An oscillating cutting arm suitable for disc bottom cutting rock

Abstract

The present application relates to a kind of oscillating cutting arm suitable for disc undercut rock breaking, belong to mechanical rock breaking equipment technical field.It includes cutting support big arm, telescopic arm, cutting arm and cutting disc, telescopic arm is slid in the front end of cutting support big arm, the front end of telescopic arm is connected with the rear end of cutting arm by cross hinged module.The present application sets up first elastic support disc and second elastic support disc in cross hinged module and constitutes double-layer elastic support structure, provides cutting displacement for disc undercut rock breaking, while effectively solve the technical problem that impact load is directly transmitted to telescopic arm through hinged joint under hard rock undercut working condition.Secondly, eccentric drive mechanism adopts combination structure, and operator can flexibly select to install different number or mass of counterweight according to different rock hardness, so as to realize the online adjustment of excitation force amplitude.Thirdly, spring buffer is set between adjusting oil cylinder and cutting support big arm, effectively relieve the impact of oscillation force on cutting support big arm.

Description

Technical Field

[0001] This invention relates to the field of mechanical rock-breaking equipment technology, and in particular to an oscillating cutting arm suitable for disc bottom cutting of rock. Background Technology

[0002] When cutting and breaking the bottom rock strata of rock tunnels or mine roadways, a vibrating cutting arm combined with a cutting disc is typically used in equipment such as tunnel boring machines, cantilever machines, or mining machines. This construction method, which uses disc-shaped cutting tools to cut and break the rock mass at the bottom of the working face, is called disc bottom cutting rock breaking. This rock breaking method utilizes the physical property that rock is more resistant to compression than tension (shear). By changing the cutting angle of the disc, the rock is directly subjected to tensile and shear damage, thereby improving rock breaking efficiency.

[0003] Currently, existing disc-type cutting arms typically include a support arm, a telescopic arm, and a cutting arm. The cutting disc is installed at the front end of the cutting arm, and feed is achieved by extending and retracting the telescopic arm, while angle adjustment is achieved by oscillating the cutting arm. Some existing technologies incorporate an eccentric block within the cutting arm, superimposing high-frequency, low-amplitude oscillating motion on top of the oscillating cutting action of the cutting disc. This combines shear force and impact load on the rock, thereby improving rock-breaking efficiency.

[0004] However, the aforementioned rock-breaking devices still have the following shortcomings in actual use, affecting the service life and rock-breaking accuracy of the equipment: First, under hard rock undercutting conditions, the irregular impact load on the cutting disc is directly transmitted to the articulated joint and telescopic arm, leading to increased joint wear and decreased guiding accuracy of the telescopic arm, which seriously affects the service life and rock-breaking positioning accuracy of the equipment; Second, in the existing technology, the amplitude of the excitation force generated by the eccentric block is usually fixed and cannot be adjusted according to the working conditions of rock layers with different hardness. When the excitation force is not matched with the current working conditions, the cutting arm cannot cut under the optimal working conditions, which not only affects the rock-breaking efficiency, but also accelerates the fatigue damage of the cutting arm and related components due to mismatched vibration, further shortening the service life of the equipment. Summary of the Invention

[0005] To solve the above-mentioned technical problems, the present invention provides an oscillating cutting arm suitable for disc bottom cutting of rock. The technical solution of the present invention is as follows: An oscillating cutting arm suitable for disc bottom cutting of rock includes a cutting support arm, a telescopic arm, a cutting arm, and a cutting disc. The telescopic arm is slidably mounted on the front end of the cutting support arm. The front end of the telescopic arm is connected to the rear end of the cutting arm through a cross hinge module. An adjustment mechanism for driving the cutting arm to extend and retract and for angle adjustment is provided on the outside of the cutting support arm. The cutting disc is detachably connected to the front end of the cutting arm. An eccentric drive mechanism is also connected inside the cutting arm. The cross-hinged module includes a fixed base and a cross hinge. The fixed base is fixedly connected to the front end of the telescopic arm. The four hinge ends of the cross hinge are rotatably connected to two lugs at the front end of the fixed base and two lugs at the rear end of the cutting arm, respectively. The cross hinge includes a square base and four central pillars. The four central pillars are detachably connected to the four sides of the square base. Each central pillar is fitted with a primary elastic support plate, a secondary elastic support plate, and a rotating ring along its axial direction from the inside to the outside. The four lugs are fitted on the outer side of the corresponding rotating ring. The primary elastic support plate elastically abuts against the square base and the secondary elastic support plate to isolate the vibration transmission between the cutting arm and the telescopic arm. The secondary elastic support plate elastically abuts against the inner side of the corresponding lug to provide the elastic displacement space required for the oscillating motion of the cutting arm. The eccentric drive mechanism includes an eccentric disk, which is rotatably installed inside the cutting arm. Multiple mounting holes for mounting counterweights are provided on the end face of the eccentric disk along its circumference. The amplitude of the excitation force generated when the eccentric disk rotates is less than the maximum elastic deformation recovery force of the first-stage elastic support disk and the second-stage elastic support disk.

[0006] Optionally, the cutting support arm includes a support arm and a bushing. The rear end of the telescopic arm is slidably disposed within the support arm. The inner diameter of the bushing is larger than the inner diameter of the support arm. A first locking flange is fixedly connected to the front end of the support arm. The first locking flange is fixedly connected to the rear end of the bushing by bolts. Placement grooves are provided on the inner ring walls of both the front and rear ends of the bushing. A wedge-shaped adjustment assembly is installed in the placement groove. The wedge-shaped adjustment assembly includes a fixed ring and an inner wedge ring. The fixed ring is embedded in the placement groove. The inner wedge ring is disposed inside the fixed ring. The inner ring wall of the fixed ring has an inner wedge surface that mates with the inner wedge ring. The inner ring wall of the inner wedge ring abuts against the outer wall of the telescopic arm. The inner wedge ring is composed of multiple arc-shaped wedge segments. A second locking flange is fixedly connected to the front end of the bushing by bolts.

[0007] Optionally, the inner rear end of the support arm is fixedly connected to a square guide post extending along its axial direction, and the rear end of the telescopic arm is fixedly connected to an end cap, the end cap having a through square hole for the square guide post to slide through.

[0008] Optionally, the square base has several placement holes on its four sides and around the central column. Guide posts corresponding to the placement holes are fixedly connected to the surface of the secondary elastic support plate facing the primary elastic support plate. Through holes corresponding to the guide posts are formed along the circumference of the surface of the primary elastic support plate. The guide posts movably pass through the corresponding through holes and extend into the corresponding placement holes. Some of the guide posts are axially penetrating hollow structures with fixing bolts passing through them. The shank of the fixing bolt passes through the guide post, and its lower end connects to a threaded hole at the bottom of the corresponding placement hole. A primary spring is sleeved inside the placement hole and outside the guide post. The two ends of the primary spring elastically abut against the bottom surface of the placement hole and the surface of the primary elastic support plate facing the placement hole, respectively. Multiple secondary springs are distributed circumferentially between the primary and secondary elastic support plates, and each secondary spring is sleeved outside the corresponding guide post.

[0009] Optionally, the primary spring is a high-stiffness spring, whose compression deformation is less than the maximum compressible stroke of the secondary spring, and the secondary spring is a low-stiffness long-stroke spring.

