Cross hinge beam type torque equalizer for belt conveyors

Abstract

This invention discloses a cross-hinged beam type anti-reverse torque balancing device for belt conveyors, belonging to the field of belt conveyor safety protection. The device includes a shaft support, a crossbeam, and a shaft. The shaft support is fixed to the equipment foundation and has shaft holes. Both the shaft support and the crossbeam have shaft holes, and the shaft passes through both the shaft holes in the shaft support and the crossbeam. The shaft support and the crossbeam swing relative to each other about the center line of the shaft. The two ends of the crossbeam are connected to the ends of the torque arms of each anti-reverse device via cross-shafts and other connecting components, forming a seesaw structure. At the instant the conveyor reverses direction, the crossbeam adaptively swings, absorbing the idling angle difference between the anti-reverse devices that are subjected to force first and the one subjected to force later. The swing adjustment causes the remaining anti-reverse devices to synchronously enter the anti-reverse state, and the lever principle equalizes the positive pressure at both ends. This invention is a purely mechanical structure, simple and reliable, easy to maintain, and low in cost. It significantly improves the operational stability of the anti-reverse system and can operate stably for a long time in harsh industrial environments.

Description

Technical Field

[0001] This invention belongs to the technical field of safety protection devices for belt conveyors, and specifically relates to a cross-hinged beam type reverse torque balancing device for belt conveyors. Background Technology

[0002] Belt conveyors are core conveying equipment in industries such as mining, ports, chemicals, and building materials. Belt conveyors that are inclined upwards are prone to reverse and slide downwards under the influence of gravity of materials when they stop, lose power, or experience drive slippage. This can lead to material accumulation at the tail of the machine, damage to equipment, and even safety accidents such as personal injury or death.

[0003] For belt conveyors with high lifting heights and large conveying capacities, the backstop torque is extremely large. Using a single backstop to bear the entire backstop torque often results in the difficulty of selecting a suitable model, necessitating non-standard designs. Furthermore, the roller shafts and hubs involved in backstop operation also need to be designed to be very large, increasing design complexity and significantly raising the procurement costs of backstops and rollers. Using multiple backstops to distribute the backstop force is an effective way to solve this problem.

[0004] Due to factors such as the required clearance in the backstop structure, machining accuracy, clearance and deformation of the backstop torque transmission system, and internal aging and wear of the backstop, there is a difference in the reverse idling angle among the various backstops when they engage in backstop operation. This results in a time difference in the force applied to each backstop, with the backstop that is applied first bearing a larger or all of the backstop force. This often leads to the individual failure of each backstop, causing them to fail one by one. The "Engineering Technical Standard for Belt Conveyors (GB50431-2020)" stipulates that "when a belt conveyor is equipped with multiple backstop devices: a torque-balanced backstop device should be used; if the force cannot be balanced, each device should be selected based on 100% of the total backstop force." In other words, when multiple backstops are used to share the backstop torque, a torque-balanced device is required. Otherwise, each backstop would still need to be considered as bearing the entire backstop torque of the belt conveyor, defeating the purpose of configuring multiple backstops.

[0005] There are two main types of torque balancing devices for backstops: spring balancing devices and hydraulic balancing devices.

[0006] The spring balancing device uses springs pressed at the ends of the torque arms of each backstop. The elastic compression of the springs absorbs the difference in reverse idling angles between the backstops. Each spring has a different pre-compression amount, allowing each backstop to bear the same (or similar) backstop torque even with varying spring compression. However, the pre-compression amount of the springs needs to be estimated based on factors such as the backstop's machining accuracy and internal clearance, the clearance and deformation of the backstop torque transmission system, the aging and wear of the backstop's internal components, and the conveyor belt tension. Precise calculation is practically impossible. Furthermore, the required spring compression stroke varies depending on the belt conveyor's shutdown conditions, and the spring balancing device cannot be adjusted in real time to adapt to changing operating conditions. In summary, although the spring balancing device for backstops has a simple structure, its torque balancing effect is poor, and its operation is cumbersome; therefore, it is rarely used in engineering practice.

