Compact wheel loader with long arm

Abstract

A long arm type compact wheel bucket excavator relates to mechanical equipment for open pit mining, comprising a supporting mechanism, a bucket wheel driving mechanism, a discharging arm rotating mechanism, a crawler walking mechanism and a tensioning mechanism, the discharging arm rotating mechanism comprising a main machine walking mechanism, a supporting base assembly, a rotating platform assembly and an adjusting plate assembly; the supporting base assembly comprising a central pipe vertically fixed on the main machine walking mechanism and a mounting seat fixed on the central pipe; the rotating platform assembly comprising a rotating platform rotatably supported on an L-shaped beam; the adjusting plate assembly comprising an adjusting plate body, a lower connecting shaft slide way symmetrically arranged on both sides of the adjusting plate body and an upper connecting shaft slide groove symmetrically arranged on the other two sides of the adjusting plate body, the guide directions of the lower connecting shaft slide way and the upper connecting shaft slide groove being perpendicular to each other. The wheel loader is not additionally arranged, and triangular coal is not generated, and the wheel bucket excavator has the advantages of good stress characteristics, good safety and the like.

Description

Technical Field

[0001] This invention relates to machinery and equipment for open-pit mining, and more particularly to excavating machinery with a receiving arm, a bucket wheel mechanism, an unloading arm and a tracked walking mechanism, specifically a long-arm compact bucket wheel excavator. Background Technology

[0002] Patent application CN114320300A discloses a bucket wheel excavator suitable for mining harder materials. This type of excavator mainly includes a traveling mechanism, a gantry slewing platform connected to the traveling mechanism via a large slewing bearing mechanism, a receiving arm mechanism mounted on the gantry slewing platform and equipped with a bucket wheel excavator, and a discharge arm device rotatably connected to the gantry slewing platform column. A discharge arm rotation mechanism is located at the lower part of the discharge arm device.

[0003] In existing technologies, firstly, both the drive unit and the receiving boom are located on one side of the bucket wheel. When the bucket wheel rotates for digging operations, the cutting resistance from the material causes a significant offset between the digging force and the centroid of the receiving boom. This results in a large torque on the receiving boom, leading to an increase in the overall center of gravity, the diameter of the stability circle, and the diameter of the large slewing bearing. Consequently, the dimensions of the tracked chassis structure increase. When the receiving boom is long, structural deformation and twisting are highly likely, requiring a substantial increase in the cross-section of the receiving boom, increasing its weight and hindering structural design. Furthermore, when the equipment has a large capacity, the drive unit and the belt width of the receiving belt also increase. When the drive side approaches the original cutting material, collisions with the material are highly likely, posing a danger. Additionally, during digging operations, the two hydraulic cylinders supporting the receiving boom will experience severe uneven stress, significantly increasing the stress amplitude at the hinge points at both ends of the hydraulic cylinders and impairing their fatigue life.

[0004] Secondly, the existing unloading arm slewing mechanism effectively reduces the large lateral load on the large slewing bearing caused by irregular bumps and vibrations when the tracks cross uneven ground, as described in the invention patent application CN1172196A, and also reduces the vibration problem of the unloading arm, thus improving the overall stability of the bucket wheel excavator. However, this mechanism has as many as 53 parts, making disassembly and installation difficult. Furthermore, the numerous internal bearing lubrication points, due to the limited space within the internal structure, make lubrication, maintenance, and repair difficult. Additionally, to ensure rigidity, the diameter of the central suspension shaft must be particularly large, requiring larger bearing sizes and increasing costs.

[0005] Secondly, in existing products, the belt conveyor tensioning device in the receiving arm is located at the end near the central transfer point. When the receiving conveyor belt is long, the tensioning stroke will also increase. This will cause the unloading point position to change significantly with the adjustment of tension, which in turn will require the unloading hopper opening to adapt to the adjustment of the stroke. When the opening is too large, the unloading range will increase accordingly, which will easily cause the unloading belt to deviate.

[0006] Meanwhile, in existing products, the track rollers in the track walking mechanism are hidden inside the track frame. When the bearings in the track rollers need repair, the entire machine must be lifted up, and the track frame raised until the repair space is exposed, causing considerable inconvenience for equipment maintenance. Furthermore, the drive wheel and axle in the track mechanism are interference-fitted, and the drive wheel and gear are an integral structure. When the gear teeth are severely worn and need to be replaced, the entire drive wheel and axle will be scrapped, resulting in high spare parts costs and significant replacement difficulties.

[0007] In addition, in the existing technology, the connecting rods between the unloading arm pitching mechanism and the unloading arm are mostly perpendicular to the unloading arm. This structure is beneficial to the structural stress when the unloading arm is short, but if the unloading arm is long, in order to ensure the rigidity of the unloading arm, the cross-sectional size of the unloading arm needs to be greatly increased, which greatly increases the weight of the equipment.

[0008] Finally, the existing technology has relatively short receiving arm and unloading arm lengths, with the receiving arm length less than 20m and the unloading arm length less than 30m. As a result, during the continuous mining process of bucket wheel excavators, when mining the first mining width, the bucket wheel excavator alone cannot unload the material onto the working face belt conveyor. It is necessary to use a transfer conveyor to achieve this, which increases the number of operation steps and requires a longer cutting length, resulting in the formation of triangular coal seams. Cleaning up the triangular coal seams will seriously affect work efficiency. Summary of the Invention

[0009] The purpose of this invention is to provide a long-arm, compact bucket wheel excavator that fundamentally solves the aforementioned problems. It possesses advantages such as good stress characteristics, comprehensive process application functions, high reliability, convenient maintenance, and good safety.

