A plate shearing machine for processing high and low voltage distribution cabinet plate

Abstract

The application belongs to the technical field of machining equipment, and particularly relates to a plate shearing machine for machining high-low voltage power distribution cabinet plates; the plate shearing machine comprises a tool holder shell which is a main body frame with an internal accommodation space; a driving part is movably arranged in the internal accommodation space of the tool holder shell; a buffer system is constructed between the tool holder shell and the driving part, part of energy is absorbed by elastic deformation of a main spring in a shearing resistance stage, compressed air in a main buffer cavity is used to enter a secondary damping cavity through a damping flow channel under the impact of a plate fracture instant, air throttling effect of a throttle hole is used to convert mechanical impact energy into heat energy to dissipate, rebound of 'overshoot' after shearing and fracture is reduced, fatigue wear of a transmission system is reduced, and the service life of the whole equipment is prolonged.

Description

Technical Field

[0001] This invention belongs to the field of mechanical processing equipment technology, specifically a shearing machine for processing high and low voltage switchgear panels. Background Technology

[0002] High and low voltage switchgear are core electrical equipment used in power systems for power distribution, control, protection, and monitoring. They can be classified into high-voltage and low-voltage switchgear according to voltage level. Their core function is to progressively reduce the voltage of electrical energy output from power plants and substations and distribute it to industrial production equipment or residential building power terminals. Through internal electrical components such as circuit breakers, disconnect switches, fuses, and transformers, they achieve circuit switching control, overload protection, short-circuit protection, and monitoring of electrical parameters. They also feature compact structure, safety and reliability, and standardized wiring. They are critical infrastructure for ensuring the stable operation of power systems and electrical safety. In the production and processing of high and low voltage switchgear, shearing machines are used to cut the panels.

[0003] In the process of shearing high and low voltage switchgear panels by existing shearing machines, the shearing machine usually uses a drive source to directly drive the tool holder to drive the blade in a linear shearing motion. Since the shearing process of metal materials is a complex physical process, it mainly includes three stages: elastic deformation, plastic deformation, and fracture separation. In the plastic deformation stage, the plate generates huge reverse resistance to the blade, and the drive system bears a high load. When the shearing stress exceeds the shear strength limit of the material, the plate will fracture and separate instantaneously, causing the resistance in front of the blade to suddenly disappear in a very short time. The elastic potential energy accumulated in the plate and the machine tool system will be released instantaneously, causing the tool holder to produce violent axial rebound or overshoot. In the existing rigid connection structure, this high-frequency, high-energy impact load will be directly transmitted to the precision lead screw and nut pair, bearings, and motor shaft. Long-term exposure to this impact will cause the lead screw and nut clearance to increase, ball wear, and thread fatigue damage, which will seriously affect the shearing accuracy of the equipment, such as causing burrs, uneven cut surfaces, and significantly shortening the service life of the core transmission components. Summary of the Invention

[0004] To address the shortcomings of existing technologies and solve the problem of sheet metal generating significant reverse resistance to the cutting tool during the plastic deformation stage, causing the drive system to bear high loads, and resulting in severe axial springback or overshoot when the shear stress exceeds the material's shear strength limit, this invention proposes a shearing machine for processing high and low voltage switchgear panels.

[0005] The technical solution adopted by this invention to solve its technical problem is: a shearing machine for processing high and low voltage switchgear panels, comprising: The blade holder housing is a main frame with an internal accommodating space, and the bottom of the blade holder housing is provided with a mounting interface for mounting a shearing blade. A driving component, which is movably disposed inside the tool holder housing, is used to connect to an external driving source and receive driving force; A composite buffer assembly is disposed between the tool holder housing and the drive component; The drive component is configured to drive the tool holder housing to move axially via the composite buffer assembly. When the shearing tool on the tool holder housing is subjected to shearing resistance or fracture rebound force, the tool holder housing can generate axial displacement relative to the drive component and squeeze the composite buffer assembly to absorb impact energy.

