A trolley for a flexible long-span crane beam

Abstract

The utility model provides a flexible large span crane beam's trolley, include: trolley frame, the upper portion fixed connection of trolley frame has the support assembly for connecting the support end of crane beam, the below of trolley frame is installed wheel group, the support assembly includes: hinge base support, bearing group and support plate, bearing group installs between the support plate of symmetry two sides, the through -hole is opened in hinge base support, hinge base support is set on bearing group through the through -hole, one end of hinge base support is fixedly connected with the support end of crane beam, and the other end is connected with trolley frame through bearing group, bearing group includes: joint bearing, positioning sleeve and pin shaft, joint bearing is coaxially set on the outer ring of pin shaft, to compensate the dynamic deformation in the operation of crane beam, at least two positioning sleeves are symmetrically set on the both ends of joint bearing, to limit the movement of joint bearing along the axial direction of pin shaft.

Description

Technical Field

[0001] This utility model relates to the technical field of trolleys for large-span crane beams, and in particular to a flexible trolley for large-span crane beams. Background Technology

[0002] The trolley of the crane beam is a wheeled traveling mechanism installed below the crane, in contact with and moving along the rails on the crane beam. It is responsible for transferring the crane's own weight, lifting load, and various dynamic loads during operation to the crane beam. This allows the crane to move laterally or longitudinally along the crane beam's rails as needed, thereby transporting the hook or lifting equipment to different locations within the factory to meet material handling requirements.

[0003] Currently, existing trolleys for large-span crane beams have the following technical problems: 1. Insufficient structural rigidity: The existing trolley structure (such as crossbeams, wheel frames, etc.) lacks sufficient rigidity, which easily leads to excessive deflection or vibration during crane operation, affecting the stability of crane operation and even inducing track deviation or rail wear. 2. Lack of displacement compensation capability: During long-term use, the crane beam and track will undergo thermal expansion and contraction. If the trolley is rigidly connected to the track or beam, it cannot compensate for the resulting expansion and contraction displacement, leading to track stress concentration or trolley malfunction. Utility Model Content

[0004] In view of the shortcomings of the prior art described above, the technical problem to be solved by this utility model is to provide a trolley for a flexible large-span crane beam, which solves the problems of insufficient structural rigidity and lack of displacement compensation capability of the existing large-span crane beam trolleys.

[0005] To achieve the above objectives, this utility model provides a trolley for a flexible, large-span crane beam, comprising:

[0006] A trolley frame, with a bracket assembly for connecting the support end of the crane beam fixedly connected to the upper part of the trolley frame, and a wheel set installed at the lower part of the trolley frame;

[0007] The support assembly includes: a hinge bracket, a bearing assembly, and a support plate. The bearing assembly is installed between the support plates on two symmetrical sides. The hinge bracket has a through hole and is sleeved on the bearing assembly through the through hole. At least two support plates are symmetrically fixed on both sides of the trolley frame. One end of the hinge bracket is fixedly connected to the support end of the crane beam, and the other end is connected to the trolley frame through the bearing assembly.

[0008] The bearing assembly includes: a spherical plain bearing, a locating sleeve, and a pin. The spherical plain bearing is coaxially sleeved on the outer ring of the pin to compensate for the dynamic deformation of the crane beam during operation. At least two locating sleeves are symmetrically sleeved on both ends of the spherical plain bearing to restrict the movement of the spherical plain bearing along the axial direction of the pin.

[0009] As a more preferred approach, the pin also passes through a through hole in the hinge bracket and a connecting hole in the support plate to limit the displacement of the bearing assembly along the axial direction of the pin. During crane beam operation, especially under dynamic loads, impacts, and starting / stopping inertial forces, if the pin is not reliably limited in the axial direction, the entire bearing assembly (especially the spherical plain bearing) may experience axial slippage or slight displacement, leading to loose connections, unstable operation, localized wear, or abnormal vibration. By passing the pin through the connecting hole in the support plate and fixing it axially, the movement of the bearing assembly along the pin's axial direction can be limited, effectively preventing overall axial movement of the bearing assembly and improving structural stability. Furthermore, since spherical plain bearings have multi-directional rotation and displacement compensation capabilities, if the pin is unstable in the axial direction, it may cause the spherical plain bearing to be subjected to additional axial loads, accelerating its wear or failure. By limiting the axial displacement of the pin, the spherical plain bearing is prevented from being subjected to forces in the non-design direction, helping to protect the bearing, reduce the failure rate, and extend its service life.