[0007] The hydraulic balancing device uses hydraulic cylinders pressed at the ends of the torque arms of each backstop. The rodless chambers of each cylinder are interconnected, balancing the oil pressure and thus providing approximately equal forces to the torque arms of the backstops, achieving torque balancing. While the hydraulic balancing device offers good torque balancing, it requires a complex hydraulic system, resulting in high system complexity and cost. Furthermore, belt conveyors operate under harsh conditions, prone to material falling, which could easily cause serious accidents if it hits the pipeline; therefore, the safety of the hydraulic balancing device needs improvement. Additionally, the hydraulic cylinders have poor absorption of the impact of the backstop force, easily generating shocks and damaging components. The hydraulic balancing device also requires a hydraulic pump for pressurization, resulting in high energy consumption.

[0008] Both spring balancing devices and hydraulic balancing devices have very obvious drawbacks and are rarely used in actual engineering practice. Summary of the Invention

[0009] To address the shortcomings of existing technologies, the purpose of this invention is to provide a cross-hinged beam type reverse torque balancing device for belt conveyors.

[0010] The technical solution adopted in the invention is: a cross-hinged shaft beam type reverse torque balancing device for belt conveyors, the key technical points of which are: including a shaft support, a shaft, and a crossbeam; The rotating shaft bracket is fixedly installed, and the rotating shaft bracket is provided with a shaft hole. The crossbeam is provided with a shaft hole, and the rotating shaft passes through both the shaft hole of the rotating shaft bracket and the shaft hole of the crossbeam. The crossbeam and the rotating shaft bracket are rotatably connected by the rotating shaft, and the rotating shaft bracket and the crossbeam swing relative to each other about the center line of the rotating shaft. Both ends of the crossbeam are respectively provided with load-bearing areas for cooperating with the end of the torque arm of the backstop; When the belt conveyor reverses, the first backstop that is subjected to force presses one end of the crossbeam through its torque arm, causing the crossbeam to rotate around the shaft. The other end of the crossbeam swings in the opposite direction and pushes another torque arm to move in the opposite direction to absorb the reverse idling angle of the corresponding backstop. The crossbeam, through the lever structure formed by the shaft, keeps the positive pressure between the two ends of the crossbeam and the torque arm equal, thereby achieving synchronous and balanced distribution of the reverse torque of each backstop.

[0011] In the above scheme, a support device is provided in the stress-bearing area. The support device is a cross hinge structure, including a cross hinge, an upper hinge frame and a lower hinge frame. The upper hinge bracket is fixed to the end of the torque arm of the backstop, and the lower hinge bracket is fixed to the end of the crossbeam; the cross hinge shaft passes through the shaft holes of the upper hinge bracket and the lower hinge bracket, connecting the torque arm to the crossbeam; the shaft hole of the upper hinge bracket is a round hole or an elongated hole with its long axis parallel to the axis of the torque arm; the shaft hole of the lower hinge bracket is a round hole or an elongated hole with its long axis parallel to the axis of the crossbeam.

[0012] In the above scheme, the cross hinge structure further includes an elastic element and a guide element. The elastic element is clamped between the cross hinge and the cross beam or between the cross hinge and the torque arm. The guide element is fixed to a corresponding component to guide the elastic element to extend and retract axially to buffer and prevent adverse impact. A gap is formed between the circular or oblong hole on the lower hinge bracket and the cross hinge installed therein. The gap is configured to allow the cross hinge to move within the hole to provide a buffer stroke. Alternatively, a gap is formed between the circular or oblong hole on the upper hinge bracket and the cross hinge installed therein. The gap is configured to allow the cross hinge to move within the hole to provide a buffer stroke.

[0013] The load-bearing area is provided with a support device, which is a cross-shaft structure, including a cross-shaft, an upper hinge shaft, a lower hinge shaft, an upper hinge shaft support, and a lower hinge shaft support. The cross shaft bracket has an upper shaft hole and a lower shaft hole. The axes of the upper shaft hole and the lower shaft hole are perpendicular to each other and do not intersect. The upper shaft hole is a circular hole or an elongated hole with its major axis parallel to the axis of the torque arm. The lower shaft hole is a circular hole or an elongated hole with its major axis parallel to the axis of the crossbeam. The upper hinge shaft bracket is fixed to the end of the torque arm, and the upper hinge shaft passes through the upper hinge shaft bracket and the upper shaft hole. The lower hinge shaft bracket is fixed to the end of the crossbeam, and the lower hinge shaft passes through the lower hinge shaft bracket and the lower shaft hole.

