Wheel-bucket excavator experimental platform suitable for high-cold environment

Abstract

The application discloses a wheel-bucket excavator experimental platform suitable for an alpine environment and relates to the technical field of mine mechanical test equipment, comprising a simulated rock wall, a wheel-bucket test device and a strain gauge; the wheel-bucket test device comprises a wheel-bucket assembly and a plurality of buckets uniformly arranged along the circumference of the wheel-bucket assembly, and a plurality of bucket teeth are arranged on the outer side of the bucket and directly contact the simulated rock wall; the strain gauge is inlaid in the connection between the bucket tooth and the bucket and is used for collecting the horizontal and vertical torsional stress changes of the bucket tooth; the simulated rock wall is arranged to simulate the physical properties of rock-soil bodies in the alpine environment, the bucket teeth directly contact the simulated rock wall to realize accurate simulation of the digging working condition, and the technical problem that the existing experimental platform cannot be adapted to the alpine environment is solved, thereby providing an experimental basis in line with actual working conditions for performance verification of the wheel-bucket excavator used in the alpine environment.

Description

Technical Field

[0001] This invention relates to the field of mining machinery testing equipment technology, and in particular to a bucket wheel excavator testing platform suitable for cold environments. Background Technology

[0002] Bucket wheel excavators, as core excavating equipment in large-scale open-pit mines and water conservancy projects, occupy an important position in earthwork excavation and material transportation due to their efficient continuous operation capabilities. As resource development extends to high-altitude and frigid regions, the extreme cold environment (typically referring to temperatures below -20℃, accompanied by permafrost, low-temperature weathered rock, and other special geological conditions) places stringent demands on the performance of bucket wheel excavators. Low temperatures cause significant changes in the physical and mechanical properties of soil and rock (such as increased hardness, increased brittleness, and changes in shear strength in permafrost), while also greatly affecting the structural strength, wear resistance, and operational reliability of key components (such as bucket teeth and bucket wheel assemblies). This can easily lead to bucket tooth breakage, accelerated component wear, and movement jamming, severely restricting the equipment's operating efficiency and service life.

[0003] To ensure the operational stability and safety of bucket wheel excavators used in cold environments, before the equipment is developed and mass-produced, it is necessary to simulate actual working conditions through a dedicated experimental platform to comprehensively verify and optimize the equipment performance, the structural reliability of key components, and operating parameters.

[0004] However, existing bucket wheel excavator test platforms are mostly designed for normal temperature environments, making them unsuitable for the special operational needs of extremely cold environments, and have many technical shortcomings, as follows: As a core, vulnerable component that directly contacts the soil and rock, the stress state of the bucket teeth directly determines the equipment's digging efficiency and component lifespan. Existing platforms mostly use external sensors or single-dimensional acquisition devices to obtain bucket tooth stress data, which cannot simultaneously capture stress and strain changes in multiple dimensions such as horizontal, vertical, and torsional stress. Furthermore, external sensors are susceptible to digging impacts and environmental interference, resulting in poor data accuracy and stability. This makes it difficult for R&D personnel to fully grasp the mechanical response characteristics of the bucket teeth during complex digging operations, and to accurately guide the structural optimization design of the bucket teeth and bucket wheel assembly.

[0005] The existing power transmission structure mostly adopts a single transmission mode, which makes it difficult to achieve precise switching of power direction and flexible adjustment of movement speed, and cannot adapt to the experimental requirements under different excavation depths and different rock and soil hardness.

[0006] Therefore, it is necessary to invent a bucket wheel excavator experimental platform suitable for cold environments to solve the above problems. Summary of the Invention

[0007] The purpose of this invention is to provide a test platform for a bucket wheel excavator suitable for cold environments, so as to solve the problems of single dimension and insufficient accuracy in the acquisition of mechanical information of key components mentioned in the background art.

[0008] To achieve the above objectives, the present invention provides the following technical solution: a bucket wheel excavator test platform suitable for cold environments, comprising a simulated rock wall, a bucket wheel test device, and strain gauges; The bucket wheel test device includes a bucket wheel assembly and multiple buckets evenly arranged around the circumference of the bucket wheel assembly. Multiple bucket teeth are provided on the outer side of the buckets to directly contact the simulated rock wall. Strain gauges are embedded inside the bucket teeth at the connection point with the bucket, and are used to collect changes in horizontal and vertical torsional stress of the bucket teeth.

[0009] Optionally, the bucket wheel assembly includes a wheel and a central motor for driving the wheel to rotate. The output end of the central motor is equipped with a shaft, and a bearing housing is installed on the outside of the shaft.

[0010] Optionally, it also includes a support assembly consisting of a rotary table, a bracket mounted on top of the rotary table, and a bucket cantilever hinged to the bracket. The bucket cantilever is connected to a bearing seat, and a telescopic support rod for driving the bucket to swing up and down is installed between the bucket cantilever and the rotary table.