[0010] Optionally, the adjustment mechanism includes multiple adjusting cylinders, with multiple adjusting rods arranged circumferentially on the outer side of the cutting support arm. Multiple support seats, each corresponding to one of the adjusting cylinders, are fixedly connected circumferentially to the rear end of the outer wall of the cutting arm. A front ear seat is fixedly connected to the rear end face of each support seat. The piston rod end of the adjusting cylinder is hinged to the corresponding front ear seat. A rear ear seat is hinged to the rear end of the cylinder body of the adjusting cylinder. Multiple cylinder seats, each corresponding to one of the adjusting cylinders, are fixedly connected circumferentially to the rear end of the outer wall of the cutting support arm. The rear ear seat is slidably mounted within the corresponding cylinder seat along the axial direction of the cutting support arm. An elastic unit is connected within the cylinder seat, and the elastic unit elastically abuts against the front and rear end faces of the rear ear seat and the front and rear side walls of the cylinder seat.

[0011] Optionally, a movable plate is fixedly connected to the lower surface of the rear ear seat. The movable plate slides on the upper surface of the cylinder seat. A front side plate and a rear side plate are fixedly connected to the front and rear sides of the upper surface of the cylinder seat, respectively. The elastic unit includes an adjusting plate and multiple adjusting bolts. The adjusting plate slides on the upper surface of the cylinder seat and is located between the movable plate and the rear side plate. The multiple adjusting bolts are threaded through the rear side plate and abut against the rear side of the adjusting plate. Multiple axially extending guide rods are fixedly connected to the rear side of the front side plate and the front side of the adjusting plate. Guide holes for the guide rods to slide on the front and rear sides of the movable plate are provided. A small spring is sleeved on the outer side of the guide rod.

[0012] Optionally, the eccentric drive mechanism further includes a fixed sleeve, a rear end seat, and a drive shaft, all disposed inside the cutting arm. A front flange is fixedly fitted on the front end of the outer side wall of the fixed sleeve. A connecting flange is fixedly connected to the rear end face of the cutting disc. The front flange is sandwiched between the connecting flange and the cutting arm, and the three are fixed together by bolts. The rear end seat is fixed to the rear end of the fixed sleeve by bolts. The eccentric disc is fixedly fitted in the middle position of the drive shaft. Both ends of the drive shaft are fitted with combined bearings. The two sets of combined bearings are respectively embedded inside the fixed sleeve and the rear end seat. A drive motor is fixedly connected to the rear end of the rear end seat. The output shaft of the drive motor is connected to the rear end of the drive shaft via a spline drive.

[0013] Optionally, the outer peripheral wall of the eccentric disk is evenly distributed with a number of axially extending micro-teeth, and the walls of the cutting arm and the fixed sleeve are provided with holes that penetrate both of them. A pulse speed sensor is fixedly installed in the hole, and the detection end of the speed sensor faces the outer peripheral wall of the eccentric disk so as to obtain the real-time speed of the eccentric disk by detecting the passing frequency of the micro-teeth.

[0014] Optionally, the combined bearing includes an inner bushing, a roller bearing, and an outer bushing. The inner bushing is fixedly sleeved on the outside of the drive shaft. The roller bearing is sandwiched between the inner bushing and the outer bushing. An inner ring pressure plate is sleeved on the outside of the inner bushing, and the inner ring pressure plate abuts against the front end of the inner ring of the roller bearing. An inner ring nut is threaded onto the front end of the inner bushing, and the inner ring nut abuts against the front end of the inner ring pressure plate. An outer ring pressure plate is provided at the front end of the inner sidewall of the outer bushing, and the outer ring pressure plate abuts against the front end of the outer ring of the roller bearing. An outer ring nut is threaded onto the front end of the inner sidewall of the outer bushing, and the outer ring nut abuts against the front end of the outer ring pressure plate. At the end, a rotary oil seal is installed in the annular gap between the inner ring pressure plate and the outer ring pressure plate. A circumferential oil inlet groove is opened on the outer side wall of the outer bushing. An oil inlet port penetrating the annular wall of the outer bushing is opened at the bottom of the oil inlet groove. The oil inlet port is connected to the outer ring raceway of the roller bearing. A circumferential oil return groove is also opened on the outer side wall of the outer bushing. An oil return port is opened at the bottom of the oil return groove. The end of the oil return port faces the inner rear side of the roller bearing. An oil return channel is opened on the side wall of the outer ring pressure plate facing the roller bearing. One end of the oil return channel is connected to the oil return port. The other end of the oil return channel faces the inner front side of the roller bearing.

[0015] All of the above-mentioned optional technical solutions can be combined arbitrarily, and the present invention will not provide a detailed description of the structure after each combination.

[0016] By means of the above solution, the beneficial effects of the present invention are as follows: 1. This invention effectively solves the technical problem of directly transmitting impact loads to the telescopic boom through the hinge joint under hard rock undercutting conditions by setting a primary elastic support plate and a secondary elastic support plate in the cross-hinged module to form a double-layer elastic support structure. The secondary elastic support plate is located near the cutting boom, providing the cutting boom with the elastic displacement space required for oscillation motion, allowing the excitation energy generated by the eccentric disc to be converted into the rock-breaking amplitude of the cutting disc to the maximum extent. The primary elastic support plate is located near the square base, forming a vibration isolation barrier between the cutting boom and the telescopic boom, effectively blocking the reverse transmission of high-frequency oscillation energy to the telescopic boom and the cutting support arm. The two-stage elastic support plates work together to reduce the vibration of the main unit caused by oscillating undercutting, significantly extending the service life of the equipment, and improving the rock-breaking positioning accuracy and overall reliability.

[0017] 2. This invention, by opening multiple mounting holes on the end face of the eccentric disc for installing counterweights, allows operators to flexibly select and install different numbers or masses of counterweights according to the hardness of different rock formations. This enables online adjustment of the excitation force amplitude, ensuring that the cutting arm always operates under optimal excitation parameters. This effectively solves the problem of fixed excitation force amplitude in existing technologies, which cannot adapt to different rock formation conditions. It also avoids fatigue damage to the cutting arm and related components caused by mismatched vibrations due to mismatch between excitation force and working conditions, further ensuring the stability and reliability of the entire machine operation.

[0018] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0019] Figure 1 A schematic diagram of the overall appearance structure of the oscillating cutting arm suitable for disc bottom cutting of rock provided by the present invention. Figure 1 ; Figure 2 A schematic diagram of the overall appearance structure of the oscillating cutting arm suitable for disc bottom cutting of rock provided by the present invention. Figure 2 ; Figure 3 An exploded structural diagram of the oscillating cutting arm suitable for disc bottom cutting of rock provided by the present invention; Figure 4 Right cross-sectional view of the vibratory cutting arm for disc bottom cutting of rock provided by the present invention; Figure 5 This is an exploded structural diagram of the scissor support arm, telescopic arm, and adjustment mechanism in this invention; Figure 6 This is an exploded structural diagram of the truncated support arm in this invention; Figure 7This is an exploded structural diagram of the cross-hinged module and the cutting arm in this invention; Figure 8 This is a front sectional view of the cross hinge in this invention; Figure 9 This is an exploded structural diagram of the cross hinge in this invention; Figure 10 This is an exploded structural diagram of the rear ear seat, the cylinder seat, and the elastic unit in this invention; Figure 11 This is an exploded structural diagram of the eccentric drive mechanism in this invention. Figure 1 ; Figure 12 This is an exploded structural diagram of the eccentric drive mechanism in this invention. Figure 2 ; Figure 13 This is an exploded structural diagram of the drive shaft, combined bearing and eccentric disk in this invention; Figure 14 This is a right-side cross-sectional view of the combined bearing in this invention.