[0014] In the above scheme, the shaft hole of the upper hinge shaft bracket is an elongated oval hole with its major axis perpendicular to the axis of the torque arm; or, the shaft hole of the lower hinge shaft bracket is an elongated oval hole with its major axis perpendicular to the axis of the crossbeam, thereby reserving a buffer stroke; the cross shaft bracket structure also includes an elastic element and a guide element, the elastic element being sandwiched between the cross shaft bracket and the upper hinge shaft bracket, or sandwiched between the cross shaft bracket and the lower hinge shaft bracket, and the guide element being fixed on the corresponding component to guide the elastic element to extend and retract axially to buffer and prevent reverse impact.

[0015] The above solution also includes a torque arm rotation guide mechanism, which is disposed on both sides of the torque arm to restrict the torque arm to rotate only around the inner ring of the backstop, so as to prevent the torque arm from laterally swaying.

[0016] The above scheme includes at least one crossbeam, a rotating shaft, a rotating shaft support, and at least one secondary crossbeam, a secondary rotating shaft, and a secondary rotating shaft support; the crossbeam is rotatably connected to the rotating shaft support via the rotating shaft, and both ends of the crossbeam are used to abut against the torque arm of a backstop; the secondary crossbeam is rotatably connected to the secondary rotating shaft support via the secondary rotating shaft, and the secondary rotating shaft support is used for fixed installation on a foundation or equipment; the rotating shaft support is fixedly installed on the secondary crossbeam; wherein, the secondary crossbeam is configured as follows: One end directly abuts against the torque arm of a backstop, and the other end is fixed to the shaft bracket; or... Each end is fixed with a shaft bracket, and the secondary crossbeam does not directly abut against the torque arm of the backstop.

[0017] The beneficial effects of this invention are as follows: When a belt conveyor is equipped with multiple backstops, the different reverse idling angles of each backstop before entering the backstop working condition cause the backstops to not be subjected to force simultaneously. The backstop that is subjected to force first bears a larger backstop torque or bears all the backstop torque required by the belt conveyor, resulting in uneven force distribution among the backstops or even their individual failure, leading to the failure of all backstops. This invention addresses the above problem by proposing a cross-hinged beam type backstop torque balancing device for belt conveyors. It adopts a seesaw-like structure, where the beam swings around the pivot to adapt to the different reverse idling angles of each backstop, enabling multiple backstops to simultaneously bear the backstop torque. Simultaneously, utilizing the torque balancing effect of the seesaw structure, the pressure values ​​at the ends of the torque arms of each backstop are basically the same, thereby achieving torque balance among the backstops.

[0018] This invention employs a purely mechanical structure, which is simple to manufacture and significantly less expensive than hydraulic balancing devices. Furthermore, the purely mechanical structure offers higher reliability than hydraulic balancing devices. This invention achieves a high degree of synchronization in the torque distribution of each backstop, solving the problem of the first backstop being overloaded and damaged, leading to the sequential failure of the remaining backstops. This invention ensures a highly uniform distribution of the backstop torque across all backstops, improving the uniformity of torque distribution. Its synchronization and torque balancing effects are far superior to spring balancing devices. This invention also incorporates elastic elements, effectively buffering the impact of the backstop torque on backstops and other equipment and structures, improving system safety and component lifespan. Its buffering performance is far superior to hydraulic balancing devices. This invention requires no secondary adjustments after installation, is simple to operate and maintain, and can adapt to the backstop requirements of belt conveyors under different operating conditions, eliminating the need for careful spring stroke calculations before installation, unlike spring balancing devices. This invention is a non-powered mechanical structure, requiring no power supply, and is more energy-efficient than hydraulic balancing devices. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the basic structure of the cross-hinged beam type reverse torque balancing device for belt conveyors in Embodiment 1 of the present invention; Figure 2 This is a schematic diagram of the conventional cross-hinged shaft connection scheme used in Embodiment 2 of the present invention; Figure 3 In Embodiment 2 of the present invention Figure 2 A side view of a conventional cross-hinged shaft connection scheme shown; Figure 4 In Embodiment 2 of the present invention Figure 2 The diagram shows the working state of a conventional cross-hinged shaft connection under non-return conditions. Figure 5 This is a schematic diagram of the cross-hinged shaft connection scheme with buffer clearance used in Embodiment 3 of the present invention; Figure 6 In Embodiment 3 of the present invention Figure 5 A side view (partial sectional view) of the cross-hinged shaft scheme with buffer clearance shown; Figure 7 This is a schematic diagram of the conventional cross-shaft bracket connection scheme used in Embodiment 4 of the present invention; Figure 8In Embodiment 4 of the present invention Figure 7 The side view shown is of a conventional cross-shaped bracket connection scheme. Figure 9 This is a schematic diagram of the cross shaft bracket 71 in Embodiment 4 of the present invention; Figure 10 This is a schematic diagram of the cross-shaft bracket connection scheme with elongated holes and buffers used in Embodiment 5 of the present invention; Figure 11 In Embodiment 5 of the present invention Figure 10 A side view of the cross-shaped bracket connection scheme with elongated holes and buffers.

