generate a magnetic attraction force in the same direction as the movement of the main counterweight 3 (during this process, the second magnetic base 82 is not opened and does not exhibit magnetism externally, so as to prevent the magnetic force generated by the second magnetic base 82 from hindering the movement of the main counterweight 3 toward the second empty position 33); when the main counterweight 3 moves to the second empty position 33, the first magnetic base 81 is closed. At this time, the first magnetic seat 81 no longer exhibits magnetism to the outside; the second magnetic seat 82 is located on the side of the counterweight position 31 away from the second unloaded position 33. The main counterweight 3 moves from the second unloaded position 33 to the counterweight position 31, controlling the second magnetic seat 82 to open and generate a magnetic attraction force in the same direction as the main counterweight 3 (during this process, the first magnetic seat 81 is not opened and does not exhibit magnetism to the outside, so as to prevent the magnetic force generated by the first magnetic seat 81 from hindering the main counterweight 3 from moving towards the counterweight position 31). The main counterweight 3 moves to the counterweight position 31, controlling the second magnetic seat 82 to close (at this time, the second magnetic seat 82 no longer exhibits magnetism to the outside).

[0047] In this embodiment, two first magnetic bases 81 and two second magnetic bases 82 are provided, respectively located on the upper and lower end faces of the supporting rod 5, thereby achieving a more balanced magnetic drive. It is understood that the magnetic bases are magnetic components widely used in the prior art, such as... Figure 13 , Figure 14 As shown, the magnetic base includes a housing 83 and a magnet 84. The housing 83 is made of a magnetically conductive material and also includes a non-magnetically conductive component 85 sandwiched in the middle of the housing 83. The magnet 84 is rotatably mounted inside the housing 83, and the non-magnetically conductive component 85 divides the housing 83 into two parts. Figure 13 As shown, when the angle between the magnet and the housing 83 is as follows: Figure 13 In the position shown, the magnetic field lines of magnet 84 originate from the N pole, pass through the magnetic field conduction of housing 83, and reach the S pole (the magnetic field lines are inside housing 83), thus making the magnetic base not exhibit magnetism externally; as shown Figure 14 As shown, when the rotating magnet 84 reaches 90°, the magnetic field lines of the magnet 84 are emitted from the N pole. Due to the obstruction of the non-magnetic component 85, the magnetic field lines emitted from the N pole will pass through the outside of the housing 83 and return to the S pole. This makes the magnetic base exhibit magnetism (because the magnetic field lines pass through the outside of the housing 83 at this time). The above description of the principle of the magnetic base is all existing technology, and will not be elaborated on here.

[0048] It is understandable that, such as Figure 10 , Figure 11As shown, magnetic shielding components, such as iron plates, can be provided on the bearing rods 5 on the side of the first magnetic base 81 and the second magnetic base 82 away from the main counterweight 3. This arrangement ensures that when the first magnetic base 81 and the second magnetic base 82 need to exhibit magnetism, they can only act on the main counterweight 3 and are used to assist the main counterweight 3 in moving in conjunction with the radial drive component 7.

[0049] Reference Figure 10-12 As shown, in one embodiment of this application, the single-arm gantry crane with automatic adjustment of structural counterweight further includes a first transmission component 91 and a second transmission component 92; wherein the first transmission component 91 includes a first transmission cylinder 911 fixedly mounted on the bearing rod 5, as shown in the figure. Figure 12 As shown, a first transmission piston 912 is movable inside the first transmission cylinder 911. The piston rod of the first transmission piston 912 extends outward and is connected to a first transmission rack 913, as shown. Figure 10 As shown, the first transmission rack 913 meshes with a first transmission gear 914 rotatably mounted on the edge of the bearing rod 5. The first transmission gear 914 is positioned at the initial position facing the second critical position and is close to the initial position. The first transmission component 91 also includes a first auxiliary cylinder, and an auxiliary piston is provided inside the first auxiliary cylinder. The piston rod of the auxiliary piston extends outward from one end of the first auxiliary cylinder and is connected to a rack. Figure 13 , Figure 14 As shown, each magnetic base has a rotary switch equipped with a gear that rotates coaxially with the magnet 84. The rack meshes with the gear that rotates coaxially with the magnet 84. The first transmission cylinder 911 and the first auxiliary cylinder are connected by a hydraulic pipe. The first transmission cylinder 911 and the first auxiliary cylinder are filled with hydraulic oil. The first auxiliary cylinder, auxiliary piston and other structural components are not shown in the figure.