[0011] Optionally, it also includes a slide rail assembly, which includes a longitudinal guide rail, a transverse guide rail that slides along the length of the longitudinal guide rail, and a slider support platform that slides along the length of the transverse guide rail. The slider support platform is provided with a power output device for driving the rotary table to rotate. A forward drive structure for driving the slider support platform to slide forward is installed on the power output device and the transverse guide rail; A backward drive structure is installed on the power output device and the longitudinal guide rail to drive the slider support platform to slide backward and drive the transverse guide rail to move laterally. A push structure is mounted on the retraction drive structure to push the slider support platform backward.

[0012] Optionally, the forward drive structure includes two gear plates mounted on the transverse guide rail and a bevel gear mounted on the outside of the output shaft of the power output device. The bevel gear and the gear plate are respectively meshed with a bevel gear and a gear. The bevel gear and the gear are coaxially fixed. A ratchet is installed between the bevel gear and the output shaft of the power output device.

[0013] Optionally, multiple gear plates are provided, with the length of the multiple gear plates decreasing sequentially from the outside to the inside or from the inside to the outside. The number of gears is the same as that of the gear plates and they are incomplete gears. The gear teeth ratio of the gears decreases sequentially from the inside to the outside or from the outside to the inside.

[0014] Optionally, gear plate one can also be configured as a single gear, which is a complete gear and meshes with gear plate one.

[0015] Optionally, the reversing drive structure includes a gear plate mounted on the longitudinal guide rail and a worm gear mounted on the outside of the output shaft of the power output device. A lead screw is installed inside the transverse guide rail, and the lead screw can slide through the push structure, the worm gear and the slider support platform. Both ends of the lead screw are equipped with gears that mesh with gear plate two via electromagnetic clutches; A ratchet is installed between the worm gear and the output shaft of the power output device.

[0016] Optionally, the push structure includes a lead screw nut fitted on the outside of the lead screw, an L-shaped frame extending to the bottom of the slider support platform is fitted on the outside of the lead screw nut, a compression spring is installed between the L-shaped frame and the side of the slider support platform, and two rollers are installed on the L-shaped frame. A ratchet is installed between the lead screw nut and the L-shaped bracket.

[0017] Optionally, the slide rail assembly also includes a limiting structure, which includes a limiting plate that slides up and down and is inserted into the transverse guide rail. When the limiting is in place, the limiting plate contacts the slider support platform. When the limiting is released, the limiting plate contacts the roller. A compression spring is installed at the bottom of the limiting plate.

[0018] The technical effects and advantages of this invention are as follows: This invention simulates the physical properties of soil and rock in a cold environment by setting up a simulated rock wall. The bucket teeth directly contact the simulated rock wall to achieve accurate simulation of the excavation working conditions. This solves the technical problem that the existing experimental platform cannot be adapted to cold environments and provides an experimental basis that fits the actual working conditions for the performance verification of bucket wheel excavators used in cold environments.

[0019] This invention, by embedding strain gauges inside the bucket teeth, can collect stress and strain data in the horizontal and vertical torsional directions of the bucket teeth in real time, and achieve stable transmission and storage of signals through a data acquisition instrument. Compared with the existing single-dimensional information acquisition methods, the acquisition dimensions are more comprehensive and the data is more accurate, providing reliable data support for the structural optimization of key components of bucket wheel excavators.

[0020] This invention achieves the up-and-down swing, rotation, and forward and backward and lateral movement of the bucket wheel assembly through the coordinated cooperation of the support component and the slide rail component. It can simulate various digging postures and actions of the bucket wheel excavator in actual operation, effectively reduce the deviation between experimental conditions and actual working conditions, and improve the reliability of experimental results.

[0021] The forward and reverse drive structures, through the cooperation of components such as ratchet, bevel gear, and worm gear, achieve precise power transmission and direction switching. At the same time, the inclusion of components such as incomplete gears and electromagnetic clutches allows for flexible adjustment of movement speed and drive mode to meet the experimental needs of different excavation conditions. The setting of the limit structure can effectively limit the movement range of the slider support platform, avoid component collision damage, and improve the operational stability and safety of the experimental platform. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of the present invention; Figure 2 This is a schematic diagram of the structure of the bucket wheel test device of the present invention; Figure 3 This is a schematic diagram of the bucket wheel assembly structure of the present invention; Figure 4 This is a schematic diagram of the strain gauge structure of the present invention; Figure 5 This is a schematic diagram of the slide rail assembly structure of the present invention; Figure 6 This is a schematic diagram of the ratchet structure of the present invention; Figure 7 This is a schematic diagram of a gear structure in Embodiment 1 of the present invention; Figure 8 For the present invention Figure 6 Enlarged schematic diagram of the structure at point A in the middle; Figure 9 This is a schematic diagram of the backward drive structure of the present invention; Figure 10 This is a schematic diagram of the gear plate structure of the present invention; Figure 11 This is a schematic diagram of the structure of the present invention; Figure 12 This is a schematic diagram of the limiting structure of the present invention; Figure 13 This is a schematic diagram showing the location of the strain gauge structure of the present invention; Figure 14 This is a schematic diagram of a gear structure in Embodiment 2 of the present invention.