[0021] Figure 12 This is a schematic diagram of the structure of the torque arm rotation guide mechanism 102 in Embodiment 6 of the present invention; Figure 13 This is a simplified connection diagram of the multi-stage balancing structure scheme under four backstop conditions in Embodiment 7 of the present invention; Figure 14 This is a simplified connection diagram of the multi-stage equalization structure scheme under three backstop conditions in Embodiment 8 of the present invention.

[0022] The serial numbers in the diagram are explained as follows: 1. Rotary shaft support; 2. Rotary shaft; 3. Crossbeam; 4. Torque arm; 5. Support device; 6. Cross hinge structure; 6. Cross hinge shaft; 6. Upper hinge shaft support; 6. Lower hinge shaft support; 6. Round hole; 6. Oblong hole; 6. Round hole; 6. Oblong hole; 6. Cross shaft support structure; 7. Cross shaft support; 7. Upper hinge shaft; 7. Lower hinge shaft; 7. Upper hinge shaft support; 7. Lower hinge shaft support; 7. Upper shaft hole; 7. Lower shaft hole; 7.11; Lower shaft hole; 7.12; Elastic element; 100; Guide element; 101; Torque arm rotation guide mechanism; 102; Secondary rotating shaft support; 1001; Secondary rotating shaft; 2001; and Secondary crossbeam; 3001. Detailed Implementation

[0023] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the following description is provided in conjunction with the accompanying drawings. Figures 1-14 The embodiments will be described in further detail below.

[0024] Example 1: Basic beam-type reverse torque balancing device.

[0025] like Figure 1As shown in this embodiment, a cross-hinged shaft beam type reverse torque balancing device for a belt conveyor includes a shaft support 1, a shaft 2, and a crossbeam 3. The shaft support 1 is fixedly installed on the equipment foundation or conveyor structural components. In this embodiment, the top of the shaft support 1 is provided with an upper connecting ear plate, and the middle of the crossbeam 3 is provided with a lower connecting ear plate. The upper and lower connecting ear plates are stacked vertically, and each has a coaxial central hole. The shaft 2 passes through the two central holes, forming a hinged structure between the shaft support 1 and the crossbeam 3, allowing the crossbeam 3 to swing freely around the central axis of the shaft 2 (i.e., a seesaw swing). At the same time, the upper and lower connecting ear plates mutually limit each other in the axial direction of the shaft 2, preventing the crossbeam 3 from moving along the axis and ensuring that the force is always within the central plane. The two ends of the crossbeam 3 are respectively provided with load-bearing areas for cooperating with the ends of the torque arms 4 of the backstop; the two ends of the crossbeam 3 (i.e. the load-bearing areas) are respectively located directly below the torque arms 4 of the two backstops (not shown in the figure), and the ends of the crossbeam 3 are in direct contact with the ends of the torque arms 4 or indirect contact through the support device 5 in the subsequent embodiment.

[0026] At the instant the belt conveyor reverses, due to the difference in reverse idling angle among the backstops, the backstop with the smaller reverse idling angle is subjected to force first, and its torque arm 4 descends to press one end of the crossbeam 3. After being subjected to force, the crossbeam 3 rotates around the shaft 2, and its other end tilts upward, pushing the torque arm 4 at that end to rotate in the opposite direction to absorb the reverse idling angle of the corresponding backstop. Since the crossbeam 3 is a rigid lever with the shaft 2 as the fulcrum, according to the torque balance principle, the positive pressure applied to the torque arm 4 at both ends of the crossbeam 3 is the same, thereby forcing each backstop to enter the backstop working state synchronously, realizing the adaptive and balanced distribution of the backstop torque.