[0020] The diagram labels are as follows: 1. Cutting support arm; 11. Support arm; 111. First locking flange; 12. Bushing; 121. Placement groove; 13. Wedge-shaped adjustment assembly; 131. Fixing ring; 1311. Inner wedge surface; 132. Inner wedge ring; 14. Second locking flange; 15. Base; 16. Square guide post; 2. Telescopic arm; 21. End cap; 211. Square hole; 22. First fixing flange; 3. Cross hinge module; 31. Fixing seat; 32. First fixing lug; 33. Cross hinge; 331. Square seat; 3311. Placement hole; 332. 333. Central column; 333. Primary elastic support plate; 3331. Annular groove; 3332. Through hole; 334. Secondary elastic support plate; 3341. Guide column; 335. Fixing bolt; 336. Rotary ring; 337. Locking cover; 338. Primary spring; 339. Secondary spring; 4. Cutting arm; 41. Second fixing lug; 42. Pulse speed sensor; 5. Adjustment mechanism; 51. Adjustment cylinder; 52. Support seat; 53. Front lug seat; 54. Rear lug seat; 541. Movable plate; 542. Guide hole; 55. Cylinder seat; 551. Cylinder seat pressure plate. 552. Front side plate; 553. Rear side plate; 56. Elastic unit; 561. Adjusting plate; 562. Adjusting bolt; 563. Guide rod; 564. Small spring; 6. Cutting disc; 61. Connecting flange; 7. Eccentric drive mechanism; 71. Fixed sleeve; 711. External oil inlet channel of front roller bearing; 712. External oil return channel of front roller bearing; 72. Front flange; 73. Rear end seat; 731. Rear flange; 732. External oil inlet channel of rear roller bearing; 733. External oil return channel of rear roller bearing; 74. Drive shaft; 741. Flower 75. Keyway; 75. Combined bearing; 751. Inner bushing; 752. Roller bearing; 753. Outer bushing; 7531. Oil inlet groove; 7532. Oil inlet port; 7533. Oil return groove; 7534. Oil return port; 754. Inner ring pressure plate; 755. Inner ring nut; 756. Outer ring pressure plate; 7561. Oil return passage; 757. Outer ring nut; 758. Rotary oil seal; 76. Eccentric disc; 761. Semicircular cavity; 762. Counterweight; 763. Mounting hole; 764. Miniature gear; 77. Drive motor; 771. Splined shaft; 78. Sealing ring. Detailed Implementation

[0021] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0022] Please see Figure 1-4This invention provides an oscillating cutting arm suitable for disc bottom cutting of rock, including a cutting support arm 1, a telescopic arm 2, a cutting arm 4, and a cutting disc 6. The telescopic arm 2 is slidably mounted on the front end of the cutting support arm 1. The front end of the telescopic arm 2 is connected to the rear end of the cutting arm 4 through a cross hinge module 3. An adjustment mechanism 5 for driving the cutting arm 4 to extend and retract and adjust its angle is provided on the outside of the cutting support arm 1. The cutting disc 6 is detachably connected to the front end of the cutting arm 4. An eccentric drive mechanism 7 is also connected inside the cutting arm 4. The eccentric drive mechanism 7 transmits the eccentric excitation force to the cutting disc 6.

[0023] In this invention, when the oscillating cutting arm 4 is working, the internal eccentric excitation force drives the cutting disc 6 to contact the rock. At the same time, the adjustment mechanism 5 pushes the telescopic arm 2 to slide along the cutting support arm 1 to control the feed depth. The adjustment mechanism 5, in conjunction with the cross-hinged module 3, adjusts the pitch and sway angles of the cutting arm 4 to change the cutting angle. During the cutting process, the eccentric drive mechanism 7 is activated, and its eccentric disc 76 rotates at high speed to generate periodic centrifugal excitation force. This excitation force is transmitted along the cutting arm 4 to the cutting disc 6 at the front end, so that the cutting disc 6 superimposes high-frequency, low-amplitude oscillating motion on the basis of oscillating cutting to enhance the crushing efficiency of hard rock.

[0024] The cutting disc 6 in this invention can be referenced from the invention patent with announcement number CN121138848B (a disc cutter suitable for oscillating bottom cutting). The front end of the cutting arm 4 is fixed to the disc cutter shaft in the patent by bolts.

[0025] Example 1: As Figure 4 and Figures 7-9 As shown, the cross-hinged module 3 includes a fixed base 31 and a cross-hinged joint 33. The fixed base 31 is fixedly connected to the front end of the telescopic arm 2. The four hinge ends of the cross-hinged joint 33 are rotatably connected to the two first fixed ears 32 at the front end of the fixed base 31 and the two second fixed ears 41 at the rear end of the cutting arm 4, respectively. The cross-hinged joint 33 includes a square base 331 and four central pillars 332. The four central pillars 332 are detachably connected to the four sides of the square base 331 by long bolts. Each central pillar 332 is provided with a primary elastic support plate 333, a secondary elastic support plate 334 and a rotating ring 336 sequentially from the inside to the outside along its axial direction. The four ear plates are respectively fitted on the outside of the corresponding rotating ring 336. The primary elastic support plate 333 elastically abuts between the square base 331 and the secondary elastic support plate 334 to isolate the vibration transmission between the cutting arm 4 and the telescopic arm 2. The secondary elastic support plate 334 elastically abuts against the inner side of the corresponding ear plate to provide the elastic displacement space required for the oscillating motion of the cutting arm 4.

[0026] In the cross-hinged module 3 of this embodiment, a double-layer elastic support structure is formed by a primary elastic support plate 333 and a secondary elastic support plate 334. The secondary elastic support plate 334 is located near the cutting arm 4 and directly abuts against the ear plate of the cutting arm 4. When the eccentric plate 76 drives the cutting arm 4 to oscillate, the deformation of the secondary elastic support plate 334 directly determines the oscillation displacement amplitude of the cutting arm 4, so that the excitation energy generated by the eccentric plate 76 can be effectively transferred to the cutting disc 6. The primary elastic support plate 333 is located near the square base 331 and directly abuts against the fixed base 31 on the telescopic arm 2 side. During the oscillation of the cutting arm 4, it isolates and absorbs the vibration energy transmitted to the telescopic arm 2. The two work together to ensure that the rock-breaking oscillation energy is efficiently transferred to the cutting disc 6 while effectively blocking the reverse transmission of high-frequency oscillation to the telescopic arm 2 and the cutting support arm 1.

[0027] Furthermore, such as Figure 8 and Figure 9 As shown, the square base 331 has several placement holes 3311 on its four sides and around the central post 332. Guide posts 3341, corresponding to the placement holes 3311, are fixedly connected to the surface of the secondary elastic support plate 334 facing the primary elastic support plate 333. An annular groove 3331 is formed on the surface of the primary elastic support plate 333 facing the secondary elastic support plate 334. Through holes 3332, corresponding to the guide posts 3341, are formed along the circumference of the annular groove 3331. The guide posts 3341 movably pass through the corresponding through holes 3332 and extend into the corresponding placement holes 3311. Some of the guide posts 3341 are axially... A through-hole structure is provided with a fixing bolt 335. The rod of the fixing bolt 335 passes through the guide post 3341 and its lower end is connected to the threaded hole at the bottom of the corresponding placement hole 3311. A primary spring 338 is sleeved inside the placement hole 3311 and outside the guide post 3341. The two ends of the primary spring 338 elastically abut against the bottom surface of the placement hole 3311 and the surface of the primary elastic support plate 333 facing the placement hole 3311, respectively. Multiple secondary springs 339 are distributed circumferentially between the primary elastic support plate 333 and the secondary elastic support plate 334. The secondary springs 339 are respectively sleeved on the outside of the corresponding guide post 3341.