[0010] To achieve the above objectives, the present invention provides the following technical solution: This long-arm compact bucket excavator includes a support mechanism, a bucket wheel drive mechanism, a discharge arm slewing mechanism, a track walking mechanism, and a tensioning mechanism. Its key technical features are: The unloading arm slewing mechanism includes a main traveling mechanism, a support base assembly, a rotating platform assembly, and an adjusting plate assembly; The support base assembly includes a central tube vertically fixed to the main traveling mechanism and a mounting base fixed to the central tube; the rotating platform assembly includes a rotatable rotating platform supported on an L-shaped beam. The adjusting plate assembly includes an adjusting plate body, lower connecting shaft slides symmetrically arranged on both sides of the adjusting plate body, and upper connecting shaft slides symmetrically arranged on the other two sides of the adjusting plate body. The guiding directions of the lower connecting shaft slides and the upper connecting shaft slides are perpendicular to each other. The mounting base is slidably fitted onto the upper connecting shaft slide groove via a pair of symmetrically arranged downward connecting shafts. The bottom of the downward connecting shaft is fitted into the mounting base. The fixed large gear ring is slidably fitted onto the lower connecting shaft slide rail via a pair of symmetrically arranged upward connecting shafts. The top of the upward connecting shaft is fitted into the fixed large gear ring. The outer edge of the slewing platform is rotatably supported on the L-shaped beam by a slewing bearing assembly. The bottom flange of the slewing platform is fixed to the small slewing bearing. The bottom of the small slewing bearing is mounted on the fixed large gear ring by a bolt assembly, so that the slewing platform and the fixed large gear ring can be rotatably engaged. A pair of slewing drive devices are symmetrically installed on the slewing platform. The output end of each slewing drive device passes through the slewing platform and is provided with a drive gear. The drive gears mesh symmetrically at both ends of the fixed large gear ring.

[0011] Furthermore, the bucket wheel drive mechanism includes a receiving boom, a short shaft assembly floatingly fixed on the receiving boom, a drive device installed at the input end of the short shaft assembly, and a wheel assembly shafted to the far drive end of the short shaft assembly. The short shaft assembly is floatingly mounted on the receiving boom, and the wheel assembly is rotatably mounted at the far drive end of the short shaft assembly. The wheel assembly and the drive device are respectively located on both sides of the floating bearing seat; a reinforcing flange is provided on the short shaft. The short shaft has a fixed end shoulder at the far drive end, and a fixed bearing housing is installed at the far end of the fixed end shoulder. The fixed bearing housing is fixed to the end cap by bolts at the far drive end. The near drive end is fitted with a fixed end labyrinth positioning ring and a fixed end through cover that cooperate with each other. A fixed end variable diameter positioning ring limits the fixed end between the fixed end labyrinth positioning ring and the fixed end shoulder. Fixed end gaskets are provided for primary sealing between the fixed bearing housing and the end cap, and between the fixed bearing housing and the fixed end through cover. The fixed end bearing is assembled between the fixed bearing housing and the short shaft.

[0012] Furthermore, the tensioning mechanism includes a hydraulic cylinder, two pairs of crossbeams arranged in the same direction as the extension and retraction of the hydraulic cylinder, two pairs of slide rails fixed to the inner side of the crossbeams, and rollers that slide and limit along the slide rails. A second column is fixed at the end of the crossbeam, and a first column with a through hole in the middle is fixed between the crossbeams. The slide is located between the first column and the second column and is provided with several slots at equal intervals. The ear plate is fixed on the first column. A positioning pin is installed on the ear plate by a wear-resistant copper sleeve. The hydraulic cylinder passes through the through hole and is radially limited by the trunnion set between the outer wall of the hydraulic cylinder and the ear plate. The piston rod of the hydraulic cylinder is hinged to one end of the drum via a first pin, and the other end of the drum is hinged to the positioning plate via a second pin. The positioning plate is adjustablely mounted on the slide rail via a clamping plate.

[0013] Furthermore, the tracked traveling mechanism includes a frame assembly with a base, two sets of symmetrically arranged track assemblies, and each track assembly includes a front drive wheel, a track bracket, a rear support wheel, and several track segments that are connected in series at equal intervals to form a closed loop. The track support is an airfoil structure with a horizontal center and downward ends. The upper center of the track support is equipped with a top support wheel set, and the front and rear ends of the track support are respectively equipped with front support wheels and rear support wheels. The front and rear protrusions of the lower part of the track support are respectively hinged with front travel wheel sets and rear travel wheel sets. The front travel wheel set or rear travel wheel set includes a primary travel frame with a symmetrical structure that is hinged to the track support, a pair of secondary travel frames with a symmetrical structure that are respectively hinged to the front and rear ends of the primary travel frame, a pair of tertiary travel frames with a symmetrical structure that are respectively hinged to the front and rear ends of the secondary travel frames, and four sets of bottom support wheels installed on each tertiary travel frame.

[0014] Furthermore, the near drive end of the short shaft is provided with a floating end shoulder, and a floating bearing housing is installed at the near end of the floating end shoulder. The far drive end and the near drive end of the floating bearing housing are each fitted with a pair of mutually cooperating floating end labyrinth-type positioning rings and floating end covers. A floating end variable diameter positioning ring limits the floating end between the floating end cover of the far drive end and the floating end shoulder. Floating end gaskets are provided for primary sealing between the floating bearing housing and the floating end covers on both sides. The floating end bearing is assembled between the floating bearing housing and the short shaft.

[0015] Furthermore, the inner side of each track section is formed by the outer wall protrusion to form a U-shaped groove. The front support wheel, the rear support wheel, and the bottom support wheel are limited and supported in the U-shaped groove, so that the closed-loop U-shaped groove formed by several track sections is spaced apart from the outer edge of the track support. At the same time, when adjacent track sections rotate in opposite directions around the coaxial axis, the adjacent outer wall protrusions form a meshing groove.