[0006] Preferably, the composite buffer assembly includes a main buffer cavity formed in the gap between the tool holder housing and the driving member. An upper floating pressure ring and a lower floating pressure ring are slidably connected to opposite ends of the main buffer cavity, as well as a main spring. The main spring is disposed between the upper floating pressure ring and the lower floating pressure ring. An upper limit transmission ring and a lower limit transmission ring are fixedly connected to the outer wall of the driving member. The upper limit transmission ring and the lower limit transmission ring are respectively used to abut against the upper floating pressure ring and the lower floating pressure ring.

[0007] Preferably, at least one secondary damping cavity is provided inside the tool holder housing. The tool holder housing is provided with a damping flow channel connecting the main buffer cavity and the secondary damping cavity. When the tool holder housing is displaced relative to the driving member, the upper floating pressure ring or the lower floating pressure ring compresses the volume of the main buffer cavity, and forces the fluid in the cavity into the secondary damping cavity through the damping flow channel to generate fluid damping force.

[0008] Preferably, a throttling piston is slidably connected inside the secondary damping cavity, and the throttling piston has several throttling holes. A damping spring is also provided inside the secondary damping cavity, with one end of the damping spring abutting against the inner wall of the secondary damping cavity and the other end abutting against the throttling piston.

[0009] Preferably, a flexible contact groove is formed on the upper end face of the upper floating pressure ring or the lower end face of the lower floating pressure ring, and an elastic buffer is provided in the flexible contact groove.

[0010] Preferably, the inner wall of the tool holder housing is provided with a plurality of axially extending guide grooves, and the outer wall of the drive component is fixedly connected with a plurality of anti-rotation guide blocks, which are slidably fitted in the axial guide grooves.

[0011] Preferably, it further includes a preload adjustment component, which is disposed in the tool holder housing and drivenly connected to the upper floating pressure ring. The preload adjustment component is configured to change the initial compression of the main spring by adjusting the initial axial position of the upper floating pressure ring in the main buffer cavity.

[0012] Preferably, the preload adjustment assembly includes a worm gear, which is rotatably mounted inside the tool holder housing. A drive cylinder is fixedly connected to the worm gear. The drive cylinder has an external thread, and an axial pressure cylinder is threadedly connected to the drive cylinder. A push rod is connected between the axial pressure cylinder and the upper floating pressure ring. The rotation of the worm gear drives the axial pressure cylinder to move axially.

[0013] Preferably, the top of the tool holder housing is provided with a bearing seat, and a driving worm gear that meshes with the worm wheel is installed in the bearing seat. The driving worm gear is connected to an adjustment interface that extends to the outside of the tool holder housing.

[0014] Preferably, an airflow disturbance plate is fixedly provided inside the secondary damping cavity, and the airflow disturbance plate is located between the damping channel and the throttling piston.

[0015] The beneficial effects of this invention are as follows: 1. The shearing machine for processing high and low voltage switchgear panels described in this invention constructs a buffer system between the tool holder housing and the drive component. During the shearing resistance stage, the elastic deformation of the main spring absorbs part of the energy. Under the severe impact at the moment of plate breakage, the main buffer chamber compresses air and enters the secondary damping chamber through the damping channel, driving the throttling piston to overcome the work of the damping spring. Combined with the air throttling effect of the throttling orifice, the severe mechanical impact energy is converted into heat energy dissipation. For the "overshoot" rebound after shearing fracture, the cooperation between the limit transmission ring and the flexible contact groove achieves flexible braking at the end. This multi-stage buffering mechanism fundamentally isolates the impact load from the transmission of precision transmission components such as the lead screw and motor, reduces the fatigue wear of the transmission system, and thus extends the overall service life of the equipment.