[0050] In this embodiment, the second transmission component 92 includes a second transmission cylinder 921 fixedly mounted on the bearing rod 5, such as... Figure 12 As shown, a second transmission piston 922 is movable inside the second transmission cylinder 921. The piston rod of the second transmission piston 922 extends outward and is connected to a second transmission rack 923, as shown. Figure 10 As shown, the second transmission rack 923 meshes with a second transmission gear 924 rotatably mounted on the edge of the bearing rod 5. The second transmission gear 924 is located in the initial position facing the first critical position and is positioned close to the initial position. The second transmission component 92 also includes a second auxiliary cylinder, and an auxiliary piston is provided inside the second auxiliary cylinder. The piston rod of the auxiliary piston extends outward from one end of the second auxiliary cylinder and is connected to a rack. The rack meshes with gears that rotate coaxially with the magnet 84. The second transmission cylinder 921 and the second auxiliary cylinder are connected by a hydraulic pipe, and the second transmission cylinder 921 and the second auxiliary cylinder are filled with hydraulic oil. The second auxiliary cylinder, auxiliary piston, and other structural components are not shown in the figure.

[0051] In this embodiment, as Figure 10 As shown, auxiliary gears, which rotate coaxially with the first transmission gear 914 and the second transmission gear 924, are rotatably mounted on one side edge of the support rod 5. A rack (not labeled in the figure) meshes with the auxiliary gears on one side wall of the auxiliary counterweight 4. When the auxiliary counterweight 4 is in its initial position, the rack on its side and the auxiliary gear rotatably mounted on the side of the support rod 5 are not meshed. When the auxiliary counterweight 4 moves from its initial position to the first critical position, the rack on its side wall meshes with the auxiliary gear corresponding to the first transmission gear 914, thereby driving the first transmission gear 914 to rotate. As the first transmission gear 914 rotates, it drives the first transmission rack 913 to move, thus driving the first transmission gear... The piston 912 moves within the first transmission cylinder 911, thereby driving the auxiliary piston located within the first auxiliary cylinder via the movement of hydraulic oil. This ultimately drives the gear that rotates coaxially with the magnet 84 to rotate, thus rotating the magnet 84 and controlling whether the magnetic base exhibits magnetism externally. It can be understood that when the rack and auxiliary gear located on the side of the auxiliary counterweight 4 disengage, the magnet 84 is driven to rotate 90° relative to the die, causing the first magnetic base 81 to exhibit magnetism externally. When the auxiliary counterweight 4 moves from the first critical position in the opposite direction towards the initial position, the magnet 84 within the first magnetic base 81 is again driven to rotate 90° in the opposite direction via the first transmission component 91, thereby causing the first magnetic base 81 to no longer exhibit magnetism externally.

[0052] In this embodiment, the auxiliary counterweight 4 moves from the initial position to the second critical position, and then moves back from the second critical position to the initial position, as described above, and will not be described in detail here; Figure 11 As shown, the first magnetic base 81 and the second magnetic base 82 are both housed within a housing (the first auxiliary cylinder, the second auxiliary cylinder, and the corresponding piston and rack are all housed within their respective housings). The housing is equipped with hydraulic lines connected to the first transmission cylinder 911 and the second transmission cylinder 921, thereby enabling the flow of hydraulic oil and achieving drive. It is understood that the aforementioned housing merely serves as a cover, enclosing the magnetic base, the first auxiliary cylinder, the second auxiliary cylinder, and the corresponding piston and rack. The material of the housing should not obstruct the passage of the magnetic field lines generated by the magnetic base, or the housing should have an opening facing the main counterweight 3 (so that the magnetic force generated by the magnetic base directly acts on the main counterweight 3 through the opening). It is understood that in this embodiment, one end of the first transmission cylinder 911 and the second transmission cylinder 921 is connected to the outside, while the other end is connected to a hydraulic line, enabling the hydraulic oil to move when the transmission piston moves within the corresponding transmission cylinder.

[0053] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principles of the present invention, and these improvements and substitutions should also be considered within the scope of protection of the present invention.

Claims

1. A gantry portal jib crane with automatically adjusted structural counterweights, characterized in that, include: The crane body has a rotatable turntable; the turntable has a lifting side and a counterweight side arranged opposite to each other; A hoisting assembly is installed on the hoisting side; as well as A main counterweight is disposed on the counterweight side; the main counterweight has a first track extending circumferentially along the turntable and a second track extending radially along the turntable; on the first track and the second track, the main counterweight has counterweight positions at the same location; on the first track, the main counterweight has a first unloaded position, and on the second track, the main counterweight has a second unloaded position; the distance the main counterweight moves from the counterweight position to the first unloaded position is greater than the distance the main counterweight moves from the counterweight position to the second unloaded position.

2. A portal jib crane with automatically adjusted structural counterweight according to claim 1, characterized in that, The single-arm gantry crane with automatically adjusting counterweight structure also includes: An auxiliary counterweight is arranged to move radially along the turntable. The auxiliary counterweight has an initial position coaxial with the turntable, a first critical position on the hoisting side, and a second critical position on the counterweight side. The main counterweight moves along the second trajectory from the counterweight position to the second unloaded position, driving the auxiliary counterweight to move from the initial position to the first critical position, and then from the first critical position back to the initial position; The main counterweight moves along the second trajectory from the second unloaded position to the counterweight position, driving the auxiliary counterweight to move from the initial position to the second critical position, and then from the second critical position back to the initial position.