[0023] In the image: 100, simulated rock wall; 200. Bucket wheel test device; 210. Bucket wheel assembly; 211. Runner; 212. Central motor; 213. Shaft; 214. Bearing housing; 220. Bucket; 230. Bucket teeth; 300. Strain gauge; 400. Support assembly; 410. Rotary table; 420. Bracket; 430. Bucket wheel cantilever; 440. Telescopic strut; 500. Slide rail assembly; 510. Longitudinal guide rail; 520. Transverse guide rail; 530. Slider support platform; 540. Power output device; 550. Forward drive structure; 551. Gear plate one; 552. Bevel gear one; 553. Bevel gear two; 554. Gear one; 555. Ratchet one; 560. Reverse drive structure; 561. Gear plate two; 562. Worm gear; 563. Lead screw; 564. Gear two; 565. Ratchet three; 570. Pushing structure; 571. Lead screw nut; 572. L-shaped frame; 573. Compression spring one; 574. Roller; 575. Ratchet two; 580. Limiting structure; 581. Limiting plate; 582. Compression spring two. Detailed Implementation

[0024] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0025] This invention provides, for example Figure 1-13 The experimental platform for a bucket wheel excavator suitable for cold environments is shown, including a simulated rock wall 100, a bucket wheel test device 200, and strain gauges 300. The bucket wheel test device 200 includes a bucket wheel assembly 210 and multiple buckets 220 evenly arranged around the circumference of the bucket wheel assembly 210. Multiple bucket teeth 230 are provided on the outer side of the buckets 220 to directly contact the simulated rock wall 100. The bucket teeth 230 directly contact and cut the simulated rock wall 100. The buckets 220 can catch the cut fragments of the simulated rock wall 100 and accumulate them under the bucket wheel assembly 210 to simulate the actual excavation situation. The number, shape, and volume of the 220 buckets can be customized and replaced according to different test requirements to simulate the bucket configuration of different models of bucket wheel excavators in actual engineering. Strain gauges 300 are embedded inside the bucket teeth 230 at the connection point with the bucket 220. They are used to collect horizontal and vertical torsional stress changes in the bucket teeth 230. The strain gauges 300 are connected to a data acquisition instrument, and the output signal of the data acquisition instrument is connected to a host computer. The strain gauges 300 collect horizontal and vertical torsional stress strains in the bucket teeth 230. The strain gauges 300 are embedded in key stress concentration areas inside the bucket teeth 230, such as the connection point between the bucket teeth 230 and the bucket 220, ensuring that the subtle mechanical changes of the bucket teeth 230 during operation can be captured most directly and accurately. The stress signals are then transmitted to the data acquisition instrument, which is equipped with a high-performance analog-to-digital converter chip, multi-channel signal conditioning circuitry, and an embedded microprocessor. It first amplifies, filters, and performs temperature compensation on the raw signals from each strain gauge 300 before transmitting the pre-processed signals to the host computer. The simulated rock wall 100 is equipped with a rock wall fixing bracket on the rear side to prevent the simulated rock wall 100 from sliding backward during cutting. At the same time, the cutting surface of the simulated rock wall 100 can be adjusted to an arc surface, a flat surface, a circular surface, etc., according to the actual situation. The simulated rock wall 100 is made of foamed cement mixed with coal and soil, and is fixed to the ground by bolts or other means using the rock wall fixing bracket.

[0026] The embedded strain gauge 300 can sensitively sense torsional stress and strain from two dimensions: horizontal (such as tension and compression along the length of the bucket tooth 230, and transverse shear) and vertical (such as bending stress along the height of the bucket tooth 230, and compressive stress at the tooth tip). These stresses are rapidly transmitted to the data acquisition instrument with which the data acquisition instrument establishes a stable signal connection via a highly reliable shielded cable or wireless transmission module (depending on the specific system configuration). Engineers can remotely or on-site acquire stress signals of the bucket tooth 230 under different operating conditions, providing crucial first-hand data support for the structural optimization design, remaining life prediction, fault warning, and construction process improvement of the bucket tooth 230.

[0027] Based on the stress changes fed back by strain gauge 300, the stress changes of bucket teeth 230 at different digging depths (such as the depth at which buckets 220 can hold small, half, and large buckets) can be determined. This leads to the wear and service life of bucket teeth 230 during use (the greater the force on bucket teeth 230, the greater the wear on bucket teeth 230 and bucket 220, and the lower the service life). By calculating the digging volume of bucket teeth 230 throughout its service life at different depths, the optimal working depth can be calculated to maximize the utilization rate of bucket teeth 230 and bucket 220.

[0028] Based on the pressure difference between strain gauges 300 at different locations, it can be determined which bucket tooth 230 is most prone to wear and damage, so that the bucket tooth 230 at the corresponding location can be replaced in advance.