[0010] As a preferred embodiment, the support assembly also includes a ring buckle that passes through the pin and is mounted on the support plate. Under long-term operation, vibration, or thermal expansion and contraction, the connection between the pin and the support plate (especially if relying solely on an interference fit or a standard shaft-hole fit) may experience slight loosening or relative displacement. The ring buckle acts as a "secondary locking mechanism," effectively suppressing pin loosening through mechanical clamping, pressing, or fixing, thereby improving the overall structural durability and safety. Furthermore, for large-span crane systems, the crane beam's trajectory, stability, and positioning accuracy play a crucial role in operation; loosening or swaying at connection points can affect the crane's operational quality. By enhancing the fixing strength between the pin and the support plate, the ring buckle indirectly improves the connection rigidity between the crane beam and the trolley, contributing to improved crane operation stability and control accuracy, and reducing sway, vibration, and abnormal noise. Furthermore, in this structure, the positioning sleeve is mainly used to restrict the movement of the spherical plain bearing along the axial direction of the pin. Through the set ring buckle, it can form a "dual function" with the positioning sleeve, which not only restricts the internal movement of the spherical plain bearing, but also restricts the macroscopic displacement of the pin and the entire bearing assembly on the support plate, thereby providing more comprehensive positioning and protection for the bearing assembly.

[0011] As a preferred embodiment, at least two annular buckles are fitted onto the symmetrical ends of the pin and fixed to the outer side walls of the support plate on opposite sides. The annular buckles are detachably connected to the support plate via connectors. After the pin passes through the support plate, its two ends are located outside the support plate. Without restraint, it may gradually loosen or even come out under the impact, vibration, and inertial forces of the crane during operation. By symmetrically setting annular buckles at both ends of the pin, the pin is "clamped" between the support plate and the annular buckles, effectively restricting its axial movement, preventing the pin from coming out of the support plate hole, and improving the safety of the overall connection. In addition, symmetrically arranging two annular buckles at both ends of the pin ensures a uniform distribution of the restraining force on the pin, avoiding twisting, tilting, or additional stress concentration caused by unilateral force. The symmetrical design ensures the stability of the pin during operation, helps maintain the balanced connection between the crane beam and the trolley, and improves the smoothness of the overall system operation. Furthermore, the ring buckle and the support plate are detachably connected via connectors (such as bolts and screws). During equipment installation, the pin and support plate can be assembled first, and then the ring buckle can be installed for positioning. During later maintenance and repair, the ring buckle can be quickly disassembled without damaging the pin or support plate structure, allowing for inspection or replacement of the pin, bearing assembly, and spherical bearing. This facilitates installation and maintenance, reducing operating costs and downtime.

[0012] As a more preferred method, the support plates are symmetrically fixed to both sides of the trolley frame by welding.

[0013] As a preferred embodiment, the wheel set includes multiple wheels evenly distributed along the underside of the trolley frame. Crane beams and the cranes running on them typically have significant self-weight and lifting loads. The trolley, as their direct support and moving mechanism, must possess sufficient load-bearing capacity. By increasing the number of wheels, the total load can be distributed across multiple wheels, reducing the pressure on individual wheels and thus improving the overall load-bearing capacity of the trolley, meeting the needs of large-tonnage and large-span applications. Furthermore, the multi-wheel layout helps reduce vibration, bumps, and impacts during trolley operation, especially when traversing uneven ground, rail joints, or curves; evenly distributed wheels better conform to the rails or support surfaces, reducing swaying and offset, improving the stability of the crane beam during operation, and enhancing safety, which is particularly crucial for the operation of large-span cranes. In addition, if the number of wheels is small or the arrangement is uneven, some wheels may bear the majority of the load, leading to local wear, deformation, or even fatigue fracture. By distributing multiple wheels evenly, the weight borne by each wheel is nearly equal, avoiding local overload, extending the service life of wheels and bearings and other related components, and reducing maintenance costs.