[0016] 2. The shearing machine for processing high and low voltage switchgear panels described in this invention, through a preload adjustment component, allows the operator to adjust the position of the upper floating pressure ring linearly without disassembling the equipment by rotating the worm gear through an external adjustment interface, via the precision transmission of the worm wheel, drive cylinder, and axial pressure cylinder. This precisely changes the initial preload of the main spring, enabling the tool holder assembly to flexibly adjust its stiffness characteristics according to the material properties of the workpiece (e.g., from thin aluminum plates to thick steel plates). This ensures both the cutting rigidity required for shearing and the buffering energy absorption effect, balancing processing accuracy and equipment protection. Attached Figure Description

[0017] The invention will now be further described with reference to the accompanying drawings.

[0018] Figure 1 This is a three-dimensional schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the tool holder housing structure of the present invention; Figure 3 This is a cross-sectional schematic diagram of the tool holder housing and its internal structure of the present invention; Figure 4 This is a cross-sectional schematic diagram of the internal structure of the tool holder housing of the present invention; Figure 5 This is a schematic diagram of the main spring and its two ends of the present invention; Figure 6 This is a schematic diagram of the floating pressure ring structure of the present invention; Figure 7 This is a schematic diagram of the driving component and its surface structure of the present invention; Figure 8 This is a schematic diagram of the driving component and its bottom structure of the present invention; Figure 9 This is a cross-sectional schematic diagram of the main buffer cavity and the secondary damping cavity structure of the present invention; Figure 10 This is a schematic diagram of the throttling piston structure of the present invention; Figure 11 This is a schematic diagram of the connection structure between the axial pressure cylinder and the upper floating pressure ring of the present invention; Figure 12 This is a cross-sectional view of the internal structure of the receiving cavity and guide cavity of the present invention.

[0019] In the picture: 100. Tool holder housing; 110. Drive component; 120. Axial guide groove; 130. Anti-rotation guide block; 140. Upper limit transmission ring; 150. Lower limit transmission ring; 200. Composite buffer assembly; 210. Main buffer chamber; 211. Main spring; 212. Damping flow channel; 220. Upper floating pressure ring; 221. Flexible contact groove; 222. Linkage lug; 230. Lower floating pressure ring; 240. Limiting slide cavity; 250. Secondary damping chamber; 251. Damping spring; 260. Throttling piston; 261. Throttling orifice; 262. Airflow disturbance plate; 300. Preload adjustment assembly; 310. Receiving cavity; 311. Worm gear; 320. Drive cylinder; 330. Guide cavity; 331. Limiting groove; 340. Axial pressure cylinder; 341. Transmission slider; 350. Push rod; 360. Bearing seat; 361. Mounting cavity; 370. Drive worm gear; 371. Input shaft; 372. Adjustment interface. Detailed Implementation

[0020] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below in conjunction with specific embodiments.

[0021] like Figure 1 As shown, this embodiment discloses an adaptive buffer blade holder assembly for shearing equipment. This assembly is suitable as an independent functional module installed at the transmission end of metal processing equipment such as shearing machines. It is used to stably clamp the shearing blade and internally buffer the impact load during the processing of metal sheets. The blade holder assembly mainly includes: a blade holder housing 100 as the supporting body, a drive component 110 as the power input interface, a built-in composite buffer assembly 200, and a preload adjustment assembly 300. The blade holder housing 100 is constructed as a rigid frame to support the blade. Its bottom is provided with an installation interface (such as a T-slot and locking structure) for rigidly fixing the shearing blade. The drive component 110 is coaxially inserted inside the blade holder housing 100, forming the input end of this assembly to receive external driving force. The composite buffer assembly 200 is integrated in the internal cavity of the blade holder housing 100 to achieve gas-liquid composite flexible buffering under the action of shearing reaction force. The preload adjustment assembly 300 is located at the inner top of the blade holder housing 100 to adjust the initial preload of the internal buffer according to the working conditions.