[0027] Example 2: Conventional cross-hinged shaft connection structure.

[0028] like Figure 2 , Figure 3 and Figure 4 As shown, in this embodiment, the support device 5 adopts a cross hinge structure 6. The cross hinge structure 6 includes a cross hinge 61, an upper hinge bracket 62, and a lower hinge bracket 63.

[0029] The upper hinge bracket 62 is fixedly installed at the end of the backstop torque arm 4. The upper hinge bracket 62 has a shaft hole, which is a round hole or an oblong hole 622 (the major axis of the oblong hole 622 is parallel to the axis of the torque arm 4). The lower hinge bracket 63 is fixedly installed at the end of the crossbeam 3. The lower hinge bracket 63 has a shaft hole, which is a round hole or an oblong hole 632 (the major axis of the oblong hole 632 is parallel to the axis of the crossbeam 3).

[0030] A cross hinge 61 passes through the shaft holes of the upper hinge bracket 62 and the lower hinge bracket 63, hingely connecting the torque arm 4 to the crossbeam 3. The cross hinge 61 contains two orthogonal hinge shafts, capable of simultaneously accommodating angular changes caused by the swinging of the crossbeam 3 and the rotation of the torque arm 4. During the swinging of the crossbeam 3, the bidirectional hinge action of the cross hinge 61 ensures effective torque transmission between the torque arm 4 and the crossbeam 3.

[0031] Example 3: Cross hinge structure with buffer gap.

[0032] like Figure 5 and Figure 6 As shown, based on Embodiment 2, this embodiment further defines a cross-hinged shaft structure 6. A gap is formed between the circular hole 631 or oblong hole 632 on the lower hinge bracket 63 and the cross-hinged shaft 61 installed therein. This gap is configured to allow the cross-hinged shaft 61 to move within the hole to provide a buffer stroke. The cross-hinged shaft structure 6 of this embodiment also includes an elastic element 100 and a guide element 101. The elastic element 100 is disposed between the bottom of the cross-hinged shaft 61 and the bearing surface of the crossbeam 3. The guide element 101 is fixed to the lower end face of the cross-hinged shaft 61 or to the upper surface of the crossbeam 3 to ensure that the extension and retraction direction of the elastic element 100 is always consistent with the axial direction of the cross-hinged shaft 61. In this embodiment, the elastic element 100 is a spring or a rubber component.

[0033] When the backstop reverses, the torque arm 4 presses down on the cross hinge shaft 61 through the upper hinge shaft bracket 62. The cross hinge shaft 61 first creates a free stroke in the large clearance circular hole of the lower hinge shaft bracket 63, compressing the elastic element 100 below to absorb the impact. After the elastic element 100 is fully compressed, the cross hinge shaft 61 makes rigid contact with the hole wall of the lower hinge shaft bracket 63, transmitting the torque to the crossbeam 3.

[0034] Example 4: Conventional cross-shaft bracket connection structure.

[0035] like Figure 7 , Figure 8 and Figure 9 As shown, the support device 5 in this embodiment adopts a cross-shaft frame structure 7. The cross-shaft frame structure 7 includes a cross-shaft frame 71, an upper hinge shaft 72, a lower hinge shaft 73, an upper hinge shaft bracket 74, and a lower hinge shaft bracket 75.

[0036] The cross shaft bracket 71 is a steel bracket machined as a whole, with an upper shaft hole 711 at the top and a lower shaft hole 712 at the bottom. The axis of the upper shaft hole 711 and the axis of the lower shaft hole 712 are perpendicular to each other in space, and the two axes do not intersect (forming a spatial intersection structure).