[0014] As a preferred approach, the central axis of the pin and the central axis of the through hole on the hinge bracket are aligned. If the pin and the through hole are misaligned (eccentric), non-uniform contact pressure will occur between the pin and the hole wall, leading to increased localized wear. The hinge bracket will be subjected to additional bending moments or eccentric loads, easily causing fatigue, deformation, or even breakage at the connection point. By ensuring axis alignment, all loads are transmitted along the design direction, avoiding eccentric forces, significantly reducing the risk of wear and structural damage, and extending the service life of components. Furthermore, the pin and the through hole of the hinge bracket form a rotary kinematic pair, and their fitting accuracy directly affects the overall mechanical performance. The axis alignment design ensures the geometric accuracy of the kinematic pair, making rotation smoother and improving the reliability and motion accuracy of the entire connection mechanism. Moreover, eccentric pin installation often leads to periodic vibrations or impacts during rotation, causing abnormal noises in the equipment (such as friction sounds or clicking sounds), affecting the stability of the crane beam operation, and even impacting the accuracy and safety of lifting operations. The coaxial design of the pin and the through hole helps ensure the stability and reliability of the crane beam system.

[0015] As a more preferred approach, the spherical plain bearing and the pin are slidably connected. Sliding spherical plain bearings typically have a large internal clearance and a spherical / arc surface contact structure, allowing for certain offsets or angular displacements between the pin and the bearing inner ring in multiple directions. This effectively absorbs deformations such as deflection, tilting, and skewing of the crane beam caused by its own weight, thermal expansion and contraction, and uneven load during operation, improving the overall system's flexibility, adaptability, and operational stability. Compared to using rolling bearings (such as tapered roller bearings, angular contact bearings, etc.) or complex motion mechanisms, the slidably connected spherical plain bearing structure is simpler, more compact, easier to process and assemble, simpler to manufacture, and has lower manufacturing and maintenance costs.

[0016] As a preferred approach, the hinge bracket is detachably connected to both the support end of the crane beam and the pin. After long-term operation of the crane beam, components such as the hinge bracket, connecting pin, and spherical bearings may experience wear, deformation, loosening, or fatigue damage. If the hinge bracket is detachably connected, there is no need to cut or damage the crane beam or trolley frame; simply loosening the connecting bolts or pins allows for quick removal of the hinge bracket for inspection, repair, or replacement, significantly reducing maintenance difficulty and time costs. Furthermore, as a vulnerable or high-load connecting component, the hinge bracket may wear out faster than other components. The detachable design allows for individual replacement of the hinge bracket without replacing the entire trolley frame, pin, or crane beam, saving costs, improving resource utilization, and extending the overall system lifespan. In actual engineering projects, crane beam specifications, connection methods, and support point positions may vary. The detachable hinge bracket allows for flexible adjustment and replacement to match different crane beam models or connection requirements, enhancing the system's versatility and on-site adaptability.

[0017] As a preferred approach, the central axis of the connecting hole on the support plate coincides with the central axis of the annular buckle. If the central axes of the connecting hole on the support plate and the annular buckle do not coincide (there is eccentricity), the pin will be in an eccentric position after installation, resulting in uneven contact pressure between the pin and the connecting hole, and between the pin and the annular buckle. This can lead to additional bending moment, localized wear, increased friction, and even jamming during operation. By ensuring that their central axes coincide, the pin is in a perfectly centered state, with uniform force, greatly reducing the risk of abnormal wear and structural damage. Furthermore, when the annular buckle and the hole on the support plate are coaxial, they together form a geometrically symmetrical and force-balanced limiting structure, which can more effectively restrict the axial movement or disengagement of the pin and prevent the pin from undergoing slight displacement or tilting under vibration or impact. This coaxial constraint method enhances the stability of the pin installation and improves the reliability of the entire connection in long-term operation. Furthermore, when the center lines of the relevant parts are aligned, the stress distribution on the contact surface is more uniform, which can avoid local stress concentration and high-frequency wear; it helps to extend the fatigue life of key parts such as pins, support plate hole edges, and ring buckles, and reduce maintenance frequency and replacement costs.

[0018] As described above, the flexible large-span crane beam trolley of this utility model has the following beneficial effects: When in use, the flexible large-span crane beam trolley of this utility model, through the combined design of joint bearings and bearing assemblies, allows for a certain range of angular displacement, rotation, or swaying between the crane beam and the trolley frame. This can effectively compensate for the dynamic deformation of the crane beam caused by factors such as self-weight deflection, thermal expansion and contraction, load offset, and start-stop impact during operation. It avoids the problems of additional stress, structural damage, and connection failure caused by deformation obstruction in traditional rigid connections, and significantly improves the safety and structural reliability of the crane system.