[0016] Furthermore, the front drive wheel is a smooth wheel, and the front drive wheel is fixed with meshing blocks at equal intervals around the center of the circle via meshing block pins. The meshing blocks include meshing protrusions with a pair of pin holes at the bottom and meshing shoulders symmetrically arranged on both sides of the meshing protrusions. The meshing shoulders are inclined downwards, so that the meshing surfaces of the outer edges of each meshing protrusion and the contact surfaces of the outer edges of each meshing shoulder are located on the same annular surface. When the front drive wheel rotates, the meshing protrusions and / or meshing shoulders are engaged in the meshing grooves of the track links.

[0017] The beneficial effects of this invention are as follows: Through targeted improvements to the core mechanism of the bucket wheel excavator, this invention achieves advantages such as optimized stress distribution, improved efficiency, convenient maintenance, and adaptability to complex working conditions. In terms of overall technical solution, the machine has a reasonable structural layout and excellent stress characteristics, making it suitable for high-capacity applications and long-arm structures, overcoming the core technical problems associated with them.

[0018] For the bucket wheel mechanism, the drive unit and conveyor are arranged on both sides of the bucket wheel body, so that the center point of the bucket lip on the bucket wheel body is close to or coincides with the center line of the entire machine, reducing the damage to the structure caused by off-center loading; at the same time, it shortens the extension distance on both sides of the bucket wheel body, realizing bidirectional material handling. The drive unit is close to the floating bearing seat, shortening the bearing span and reducing the lateral dimension; the drive unit and bucket wheel body are arranged as a whole on one side of the boom, ensuring free cutting angles on both sides, adapting to bidirectional excavation, and improving operating efficiency. The short shaft structure increases the torsional stiffness of the receiving boom, optimizes the weight of the bucket wheel mechanism, enhances the stability of the entire machine, and allows for an increase in wheel size within the boom load limit.

[0019] For the tensioning device, the receiving belt tensioning device is positioned at the front (on the bucket wheel side), fixing the intermediate transfer and unloading point to prevent the conveyor belt from deviating due to changes in the unloading point. A rigid frame with "double crossbeams and double columns" is adopted, integrating the roller axial positioning function, reducing space occupancy by more than 30% compared to traditional structures. The linkage system achieves automatic belt tension adjustment, stabilizing the tension within the optimal range, reducing belt slippage and wear during heavy-load starts, and extending component life; hydraulic cylinder disassembly and assembly takes only 30 minutes (traditionally 2-3 hours), significantly reducing downtime losses and maintenance costs. The design of the slide rail slots, positioning plates, and wear-resistant copper sleeves resists vibration and dust impact, ensuring the stability of the mechanism in harsh mining environments.

[0020] For the unloading boom, the connection point between the pitch mechanism connecting rod and the unloading boom is moved towards the receiving end, making the connecting rod and the unloading boom arranged at an acute angle, reducing the risk of bending deformation of the unloading boom and facilitating structural weight reduction. The slewing mechanism eliminates the central suspension shaft system and adopts a direct connection of "small slewing bearing + fixed large gear ring", which improves the resistance to eccentric loads and avoids the stress concentration problem of traditional shaft systems; the assembly process is simplified, reducing cumulative errors, reducing operational failures, and facilitating maintenance; the flexible sliding structure (adjusting plate, large gear ring, fixed central tube) can absorb the impact vibration of the traveling mechanism, preventing vibration from being transmitted to the bucket wheel and boom, ensuring smooth operation and extending the life of core components.

[0021] For the tracked walking mechanism, a split drive wheel with a "smooth wheel body + detachable meshing block" is adopted, with the meshing function achieved by an independent meshing block. When replacing worn meshing blocks, it is not necessary to disassemble the entire drive wheel and shaft system; simply rotate the drive wheel to the non-meshing state and insert or remove the pin to complete the replacement. This saves on spare parts costs, simplifies the operation process, shortens maintenance downtime, reduces labor costs and equipment operation interruption losses, and achieves "cost-saving, fast, time-saving, and labor-saving" maintenance.

[0022] In summary, the overall product structure of the present invention has the advantages of reasonable structural layout, good stress characteristics, full range of process application functions, high reliability, convenient maintenance, and good safety. It can adapt to and overcome various technical problems brought about by large production capacity and long arm structure. Attached Figure Description

[0023] Figure 1 This is a front view schematic diagram of the bucket wheel drive mechanism of the present invention.

[0024] Figure 1a for Figure 1 A partially enlarged structural diagram.

[0025] Figure 2 This is a schematic diagram of the unloading arm rotation mechanism of the present invention.

[0026] Figure 2a for Figure 2 A partially enlarged structural diagram.

[0027] Figure 2b for Figure 2 A cross-sectional view of the structure along line CC.

[0028] Figure 2c for Figure 2 A schematic diagram of the cross-sectional structure along line DD.

[0029] Figure 3 This is a schematic diagram of the tracked walking mechanism of the present invention in use.

[0030] Figure 3a for Figure 3 A magnified schematic diagram of part E in the middle section.

[0031] Figure 4 for Figure 3 A schematic diagram of the front drive wheel.

[0032] Figure 4a for Figure 4 A cross-sectional structural diagram.

[0033] Figure 5 This is a schematic diagram of the main structure of the tensioning mechanism of the present invention.

[0034] Figure 6 This is a top view of the tensioning mechanism of the present invention.

[0035] Figure 6a for Figure 6 A partially enlarged structural diagram.

[0036] Figure 7 This is a schematic diagram of the overall assembly structure of the present invention.