[0028] Specifically, the secondary elastic support plate 334 is located near the cutting arm 4 and directly abuts against the ear plate of the cutting arm 4. When the eccentric plate 76 drives the cutting arm 4 to oscillate, the secondary elastic support plate 334 and its corresponding secondary spring 339 undergo elastic deformation, providing oscillation displacement space for the cutting arm 4. The primary elastic support plate 333 is located near the square seat 331 and directly abuts against the fixed seat 31. During the oscillation of the cutting arm 4, the primary elastic support plate 333 and its corresponding primary spring 338 isolate and absorb the vibration energy transmitted to the telescopic arm 2. The guide post 3341 slides and guides within the through hole 3332 of the primary elastic support plate 333 and the placement hole 3311 of the square seat 331, ensuring that the axial movement of the primary elastic support plate 333 does not deviate. When the secondary elastic support plate 334 rebounds, the fixing bolt 335 inside the hollow guide post 3341 pulls the upper end face of the guide post 3341 through its head, preventing the secondary elastic support plate 334 from disengaging from the square seat 331. The two-stage elastic support plates work together to ensure that the rock-breaking oscillation energy is efficiently transmitted to the cutting disc 6, while effectively blocking the reverse transmission of high-frequency oscillation to the telescopic arm 2 and the cutting support arm 1.

[0029] In this embodiment, the primary spring 338 is a high-stiffness spring, whose compression deformation is less than the maximum compressible stroke of the secondary spring 339. The secondary spring 339 is a low-stiffness, long-stroke spring. The rotation of the eccentric disk 76 generates a periodic excitation force, driving the cutting arm 4 to oscillate. The low-stiffness characteristic of the secondary spring 339 provides sufficient flexible displacement for the cutting arm 4, maximizing the conversion of excitation energy into the rock-breaking amplitude of the cutting disc 6. The high-stiffness characteristic of the primary spring 338 forms a vibration isolation barrier between the cutting arm 4 and the telescopic arm 2, blocking the reverse transmission of high-frequency oscillation energy to the telescopic arm 2 and the cutting support arm 1. The load on the cross-hinged module 3 is first transmitted to the secondary spring 339. Due to its low stiffness and long stroke design, within the normal oscillation range of the cutting arm 4, the secondary spring 339 independently completes the reciprocating compression and rebound, absorbing high-frequency vibration energy with relatively small elastic resistance. When the impact load causes the compression stroke of the secondary spring 339 to approach its maximum design stroke, the lower end of the guide post 3341 pushes the primary elastic support plate 333 to begin compressing the primary spring 338. At this time, the primary spring 338 generates a strong elastic restoring force to resist the overload impact. With the synergistic cooperation of low stiffness vibration transmission and high stiffness vibration isolation, the two-stage springs ensure efficient utilization of rock-breaking oscillation energy and protect key components of the machine body from fatigue damage caused by oscillation impact.

[0030] Furthermore, ignoring the frictional resistance of the internal bearings, the cutting arm 4 performs a stable circular oscillation motion under no-load conditions, driven by the excitation of the eccentric disk 76. Combined with the feed speed of the cutting disc 6, the cutting wrap angle when the disc cuts into the rock is always controlled within a range smaller than the disc diameter, avoiding an excessively long cutting arc length that would cause a sharp increase in the peak cutting resistance, thereby effectively reducing the cutting force and improving the cutting efficiency.

[0031] Furthermore, such as Figures 7-9 As shown, the first fixing ear 32 and the second fixing ear 41 are also detachably connected to a locking cover 337 by bolts on the side away from the first-stage elastic support plate 333. The locking cover 337 is fastened to the upper end of the rotating ring 336 and the central column 332.

[0032] Specifically, when assembling the cross-hinged module 3, firstly, the square base 331 is placed between the two first fixing ears 32 of the fixed base 31 and the two second fixing ears 41 of the cutting arm 4, and the four sides of the square base 331 are aligned with the corresponding ear plates; then, each central post 332 is passed through the corresponding first fixing ear 32 or second fixing ear 41 and fixedly connected to the corresponding side of the square base 331 by bolts; then, a primary spring 338, a primary elastic support plate 333, a secondary spring 339, and a secondary elastic support plate 334 are installed sequentially from the inside to the outside on each central post 332. Once in place, the fixing bolt 335 is passed through the hollow guide post 3341 and screwed into the threaded hole at the bottom of the corresponding placement hole 3311 to axially limit the primary elastic support plate 333 and the secondary elastic support plate 334; then, the rotating ring 336 is sleeved on the outside of the central post 332 and clamped between the central post 332 and the corresponding first fixing ear 32 or second fixing ear 41; finally, the locking cover 337 is fastened to the upper end of the rotating ring 336 and the central post 332, and fixedly connected to the corresponding first fixing ear 32 or second fixing ear 41 by bolts to axially encapsulate and limit the various components.

[0033] Example 2: Figure 4 and Figure 13 As shown, the eccentric drive mechanism 7 includes an eccentric disk 76, which is rotatably installed inside the cutting arm 4. Half of the eccentric disk 76 along its circumference is a semi-circular cavity 761, and the other half is a solid structure. Multiple axial mounting holes 763 for mounting counterweights 762 are opened along its circumference on the solid end face of the eccentric disk 76. The amplitude of the excitation force generated when the eccentric disk 76 rotates is less than the maximum elastic deformation recovery force of the first-stage elastic support disk 333 and the second-stage elastic support disk 334.

[0034] In this embodiment, when the eccentric disk 76 rotates, the counterweight 762 installed in the mounting hole 763 rotates synchronously with the eccentric disk 76. Since the center of mass of the counterweight 762 is offset from the rotation axis of the eccentric disk 76, a periodic centrifugal force is generated during the rotation. This centrifugal force is the excitation force that drives the cutting arm 4 to oscillate. By selectively installing different numbers or masses of counterweights 762 in each mounting hole 763, the total eccentric mass of the eccentric disk 76 can be changed, thereby adjusting the amplitude of the excitation force: when breaking hard rock, the number of counterweights 762 can be increased or heavier counterweights 762 can be selected to increase the amplitude of the excitation force and improve the rock-breaking ability; when breaking soft rock, the number of counterweights 762 can be reduced or lighter counterweights 762 can be selected to reduce the amplitude of the excitation force and avoid excessive oscillation leading to energy waste and equipment wear.

[0035] Meanwhile, the eccentric disc 76 adopts a full-circle design, which reduces wind resistance during high-speed rotation, thus reducing the load and energy loss of the drive motor 77. The excitation force amplitude is limited to less than the maximum elastic deformation recovery force of the first-stage elastic support disc 333 and the second-stage elastic support disc 334, ensuring that the two-stage elastic support discs remain within the elastic deformation range when the cross-hinged module 3 is subjected to oscillating loads: on the one hand, the excitation force can be effectively transmitted to the cutting arm 4, driving the cutting disc 6 to generate high-frequency oscillations to assist in rock breaking; on the other hand, the elastic support discs will not be crushed due to overload of the excitation force, thereby avoiding impact damage to the cross-hinged module 3 and the telescopic arm 2 caused by rigid collisions, ensuring the stability and reliability of the entire machine operation.