[0037] The upper hinge bracket 74 is fixed to the end of the torque arm 4, and the upper hinge shaft 72 passes through the shaft hole of the upper hinge bracket 74 and the upper shaft hole 711 of the cross shaft bracket 71, achieving a hinge connection. The lower hinge bracket 75 is fixed to the end of the cross beam 3, and the lower hinge shaft 73 passes through the shaft hole of the lower hinge bracket 75 and the lower shaft hole 712 of the cross shaft bracket 71, achieving a hinge connection. The cross shaft bracket 71, as a force transmission medium, isolates the lateral deflection of the torque arm 4 and the angular change of the longitudinal swing of the cross beam 3, and realizes the transmission of force, making the device operate more smoothly.

[0038] Example 5: Cross-shaped bracket structure with elongated hole and buffer.

[0039] like Figure 10 and Figure 11 As shown, based on Embodiment 4, this embodiment further introduces a buffer and sliding structure. The shaft hole of the upper hinge shaft bracket 74 is set as an oblong hole, the major axis of which is perpendicular to the axial direction of the torque arm 4; and / or, the shaft hole of the lower hinge shaft bracket 75 is set as an oblong hole, the major axis of which is perpendicular to the axial direction of the crossbeam 3.

[0040] The cross-shaft frame structure 7 also includes an elastic element 100 and a guide element 101. In this embodiment, the elastic element 100 is a spring or a rubber component. The elastic element 100 is disposed between the intermediate connecting plate of the cross-shaft frame 71 and the upper hinge shaft support 74, or between the intermediate connecting plate of the cross-shaft frame 71 and the lower hinge shaft support 75. The guide element 101 is fixed between the cross-shaft frame 71 and the corresponding support to ensure that the extension and retraction direction of the elastic element 100 is always consistent with the direction of its corresponding hinge shaft axis. This structure utilizes the sliding stroke provided by the elongated hole and the deformation of the elastic element 100 to effectively absorb the instantaneous severe impact load generated by the counter-torque, protecting the structural components of the device from damage.

[0041] Example 6: Torque arm rotation guide mechanism.

[0042] like Figure 12 As shown, based on all the above embodiments, this device also includes a torque arm rotation guide mechanism 102. The torque arm rotation guide mechanism 102 is disposed on the left and right sides of the backstop torque arm 4, and can specifically adopt a structure such as a limiting plate, guide rail or stop block that abuts against both sides of the torque arm 4.

[0043] The torque arm rotation guide mechanism 102 is used to strictly limit the torque arm 4 to rotate vertically only around the central axis of the inner ring of the backstop, preventing the torque arm 4 from laterally swaying due to the slight lateral displacement caused by the swing of the crossbeam 3. This effectively avoids harmful torque caused by the deviation of the positive pressure between the torque arm 4 and the support device 5 from the rotation plane of the backstop, thereby preventing the backstop's internal components from being "broken" or damaged.

[0044] Example 7: Multi-stage equalization structure under four backstop conditions.

[0045] When a belt conveyor is equipped with three, four, or even more backstops, a single crossbeam 3 cannot balance the torque of all the backstops. To address this situation, this embodiment can be expanded in multiple stages. Specifically, multiple sets of the aforementioned shaft support 1, shaft 2, and crossbeam 3 are combined to form a multi-stage series-parallel structure.

[0046] like Figure 13 As shown, for the four-way check valve operation, a two-stage seesaw series-parallel structure is adopted, consisting of three sets of rotating shaft supports, rotating shafts, and crossbeams. The connection relationships of the three sets of rotating shaft supports, rotating shafts, and crossbeams are not entirely the same. To distinguish them, two sets of rotating shaft supports, rotating shafts, and crossbeams have the same connection relationship and are still labeled as rotating shaft support 1, rotating shaft 2, and crossbeam 3; the third set is labeled as secondary rotating shaft support 1001, secondary rotating shaft 2001, and secondary crossbeam 3001. The specific connection relationship is as follows: the left and right ends of the two crossbeams 3 respectively abut against the torque arms 4 of one check valve, abutting against the torque arms 4 of four check valves in total; each crossbeam 3 is rotatably connected to its respective rotating shaft support 1 through its own rotating shaft 2, and the two rotating shaft supports 1 are respectively fixed to the two ends of the secondary crossbeam 3001; the secondary crossbeam 3001 is rotatably connected to the secondary rotating shaft support 1001 through the secondary rotating shaft 2001, and the secondary rotating shaft support 1001 is fixed to the foundation or equipment. When there is a time difference in the force applied to the four backstops, the crossbeam 3 swings adaptively around the rotating shaft 2, and the secondary crossbeam 3001 swings adaptively around the secondary rotating shaft 2001, so that all backstops enter the backstop state synchronously, achieving a balanced distribution of torque among the four backstops.