[0037] Explanation of reference numerals in the attached drawings: 1 Support mechanism, 11 Central bearing gantry, 12 Hydraulic cylinder, 14 Receiving arm, 141 Receiving belt conveyor, 142 Lower conveyor, 143 Head roller, 15 Pitching mechanism hinge point, 16 Unloading arm, 161 Hinge point, 17 Gantry rotary table, 13 Unloading arm pitching mechanism; 2. Bucket wheel drive mechanism; 21. Wheel body assembly; 22. Short shaft assembly; 221. Short shaft; 222. End plate; 223. Reinforcing flange; 224. Fixed end shoulder; 225. Floating end shoulder; 23. End cover; 24. Fixed bearing seat; 241. Fixed end bearing; 242. Fixed end washer; 243. Fixed end cover; 244. Fixed end variable diameter positioning ring; 245. Fixed end labyrinth positioning ring; 25. Floating bearing seat; 251. Floating end bearing; 252. Floating end washer; 253. Floating end cover; 254. Floating end variable diameter positioning ring; 255. Floating end labyrinth positioning ring; 2551. Outer rubber V-ring seal; 2552. Inner rubber V-ring seal; 256. Locking disc; 26. Drive unit; 27. Receiving boom; 3. Unloading arm slewing mechanism, 31. Support base assembly, 311. Mounting seat, 312. Central tube, 32. Slewing drive device, 321. Drive gear, 33. Fixed large gear ring, 34. Hook, 35. Small slewing bearing, 36. L-beam, 37. Slewing bearing assembly, 38. Slewing platform, 381. Flange face, 39. Adjusting plate assembly, 391. Lower connecting shaft slide, 392. Adjusting plate body, 393. Upper connecting shaft groove, 394. Downward connecting shaft, 395. Upward connecting shaft; 4 Tracked traveling mechanism, 41 Front drive wheel, 411 Meshing block, 4111 Meshing protrusion, 4112 Meshing surface, 4113 Meshing shoulder, 4114 Shoulder contact surface, 4115 Outer end, 412 Meshing block pin, 413 Drive shaft, 42 Track link, 421 Outer wall protrusion, 43 Track bracket, 431 Rear traveling wheel set, 432 Chassis, 433 Top support wheel set, 4331 Front support wheel, 4332 Middle support wheel, 4333 Rear support wheel, 434 Front traveling wheel set, 4341 Primary traveling frame, 4342 Secondary traveling frame, 4343 Tertiary traveling frame, 4344 Bottom support wheel, 44 Rear support wheel; 5. Tensioning mechanism, 51. Hydraulic cylinder body, 511. Trunnion, 512. Ear plate, 5121. Wear-resistant copper sleeve, 5122. Positioning pin sleeve, 513. Piston rod, 52. Roller, 521. First pin, 522. Positioning plate, 523. Clamping plate, 524. Second pin, 53. Crossbeam assembly, 531. First column, 5311. Through hole, 532. Second column, 533. Crossbeam, 5331. Slide, 5332. Slot. Detailed Implementation

[0038] The following combination Figures 1-7 The specific content of the present invention will be described in detail through specific embodiments.

[0039] [Bucket excavator assembly].

[0040] like Figure 7 As shown, this long-arm compact bucket excavator comprises a support mechanism 1, a bucket wheel drive mechanism 2, a discharge arm slewing mechanism 3, a track walking mechanism 4, and a tensioning mechanism 5. The support mechanism 1 includes a central support gantry 11, a receiving arm 14, a gantry-shaped rotary table 17, and a discharge arm 16. The tail of the receiving arm 14 is hinged to the central support gantry 11, and the bottom of the receiving arm 14 is hinged to the bottom of the central support gantry 11 via two hydraulic cylinders 12. One end of the discharge arm 16 is rotatably mounted on the gantry-shaped rotary table 17, and the middle of the discharge arm 16 is connected to the central support gantry 11 via a discharge arm pitching mechanism 13. The upper end of the discharge arm pitching mechanism 13 is hinged to the upper part of the central support gantry 11 via a pitching mechanism hinge point 15. The short beam of the discharge arm pitching mechanism 13 and the hinge point 161 of the discharge arm 16 move from the vertical point towards the receiving end, arranged at an acute angle. The upper cover plate at the center rotation position of the central bearing gantry 11 is connected to the lower part of the receiving point. The slewing bearing assembly 37 is connected to the chassis 432 through its own central tube 312. The tracked traveling mechanism 4 is connected to the gantry turntable 17 through the slewing bearing assembly 37. The lower part of the chassis 432 of the tracked traveling mechanism 4 has a zigzag design to ensure external maintenance space at the lubrication points of the multi-stage balance beams.

[0041] [Bucket wheel drive mechanism]

[0042] The bucket wheel drive mechanism 2 includes a receiving boom 27, a short shaft assembly 22 floatingly fixed on the receiving boom 27, a drive device 26 installed at the drive end of the short shaft assembly 22, and a wheel assembly 21 fixed on the short shaft assembly 22. The short shaft assembly 22 includes a short shaft 221, a fixed bearing seat 24 rotatably fitted at the far end of the short shaft 221 for mounting the wheel assembly 21, and a floating bearing seat 25 rotatably fitted at the near end of the short shaft 221 for floatingly assembling the short shaft assembly 22 on the receiving boom 27. A receiving belt conveyor 141 is arranged inside the receiving boom 27. The receiving belt conveyor 141 is arranged at a certain angle to the central axis of symmetry in the width direction of the entire machine, intersecting the axis of symmetry at the support center point of the rotary platform 38. The lower conveyor 142 is located below the receiving boom 27, receiving the material transferred by the receiving belt conveyor 141 and conveying it backward; the head roller 143 is installed at the front end of the receiving boom 27, providing transmission power and tension adjustment for the receiving belt conveyor 141 to ensure stable conveying.