[0022] Furthermore, during the shearing of high and low voltage distribution cabinet panels using this component, the shearing surface gradually forms after the plate enters the plastic deformation stage. The blade squeezes the plate to generate shear stress. During this process, the frequency of sudden changes in the thrust of the plate to the blade increases. Traditional rigid connections will cause the transmission screw to bear periodic impact loads until the shear stress of the plate reaches the shear strength limit, the shearing surface is completely separated, and the plate breaks into two parts. At the moment of fracture, the elastic potential energy accumulated inside the plate is suddenly released, causing the constraint reaction force on the blade to disappear rapidly (i.e., the "unload" phenomenon). This long-term rebound impact will cause the gap between the drive component 110 and the external transmission shaft to increase and cause fatigue damage.

[0023] In the shearing process described in this embodiment, an external drive source (such as a motor screw module) drives the drive component 110 to move. When the drive component 110 receives the driving force and moves downward along the axis, its movement trajectory is subject to the dual radial constraints of the upper limit transmission ring 140 and the lower limit transmission ring 150. At the same time, under the preload of the main spring 211, the drive component 110 drives the blade holder housing 100 to move smoothly downward along the external guide rail through the friction of the end face contact surface and mechanical cooperation. The blade holder housing 100 drives the blade to move downward synchronously through the rigid interface at the bottom until the blade edge makes precise contact with the upper surface of the plate to be sheared. When the blade continues to move downward and applies a compressive shearing force to the plate, the plate will generate a reverse horizontal push against the blade due to its resistance to plastic deformation. The force is directly transmitted to the tool holder housing 100, causing the tool holder housing 100 to slide slightly upward relative to the outer cylindrical surface of the drive member 110. As the tool holder housing 100 moves upward, it simultaneously drives the upper floating pressure ring 220 and the lower floating pressure ring 230 to move upward along the axis. When the upper floating pressure ring 220 reaches contact with the lower end face of the upper limit transmission ring 140, the upper limit transmission ring 140, through axial limiting, locks the upper floating pressure ring 220, restricting its further upward movement. The subsequent continuous upward force of the tool holder housing 100, through the contact between the end faces of the upper floating pressure ring 220 and the lower floating pressure ring 230, is converted into an axial compressive force on the main spring 211. The main spring 211 absorbs the instantaneous impact thrust of the plate material on the tool through its own elastic deformation. During the upward sliding of body 100, the volume of its internal main buffer chamber 210 is gradually compressed by the relative movement of the upper floating pressure ring 220. The sealed air in the main buffer chamber 210 experiences a pressure increase due to volume contraction. The high-pressure air is directionally squeezed into the secondary damping chamber 250 at the lower part of the tool holder housing 100 through the damping flow channel 212. Due to the throttling effect of the throttling orifice 261 on the throttling piston 260 on the airflow, the air cannot be discharged quickly, causing the air pressure in the secondary damping chamber 250 to rise sharply in a short period of time. The high-pressure air pushes the throttling piston 260 to slide upward along the inner wall of the secondary damping chamber 250, and simultaneously squeezes the damping spring 251. This process achieves a second-stage buffer through the air damping effect and the elastic deformation of the damping spring 251, further absorbing the thrust of the plate. The fluctuating energy is released until the air in the main buffer chamber 210 and the secondary damping chamber 250 flows slowly through the throttle hole 261. The air pressure on the upper and lower sides of the throttle piston 260 is restored to balance. When the shear stress of the plate reaches the shear strength limit and it breaks, the reverse thrust of the plate on the tool disappears instantly. Under the inertia of the downward motion, the tool holder housing 100 continues to slide downward along the surface of the drive member 110 (overshooting occurs). At this time, the lower floating pressure ring 230 moves downward with the tool holder housing 100. Its lower end face will contact the upper end face of the lower limit transmission ring 150. The lower limit transmission ring 150 causes the lower floating pressure ring 230 to squeeze the flexible contact groove 221 (with an arc-shaped structure and built-in elastic rubber pad) opened at the upper end of the upper floating pressure ring 220 through the axial limiting effect.The elastic deformation of the flexible contact groove 221 and the contact friction with the lower floating pressure ring 230 effectively absorb the rebound impact energy generated by the disappearance of the constraint reaction force of the tool holder.