[0036] With the aforementioned adjustable counterweight structure, operators can adjust the number or mass of counterweight blocks 762 according to the actual rock surface hardness, so that the excitation force and load are dynamically matched. This avoids the problems of excessive and useless impacts in soft rock caused by fixed counterweight structures and repeated impacts due to insufficient excitation force in hard rock. It optimizes the vibration environment from the source of excitation force and further extends the service life of the equipment under varying working conditions.

[0037] Furthermore, such as Figure 3 and Figure 4 As shown, a connecting flange 61 is fixedly connected to the rear end face of the cutting disc 6. The connecting flange 61 adopts an external connection structure, which facilitates the operator to directly remove and install bolts from the outside, so as to realize the overall quick replacement or maintenance of the cutting disc 6.

[0038] Furthermore, such as Figure 4 and Figures 11-13As shown, the eccentric drive mechanism 7 also includes a fixed sleeve 71, a rear end seat 73, and a drive shaft 74, all disposed inside the cutting arm 4. A front flange 72 is fixedly fitted onto the front end of the outer wall of the fixed sleeve 71, sandwiched between the connecting flange 61 and the cutting arm 4, and the three are fixed together by bolts. A rear flange 731 is fixedly connected to the rear end of the rear end seat 73, and the rear flange 731 is fixed to the rear end of the fixed sleeve 71 by bolts. An eccentric disc 76 is fixedly fitted onto the middle position of the drive shaft 74, driving... Both ends of the shaft 74 are fitted with combined bearings 75. The two sets of combined bearings 75 are respectively embedded in the fixed sleeve 71 and the rear end seat 73. The rear end of the rear end seat 73 is fixedly connected to the drive motor 77. The output shaft of the drive motor 77 is connected to the rear end of the drive shaft 74 through spline drive. The rear end of the drive shaft 74 is provided with a spline groove 741. The spline shaft 771 of the drive motor 77 is inserted into the spline groove 741. A sealing ring 78 is also sandwiched between the drive shaft 74 and the end seat of the drive motor 77.

[0039] Specifically, the drive motor 77 drives the drive shaft 74 to rotate at high speed via spline transmission. The drive shaft 74 is rotatably supported in the fixed sleeve 71 and the rear end seat 73 by two sets of combined bearings 75 at the front and rear ends, respectively. The eccentric disk 76, which is fixedly sleeved in the middle of the drive shaft 74, rotates synchronously with the drive shaft 74. Its center of mass deviates from the axis of rotation, generating a periodic centrifugal excitation force. This excitation force is transmitted to the fixed sleeve 71 and the rear end seat 73 via the combined bearings 75 at both ends of the drive shaft 74. Since the front end of the fixed sleeve 71 is fixedly connected to the connecting flange 61 at the rear end of the cutting disc 6 and the front end face of the cutting arm 4 through the front flange 72, the excitation force borne by the fixed sleeve 71 is directly transmitted to the front end of the cutting arm 4 and further to the cutting disc 6, so that the cutting disc 6 superimposes high-frequency oscillation on the basis of the oscillating cutting motion. In addition, the sealing ring 78 sandwiched between the drive shaft 74 and the end seat of the drive motor 77 is used to prevent lubricating oil or impurities from entering the drive motor 77 along the spline connection, ensuring the sealing performance and operational reliability of the transmission system.

[0040] Furthermore, such as Figure 4 and Figure 13 As shown, a number of axially extending micro-teeth 764 are evenly distributed along the circumference of the outer peripheral wall of the eccentric disk 76. Holes penetrating the cutting arm 4 and the fixed sleeve 71 are opened on their walls. A pulse speed sensor 42 is fixedly installed in the hole. The detection end of the pulse speed sensor 42 faces the outer peripheral wall of the eccentric disk 76, so as to obtain the real-time rotational speed of the eccentric disk 76 by detecting the passing frequency of the micro-teeth 764.

[0041] Specifically, when the eccentric disk 76 rotates, the miniature teeth 764 on its outer peripheral wall pass sequentially in front of the detection end of the pulse speed sensor 42. The pulse speed sensor 42 senses the physical quantity change caused by the alternating changes in the tooth tip and tooth groove, and converts this change into an electrical pulse signal output. Each miniature tooth 764 generates a pulse when passing the pulse speed sensor 42. The pulse frequency is proportional to the real-time rotational speed of the eccentric disk 76. The control system can obtain the current rotational speed of the eccentric disk 76 by collecting the pulse signal and calculating the number of pulses per unit time. By comparing the actual rotational speed with the target rotational speed, the output of the drive motor 77 is adjusted in real time to achieve closed-loop control of the excitation frequency.

[0042] Furthermore, such as Figures 11-14As shown, the combined bearing 75 includes an inner bushing 751, a roller bearing 752, and an outer bushing 753. The inner bushing 751 is fixedly sleeved on the outside of the drive shaft 74. The roller bearing 752 is sandwiched between the inner bushing 751 and the outer bushing 753. The outer bushing 753 is fixedly installed inside the fixed sleeve 71 or the rear end seat 73. An inner ring pressure plate 754 is sleeved on the outside of the inner bushing 751, and the inner ring pressure plate 754 abuts against the front end of the inner ring of the roller bearing 752. An inner ring nut 755 is threaded onto the front end of the inner bushing 751, and the inner ring nut 755 abuts against the front end of the inner ring pressure plate 754. An outer ring pressure plate 756 is provided at the front end of the inner side wall of the outer sleeve 753. The outer ring pressure plate 756 abuts against the front end of the outer ring of the roller bearing 752. An outer ring nut 757 is threadedly connected to the front end of the inner side of the outer sleeve 753. The outer ring nut 757 abuts against the front end of the outer ring pressure plate 756. A rotary oil seal 758 is installed in the annular gap between the inner ring pressure plate 754 and the outer ring pressure plate 756. A circumferential oil inlet groove 7531 is opened on the outer side wall of the outer sleeve 753. An oil inlet port 7532 penetrating the annular wall of the outer sleeve 753 is opened at the bottom of the oil inlet groove 7531. The oil inlet port 7532 is connected to the roller bearing 752. The outer ring raceway is connected, and the outer side wall of the outer bushing 753 is also provided with a circumferential oil return groove 7533. The bottom of the oil return groove 7533 is provided with an oil return port 7534. The end of the oil return port 7534 faces the inner rear side of the roller bearing 752. The outer ring pressure plate 756 is provided with an oil return channel 7561 on the side wall facing the roller bearing 752. One end of the oil return channel 7561 is connected to the oil return port 7534, and the other end of the oil return channel 7561 faces the inner front side of the roller bearing 752. The outer peripheral wall of the front flange 72 is provided with an external oil inlet channel 711 for the front roller bearing and an external oil inlet channel 711 for the front roller bearing. The oil return channel 712 has an oil inlet groove 7531 corresponding to the combined bearing 75 located inside the fixed sleeve 71 that is connected to the external oil inlet channel 711 of the front roller bearing and an oil return groove 7533 that is connected to the external oil return channel 712 of the front roller bearing. The outer peripheral wall of the rear flange 731 is provided with an external oil inlet channel 732 and an external oil return channel 733 for the rear roller bearing. The oil inlet groove 7531 corresponding to the combined bearing 75 located inside the rear end seat 73 is connected to the external oil inlet channel 732 of the rear roller bearing and an oil return groove 7533 that is connected to the external oil return channel 733 of the rear roller bearing.