[0043] The short shaft 221 is bolted to the web of the wheel assembly 21 using a reinforcing flange 223 in the middle. A stop structure is used for radial positioning. The far drive end of the short shaft 221 has a large transition fillet and a fixed end shoulder 224. A fixed bearing seat 24 is installed at the far end of the fixed end shoulder 224. The fixed bearing seat 24 and the floating bearing seat 25 are bolted to the receiving boom 27, so that the entire bucket wheel mechanism is arranged on one side of the receiving boom 27.

[0044] A fixed-end bearing 241, preferably a ball bearing, is assembled between the fixed bearing housing 24 and the short shaft 221. The near-drive device 26 end of the fixed bearing housing 24 is axially positioned using a fixed-end variable-diameter positioning ring 244, a fixed-end labyrinth-type positioning ring 245, and a fixed-end through-cap 243. The far-drive device 26 end of the fixed bearing housing 24 is axially positioned using an end plate 222 and an end cap 23. Fixed-end washers 242 are respectively provided between the fixed bearing housing 24 and the end cap 23 or between the fixed-end through-cap 243 for cavity sealing. The fixed-end through-cap 243 adopts an integrated positioning and labyrinth structure, forming a labyrinth seal when combined with the fixed-end labyrinth-type positioning ring 245. The fixed-end through-cap 243 is fitted onto the fixed-end labyrinth-type positioning ring 245, with a pair of rubber V-rings providing secondary sealing.

[0045] Similarly, the near-drive end of the short shaft 221 has a transition fillet and a floating end shoulder 225. A floating bearing seat 25 is installed near the floating end shoulder 225. A floating end bearing 251, preferably a ball bearing, is assembled between the floating bearing seat 25 and the short shaft 221. The floating bearing seat 25 is axially positioned by a pair of symmetrically arranged floating end covers 253 and floating end labyrinth-type positioning rings 255. The floating end labyrinth-type positioning ring 255 assembled at the far-drive end 26 along the axial direction is positioned by a floating end variable diameter positioning ring 254, and the floating end labyrinth-type positioning ring 255 assembled at the near-drive end 26 is positioned by a locking disc 256. Floating end washers 252 are respectively provided between the floating bearing seat 25 and the floating end covers 253 at both ends for cavity sealing. The floating end cover 253 adopts an integrated positioning and labyrinth structure, which, together with the floating end labyrinth-type positioning ring 255, forms a labyrinth seal. The floating end cover 253 is fitted onto the floating end labyrinth positioning ring 255, and the labyrinth seal is secondary sealed by the inner rubber V-shaped sealing ring 2552 and the outer rubber V-shaped sealing ring 2551.

[0046] Through the above scheme, the short shaft assembly 22 can float relative to the width direction of the receiving boom 27. The floating range of the wheel assembly 21 is determined by the floating stroke of the floating bearing seat 25 on the short shaft 221. The drive device 26 and the wheel assembly 21 are respectively located at opposite ends of the floating bearing seat 25. In the non-working state, the weight of the drive device 26 end is greater than that of the wheel assembly 21. When the wheel assembly 21 rotates in the working state, the drive device 26 acts as a power source, driving the wheel assembly 21, which is coaxial with it, to rotate. According to the centrifugal force formula F=mω²r (where F is the centrifugal force, m is the mass, ω is the angular velocity, and r is the radius of rotation), when the wheel rotates, it generates a larger centrifugal force due to its larger radius of rotation relative to the motor. In the high-speed rotation state, the direction of the centrifugal force is away from the center of rotation. Since the wheel and the motor are located at opposite ends of the floating bearing seat 25, they can balance each other at a specific speed, keeping the entire shaft system stable during rotation. This avoids the imbalance problem caused by the superposition of the wheel assembly 21 and the drive device 26, thus ensuring that both sides of the wheel assembly 21 have reasonable free cutting angles, meeting the requirements of reciprocating digging operations and improving work efficiency.

[0047] [Unloading arm rotary mechanism].

[0048] The unloading arm rotation mechanism 3 is fixed on the track walking mechanism 4, and includes a support base assembly 31, a rotating platform assembly, and an adjusting plate assembly 39.

[0049] like Figure 1 , Figure 2 As shown, the support base assembly 31 includes a central tube 312 vertically fixed to the main unit's traveling mechanism and a mounting base 311 fixed to the central tube 312. To facilitate manufacturing and on-site assembly and maintenance, the central tube 312 adopts a three-section structure and is fixedly connected by bolts.

[0050] The adjusting plate assembly 39 includes an adjusting plate body 392, lower connecting shaft slides 391 symmetrically arranged on both sides of the adjusting plate body 392, and upper connecting shaft slide grooves 393 symmetrically arranged on the other two sides of the adjusting plate body 392. The guiding directions of the lower connecting shaft slides 391 and the upper connecting shaft slide grooves 393 are perpendicular to each other. The mounting base 311 is slidably engaged with the upper connecting shaft slide grooves 393 via a pair of symmetrically arranged lower connecting shafts 394. The bottom of the lower connecting shafts 394 is fitted into the mounting base 311. The fixed large gear ring 33 is slidably engaged with the lower connecting shaft slides 391 via a pair of symmetrically arranged upper connecting shafts 395. The top of the upper connecting shafts 395 is fitted into the fixed large gear ring 33.