[0024] like Figure 3 and Figure 5 As shown, the composite buffer assembly 200 includes a main buffer cavity 210 opened in the tool holder housing 100. The upper and lower ends of the main buffer cavity 210 are slidably connected to an upper floating pressure ring 220 and a lower floating pressure ring 230, respectively. A main spring 211 is provided between the upper floating pressure ring 220 and the lower floating pressure ring 230, which is used for buffering and pressure compensation when the tool holder is shearing the plate. Four secondary damping cavities 250 are opened around the main buffer cavity 210 inside the tool holder housing 100, which are used to cooperate with the main spring 211 through pressure. Throttling pistons 260 are slidably connected in each of the four secondary damping cavities 250. Each of the four throttling pistons 260 has five throttling holes 261. The purpose of the throttling holes 261 is to limit the airflow speed, so that the air slowly passes through the throttling pistons 260 to form a stable damping effect. Four linkage lugs 222 are fixedly connected at equal intervals on the side of the upper floating pressure ring 220.

[0025] like Figure 7 As shown, an upper limit transmission ring 140 and a lower limit transmission ring 150 are symmetrically fixedly connected to the drive component 110, as follows: Figure 5 and Figure 6 As shown, both the upper floating pressure ring 220 and the lower floating pressure ring 230 have flexible contact grooves 221 on the side away from the middle of the drive member 110. The lower end face of the upper limit transmission ring 140 and the upper groove wall of the flexible contact groove 221, and the upper end face of the lower limit transmission ring 150 and the lower groove wall of the flexible contact groove 221 form surface contact abutments. When the drive member 110 slides relative to the tool holder housing 100, when the drive member 110 slides axially relative to the tool holder housing 100, the upper limit transmission ring 140 and the lower limit transmission ring 150 generate axial thrust through end face abutments, which respectively drive the upper floating pressure ring 220 to move upward and the lower floating pressure ring 230 to move downward, thereby triggering the compression buffer action of the main spring 211.

[0026] like Figure 4 and Figure 9 As shown, four damping channels 212 are equidistantly arranged around the main buffer cavity 210 inside the tool holder housing 100. One end of the four damping channels 212 is connected to the main buffer cavity 210, and the other end of the four damping channels 212 away from the main buffer cavity 210 is connected to the secondary damping cavity 250. When the upper floating pressure ring 220 or the lower floating pressure ring 230 squeezes the internal space of the main buffer cavity 210, the sealed air in the main buffer cavity 210 will be directionally squeezed into the secondary damping cavity 250 through the set of damping channels 212, providing a power source for pneumatic damping buffering.

[0027] like Figure 2 and Figure 4 As shown, four axial guide grooves 120 are equally spaced at both the upper and lower ends of the tool holder housing 100. Four anti-rotation guide blocks 130 are equally spaced and fixedly connected at both the upper and lower ends of the drive member 110. The anti-rotation guide blocks 130 are slidably connected to the axial guide grooves 120. The sliding cooperation between the anti-rotation guide blocks 130 and the axial guide grooves 120 constitutes axial guidance, which strictly restricts the circumferential rotational freedom of the tool holder housing 100 and ensures that the tool holder housing 100 can only slide vertically up and down along the outer cylindrical surface of the drive member 110, thus ensuring the motion accuracy during the shearing process.

[0028] like Figure 4 As shown, two limiting slide cavities 240 are symmetrically formed inside the tool holder housing 100. Both limiting slide cavities 240 are connected to the main buffer cavity 210. The upper limiting transmission ring 140 and the lower limiting transmission ring 150 are slidably connected to the two limiting slide cavities 240 respectively, providing radial positioning for the upper limiting transmission ring 140 and the lower limiting transmission ring 150.