[0029] The working principle of this embodiment is as follows: In use, the bucket wheel assembly 210 is activated, causing the bucket 220 and bucket teeth 230 to rotate. During the rotation of the bucket 220 and bucket teeth 230, the bucket cuts the simulated rock wall 100. During the cutting of the simulated rock wall 100, stress changes occur inside the bucket teeth 230. Strain gauges 300 at three positions test the pressure on the tooth root, the torsional pressure on the tooth root, and the downward pressure on the tooth root of the bucket teeth 230, respectively. The tested pressure is transmitted to a multi-channel data acquisition instrument through a signal line for preliminary stress signal processing, and then converted into a digital signal and transmitted to the host computer for numerical reading and analysis.

[0030] In some embodiments of the present invention, reference is made to... Figure 3 As shown, the bucket wheel assembly 210 includes a wheel 211 and a central motor 212 for driving the wheel 211 to rotate. The central motor 212, as the driving core, is selected as a servo motor or a geared motor with high torque and high precision control characteristics to ensure that the wheel 211 can achieve stable and efficient rotation under different working conditions. A shaft 213 is installed at the output end of the central motor 212. In order to ensure the stability and concentricity of the shaft 213 during high-speed rotation, and to reduce the adverse effects of radial and axial loads generated by rotation on the motor and other components, at least one bearing seat 214 is also precisely installed on the outer side of the shaft 213, near the installation position of the wheel 211 or the middle of the shaft 213, and other key stress points.

[0031] In some embodiments of the present invention, reference is made to... Figure 2 and Figure 5 As shown, it also includes a support assembly 400 consisting of a rotary table 410, a bracket 420 mounted on top of the rotary table 410, and a bucket cantilever 430 hinged to the bracket 420. The rotary table 410 provides stable bottom support for the bucket test device 200 and enables horizontal rotation. The bracket 420 is welded from high-strength alloy materials, providing a solid connection platform for the installation of subsequent components. The hinge of the bucket cantilever 430 allows it to rotate around the hinge point at a certain angle, thereby increasing operational flexibility. The bearing seat 214 is mounted on the bucket cantilever 430 to support the shaft 213. In order to enable the bucket 220 to swing up and down during operation to adapt to different digging depths or material stacking heights, a power drive device—telescopic support rod 440—is also installed between the middle of the bucket cantilever 430 and the side of the rotary table 410. The telescopic support rod 440 is installed between the bucket cantilever 430 and the rotary table 410.

[0032] The telescopic support rod 440 is hydraulically driven. Through the telescopic movement of its internal piston rod, it can precisely push or pull the bucket cantilever 430 to pitch around the hinge point with the support 420, thereby driving the bucket 220 connected to it to complete the up-and-down swinging action.

[0033] In some embodiments of the present invention, reference is made to... Figure 5 and Figure 6 As shown, it also includes a slide rail assembly 500, which includes a longitudinal guide rail 510, a transverse guide rail 520 that slides along the length of the longitudinal guide rail 510, and a slider support platform 530 that slides along the length of the transverse guide rail 520. The longitudinal guide rail 510 serves to guide and support the longitudinal sliding of the transverse guide rail 520 and the slider support platform 530, and the transverse guide rail 520 serves to guide and support the transverse sliding of the slider support platform 530. The slider support platform 530 is provided with a power output device 540 for driving the rotary table 410 to rotate. The forward rotation of the power output device 540 is converted into the linear forward movement of the slider support platform 530 along the transverse guide rail 520, and the reverse rotation of the power output device 540 is converted into the linear forward movement of the transverse guide rail 520 along the longitudinal guide rail 510 and the linear backward movement of the slider support platform 530 along the transverse guide rail 520. In this embodiment, the power output device 540 can be driven by a motor, a lead screw, or a hydraulic cylinder. In order to drive the slider support platform 530 to slide forward on the transverse guide rail 520, a forward drive structure 550 is installed between the power output end of the power output device 540 and a specific part of the transverse guide rail 520. The forward drive structure 550 is installed on the power output device 540 and the transverse guide rail 520 to drive the slider support platform 530 to slide forward, so as to realize the linear forward movement of the slider support platform 530 along the transverse guide rail 520, and can realize precise control of the movement speed and position through the control system. To meet the combined motion requirements of the slider support platform 530 sliding backward and driving the entire transverse guide rail 520 to move longitudinally along the longitudinal guide rail 510, the power output device 540 and the longitudinal guide rail 510 are equipped with a backward drive structure 560 for driving the slider support platform 530 to slide backward and driving the transverse guide rail 520 to move laterally. The reverse drive structure 560 drives the slider support platform 530 to move backward on the transverse guide rail 520, and drives the transverse guide rail 520 to adjust the transverse position of the slider support platform 530 along the longitudinal guide rail 510, thereby realizing the complex trajectory motion of the slider support platform 530 in the two-dimensional plane. A push structure 570 is installed on the retracting drive structure 560 to push the slider support platform 530 backward. The push structure 570 acts directly on the slider support platform 530, providing thrust to ensure that the slider support platform 530 can complete the backward sliding action stably and accurately. At the same time, the push structure 570 can also limit or buffer the slider support platform 530 when needed, protecting the entire slide rail assembly 500 and the connected rotary table 410 from impact damage.