[0051] The adjusting plate assembly 39 is a flexible connector between the fixed large gear ring 33 and the central tube 312. In the vertical direction of the adjusting plate assembly 39, a pair of symmetrically arranged lower connecting shaft slides 391 and upper connecting shaft grooves 393 are respectively provided. The fixed large gear ring 33 is slidably connected to the left and right sides of the adjusting plate assembly 39, and the front and rear sides of the adjusting plate assembly 39 are slidably connected to the central tube 312. Figure 2 Viewpoint. The downward connecting shaft 394 and the upward connecting shaft 395 slide laterally in the plane of the adjusting plate assembly 39 under the guidance of the upper connecting shaft slide groove 393 and the lower connecting shaft slide 391, respectively, and the extension lines of the sliding trajectories are perpendicular to each other.

[0052] The rotating platform assembly includes a rotating platform 38 rotatably supported on a small slewing bearing 35. The rotating platform 38 is rotatably supported on the small slewing bearing 35 by an L-shaped beam 36. The outer ring of the L-shaped beam 36 is fixed to the small slewing bearing 35, and the inner ring of the L-shaped beam 36 is fixed to the outer edge of the rotating platform 38.

[0053] The bottom flange face 381 of the rotary platform 38 is bolted to the upper surface of the hook 34. The bottom of the hook 34 is bolted to the fixed large gear ring 33, allowing the rotary platform 38 and the fixed large gear ring 33 to rotatably engage. A pair of rotary drive devices 32 are symmetrically mounted on the rotary platform 38. The output end of each rotary drive device 32 passes through the rotary platform 38 and is equipped with a drive gear 321, which meshes symmetrically with both ends of the fixed large gear ring 33. When the rotary drive device 32 drives the drive gear 321 to rotate, it is subjected to the reaction force of the fixed large gear ring 33, causing the rotary drive device 32 to push the rotary platform 38 to rotate. The rotary platform 38 is also equipped with a hook 34 for easy lifting. The rotary platform 38 is bolted to the fixed large gear ring 33 via the hook 34, which is the only component connecting the rotary platform 38 and the fixed large gear ring 33. All the gravity load of the fixed large gear ring 33 is borne by the hook 34. The fixed large gear ring 33 and the hook 34 are provided with a coaxial positioning structure. The fixed large gear ring 33 cannot rotate, while the hook 34 can rotate around the center of the central tube 312 after it is installed with the rotary platform 38.

[0054] [Tracked walking mechanism].

[0055] The tracked walking mechanism 4 includes a frame assembly with a chassis 432 and two sets of symmetrically arranged track assemblies. Each track assembly includes a front drive wheel 41, a track bracket 43, a rear support wheel 44, and several track sections 42 that are connected in series at equal intervals to form a closed loop.

[0056] The track support 43 is an airfoil structure with a horizontal center and downward ends. The upper center of the track support 43 is provided with a top support wheel set 433. The front and rear ends of the track support 43 are respectively provided with front support wheels 4331 and rear support wheels 4333, and the middle is provided with a middle support wheel 4332. The front and rear protrusions of the lower part of the track support 43 are respectively hinged to the front and rear travel wheel sets 434 and rear travel wheel sets 431. The front travel wheel set 434 or the rear travel wheel set 431 includes a first-level travel frame 4341 with a symmetrical structure that is hinged to the track support 43, a pair of second-level travel frames 4342 with a symmetrical structure that are respectively hinged to the front and rear ends of the first-level travel frame 4341, a pair of third-level travel frames 4343 with a symmetrical structure that are respectively hinged to the front and rear ends of the second-level travel frames 4342, and four sets of bottom support wheels 4344 installed on each third-level travel frame 4343. Each track section 42 has a U-shaped groove formed by an outer wall protrusion 421 on its inner side. The front support wheel 4331, the rear support wheel 4333, and the bottom support wheel 4344 are limited and supported in the U-shaped groove, so that the closed-loop U-shaped groove formed by several track sections 42 is spaced apart from the outer edge of the track bracket 43. At the same time, when adjacent track sections 42 rotate in opposite directions around the coaxial axis, a meshing groove is formed between adjacent outer wall protrusions 421. The front drive wheel 41 is a smooth wheel, which is mounted on the track bracket 43 via the drive shaft 413 and driven by the motor reducer 431. The front drive wheel 41 is fixed with meshing blocks 411 at equal intervals around the center of the circle via meshing block pins 412. The meshing block 411 includes a meshing protrusion 4111 with a pair of pin holes at the bottom and meshing shoulders 4113 symmetrically arranged on both sides of the meshing protrusion 4111. The outer end 4115 of the meshing shoulder 4113 is inclined downward, so that the meshing surface 4112 of the outer edge of each meshing protrusion 4111 and the shoulder contact surface 4114 of the outer edge of each meshing shoulder 4113 are located on the same annular surface. When the front drive wheel 41 rotates, the meshing protrusion 4111 and / or the meshing shoulder 4113 are engaged in the meshing groove of the track link 42.

[0057] The above method allows the meshing block 411 to replace the original drive wheel gear and mesh with the track link. When the meshing block 411 is severely worn and needs to be replaced, the meshing block 411 to be replaced is rotated to a non-meshing state by moving the main unit, the meshing block pin 412 is pulled out, the new meshing block 411 to be replaced is removed, and the new meshing block 411 is replaced. It is then fixed again with the meshing block pin 412 to complete the replacement.

[0058] [Tensioning mechanism]

[0059] The receiving belt conveyor 141 has two symmetrical tensioning mechanisms 5 arranged at one end of the wheel assembly 21. The tensioning mechanism 5 mainly consists of a hydraulic cylinder 51, a crossbeam assembly 53, a guide assembly, and a roller adjustment assembly. These components work together to achieve dynamic control of the belt conveyor's tension and quick assembly / disassembly. The crossbeam assembly 53 includes a pair of parallel crossbeams 533, whose extension direction is consistent with the extension / retraction direction of the hydraulic cylinder 51, forming the basic load-bearing frame of the mechanism. Both ends of the crossbeams 533 are rigidly connected to the column assembly: a second column 532 is fixedly connected to the end, and the middle area is connected as a whole through a first column 531. The first column 531 has a through hole 5311 in its middle for the hydraulic cylinder to pass through. The double-column structure strengthens the torsional stiffness and support stability of the crossbeam assembly 53.