[0043] Specifically, the lubricating oil from the external lubrication system enters the oil inlet groove 7531 of the corresponding combined bearing 75 through the external oil inlet channel on the front flange 72 or the rear flange 731. After being evenly distributed circumferentially along the oil inlet groove 7531, the lubricating oil enters the interior of the outer bushing 753 through the oil inlet port 7532 and is delivered to the outer ring raceway of the roller bearing 752 to lubricate the rolling elements and raceway. As the roller bearing 752 rotates, the lubricating oil is evenly distributed inside the roller bearing 752 and lubricates each rolling contact surface. After lubrication, the lubricating oil collects in the bottom area of ​​the roller bearing 752. Part of it flows into the oil return groove 7533 through the oil return port 7534, and the other part flows into the oil return port 7534 through the oil return channel 7561 on the outer ring pressure plate 756 and then merges into the oil return groove 7533. Finally, it is discharged through the external oil return channel on the front flange 72 or the rear flange 731 and flows back to the lubrication system.

[0044] In this embodiment, the oil inlet 7532 and the oil return port 7534 are arranged 180 degrees opposite each other, ensuring that the lubricating oil flows through the complete raceway area inside the roller bearing 752, achieving effective lubrication and cooling. During this process, the rotary oil seal 758 between the inner ring pressure plate 754 and the outer ring pressure plate 756 prevents the lubricating oil from leaking outward along the axial direction, ensuring that the lubricating oil flows through the inside of the roller bearing 752 along a preset path. The roller bearing 752 adopts a shock-resistant bearing, combined with a high-pressure sealing structure, to adapt to the high-frequency vibration environment generated by the continuous eccentric rotation of the eccentric disc 76, effectively improving the vibration resistance and service life of the roller bearing 752. In addition, the oil inlet 7532 and the oil return port 7534 are opened on the outer peripheral wall of the outer bushing 753 and are connected to the external oil inlet groove 7531 and the oil return groove 7533, respectively. The installation angle of the combined bearing 75 does not affect its lubrication effect, reducing the installation difficulty for workers.

[0045] Example 3: Figures 4-6As shown, the cutting support arm 1 includes a support arm 11 and a bushing 12. The rear end of the telescopic arm 2 is slidably disposed within the support arm 11. The inner diameter of the bushing 12 is larger than the inner diameter of the support arm 11. A first locking flange 111 is fixedly connected to the front end of the support arm 11. The first locking flange 111 is fixedly connected to the rear end of the bushing 12 by bolts. The inner ring walls of both the front and rear ends of the bushing 12 are provided with placement grooves 121. A wedge-shaped adjustment assembly 13 is installed in the placement grooves 121. The wedge-shaped adjustment assembly 13 includes a fixing ring 131 and an inner wedge ring 132. The fixing ring 131 is embedded in the placement groove 121, and the inner wedge ring 132 is disposed inside the fixing ring 131. The inner ring wall of the fixing ring 131 is provided with an inner wedge surface that mates with the inner wedge ring 132. 1311, the inner ring wall of the inner wedge ring 132 abuts against the outer wall of the telescopic arm 2. The inner wedge ring 132 is composed of multiple arc-shaped wedge segments. The front end of the bushing 12 is fixedly connected to the second locking flange 14 by bolts. The inner wedge surface 1311 of the fixing ring 131 at the front end of the bushing 12 is a conical surface that gradually tapers inward from front to back along the axial direction. The inner wedge surface 1311 of the fixing ring 131 at the rear end of the bushing 12 is a conical surface that gradually tapers inward from back to front along the axial direction. The outer ring wall of the inner wedge ring 132 is provided with an outer wedge surface that matches the slope of the corresponding inner wedge surface 1311. When each arc-shaped wedge segment is subjected to axial preload, it can slide radially inward along the corresponding inner wedge surface 1311 to tighten the radial clamping force on the outer wall of the telescopic arm 2. A base 15 for connecting equipment is fixedly connected to the outer side of the support arm 11.

[0046] Specifically, the rear end of the telescopic arm 2 slides within the support arm 11 to achieve telescopic feeding, while its front end passes through the bushing 12 and is radially constrained by the wedge-shaped adjustment assembly 13. When the telescopic arm 2 experiences increased clearance due to long-term heavy-load oscillation, the wedge-shaped adjustment assembly 13 at the front end converts the axial force into a radial component force via the inner wedge surface 1311 of the fixing ring 131 by axially pressing the second locking flange 14 or adding a gasket, pushing each arc-shaped wedge segment of the inner wedge ring 132 to slide synchronously inward along the conical surface. Similarly, the wedge-shaped adjustment assembly 13 at the rear end converts the axial force into a radial component force by axially pressing the first locking flange 111 or adding a gasket, pushing each arc-shaped wedge segment to slide synchronously inward along the conical surface. The inner ring walls of each arc-shaped wedge segment uniformly converge and tightly abut against the outer wall of the telescopic arm 2, thereby eliminating the clearance and restoring the guiding accuracy. The multi-segmented structure allows the inner wedge ring 132 to contract uniformly in the circumferential direction and provides adaptive radial compensation. Combined with the rigid connection of the first locking flange 111 and the second locking flange 14, the telescopic arm 2 maintains a stable linear motion trajectory when subjected to high-frequency excitation and off-center load.

[0047] In this embodiment, due to the continuous vibration under rock-breaking conditions, the clearance between the telescopic arm 2 and the bushing 12 gradually increases, causing radial swaying of the telescopic arm 2. This swaying not only exacerbates the wear of the bushing 12 itself but also transmits additional impact loads to the cross-hinged module 3 and the eccentric drive mechanism 7, further worsening the vibration environment of the entire machine. This embodiment addresses this by providing wedge-shaped adjustment components 13 at both ends of the bushing 12, which can compensate for the clearance according to wear conditions, maintaining the radial positioning accuracy of the telescopic arm 2. This avoids additional impact loads caused by increased clearance. Combined with the elastic damping structure of the cross-hinged module 3, this further extends the service life of the entire machine under long-term vibration conditions.

[0048] Furthermore, such as Figure 4 and Figure 5 As shown, a square guide post 16 extending along its axial direction is fixedly connected to the rear end of the support arm 11. An end cap 21 is fixedly connected to the rear end of the telescopic arm 2. A square hole 211 for sliding the square guide post 16 is opened through the end cap 21. A first fixed flange 22 is fixedly connected to the front end of the telescopic arm 2. The first fixed flange 22 is fixedly connected to the fixed seat 31 by bolts.

[0049] Specifically, when the telescopic arm 2 extends or retracts, the square hole 211 on the end cap 21 slides along the square guide post 16, forming an axial guide pair. When the cutting torque generated by the cutting disc 6 breaking the rock is transmitted to the telescopic arm 2, the four side walls of the square guide post 16 and the four walls of the square hole 211 form a surface contact limit, directly transmitting the torque to the support arm 11 and preventing the telescopic arm 2 from rotating circumferentially. The continuous axial guidance of the square guide post 16 ensures that the telescopic arm 2 maintains linear motion during extension or retraction, ensuring the stability of the cutting posture of the cutting disc 6.