[0034] The working principle of this embodiment is as follows: When the power output device 540 is driven in the forward direction, the power output device 540 drives the forward drive structure 550 to run, which in turn drives the slider support platform 530 to move forward. The distance moved each time may be different.

[0035] When the power output device 540 is reverse driven, the power output device 540 drives the reversing drive structure 560 to run, causing the reversing drive structure 560 to drive the transverse guide rail 520 to move longitudinally along the longitudinal guide rail 510, while simultaneously driving the push structure 570 to slide backward, and pushing the slider support platform 530 to move backward while sliding.

[0036] In some embodiments of the present invention, reference is made to... Figure 6 Figure 7 and Figure 8 As shown, the forward drive structure 550 includes two gear plates 551 mounted on the transverse guide rail 520 and a bevel gear 552 mounted on the outside of the output shaft of the power output device 540. The bevel gear 552 and the gear plate 551 are respectively meshed with bevel gear 553 and gear 554. The gear plate 551 is a key transmission component. The bevel gear 553 and the bevel gear 552 on it form a bevel gear pair transmission, which can realize the change of power transmission direction. At the same time, the power is transmitted to the gear 554 through gear meshing, which can ensure that there is no relative rotation during the transmission process. The bevel gear 553 and the gear 554 are fixed coaxially. When the gear 554 meshes with the gear plate 551 and rotates, the rotation of the bevel gear 552 will drive the slider support platform 530 to slide forward. A ratchet 555 is installed between the bevel gear 552 and the output shaft of the power take-off device 540. When the output shaft of the power take-off device 540 rotates in the forward direction, the ratchet 555 allows the bevel gear 552 to rotate normally. When the output shaft attempts to rotate in the reverse direction, the ratchet 555 will prevent the bevel gear 552 from reversing, thereby protecting other components in the forward drive structure 550 from the impact of the reverse force.

[0037] In some embodiments of the present invention, reference is made to... Figure 7As shown, multiple gear plates 551 are provided, with their lengths decreasing sequentially from the outside to the inside or from the inside to the outside. The number of gears 554 is the same as that of gear plates 551, and they are incomplete gears to accommodate the meshing stroke requirements of different gears 554. This allows gear plates 551 at different positions to adapt to different transmission distances. The outer gear plates 551 are longer to avoid a midpoint in the transmission between gear plates 551 and gears 554, preventing the slider support platform 530 from continuing to slide forward after one rotation of gear 554. Furthermore, the gear tooth ratio (i.e., the proportional relationship of gear diameter-related parameters, with the number of teeth of gear 554 gradually decreasing) of gears 554 decreases sequentially from the inside to the outside or from the outside to the inside. Incomplete gears refer to gears where teeth are not made all around the circumference, but are set at specific positions as needed. This allows for intermittent motion, positioning, or transmission at specific angles during gear rotation, avoiding interference or unnecessary power consumption that may result from continuous transmission of complete gears.

[0038] Among them, multiple sets of gear plates 551 are provided. The longest gear plate 551 in the first set and the second set overlap by a part, so that the slider support platform 530 can smoothly transition to the next stroke after moving one stroke, thereby increasing the number of detections. Experiments are conducted to compare the results through multiple detections.

[0039] The working principle of this embodiment is as follows: When bevel gear 552 rotates, it drives bevel gear 553 to rotate as well, which in turn drives gear 554 to rotate. During the rotation, gear 554 meshes with gear plate 551 and moves forward under the action of gear plate 551. In the initial stage, gear plate 551 will be fully engaged with gear 554, causing the slider support platform 530 to move. Gear 554 with the longest stroke will disengage from gear plate 551 last, and the maximum stroke is reached at this time. In the next movement, gear 554 with the longest stroke will disengage first or not at all because gear plate 551 with the shortest stroke is corresponding to it. During this movement, except for gear 554 that is not engaged, gear 554 with the longest stroke will disengage from gear plate 551 last. The stroke of this movement will be less than the distance of the first stroke, and the above actions are repeated.