[0060] The guide assembly consists of a pair of slide rails 5331, which are fixed to the inner wall of the crossbeam 533 by welding and are continuously arranged along the span direction between the first column 531 and the second column 532. The inner wall of the slide rails 5331 has several equally spaced slots 5332 pre-set. The cross-sectional dimensions of the slots 5332 match the positioning components, providing an axial sliding trajectory for the roller 52 and achieving rigid positioning of the roller 52 through a snap-fit ​​structure.

[0061] The assembly structure of the hydraulic cylinder body 51 adopts a modular design: symmetrical ear plates 512 are welded to the outer wall of the first column 531, and locating pin sleeves 5122 are fitted on the outer side of the ear plates 512. A wear-resistant copper sleeve 5121 is embedded between the two, and the self-lubricating properties of the copper sleeve reduce frictional loss during relative rotation. After the hydraulic cylinder body 51 passes through the through hole 5311 of the first column 531, its outer wall forms a radial limiting fit with the ear plates 512 through the trunnion 511. The trunnion 511 and the locating pin sleeve 5122 form a hinge pair, allowing the hydraulic cylinder body 51 to swing slightly around the axis of the trunnion 511, compensating for assembly errors and minor deformations during operation.

[0062] The roller adjustment assembly is the core actuator for achieving the tensioning function. Both ends of the roller 52 are connected to the drive component and the positioning component via pin structures: the side closer to the hydraulic cylinder 51 is hinged to the piston rod 513 of the hydraulic cylinder 51 via a first pin 521, forming the drive end; the side farther from the hydraulic cylinder 51 is hinged to the positioning plate 522 via a second pin 524. The positioning plate 522 is symmetrically arranged on both sides of the slide rail 5331, and its bottom is detachably engaged with the slot 5332 of the slide rail 5331 via a locking plate 523. This structure allows the positioning plate 522 to be adjusted to multiple positions along the slide rail 5331, and the roller 52 is pre-positioned through the cooperation of the locking plate 523 with different slots 5332.

[0063] During operation, when the conveyor belt tension needs to be adjusted, the control system drives the piston rod 513 of the hydraulic cylinder 51 to extend and retract, and drives the roller 52 to slide axially along the slide rail 5331 through the first pin 521. At this time, the positioning plate 522 moves synchronously with the roller, and the clamping plate 523 is in the unlocked state and does not participate in positioning, so as to realize the dynamic stepless adjustment of the tension stroke and ensure that the conveyor belt always maintains the best tension.

[0064] When tension adjustment is required, the piston rod 513 of the hydraulic cylinder 51 pushes the roller 52 to move along the slide rail 5331, and the tension stroke is adjusted at any time according to the program settings. At this time, the positioning plate 522 does not need to be fixed by the clamping plate 523. When the maintenance worker is in operation, the clamping plate 523 is inserted into the clamping groove 5332 of the slide rail 5331 to fix the roller 52. Then, the oil pressure in the hydraulic cylinder 51 is released, the positioning pin sleeve 5122 is pulled out, and the hydraulic cylinder 51 and the piston rod 513 can be removed from the through hole 5311 of the first column 531 at the same time.

Claims

1. A long-arm compact bucket excavator, comprising a support mechanism (1), a bucket wheel drive mechanism (2), a discharge arm slewing mechanism (3), a track walking mechanism (4), and a tensioning mechanism (5), characterized in that: The unloading arm slewing mechanism (3) includes a main traveling mechanism, a support base assembly (31), a rotating platform assembly, and an adjusting plate assembly (39); the support base assembly (31) includes a central tube (312) vertically fixed on the main traveling mechanism and a mounting seat (311) fixed on the central tube (312); the rotating platform assembly includes a rotating platform (38) supported on an L-shaped beam; the adjusting plate assembly (39) includes an adjusting plate body (392), lower connecting shaft slides (391) symmetrically arranged on both sides of the adjusting plate body (392), and upper connecting shaft slides (393) symmetrically arranged on the other two sides of the adjusting plate body (392), the guiding directions of the lower connecting shaft slides (391) and the upper connecting shaft slides (393) are perpendicular to each other; The mounting base (311) is slidably fitted onto the upper connecting shaft groove (393) via a pair of symmetrically arranged downward connecting shafts (394). The bottom of the downward connecting shafts (394) is fitted into the mounting base (311). The fixed large gear ring (33) is slidably fitted onto the lower connecting shaft slide (391) via a pair of symmetrically arranged upward connecting shafts (395). The top of the upward connecting shafts (395) is fitted into the fixed large gear ring (33). The outer edge of the rotary platform (38) is rotatably supported on the L-shaped beam by the rotary bearing assembly (37). The bottom flange face (381) of the rotary platform (38) is fixed on the small slewing bearing (35). The bottom of the small slewing bearing (35) is mounted on the fixed large gear ring (33) by bolt assembly, so as to realize the rotational engagement between the rotary platform (38) and the fixed large gear ring (33). A pair of rotary drive devices (32) are symmetrically installed on the rotary platform (38). The output end of each rotary drive device (32) passes through the rotary platform (38) and is provided with a drive gear (321). The drive gear (321) meshes symmetrically at both ends of the fixed large gear ring (33). The bucket wheel drive mechanism (2) includes a receiving boom (27), a short shaft assembly (22) floatingly fixed on the receiving boom (27), a drive device (26) installed at the input end of the short shaft assembly (22), and a wheel assembly (21) shafted to the far drive end of the short shaft assembly (22). The short shaft assembly (22) is floatingly installed on the receiving boom (27), and the wheel assembly (21) is rotatably installed at the far drive end of the short shaft assembly (22). The wheel assembly (21) and the drive device (26) are respectively located on both sides of the floating bearing seat (25); a reinforcing flange (223) is provided on the short shaft (221). The short shaft (221) has a fixed end shoulder (224) at the far drive end. A fixed bearing housing (24) is installed at the far end of the fixed end shoulder (224). An end cover (23) is fixed to the far drive end of the fixed bearing housing (24) by bolts. A fixed end labyrinth positioning ring (245) and a fixed end through cover (243) are fitted together at the near drive end. A fixed end variable diameter positioning ring (244) limits the fixed end between the fixed end labyrinth positioning ring (245) and the fixed end shoulder (224). Fixed end gaskets (242) are respectively provided between the fixed bearing housing (24) and the end cover (23) and between the fixed bearing housing (24) and the fixed end through cover (243) for primary sealing. The fixed end bearing (241) is assembled between the fixed bearing housing (24) and the short shaft (221).