[0029] like Figure 3 and Figure 10 As shown, each of the four secondary damping cavities 250 has two damping springs 251 symmetrically arranged inside. The top ends of each pair of damping springs 251 are fixedly connected to the throttling piston 260. Each of the four secondary damping cavities 250 has an airflow disturbance plate 262 fixedly connected inside. The airflow disturbance plate 262 is located above the damping channel 212 and directly below the throttling piston 260. When the throttling piston 260 is not compressed by external air pressure, the damping springs 251 are in a naturally extended state, pushing the throttling piston 260 to tightly contact the top end face of the airflow disturbance plate 262, ensuring airtightness and positional stability in the initial state.

[0030] like Figure 4 and Figure 12 As shown, the preload adjustment assembly 300 includes a receiving cavity 310 inside the tool holder housing 100. A worm gear 311 is rotatably connected inside the receiving cavity 310. A drive cylinder 320 is fixedly connected to the bottom of the worm gear 311. A guide cavity 330 is provided inside the tool holder housing 100. Four limiting grooves 331 are provided around the guide cavity 330 inside the tool holder housing 100. All four limiting grooves 331 are connected to the guide cavity 330. An axial pressure cylinder 340 is slidably connected inside the guide cavity 330. The axial pressure cylinder 340 is threadedly connected to the drive cylinder 320. Four transmission sliders 341 are fixedly connected at equal intervals to the outer side of the axial pressure cylinder 340. All four transmission sliders 341 are slidably connected to the limiting grooves 331. The four transmission sliders 341 and the limiting grooves 331 can simultaneously form a limiting engagement, so that the axial pressure cylinder 340 slides vertically up and down when the drive cylinder 320 rotates. All four linkage lugs 222 are slidably connected to the limiting grooves 331. Figure 11As shown, push rods 350 are fixedly connected to the bottom of each of the four transmission sliders 341. The bottom of each of the four push rods 350 is fixedly connected to the linkage lugs 222. When the drive cylinder 320 rotates around its own axis, the axial pressure cylinder 340 slides smoothly downward along the axial direction. When the axial pressure cylinder 340 slides downward, it transmits axial thrust through the transmission sliders 341, drives the push rods 350 to rotate around the hinge point and pushes the upper floating pressure ring 220 to move downward along the inner wall of the main buffer cavity 210. As the upper floating pressure ring 220 continues to move downward, the main spring 211 in the flexible contact groove 221 is further compressed, and the deformation of the main spring 211 gradually increases to adapt to the rebound impact compensation requirements when shearing plates of different thicknesses and hardnesses, ensuring the stability and adaptability of the buffering effect on the tool holder housing 100.

[0031] like Figure 12 As shown, a bearing housing 360 is fixedly connected to one side of the top of the tool holder housing 100. The bearing housing 360 has an installation cavity 361 inside, which is connected to the receiving cavity 310. A drive worm gear 370 is rotatably connected inside the installation cavity 361. An input shaft 371 is fixedly connected to the middle of the drive worm gear 370. One end of the input shaft 371 passes through the bearing housing 360, and an adjustment interface 372 is fixedly connected to the other end of the input shaft 371 that passes through the bearing housing 360. When the operator uses a wrench or other tools to rotate the adjustment interface 372, the adjustment interface 372 drives the drive worm gear 370 to rotate around its own axis through the input shaft 371. The drive worm gear 370 drives the worm wheel 311 to rotate synchronously through meshing transmission, which in turn drives the drive cylinder 320 to rotate. Finally, the position of the upper floating pressure ring 220 is precisely adjusted, thereby changing the deformation degree and preload of the main spring 211 and achieving adaptive adjustment for different working conditions.

[0032] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the present invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of the present invention is defined by the appended claims and their equivalents.