3. A portal jib crane with automatically adjusted structural counterweight according to claim 2, characterized in that, The single-arm gantry crane with automatically adjusting counterweight structure also includes: A support rod is coaxially rotatably mounted on the turntable; the main counterweight is radially movable along the turntable and arranged on the support rod, so that the main counterweight has a second trajectory on the turntable; an auxiliary counterweight is radially movable along the turntable and arranged on the support rod, so that the auxiliary counterweight moves between the initial position, the first critical position, and the second critical position; and A circumferential drive member, at least partially disposed on the support rod, is used to drive the support rod to move circumferentially along the turntable so that the main counterweight has the first trajectory on the turntable.

4. A portal jib crane with automatically adjusted structural counterweight according to claim 3, characterized in that, The single-arm gantry crane with automatically adjustable counterweight structure also includes a radial drive component; The radial drive unit drives the main counterweight to move from the counterweight position along the second trajectory to the second unloaded position, and simultaneously drives the auxiliary counterweight to move from the initial position to the first critical position, and then from the first critical position back to the initial position; The radial drive component drives the main counterweight to move from the second unloaded position along the second trajectory to the counterweight position, and simultaneously drives the auxiliary counterweight to move from the initial position to the second critical position, and then from the second critical position back to the initial position.

5. A portal jib crane with automatically adjusted structural counterweight according to claim 4, characterized in that, The radial drive component includes: A first cavity is disposed within the supporting rod. A first piston is movably disposed within the first cavity, and the first piston divides the first cavity into a first sub-cavity and a second sub-cavity. The first piston extends at least partially outward from the first cavity for connection with the main counterweight. A second cavity is provided on the bearing rod, and a second piston is movable within the second cavity, which divides the second cavity into a third sub-cavity and a fourth sub-cavity; the second piston extends at least partially outward from the second cavity for connection with the auxiliary counterweight; both the first cavity and the second cavity are filled with a liquid medium. A pump assembly for driving the liquid medium to flow between the first sub-cavity, the second sub-cavity, the third sub-cavity, and the fourth sub-cavity.

6. A portal jib crane with automatically adjusted structural counterweight according to claim 5, characterized in that, The pump assembly includes: A first tube has a first end and a second end, the first end communicating with a first sub-cavity, and the second end having a first sub-end and a second sub-end communicating with a third sub-cavity and a fourth sub-cavity; and The second tube has a third end and a fourth end, the third end being connected to the second sub-cavity, and the fourth end having a third sub-end and a fourth sub-end connected to the third sub-cavity and the fourth sub-cavity; Solenoid valves are respectively located at the first sub-end, the second sub-end, the third sub-end, and the fourth sub-end; A liquid pump is provided in the first pipe and / or the second pipe.

7. A portal jib crane with automatically adjusted structural counterweight according to any of claims 3-6, characterized in that, The single-arm gantry crane with automatic adjustable counterweight structure also includes a magnetic suction component mounted on the bearing rod; The magnetic attractor is used to apply a magnetic force to the main counterweight in the same direction as the main counterweight's movement, so as to drive the main counterweight to move.

8. A portal jib crane with automatically adjusted structural counterweight according to claim 7, characterized in that, The magnetic attraction component includes: A first magnetic base is located on the side of the second unloaded position opposite to the counterweight position; when the main counterweight moves from the counterweight position to the second unloaded position, the first magnetic base activates and generates a magnetic attraction force in the same direction as the main counterweight's movement; when the main counterweight moves to the second unloaded position, the first magnetic base closes; and The second magnetic base is located on the side of the counterweight position opposite to the second unloaded position; when the main counterweight moves from the second unloaded position to the counterweight position, the second magnetic base is activated and generates a magnetic attraction force in the same direction as the main counterweight; when the main counterweight moves to the counterweight position, the second magnetic base is deactivated.

9. A portal jib crane with automatically adjusted structural counterweight according to claim 8, characterized in that, The single-arm gantry crane with automatically adjusting counterweight structure also includes: A first transmission component, wherein the auxiliary counterweight moves from the initial position to the first critical position, driving the rotary switch of the first magnetic base to rotate and opening the first magnetic base; the auxiliary counterweight moves from the first critical position to the initial position, driving the rotary switch of the first magnetic base to rotate and closing the first magnetic base; and The second transmission component, wherein the auxiliary counterweight moves from the initial position to the second critical position, thereby driving the rotary switch of the second magnetic base to rotate and opening the second magnetic base; the auxiliary counterweight moves from the second critical position to the initial position, thereby driving the rotary switch of the second magnetic base to rotate and closing the second magnetic base.

10. The cantilevered gantry crane with automatically adjusted structural counterweight according to claim 3, characterized in that, The circumferential drive component includes: The motor is mounted on one end of the support rod along its length; and The first gear is driven by the motor; The gear system is located on the inner sidewall of the turntable and is used to mesh with the first gear.

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