[0047] Example 8: Multi-stage equalization structure under three backstop conditions.

[0048] like Figure 14As shown, for the three-way check valve operation, a two-stage seesaw series structure is adopted, consisting of two sets of rotating shaft supports, rotating shafts, and crossbeams. The connection relationships of the two sets of rotating shaft supports, rotating shafts, and crossbeams are not exactly the same. To distinguish them, one set of rotating shaft supports, rotating shafts, and crossbeams is still labeled as rotating shaft support 1, rotating shaft 2, and crossbeam 3, while the other set is labeled as secondary rotating shaft support 1001, secondary rotating shaft 2001, and secondary crossbeam 3001. The specific connection relationship is as follows: the left and right ends of the crossbeam 3 respectively abut against the torque arm 4 of one backstop, for a total of two backstop torque arms 4; the crossbeam 3 is rotatably connected to the shaft bracket 1 via the rotating shaft 2, and the rotating shaft bracket 1 is fixed to one end of the secondary crossbeam 3001; the other end of the secondary crossbeam 3001 abuts against the torque arm 4 of one backstop; the secondary crossbeam 3001 is rotatably connected to the secondary rotating shaft bracket 1001 via the secondary rotating shaft 2001, and the connection point is located at 2 / 3 of the length of the secondary crossbeam 3001 from the end of the secondary crossbeam 3001 that abuts against the torque arm 4 of the backstop; the secondary rotating shaft bracket 1001 is fixed to the foundation or equipment. When there is a time difference in the force applied to the three backstops, the crossbeam 3 adaptively swings around the rotating shaft 2, and the secondary crossbeam 3001 adaptively swings around the secondary rotating shaft 2001, so that all backstops enter the backstop state synchronously, achieving a balanced distribution of the torque of the three backstops.

[0049] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A cross-hinged beam type reverse torque balancing device for belt conveyors, characterized in that, Includes a pivot bracket (1), a pivot (2), and a crossbeam (3); The rotating shaft bracket (1) is fixedly installed. The rotating shaft bracket (1) is provided with a shaft hole. The crossbeam (3) is provided with a shaft hole. The rotating shaft (2) passes through both the shaft hole of the rotating shaft bracket (1) and the shaft hole of the crossbeam (3). The crossbeam (3) and the rotating shaft bracket (1) are rotatably connected through the rotating shaft (2). The rotating shaft bracket (1) and the crossbeam (3) swing relative to each other about the center line of the rotating shaft (2). The two ends of the crossbeam (3) are respectively provided with a load-bearing area for cooperating with the end of the torque arm (4) of the backstop; When the belt conveyor reverses, the first backstop that is subjected to force presses one end of the crossbeam (3) through its torque arm (4), causing the crossbeam (3) to rotate around the shaft (2). The other end of the crossbeam (3) swings in the opposite direction and pushes another torque arm (4) to move in the opposite direction to absorb the reverse idling angle of the corresponding backstop. The crossbeam (3) is connected to the lever structure formed by the shaft (2) so that the positive pressure between the two ends of the crossbeam (3) and the torque arm (4) is kept equal, thereby realizing the synchronous and balanced distribution of the reverse torque of each backstop.

2. The cross-hinged beam type reverse torque balancing device for belt conveyors according to claim 1, characterized in that: The load-bearing area is provided with a support device (5), which is a cross hinge structure (6), including a cross hinge (61), an upper hinge frame (62) and a lower hinge frame (63). The upper hinge bracket (62) is fixed to the end of the torque arm (4) of the backstop, and the lower hinge bracket (63) is fixed to the end of the crossbeam (3); the cross hinge shaft (61) passes through the shaft hole of the upper hinge bracket (62) and the shaft hole of the lower hinge bracket (63) to connect the torque arm (4) to the crossbeam (3); the shaft hole of the upper hinge bracket (62) is a round hole (621) or an elongated hole (622) with its long axis parallel to the axis of the torque arm (4); the shaft hole of the lower hinge bracket (63) is a round hole (631) or an elongated hole (632) with its long axis parallel to the axis of the crossbeam (3).