[0019] The flexible connection structure enables the crane beam to adaptively adjust its posture during movement, reducing instability, rail wear, vibration, and sway caused by deformation. It helps improve the stability, positioning accuracy, and operational safety of the crane, and is particularly suitable for industrial hoisting scenarios with high requirements for operational quality.

[0020] Because it allows for a certain degree of relative movement between the crane beam and the trolley frame, it effectively avoids phenomena such as concentrated stress, abnormal friction, and jamming. The combination of spherical bearings and positioning sleeves makes the load transfer more even, reducing local wear and fatigue damage to components such as pins, support plates, and trolley frames. This helps to extend the service life of key moving parts, reduce maintenance frequency and replacement costs, and improve the system's economy.

[0021] By symmetrically arranging support plates, centrally installing bearing assemblies, and providing multi-directional compensation with spherical bearings, the system achieves "flexibility" while maintaining the stability and load-bearing capacity of the overall structure. The design of the pin shaft and positioning sleeve ensures axial limiting and structural reliability, avoiding loose connections or abnormal displacement. It is suitable for the long-term reliable operation of large-span, large-tonnage crane beams.

[0022] Key components such as bearing assemblies and hinge brackets often adopt detachable connection methods, which facilitates quick inspection, replacement or adjustment when wear, deformation or failure occurs, improving the adaptability of the equipment and reducing the difficulty of operation and maintenance and downtime. Attached Figure Description

[0023] Figure 1 The image shown is a first perspective view of a trolley for a flexible, large-span crane beam according to this utility model.

[0024] Figure 2 The image shown is a second perspective view of a trolley for a flexible, large-span crane beam according to this utility model.

[0025] Figure 3 The diagram shown is an exploded view of the trolley of a flexible large-span crane beam according to this utility model.

[0026] Figure 4 The diagram shown is a schematic of the bearing assembly structure of the trolley of a flexible, large-span crane beam according to this utility model.

[0027] Component designation explanation

[0028] 1 trolley frame 2 Wheelset 3 bracket assembly 31 Hinge bracket 32 Ring buckle 33 bearing assembly 331 Pin 332 Spherical plain bearing 333 positioning sleeve 34 support plate Detailed Implementation

[0029] The following specific embodiments illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification.

[0030] It should be understood that the structures, proportions, sizes, etc., illustrated in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and are not intended to limit the implementation of this utility model. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and purpose of this utility model, should still fall within the scope of the technical content disclosed in this utility model. The following detailed description should not be considered restrictive, and the scope of the embodiments of this application is limited only by the claims of the published patents. The terminology used herein is for describing specific embodiments only and is not intended to limit this application. Spatial terms such as "upper," "lower," "left," "right," "below," "below," "lower part," "above," "upper part," etc., may be used in the text to illustrate the relationship between one element or feature shown in the figures and another element or feature.

[0031] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," "fixing," and "holding" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0032] Furthermore, as used herein, the singular forms “a,” “an,” and “the” are intended to include the plural forms as well, unless the context indicates otherwise. It should be further understood that the terms “comprising,” “including,” indicate the presence of the stated feature, operation, element, component, item, kind, and / or group, but do not preclude the presence, occurrence, or addition of one or more other features, operations, elements, components, items, kinds, and / or groups. The terms “or” and “and / or” as used herein are interpreted as inclusive, or mean any one or any combination thereof. Thus, “A, B, or C” or “A, B, and / or C” means “any one of: A; B; C; A and B; A and C; B and C; A, B, and C.” Exceptions to this definition arise only when combinations of elements, functions, or operations are inherently mutually exclusive in some manner.

[0033] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions in the embodiments of this utility model are further described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only for explaining this utility model and are not intended to limit the utility model.

[0034] like Figures 1 to 4 As shown, this utility model provides a trolley for a flexible, large-span crane beam, comprising:

[0035] A trolley frame 1, with a bracket assembly 3 fixedly connected to the upper part of the trolley frame 1 for connecting the support end of the crane beam, and a wheel set 2 installed below the trolley frame 1;

[0036] The support assembly 3 includes: a hinge bracket 31, a bearing assembly 33, and a support plate 34. The bearing assembly 33 is installed between the support plates 34 on both symmetrical sides. The hinge bracket 31 has a through hole and is sleeved on the bearing assembly 33 through the through hole. At least two support plates 34 are symmetrically fixed on both sides of the trolley frame 1. One end of the hinge bracket 31 is fixedly connected to the support end of the crane beam, and the other end is connected to the trolley frame 1 through the bearing assembly 33.