[0040] In some embodiments of the present invention, reference is made to... Figure 8 Figure 9 and Figure 10As shown, the reversing drive structure 560 includes a gear plate 561 mounted on the longitudinal guide rail 510 and a worm gear 562 mounted on the outside of the output shaft of the power output device 540. A lead screw 563 is installed inside the transverse guide rail 520. The lead screw 563 can slide through the push structure 570, the worm gear 562 and the slider support platform 530. The slide rail on the outside of the lead screw 563 and the protrusion on the inner wall of the worm gear 562 cooperate, so that the worm gear 562 can slide along the lead screw 563 and drive the lead screw 563 to rotate, or only slide without driving the lead screw 563 to rotate. At the same time, the depth and width of the slide rail are much smaller than the depth and width of the slide rail of the lead screw 563. When the power output device 540 is started, the output shaft drives the worm gear 562 to rotate, which in turn drives the lead screw 563 to rotate. Both ends of the lead screw 563 are equipped with gears 564 that mesh with gear plate 561 via electromagnetic clutches. As a key transmission control component, the electromagnetic clutch can engage and disengage the clutch according to the electrical signal sent by the control system, thereby controlling whether gear 564 rotates synchronously with the lead screw 563. When the electromagnetic clutch is energized, the electromagnet inside generates magnetic force, driving the friction plates or meshing elements to make close contact, so that gear 2 564 and lead screw 563 form a rigid connection. At this time, the rotational motion of lead screw 563 can be transmitted to gear plate 2 561 through gear 2 564, thereby driving gear plate 2 561 to rotate or move accordingly. When the electromagnetic clutch is de-energized, the magnetic force disappears, and the friction plates or meshing elements are separated under the action of springs or other reset devices. The power transmission between gear 2 564 and lead screw 563 is cut off, and gear plate 2 561 can remain stationary or be driven by other power sources. A ratchet 565 is installed between the worm gear 562 and the output shaft of the power output device 540. Its main function is to achieve unidirectional transmission or prevent reverse rotation. When the output shaft of the power output device 540 rotates in the reverse direction, the pawl will engage in the tooth groove of the ratchet 565, driving the ratchet 565 to rotate synchronously, thereby transmitting power to the worm gear 562. When the output shaft of the power output device 540 rotates in the forward direction, the pawl will slide on the tooth surface of the ratchet 565, thereby preventing the ratchet 565 from rotating in the reverse direction and ensuring that the worm gear 562 can only receive power in the predetermined direction.

[0041] The working principle of this embodiment is as follows: When the output shaft of the power output device 540 rotates in the reverse direction, it will drive the worm gear 562 to run under the action of the ratchet 3 565, which in turn drives the lead screw 563 to rotate, causing the lead screw 563 to drive the push structure 570 to move. Then, the push structure 570 drives the slider support platform 530 to slide backward. At the same time, the lead screw 563 will also drive the gear 2 564 to rotate, causing the gear 2 564 to be fixed along the gear plate 2 561, which in turn drives the transverse guide rail 520 to slide along the longitudinal guide rail 510.

[0042] In some embodiments of the present invention, reference is made to... Figure 11 As shown, the pushing structure 570 includes a lead screw nut 571 sleeved on the outside of the lead screw 563. An L-shaped frame 572 extending to the bottom of the slider support platform 530 is sleeved on the outside of the lead screw nut 571. The lead screw nut 571 achieves axial movement through threaded engagement with the lead screw 563. When the lead screw 563 rotates, the lead screw nut 571 will be displaced along the axial direction of the lead screw 563, thereby driving the L-shaped frame 572 on its outside to move synchronously. A compression spring 573 is installed between the L-shaped frame 572 and the side of the slider support platform 530 to effectively offset the clearance error and impact load during the transmission process. Two rollers 574 are installed on the L-shaped frame 572. The rolling friction of the rollers 574 replaces the sliding friction, reducing the energy consumption and wear during the operation of the structure. A ratchet 575 is installed between the lead screw nut 571 and the L-shaped bracket 572 to ensure that the movement can only proceed in a predetermined unidirectional direction, thereby playing the role of limiting, preventing loosening, or transmitting power.

[0043] The working principle of this embodiment is as follows: When the lead screw 563 rotates, it drives the L-shaped frame 572 to move backward. Since the slider support platform 530 and the structure mounted on it have a large overall weight, when the L-shaped frame 572 moves, it will compress the compression spring 573 and drive the rear roller 574 to move relative to the slider support platform 530, so that the roller 574 moves to the front side of the platform. When the lead screw 563 stops rotating, the elastic force of the compression spring 573 is released and pushes the L-shaped frame 572 to move forward, so that the front roller 574 moves to the front side of the slider support platform 530.

[0044] In some embodiments of the present invention, reference is made to... Figure 12As shown, the slide rail assembly 500 also includes a limiting structure 580, which includes a limiting plate 581 that slides vertically and vertically within the transverse guide rail 520. During limiting, the middle portion of the limiting plate 581 is a plate-like structure that directly contacts the slider support platform 530. The two ends of the limiting plate 581 are provided with trapezoidal structures (the slope of the trapezoidal structures can be adjusted according to actual requirements), and the height of the trapezoidal structures is lower than the height of the plate-like structure. During limiting, the plate-like structure of the limiting plate 581 contacts the slider support platform 530, thereby limiting the movement of the slider support platform 530 within the transverse guide rail 520. To prevent the slider support platform 530 from moving backward during the test cutting process, when the limit is released, the trapezoidal structure of the limit plate 581 contacts the roller 574, causing the plate-like structure of the limit plate 581 to descend below the slider support platform 530. A compression spring 582 is installed at the bottom of the limit plate 581. The function of the compression spring 582 is to generate elastic deformation when the limit plate 581 is subjected to external force (such as the squeezing of the slider support platform 530 or the roller 574), thereby providing a restoring force for the limit plate 581, so that it can automatically return to the initial position after the external force is released, ensuring the reliability and reusability of the limit structure 580.