Claims

1. A shearing machine for processing high and low voltage switchgear panels, characterized in that, Including: The blade holder housing (100) is a main frame with an internal accommodating space, and the bottom of the blade holder housing (100) is provided with a mounting interface for mounting a shearing blade. A drive unit (110) is movably disposed inside the tool holder housing (100) for connecting to an external drive source and receiving drive force; A composite buffer assembly (200) is disposed between the tool holder housing (100) and the drive member (110). The composite buffer assembly (200) includes a main buffer cavity (210) formed in the gap between the tool holder housing (100) and the drive member (110). An upper floating pressure ring (220) and a lower floating pressure ring (230) are slidably connected to opposite ends of the main buffer cavity (210), as well as a main spring (211). Between the upper floating pressure ring (220) and the lower floating pressure ring (230) A main spring (211) is provided. An upper limit transmission ring (140) and a lower limit transmission ring (150) are fixedly connected to the outer wall of the driving member (110). The upper limit transmission ring (140) and the lower limit transmission ring (150) are respectively used to abut against the upper floating pressure ring (220) and the lower floating pressure ring (230). A flexible contact groove (221) is provided on the upper end face of the upper floating pressure ring (220) or the lower end face of the lower floating pressure ring (230). An elastic buffer is provided in the flexible contact groove (221). The tool holder housing (100) is also provided with at least one secondary damping cavity (250). The tool holder housing (100) is provided with a damping flow channel (212) connecting the main buffer cavity (210) and the secondary damping cavity (250). When the tool holder housing (100) is displaced relative to the driving member (110), the upper floating pressure ring (220) or the lower floating pressure ring (230) compresses the volume of the main buffer cavity (210) and forces the compressible gas into the secondary damping cavity (250) through the damping flow channel (212) to generate fluid damping force. A throttling piston (260) is slidably connected inside the secondary damping cavity (250). The throttling piston (260) has several throttling holes (261). A damping spring (251) is also provided inside the secondary damping cavity (250). One end of the damping spring (251) abuts against the inner wall of the secondary damping cavity (250), and the other end abuts against the throttling piston (260). The drive member (110) is configured to drive the tool holder housing (100) to move axially via the composite buffer assembly (200). When the shearing tool on the tool holder housing (100) is subjected to shearing resistance or fracture rebound force, the tool holder housing (100) can generate axial displacement relative to the drive member (110) and squeeze the composite buffer assembly (200) to absorb impact energy.

2. The shearing machine for processing high and low voltage switchgear panels according to claim 1, characterized in that, The inner wall of the tool holder housing (100) is provided with a plurality of axial guide grooves (120) extending along the axial direction, and the outer wall of the drive member (110) is fixedly connected with a plurality of anti-rotation guide blocks (130), and the anti-rotation guide blocks (130) are slidably fitted in the axial guide grooves (120).

3. A shearing machine for processing high and low voltage switchgear panels according to claim 1, characterized in that, It also includes a preload adjustment assembly (300), which is disposed in the tool holder housing (100) and drivenly connected to the upper floating pressure ring (220). The preload adjustment assembly (300) is configured to change the initial compression of the main spring (211) by adjusting the initial axial position of the upper floating pressure ring (220) in the main buffer cavity (210).

4. A shearing machine for processing high and low voltage switchgear panels according to claim 3, characterized in that, The preload adjustment assembly (300) includes a worm gear (311), which is rotatably mounted inside the tool holder housing (100). A drive cylinder (320) is fixedly connected to the worm gear (311). The drive cylinder (320) has an external thread. An axial pressure cylinder (340) is threadedly connected to the drive cylinder (320). A push rod (350) is connected between the axial pressure cylinder (340) and the upper floating pressure ring (220). The rotation of the worm gear (311) drives the axial pressure cylinder (340) to move axially.

5. A shearing machine for processing high and low voltage switchgear panels according to claim 4, characterized in that, The top of the tool holder housing (100) is provided with a bearing seat (360), and an active worm (370) that meshes with the worm gear (311) is installed in the bearing seat (360). The active worm (370) is connected to an adjustment interface (372) that extends to the outside of the tool holder housing (100).

6. A shearing machine for processing high and low voltage switchgear panels according to claim 1, characterized in that, An airflow disturbance plate (262) is fixedly provided inside the secondary damping cavity (250), and the airflow disturbance plate (262) is located between the damping channel (212) and the throttling piston (260).

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