[0037] The bearing assembly 33 includes: a spherical plain bearing 332, a positioning sleeve 333, and a pin 331. The spherical plain bearing 332 is coaxially sleeved on the outer ring of the pin 331 to compensate for the dynamic deformation of the crane beam during operation. At least two positioning sleeves 333 are symmetrically sleeved on both ends of the spherical plain bearing 332 to restrict the movement of the spherical plain bearing 332 along the axial direction of the pin 331.

[0038] In some embodiments of this utility model, such as Figures 3 to 4 As shown, the pin 331 also passes through the through hole on the hinge bracket 31 and the connecting hole on the support plate 34 to limit the displacement of the bearing assembly 33 along the axial direction of the pin 331. During the operation of the crane beam, especially when subjected to dynamic loads, impacts, and starting and stopping inertial forces, if the pin 331 is not reliably limited in the axial direction, the entire bearing assembly 33 (especially the spherical plain bearing 332) may experience axial slippage or slight displacement, leading to loose connections, unstable operation, localized wear, or abnormal vibration. By passing the pin 331 through the connecting hole of the support plate 34 and fixing it axially, the movement of the bearing assembly 33 along the axial direction of the pin 331 can be limited, effectively preventing the overall axial movement of the bearing assembly 33 and improving structural stability. Furthermore, since the spherical plain bearing 332 has multi-directional rotation and displacement compensation capabilities, if the pin 331 is unstable in the axial direction, it may cause the spherical plain bearing 332 to be subjected to additional axial load, accelerating its wear or failure. By limiting the axial displacement of the pin 331, the spherical plain bearing 332 is prevented from being subjected to forces in the non-design direction, which helps to protect the bearing, reduce the failure rate, and extend its service life.

[0039] In some embodiments of this utility model, such as Figures 3 to 4As shown, the support assembly 3 also includes an annular buckle 32, which passes through the pin 331 and is mounted on the support plate 34. Under long-term operation, vibration, or thermal expansion and contraction, the connection between the pin 331 and the support plate 34 (especially if relying solely on an interference fit or ordinary shaft-hole fit) may experience slight loosening or relative displacement. The annular buckle 32 acts as a "secondary locking mechanism," effectively suppressing the loosening of the pin 331 through mechanical clamping, pressing, or fixing, thereby improving the overall structural durability and safety. Furthermore, for large-span crane systems, the crane beam's running trajectory, stability, and positioning accuracy play a crucial role during operation. Loosening or swaying at connection points can affect the crane's operational quality. By enhancing the fixing strength between the pin 331 and the support plate 34, the annular buckle 32 indirectly improves the connection rigidity between the crane beam and the trolley, helping to improve the crane's operational stability and control accuracy, and reducing sway, vibration, and abnormal noise. Furthermore, in this structure, the positioning sleeve 333 is mainly used to restrict the movement of the spherical plain bearing 332 along the axial direction of the pin shaft 331. Through the provided annular buckle 32, it can form a "dual function" with the positioning sleeve 333, which restricts the internal movement of the spherical plain bearing 332 and restricts the macroscopic displacement of the pin shaft 331 and the entire bearing assembly 33 on the support plate 34, thereby providing more comprehensive positioning and protection for the bearing assembly 33.