[0045] When the travel distance of the slider support platform 530 is too long (due to transmission difference, inertia, etc.), when the bucket teeth 230 contact the simulated rock wall 100, the simulated rock wall 100 will exert a backward pushing force on the bucket teeth 230, thereby causing the slider support platform 530 to slide backward until it contacts the corresponding limit plate 581. This ensures the accuracy of the travel distance of the slider support platform 530. At the same time, the digging depth of the bucket teeth 230 is precisely controlled according to the distance between the limit plates 581, without relying on the precise control of gear plates 551 and 554, thus improving the error range of gear plates 551 and 554. In addition, the limit plate 581 can also be controlled by sliding up and down with the telescopic structure to control the position and the distance between two adjacent limit plates 581, thereby adapting to the usage requirements of different buckets 220 and bucket teeth 230.

[0046] The working method of this invention: During the testing process, as the bucket tooth 230 cuts the simulated rock wall 100, stress changes occur inside the bucket tooth 230. Strain gauges 300 at three locations test the pressure on the tooth root, the torsional pressure on the tooth root, and the downward pressure on the tooth root inside the bucket tooth 230, respectively. The tested pressure is transmitted to a multi-channel data acquisition instrument via a signal line for preliminary stress signal processing, and then converted into a digital signal and transmitted to the host computer for numerical reading and analysis.

[0047] When the bucket wheel test device 200 is running, the power output device 540 (motor) is activated, causing the output shaft of the power output device 540 to rotate in the forward direction, driving the bevel gear 552, the rotary table 410, and the bucket wheel test device 200 to rotate (the first half of the rotation of the bucket wheel test device 200 is used to cut the simulated rock wall 100, and the second half of the rotation is used to adjust the position). Due to the ratchet 565, the output shaft of the power output device 540 does not drive the worm gear 562 when rotating in the forward direction, causing the bucket teeth 230 to cut the simulated rock wall 100. The bevel gear 552 drives the bevel gear 553 and the gear 554 to rotate. In the initial stage, the gear plate 551 will be fully engaged with the gear 554, causing the slider support platform 530 to move. When moving forward, the slider support platform 530 will also push the roller 574 to move synchronously. (Due to the relatively small overall resistance of the pushing structure 570, the compression spring 573 in the pushing structure 570 is not compressed.) When the slider support platform 530 is blocked at the limiting plate 581, the front roller 574 will first contact the limiting plate 581 and press down the limiting plate 581, allowing the slider support platform 530 to pass normally. When the gear plate 551 and gear 554 disengage, the slider support platform 530 stops moving and is blocked by the limiting plate 581 at the corresponding position and cannot move backward. The gear 554 with the longest stroke disengages from the gear plate 551 last, and the movement stroke reaches its maximum. After the bucket tooth 230 cuts a layer, the same steps are repeated, except that the transmission stroke of gear 554 and gear plate 551 is different, so that different distances of travel are achieved.

[0048] When the push structure 570 moves forward, the lead screw nut 571 rotates in the opposite direction while sliding along the lead screw 563 (the lead screw nut 571 and the lead screw 563 adopt a structure that is commercially available and can be driven in opposite directions). This rotation is not locked by the ratchet 575, and the lead screw nut 571 can rotate relative to the L-shaped frame 572 to achieve normal movement of the push structure 570.

[0049] When the test device 200 needs to change its lateral position for the next test after completing one round of testing, the power output device 540 is activated. The power output device 540 rotates in the reverse direction, driving the worm gear 562 to rotate under the action of ratchet three 565. Due to the setting of ratchet one 555, the bevel gear one 552 and the rotating table 410 are not driven to rotate at this time. When the worm gear 562 rotates, it drives the lead screw 563 to rotate forward through the keyway. Due to the restriction of ratchet two 575, the lead screw nut 571 cannot rotate forward relative to the L-shaped frame 572. When the lead screw 563 rotates, it drives the L-shaped frame 572 to move backward. Because the slider support platform 530 and the structure mounted on it have a large overall weight, the L-shaped... When the frame 572 moves, it compresses the compression spring 573, which in turn drives the rear roller 574 to move relative to the slider support platform 530. This causes the roller 574 to move to the front of the platform. During travel, the roller 574 first presses down the limit plate 581, causing the slider support platform 530 to move past the limit plate 581 to the initial position. Simultaneously, as the lead screw 563 rotates, it also drives the gear 564 to move along the gear plate 561, which in turn drives the transverse guide rail 520 to slide. After the transverse guide rail 520 moves to the corresponding position, the reverse drive of the power output device 540 is stopped, the elasticity of the compression spring 573 is released, and the L-shaped frame 572 is pushed forward, causing the front roller 574 to move to the front of the slider support platform 530.