3. The cross-hinged beam type reverse torque balancing device for belt conveyors according to claim 2, characterized in that: The cross hinge structure (6) further includes an elastic element (100) and a guide element (101). The elastic element (100) is clamped between the cross hinge (61) and the cross beam (3) or between the cross hinge (61) and the torque arm (4). The guide element (101) is fixed on the corresponding component to guide the elastic element (100) to extend and retract axially to buffer and stop the impact. A gap is formed between the round hole (631) or oblong hole (632) on the lower hinge bracket (63) and the cross hinge shaft (61) installed therein, the gap being configured to allow the cross hinge shaft (61) to move within the hole to provide a buffer stroke; or, a gap is formed between the round hole (621) or oblong hole (622) on the upper hinge bracket (62) and the cross hinge shaft (61) installed therein, the gap being configured to allow the cross hinge shaft (61) to move within the hole to provide a buffer stroke.

4. The cross-hinged beam type reverse torque balancing device for belt conveyors according to claim 1, characterized in that: The load-bearing area is provided with a support device (5), which is a cross shaft frame structure (7), including a cross shaft frame (71), an upper hinge shaft (72), a lower hinge shaft (73), an upper hinge shaft support (74), and a lower hinge shaft support (75). The cross shaft bracket (71) has an upper shaft hole (711) and a lower shaft hole (712). The axes of the upper shaft hole (711) and the lower shaft hole (712) are perpendicular to each other and do not intersect. The upper shaft hole (711) is a round hole or an elongated hole with its long axis parallel to the axis of the torque arm 4. The lower shaft hole (712) is a round hole or an elongated hole with its long axis parallel to the axis of the crossbeam 3. The upper hinge shaft bracket (74) is fixed at the end of the torque arm (4). The upper hinge shaft (72) passes through the upper hinge shaft bracket (74) and the upper shaft hole (711). The lower hinge shaft bracket (75) is fixed at the end of the crossbeam (3). The lower hinge shaft (73) passes through the lower hinge shaft bracket (75) and the lower shaft hole (712).

5. The cross-hinged beam type reverse torque balancing device for belt conveyors according to claim 4, characterized in that: The shaft hole of the upper hinge bracket (74) is an elongated hole with its long axis perpendicular to the axis of the torque arm (4); or, the shaft hole of the lower hinge bracket (75) is an elongated hole with its long axis perpendicular to the axis of the crossbeam (3), thereby reserving a buffer stroke; the cross shaft frame structure (7) also includes an elastic element (100) and a guide element (101). The elastic element (100) is sandwiched between the cross shaft frame (71) and the upper hinge bracket (74), or between the cross shaft frame (71) and the lower hinge bracket (75). The guide element (101) is fixed on the corresponding component to guide the elastic element (100) to extend and retract axially to buffer and stop the impact.

6. A cross-hinged beam type reverse torque balancing device for belt conveyors according to any one of claims 1 to 5, characterized in that: It also includes a torque arm rotation guide mechanism (102), which is disposed on both sides of the torque arm (4) to restrict the torque arm (4) to rotate only around the inner ring of the backstop, so as to prevent the torque arm (4) from lateral swaying.

7. The cross-hinged beam type reverse torque balancing device for belt conveyors according to claim 1, characterized in that: It includes at least one crossbeam (3), a rotating shaft (2), a rotating shaft support (1), and at least one secondary crossbeam (3001), a secondary rotating shaft (2001), and a secondary rotating shaft support (1001); the crossbeam (3) is rotatably connected to the rotating shaft support (1) via the rotating shaft (2), and both ends of the crossbeam (3) are respectively used to abut the torque arm of a backstop; the secondary crossbeam (3001) is rotatably connected to the secondary rotating shaft support (1001) via the secondary rotating shaft (2001), and the secondary rotating shaft support (1001) is used for fixed installation on a foundation or equipment; the rotating shaft support (1) is fixedly installed on the secondary crossbeam (3001); wherein, the secondary crossbeam (3001) is configured as follows: One end directly abuts against the torque arm of a backstop, and the other end is fixed to the rotating shaft bracket (1); or, Each end is fixed with a shaft bracket (1), and the secondary crossbeam (3001) does not directly abut against the torque arm of the backstop.

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