[0040] In some embodiments of this utility model, such as Figures 3 to 4As shown, at least two annular buckles 32 are sleeved on the symmetrical ends of the pin 331 and fixed to the outer side walls of the support plate 34 on opposite sides. The annular buckles 32 and the support plate 34 are detachably connected by connectors. After the pin 331 passes through the support plate 34, its two ends are located outside the support plate 34. Without restraint, it may gradually loosen or even fall out under the impact, vibration, and inertial force of starting and stopping during crane operation. By symmetrically setting annular buckles 32 at both ends of the pin 331, the pin 331 is "clamped" between the support plate 34 and the annular buckles 32, which can effectively limit its axial movement, prevent the pin 331 from falling out of the hole in the support plate 34, and improve the safety of the overall connection. Furthermore, the two annular buckles 32 are symmetrically arranged at both ends of the pin 331, ensuring a uniform distribution of the limiting force on the pin 331 and preventing twisting, tilting, or additional stress concentration caused by unilateral force. The symmetrical design ensures the stability of the pin 331 during operation, helps maintain the balanced connection between the crane beam and the trolley, and improves the overall system's smooth operation. Moreover, the annular buckles 32 and the support plate 34 are detachably connected via connectors (such as bolts and screws). During equipment installation, the pin 331 and support plate 34 can be assembled first, and then the annular buckles 32 can be installed for limiting. During later maintenance and repair, the annular buckles 32 can be quickly disassembled without damaging the structure of the pin 331 or support plate 34, allowing for inspection or replacement of the pin 331, bearing assembly 33, and spherical bearing 332. This facilitates installation and maintenance, reducing operating costs and downtime.

[0041] In some embodiments of this utility model, such as Figures 2 to 3 As shown, the support plate 34 is symmetrically fixed to both sides of the trolley frame 1 by welding.

[0042] In some embodiments of this utility model, such as Figure 1As shown, the wheel set 2 includes multiple wheels, which are evenly distributed along the underside of the trolley frame 1. Crane beams and the cranes running on them typically have significant self-weight and lifting loads. The trolley, as their direct support and moving mechanism, must possess sufficient load-bearing capacity. By increasing the number of wheels, the total load can be distributed across multiple wheels, reducing the pressure on individual wheels and thus improving the overall load-bearing capacity of the trolley, meeting the needs of large-tonnage and large-span applications. Furthermore, the multi-wheel layout helps reduce vibration, bumps, and impacts during trolley operation, especially when traversing uneven ground, rail joints, or curves; evenly distributed wheels better conform to the rails or support surfaces, reducing swaying and offset, improving the stability of the crane beam during operation, and enhancing safety, which is particularly crucial for the operation of large-span cranes. In addition, if the number of wheels is small or the arrangement is uneven, some wheels may bear the majority of the load, leading to local wear, deformation, or even fatigue fracture. By distributing multiple wheels evenly, the weight borne by each wheel is nearly equal, avoiding local overload, extending the service life of wheels and bearings and other related components, and reducing maintenance costs.

[0043] In some embodiments of this utility model, such as Figure 4 As shown, the central axis of the pin 331 and the central axis of the through hole on the hinge bracket 31 are on the same straight line. If the pin 331 is not aligned with the axis of the through hole (eccentric), it will cause uneven contact pressure between the pin 331 and the hole wall, resulting in increased local wear; the hinge bracket 31 will be subjected to additional bending moment or eccentric load, which can easily cause fatigue, deformation or even breakage of the connection part. By ensuring the alignment of the axes, all loads are transmitted along the design direction, avoiding eccentric force, significantly reducing the risk of wear and structural damage, and extending the service life of the components. In addition, the pin 331 and the through hole of the hinge bracket 31 are a rotary kinematic pair, and their fitting accuracy directly affects the overall mechanical performance; the design of axis alignment ensures the geometric accuracy of the kinematic pair, making the rotation smoother and improving the reliability and motion accuracy of the entire connection mechanism. Furthermore, the eccentric installation of the pin 331 often leads to periodic vibrations or impacts during rotation, causing abnormal noises in the equipment (such as friction sounds or clicking sounds), affecting the stability of the crane beam operation, and even affecting the accuracy and safety of the lifting operation; the coaxial design of the pin 331 and the through hole helps to ensure the stability and reliability of the crane beam system operation.

[0044] In some embodiments of this utility model, such as Figure 4As shown, the spherical plain bearing 332 and the pin 331 are slidably connected. The sliding spherical plain bearing 332 typically has a large internal clearance and a spherical / arc surface contact structure, allowing for certain offsets or angular displacements between the pin 331 and the bearing inner ring in multiple directions. This effectively absorbs deformations such as deflection, tilting, and rotation of the crane beam caused by its own weight, thermal expansion and contraction, and uneven load during operation, improving the overall system's flexibility, adaptability, and operational stability. Compared to using rolling bearings (such as tapered roller bearings, angular contact bearings, etc.) or complex motion mechanisms, the spherical plain bearing 332 with a sliding connection has a simpler, more compact structure, is easier to process and assemble, is simpler to manufacture, and has lower manufacturing and maintenance costs.