[0050] After the test is completed, the electromagnetic clutch on the lead screw 563 can be closed, and then the transverse guide rail 520 can be pushed to move to the initial position.

[0051] In some embodiments of the present invention, reference is made to... Figure 14 As shown, gear plate 551 can also be set as one, and gear 554 is set as a complete gear and meshes with gear plate 551. That is, the two achieve power transmission through direct contact between teeth, so that bucket 220 and bucket teeth 230 move forward during the cutting process and maintain a certain cutting depth. At the same time, the cutting depth of bucket 220 and bucket teeth 230 can be changed according to the specific shape of the simulated rock wall 100.

[0052] The working principle of this embodiment is as follows: The working principle is the same as the steps in the above embodiments, except that: When the conical tooth 552 rotates, it drives the conical tooth 553 to rotate as well, which in turn drives the gear 554 to rotate, causing the gear 554 to move along the gear plate 551, thereby causing the bucket 220 and the bucket tooth 230 to move forward during the cutting process.

[0053] Finally, it should be noted that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A test platform for a bucket wheel excavator suitable for cold-weather environments, characterized in that, Includes simulated rock wall, bucket wheel test device, and strain gauges; The bucket wheel test device includes a bucket wheel assembly and multiple buckets evenly arranged around the circumference of the bucket wheel assembly. Multiple bucket teeth are provided on the outer side of the buckets to directly contact the simulated rock wall. Strain gauges are embedded inside the bucket teeth at the connection point with the bucket, and are used to collect changes in horizontal and vertical torsional stress of the bucket teeth.

2. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 1, characterized in that: The bucket wheel assembly includes a wheel and a central motor for driving the wheel to rotate. A shaft is mounted on the output end of the central motor, and a bearing housing is mounted on the outside of the shaft.

3. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 2, characterized in that: It also includes a support assembly consisting of a rotating platform, a bracket mounted on top of the rotating platform, and a bucket cantilever hinged to the bracket. The bucket cantilever is connected to a bearing seat, and a telescopic support rod for driving the bucket to swing up and down is installed between the bucket cantilever and the rotating platform.

4. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 1, characterized in that: It also includes a slide rail assembly, which includes a longitudinal guide rail, a transverse guide rail that slides along the length of the longitudinal guide rail, and a slider support platform that slides along the length of the transverse guide rail. The slider support platform is equipped with a power output device for driving the rotary table to rotate. A forward drive structure for driving the slider support platform to slide forward is installed on the power output device and the transverse guide rail; A backward drive structure is installed on the power output device and the longitudinal guide rail to drive the slider support platform to slide backward and drive the transverse guide rail to move laterally. A push structure is mounted on the retraction drive structure to push the slider support platform backward.

5. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 4, characterized in that: The forward drive structure includes two gear plates mounted on the transverse guide rail and a bevel tooth mounted on the outside of the output shaft of the power output device. The bevel tooth and the gear plate are respectively meshed with a bevel tooth and a gear. The bevel tooth and the gear are coaxially fixed. A ratchet is installed between the bevel gear and the output shaft of the power output device.

6. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 5, characterized in that: Multiple gear plates are provided, and the length of the multiple gear plates decreases from the outside to the inside or from the inside to the outside. The number of gears is the same as that of the gear plates and they are incomplete gears. The gear teeth ratio of the gears decreases from the inside to the outside or from the outside to the inside.

7. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 6, characterized in that: Gear plate one can also be set as a single gear, which is a complete gear and meshes with gear plate one.

8. The experimental platform for a bucket wheel excavator suitable for cold environments according to claim 4, characterized in that: The reversing drive structure includes a gear plate mounted on the longitudinal guide rail and a worm gear mounted on the outside of the output shaft of the power output device. A lead screw is installed inside the transverse guide rail, and the lead screw can slide through the push structure, the worm gear and the slider support platform. Both ends of the lead screw are equipped with gears that mesh with gear plate two via electromagnetic clutches; A ratchet is installed between the worm gear and the output shaft of the power output device.

9. A bucket wheel excavator test platform suitable for cold environments according to claim 8, characterized in that: The pushing structure includes a lead screw nut fitted on the outside of the lead screw, an L-shaped frame extending to the bottom of the slider support platform fitted on the outside of the lead screw nut, a compression spring installed between the L-shaped frame and the side of the slider support platform, and two rollers installed on the L-shaped frame. A ratchet is installed between the lead screw nut and the L-shaped bracket.

10. A bucket wheel excavator test platform suitable for cold environments according to claim 9, characterized in that: The slide rail assembly also includes a limiting structure, which includes a limiting plate that slides up and down and is inserted into the transverse guide rail. When the limiting is in place, the limiting plate contacts the slider support platform. When the limiting is released, the limiting plate contacts the roller. A compression spring is installed at the bottom of the limiting plate.

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