2. The long-arm compact bucket excavator according to claim 1, characterized in that: The tensioning mechanism (5) includes a hydraulic cylinder body (51), two pairs of crossbeams (533) arranged in the same direction as the extension and retraction direction of the hydraulic cylinder body (51), two pairs of slide rails (5331) fixed inside the crossbeams (533), and rollers (52) that slide and limit along the slide rails (5331). A second column (532) is fixed to the end of the crossbeam (533), and a first column (531) with a through hole (5311) in the middle is fixed between the crossbeams (533). The slide rail (5331) is located between the first column (531) and the second column (532), and several slots (5332) are provided at equal intervals. The ear plate (512) is fixed on the first column (531), and a positioning pin sleeve (5122) is installed on the ear plate (512) through a wear-resistant copper sleeve (5121). The cylinder body (51) passes through the through hole (5311) and is radially limited by the trunnion (511) provided between the outer wall of the hydraulic cylinder body (51) and the ear plate (512); the piston rod (513) of the hydraulic cylinder body (51) is hinged to one end of the roller (52) by the first pin (521), and the other end of the roller (52) is hinged to the positioning plate (522) by the second pin (524). The positioning plate (522) is adjusted and assembled on the slide rail (5331) by the clamping plate (523).

3. The long-arm compact bucket excavator according to claim 1, characterized in that: The tracked walking mechanism (4) includes a frame assembly with a base, two sets of symmetrically arranged track assemblies, each track assembly including a front drive wheel (41), a track bracket (43), a rear support wheel (44), and several track sections (42) that are connected in series at equal intervals to form a closed loop. The track support (43) is a wing-shaped structure with a horizontal middle section and downward ends. The upper middle section of the track support (43) is provided with a top support wheel set (433). The front and rear ends of the track support (43) are respectively provided with a front support wheel (4331) and a rear support wheel (4333). The front and rear protrusions of the lower part of the track support (43) are respectively hinged to a front travel wheel set (434) and a rear travel wheel set (431). The front travel wheel set (434) or the rear travel wheel set (431) includes a first-level travel frame (4341) with a symmetrical structure that is hinged to the track support (43), a pair of second-level travel frames (4342) with a symmetrical structure that are respectively hinged to the front and rear ends of the first-level travel frame (4341), a pair of third-level travel frames (4343) with a symmetrical structure that are respectively hinged to the front and rear ends of the second-level travel frames (4342), and four sets of bottom support wheels (4344) installed on each third-level travel frame (4343).

4. The long-arm compact bucket excavator according to claim 1, characterized in that: The short shaft (221) has a floating end shoulder (225) at the near drive end. A floating bearing seat (25) is installed at the near end of the floating end shoulder (225). A pair of mutually cooperating floating end labyrinth positioning rings (255) and floating end covers (253) are fitted on the far drive end and the near drive end of the floating bearing seat (25). A floating end variable diameter positioning ring (254) limits the floating end between the floating end cover (253) of the far drive end and the floating end shoulder (225). A floating end washer (252) is provided between the floating bearing seat (25) and the floating end covers (253) on both sides for primary sealing. The floating end bearing (251) is assembled between the floating bearing seat (25) and the short shaft (221).

5. The long-arm compact bucket excavator according to claim 3, characterized in that: The inner side of each track section (42) is formed by the outer wall protrusion (421) to form a U-shaped groove. The front support wheel (4331), the rear support wheel (4333), and the bottom support wheel (4344) are limited and supported in the U-shaped groove, so that the closed-loop U-shaped groove formed by several track sections (42) is spaced apart from the outer edge of the track support (43). At the same time, when adjacent track sections (42) rotate in opposite directions around the coaxial axis, a meshing groove is formed between adjacent outer wall protrusions (421).

6. The long-arm compact bucket excavator according to claim 5, characterized in that: The front drive wheel (41) is a smooth wheel. The front drive wheel (41) is fixed with meshing blocks (411) at equal intervals around the center of the circle via meshing block pins (412). The meshing blocks (411) include meshing protrusions (4111) with a pair of pin holes at the bottom and meshing shoulders (4113) symmetrically arranged on both sides of the meshing protrusions (4111). The meshing shoulders (4113) are inclined downward so that the meshing surfaces (4112) of the outer edges of each meshing protrusion (4111) and the shoulder contact surfaces (4114) of the outer edges of each meshing shoulder (4113) are located on the same annular surface. When the front drive wheel (41) rotates, the meshing protrusions (4111) and / or the meshing shoulders (4113) are engaged in the meshing groove of the track section (42).

Images