[0050] Example 4: Figure 4 and Figure 5As shown, the adjustment mechanism 5 includes multiple adjustment cylinders 51, which are arranged circumferentially on the outside of the cutting support arm 1. The number of adjustment cylinders 51 is preferably 3. Multiple support seats 52, corresponding one-to-one with the adjusting cylinder 51, are fixedly connected to the rear end of the outer side wall of the cutting arm 4. A front ear seat 53 is fixedly connected to the rear end face of the support seat 52. The piston rod end of the adjusting cylinder 51 is hinged to the corresponding front ear seat 53. A rear ear seat 54 is hinged to the rear end of the cylinder body of the adjusting cylinder 51. Multiple cylinder seats 55, corresponding one-to-one with the adjusting cylinder 51, are fixedly connected to the rear end of the outer side wall of the cutting support arm 1. The rear ear seat 54 is slidably assembled in the corresponding cylinder seat 55 along the axial direction of the cutting support arm 1. An elastic unit 56 is connected in the cylinder seat 55. The elastic unit 56 elastically abuts between the front and rear end faces of the rear ear seat 54 and the front and rear side walls of the cylinder seat 55. The axial floating displacement direction of the rear ear seat 54 is parallel to the axial direction of the adjusting cylinder 51 to compensate for the change in axial distance between the front end of the piston rod and the rear end of the cylinder body when the cutting arm 4 swings.

[0051] Specifically, when the swaying of the cutting arm 4 causes a change in the axial distance between the two ends of the adjusting cylinder 51, the rear ear seat 54 moves forward or backward along the axial direction within the cylinder seat 55 to perform floating compensation. At this time, the elastic units 56 that abut against the front and rear end faces of the rear ear seat 54 are compressed accordingly. At the same time, when the load generated by the high-frequency oscillation of the cutting arm 4 is transmitted to the rear ear seat 54 along the adjusting cylinder 51, the elastic units 56 on both the front and rear sides are alternately compressed and rebounded, forming an elastic buffer layer in both reciprocating directions. This effectively absorbs and isolates the vibration energy in both directions, preventing the high-frequency excitation force from being directly transmitted along a rigid path, thereby effectively reducing the vibration impact on the cutting support arm 1 and the machine body.

[0052] Furthermore, such as Figure 5 and Figure 10As shown, a movable plate 541 is fixedly connected to the lower surface of the rear ear seat 54. The movable plate 541 slides on the upper surface of the cylinder seat 55. Inverted L-shaped cylinder seat pressure plates 551 are bolted to both sides of the upper surface of the cylinder seat 55. The two sets of symmetrical cylinder seat pressure plates 551 together guide the sliding of the movable plate 541. A front side plate 552 and a rear side plate 553 are fixedly connected to the front and rear sides of the upper surface of the cylinder seat 55, respectively. The elastic unit 56 includes an adjusting plate 561 and multiple adjusting bolts 562. The adjusting plate 561 slides on the upper surface of the cylinder seat 55 and is located between the movable plate 541 and the rear side plate 553. Multiple adjusting bolts 562 are threaded through the rear side plate 553 and abut against the rear side of the adjusting plate 561. Multiple axial bolts are fixedly connected to the rear side of the front side plate 552 and the front side of the adjusting plate 561. The extended guide rod 563 and the movable plate 541 both have guide holes 542 on their front and rear sides for sliding the guide rod 563. A small spring 564 is fitted onto the outer side of the guide rod 563. The small spring 564 located between the front side plate 552 and the movable plate 541 elastically abuts against the front sides of the front side plate 552 and the movable plate 541. The small spring 564 located between the adjusting plate 561 and the movable plate 541 elastically abuts against the rear sides of the adjusting plate 561 and the movable plate 541. By turning the adjusting bolt 562, the adjusting plate 561 is moved back and forth, thereby synchronously adjusting the pre-compression of the small springs 564 on both sides of the movable plate 541.

[0053] Specifically, when the swing of the cutting arm 4 causes a change in the axial distance between the two ends of the adjusting cylinder 51, the movable plate 541 slides back and forth on the upper surface of the cylinder seat 55. The small springs 564 sleeved on the outer sides of the front and rear sets of guide rods 563 are compressed by the movable plate 541. The compressed small springs 564 generate a reverse restoring force acting on the movable plate 541, which not only provides flexible buffering for the floating displacement, but also pushes the movable plate 541 back to the neutral position where the front and rear spring forces are balanced after adjustment. The operator can rotate the adjusting bolt 562 to push the adjusting plate 561 forward or backward along the upper surface of the cylinder seat 55 to change the distance between the adjusting plate 561 and the front side plate 552, thereby simultaneously changing the pre-compression of the small springs 564 on both sides of the movable plate 541, realizing on-site adjustment of the initial stiffness and pre-tightening force of the elastic support to adapt to the buffering requirements under different oscillation conditions.

[0054] In summary, by setting spring buffers between the three sets of adjusting cylinders 51 and the cutting support arm 1, the impact of vibration on the cutting support arm 1 is effectively mitigated, thereby improving the fatigue life of the cutting support arm 1 and the whole machine, and improving the overall reliability of the machine.

[0055] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. An oscillating cutting arm suitable for disc bottom cutting of rock, characterized in that: The device includes a cutting support arm (1), a telescopic arm (2), a cutting arm (4), and a cutting disc (6). The telescopic arm (2) is slidably mounted on the front end of the cutting support arm (1). The front end of the telescopic arm (2) is connected to the rear end of the cutting arm (4) through a cross hinge module (3). The cutting support arm (1) is provided with an adjustment mechanism (5) for driving the cutting arm (4) to extend and retract and adjust its angle. The cutting disc (6) is detachably connected to the front end of the cutting arm (4). An eccentric drive mechanism (7) is also connected inside the cutting arm (4). The cross-hinged module (3) includes a fixed base (31) and a cross hinge (33). The fixed base (31) is fixedly connected to the front end of the telescopic arm (2). The four hinge ends of the cross hinge (33) are rotatably connected to the two ear plates at the front end of the fixed base (31) and the two ear plates at the rear end of the cutting arm (4). The cross hinge (33) includes a square base (331) and four central posts (332). The four central posts (332) are detachably connected to the four sides of the square base (331). Each central post (332) has a cross hinge along its axial direction. From the inside out, a primary elastic support plate (333), a secondary elastic support plate (334), and a rotating ring (336) are sequentially fitted. The four ear plates are respectively fitted on the outside of the corresponding rotating ring (336). The primary elastic support plate (333) elastically abuts between the square base (331) and the secondary elastic support plate (334) to isolate the vibration transmission between the cutting arm (4) and the telescopic arm (2). The secondary elastic support plate (334) elastically abuts against the inner side of the corresponding ear plate to provide the cutting arm (4) with the elastic displacement space required for the oscillating motion. The eccentric drive mechanism (7) includes an eccentric disk (76), which is rotatably mounted inside the cutting arm (4). The end face of the eccentric disk (76) is provided with a plurality of mounting holes (763) for mounting counterweights (762) along its circumference. The amplitude of the excitation force generated when the eccentric disk (76) rotates is less than the maximum elastic deformation recovery force of the first-level elastic support disk (333) and the second-level elastic support disk (334).

2. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 1, characterized in that, The cutting support arm (1) includes a support arm (11) and a bushing (12). The rear end of the telescopic arm (2) is slidably disposed inside the support arm (11). The inner diameter of the bushing (12) is larger than the inner diameter of the support arm (11). A first locking flange (111) is fixedly connected to the front end of the support arm (11). The first locking flange (111) is fixedly connected to the rear end of the bushing (12) by bolts. Placement grooves (121) are provided on the inner ring walls of both the front and rear ends of the bushing (12). A wedge-shaped adjustment assembly (13) is installed in the placement groove (121). The section assembly (13) includes a fixed ring (131) and an inner wedge ring (132). The fixed ring (131) is embedded in the placement groove (121). The inner wedge ring (132) is located inside the fixed ring (131). The inner ring wall of the fixed ring (131) is provided with an inner wedge surface (1311) that cooperates with the inner wedge ring (132). The inner ring wall of the inner wedge ring (132) abuts against the outer wall of the telescopic arm (2). The inner wedge ring (132) is composed of multiple arc-shaped wedge segments. The front end of the bushing (12) is fixedly connected to a second locking flange (14) by bolts.

3. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 2, characterized in that, The support arm (11) has a square guide post (16) that extends along its axial direction fixedly connected to its internal rear end. The telescopic arm (2) has an end cap (21) fixedly connected to its rear end. The end cap (21) has a square hole (211) through which the square guide post (16) slides.

4. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 1, characterized in that, The square base (331) has several placement holes (3311) on its four sides and around the central column (332). The secondary elastic support plate (334) has guide posts (3341) fixedly connected to the surface of the primary elastic support plate (333) facing the placement holes (3311). The surface of the primary elastic support plate (333) has through holes (3332) that correspond to the guide posts (3341) in a circumferential manner. The guide posts (3341) movably pass through the corresponding through holes (3332) and extend into the corresponding placement holes (3311). Some of the guide posts (3341) are hollow structures that are axially continuous and have fixing bolts inside. (335) The rod of the fixing bolt (335) passes through the guide post (3341) and its lower end is connected to the threaded hole at the bottom of the corresponding placement hole (3311). A first-level spring (338) is sleeved inside the placement hole (3311) and outside the guide post (3341). The two ends of the first-level spring (338) elastically abut against the bottom surface of the placement hole (3311) and the surface of the first-level elastic support plate (333) facing the placement hole (3311). Multiple second-level springs (339) are distributed circumferentially between the first-level elastic support plate (333) and the second-level elastic support plate (334). The second-level springs (339) are respectively sleeved on the outside of the corresponding guide post (3341).

5. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 4, characterized in that, The primary spring (338) is a high-stiffness spring, and its compression deformation is less than the maximum compressible stroke of the secondary spring (339). The secondary spring (339) is a low-stiffness long-stroke spring.

6. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 1, characterized in that, The adjusting mechanism (5) includes multiple adjusting cylinders (51), which are arranged circumferentially on the outside of the cutting support arm (1). Multiple support seats (52) corresponding to each adjusting cylinder (51) are fixedly connected circumferentially to the rear end of the outer side wall of the cutting arm (4). A front ear seat (53) is fixedly connected to the rear end face of each support seat (52). The piston rod end of each adjusting cylinder (51) is hinged to the corresponding front ear seat (53). The rear end of the body is hinged with a rear ear seat (54). The rear end of the outer side wall of the cutting support arm (1) is fixedly connected with a plurality of cylinder seats (55) corresponding to the adjusting cylinder (51) along its circumference. The rear ear seat (54) is slidably assembled in the corresponding cylinder seat (55) along the axial direction of the cutting support arm (1). An elastic unit (56) is connected in the cylinder seat (55). The elastic unit (56) elastically abuts between the front and rear end faces of the rear ear seat (54) and the front and rear side walls of the cylinder seat (55).

7. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 6, characterized in that, A movable plate (541) is fixedly connected to the lower surface of the rear ear seat (54). The movable plate (541) slides on the upper surface of the cylinder seat (55). A front side plate (552) and a rear side plate (553) are fixedly connected to the front and rear sides of the upper surface of the cylinder seat (55). The elastic unit (56) includes an adjusting plate (561) and multiple adjusting bolts (562). The adjusting plate (561) slides on the upper surface of the cylinder seat (55) and is located between the movable plate (541) and the rear side plate. Between (553), multiple adjusting bolts (562) are threaded through the rear side plate (553) and abut against the rear side of the adjusting plate (561). Multiple axially extending guide rods (563) are fixedly connected to the rear side of the front side plate (552) and the front side of the adjusting plate (561). Guide holes (542) for sliding of the guide rods (563) are provided on the front and rear sides of the movable plate (541). Small springs (564) are sleeved on the outer side of the guide rods (563).

8. The vibratory cutting arm suitable for disc bottom cutting of rock according to claim 1, characterized in that, The eccentric drive mechanism (7) further includes a fixed sleeve (71), a rear end seat (73), and a drive shaft (74) all disposed inside the cutting arm (4). A front flange (72) is fixedly fitted on the front end of the outer side wall of the fixed sleeve (71). A connecting flange (61) is fixedly connected to the rear end face of the cutting disc (6). The front flange (72) is sandwiched between the connecting flange (61) and the cutting arm (4), and the three are fixed together by bolts. The rear end seat (73) is fixed to the rear end of the fixed sleeve (71) by bolts. The eccentric disc (76) is fixedly fitted in the middle position of the drive shaft (74). Both ends of the drive shaft (74) are fitted with combined bearings (75). The two sets of combined bearings (75) are respectively embedded in the fixed sleeve (71) and the rear end seat (73). A drive motor (77) is fixedly connected to the rear end of the rear end seat (73). The output shaft of the drive motor (77) is connected to the rear end of the drive shaft (74) by spline drive.

9. A vibratory cutting arm suitable for disc bottom cutting of rock according to claim 8, characterized in that, The outer peripheral wall of the eccentric disk (76) is evenly distributed with a number of axially extending micro-teeth (764) along its circumference. The walls of the cutting arm (4) and the fixed sleeve (71) are provided with holes that penetrate both of them. A pulse speed sensor (42) is fixedly installed in the hole. The detection end of the pulse speed sensor (42) faces the outer peripheral wall of the eccentric disk (76) so as to obtain the real-time rotational speed of the eccentric disk (76) by detecting the passing frequency of the micro-teeth (764).

10. A vibratory cutting arm suitable for disc bottom cutting of rock according to claim 8, characterized in that, The combined bearing (75) includes an inner bushing (751), a roller bearing (752), and an outer bushing (753). The inner bushing (751) is fixedly sleeved on the outside of the drive shaft (74). The roller bearing (752) is sandwiched between the inner bushing (751) and the outer bushing (753). An inner ring pressure plate (754) is sleeved on the outside of the inner bushing (751). The inner ring pressure plate (754) abuts against the front end of the inner ring of the roller bearing (752). 1) The front end of the bushing (753) is threaded with an inner ring nut (755), which abuts against the front end of the inner ring pressure plate (754). The front end of the inner side wall of the outer bushing (753) is provided with an outer ring pressure plate (756), which abuts against the front end of the outer ring of the roller bearing (752). The front end of the inner side of the outer bushing (753) is threaded with an outer ring nut (757), which abuts against the front end of the outer ring pressure plate (756). A rotary oil seal (758) is installed in the annular gap between the inner ring pressure plate (754) and the outer ring pressure plate (756). A circumferential oil inlet groove (7531) is provided on the outer side wall of the outer bushing (753). An oil inlet port (7532) penetrating the annular wall of the outer bushing (753) is provided at the bottom of the oil inlet groove (7531). The oil inlet port (7532) is connected to the outer ring raceway of the roller bearing (752). A circumferential oil return groove is also provided on the outer side wall of the outer bushing (753). (7533) The bottom of the oil return groove (7533) is provided with an oil return port (7534). The end of the oil return port (7534) faces the inner rear side of the roller bearing (752). The outer ring pressure plate (756) is provided with an oil return channel (7561) on the side wall facing the roller bearing (752). One end of the oil return channel (7561) is connected to the oil return port (7534), and the other end of the oil return channel (7561) faces the inner front side of the roller bearing (752).

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