[0045] In some embodiments of this utility model, such as Figures 3 to 4 As shown, the hinge bracket 31 is detachably connected to the support end of the crane beam and the pin 331. After long-term operation of the crane beam, components such as the hinge bracket 31, connecting pin 331, and spherical bearing 332 may experience wear, deformation, loosening, or fatigue damage. If the hinge bracket 31 is detachably connected, there is no need to cut or damage the crane beam or trolley frame 1. The hinge bracket 31 can be quickly removed for inspection, repair, or replacement simply by loosening the connecting bolts or pins, significantly reducing maintenance difficulty and time costs. In addition, as a vulnerable or high-load connecting component, the wear rate of the hinge bracket 31 may be higher than that of other components. With the detachable design, the hinge bracket 31 can be replaced individually without replacing the entire trolley frame 1, pin 331, or crane beam, saving costs, improving resource utilization, and extending the overall service life of the system. In actual engineering projects, the specifications, connection methods, and support point positions of crane beams may vary. The detachable hinge bracket 31 can be flexibly adjusted and replaced to match different models of crane beams or connection requirements, thereby enhancing the system's versatility and on-site adaptability.

[0046] In some embodiments of this utility model, such as Figures 3 to 4As shown, the central axis of the connecting hole on the support plate 34 coincides with the central axis of the annular buckle 32. If the central axis of the connecting hole on the support plate 34 and the central axis of the annular buckle 32 do not coincide (there is eccentricity), the pin 331 will be in an eccentric position after installation, resulting in non-uniform contact pressure between the pin 331 and the connecting hole, and between the pin 331 and the annular buckle 32. This can lead to additional bending moment, local wear, increased friction, or even jamming during operation. By ensuring that the central axes of the two coincide, the pin 331 is in a perfectly centered state, with uniform force, which greatly reduces the risk of abnormal wear and structural damage. In addition, when the annular buckle 32 and the hole on the support plate 34 are coaxial, they together form a geometrically symmetrical and force-balanced limiting structure, which can more effectively restrict the axial movement or disengagement of the pin 331 and prevent the pin 331 from undergoing slight displacement or tilting under vibration or impact. This coaxial constraint method enhances the stability of the pin 331 installation and improves the reliability of the entire connection part in long-term operation. Furthermore, when the center lines of the relevant parts are aligned, the stress distribution on the contact surface is more uniform, which can avoid local stress concentration and high-frequency wear; it helps to extend the fatigue life of key parts such as pin 331, the edge of the hole in support plate 34, and ring buckle 32, and reduce maintenance frequency and replacement costs.

[0047] As described above, the flexible large-span crane beam trolley of this utility model has the following beneficial effects: When in use, the flexible large-span crane beam trolley of this utility model, through the combined design of the joint bearing 332 and the bearing assembly 33, allows for a certain range of angular displacement, rotation, or swaying between the crane beam and the trolley frame 1, which can effectively compensate for the dynamic deformation of the crane beam caused by factors such as self-weight deflection, thermal expansion and contraction, load offset, and start-stop impact during operation; it avoids the problems of additional stress, structural damage, and connection failure caused by deformation obstruction in traditional rigid connections, and significantly improves the safety and structural reliability of the crane system operation.

[0048] The flexible connection structure enables the crane beam to adaptively adjust its posture during movement, reducing instability, rail wear, vibration, and sway caused by deformation. It helps improve the stability, positioning accuracy, and operational safety of the crane, and is particularly suitable for industrial hoisting scenarios with high requirements for operational quality.

[0049] Because a certain degree of relative movement is allowed between the crane beam and the trolley frame 1, phenomena such as concentrated stress, abnormal friction, and jamming are effectively avoided. The combination of the spherical bearing 332 and the positioning sleeve 333 makes the load transmission more uniform, reduces local wear and fatigue damage to components such as the pin 331, support plate 34, and trolley frame 1, thereby helping to extend the service life of key moving parts, reduce maintenance frequency and replacement costs, and improve the system economy.

[0050] With the support plate 34 symmetrically arranged, the bearing group 33 centrally installed, and the spherical bearing 332 providing multi-directional compensation, the overall structure maintains stability and load-bearing capacity while achieving "flexibility". The design of the pin 331 and the positioning sleeve 333 ensures axial limit and structural reliability, avoiding loose connection or abnormal displacement. It is suitable for long-term reliable operation of large-span, large-tonnage crane beams.

[0051] Key components such as bearing assembly 33 and hinge bracket 31 adopt detachable connection methods, which facilitates quick inspection, replacement or adjustment when wear, deformation or failure occurs, improves the adaptability of the equipment and reduces the difficulty of operation and maintenance and downtime.

[0052] In summary, the trolley for the flexible large-span crane beam of this utility model has the following advantages:

[0053] 1. Effectively compensates for dynamic deformation, improving system safety and structural reliability:

[0054] The crane beam avoids the additional stress, structural damage and connection failure caused by traditional rigid connections due to angular displacement, rotation or sway caused by self-weight deflection, thermal expansion and contraction, load offset, start-stop impact, etc., which significantly improves the safety, stability and structural durability of the crane system.

[0055] 2. The structure is stable and reliable with strong load-bearing capacity:

[0056] By symmetrically arranging the support plates 34, centrally installing the bearing assembly 33, and multi-directionally compensating with the spherical bearing 332, "flexibility" is achieved while maintaining the high rigidity and load-bearing capacity of the overall structure. The pin shaft 331 and the positioning sleeve 333 provide reliable axial limiting and structural stability to prevent loosening of the connection or abnormal displacement. It is suitable for the long-term safe and reliable operation of large-span, large-tonnage crane beams.

[0057] 3. Reduce wear and fatigue damage, and extend component service life:

[0058] The reasonable combination of the spherical bearing 332 and the positioning sleeve 333 makes the key moving parts such as the pin 331, the support plate 34, and the trolley frame 1 more evenly stressed and reduces local wear; it extends the service life of key parts, reduces the maintenance frequency and replacement cost, and improves the economic efficiency of system operation.

[0059] In summary, this utility model effectively overcomes the various shortcomings of the prior art and has high industrial application value.

[0060] The above embodiments are merely illustrative of the principles and effects of this utility model and are not intended to limit the scope of this utility model. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of this utility model. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in this utility model should still be covered by the claims of this utility model.

Claims

1. A trolley for a flexible, large-span crane beam, characterized in that, include: A trolley frame, with a bracket assembly for connecting the support end of the crane beam fixedly connected to the upper part of the trolley frame, and a wheel set installed at the lower part of the trolley frame; The support assembly includes: a hinge bracket, a bearing assembly, and a support plate. The bearing assembly is installed between the support plates on two symmetrical sides. The hinge bracket has a through hole and is sleeved on the bearing assembly through the through hole. At least two support plates are symmetrically fixed on both sides of the trolley frame. One end of the hinge bracket is fixedly connected to the support end of the crane beam, and the other end is connected to the trolley frame through the bearing assembly. The bearing assembly includes: a spherical plain bearing, a locating sleeve, and a pin. The spherical plain bearing is coaxially sleeved on the outer ring of the pin to compensate for the dynamic deformation of the crane beam during operation. At least two locating sleeves are symmetrically sleeved on both ends of the spherical plain bearing to restrict the movement of the spherical plain bearing along the axial direction of the pin.

2. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The pin also passes through a through hole on the hinge bracket and a connecting hole on the support plate to limit the displacement of the bearing assembly along the axial direction of the pin.

3. The trolley for a flexible large-span crane beam according to claim 1 or 2, characterized in that: The bracket assembly also includes a ring buckle that passes through the pin and is mounted on the support plate.

4. The trolley for a flexible large-span crane beam according to claim 3, characterized in that: At least two of the ring buckles are sleeved on the symmetrical ends of the pin and fixed to the outer side walls of the opposite sides of the support plate. The ring buckles are detachably connected to the support plate through connectors.

5. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The support plates are symmetrically fixed to both sides of the trolley frame by welding.

6. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The wheel assembly includes multiple wheels, which are evenly distributed along the underside of the trolley frame.

7. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The central axis of the pin is on the same straight line as the central axis of the through hole on the hinge bracket.

8. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The spherical bearing and the pin are slidably connected.

9. The trolley for a flexible large-span crane beam according to claim 1, characterized in that: The hinge bracket is detachably connected to the support end of the crane beam and the pin shaft, respectively.

10. The trolley for a flexible large-span crane beam according to claim 3, characterized in that: The central axis of the connecting hole on the support plate coincides with the central axis of the ring buckle.

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