A vibrating knife amplitude compensation system

Abstract

The present application belongs to the technical field of cutting knife cutting, and particularly relates to a vibration knife amplitude compensation system. The present application provides a vibration knife amplitude compensation system, which comprises a machine head shell fixed to a cutting bed crossbeam, and a vibration assembly, an eccentric block assembly and a driving adjustment assembly arranged in the machine head shell. The vibration assembly comprises a U-shaped vibration base made of a leaf spring and a bidirectional reverse rotation driven shaft driven by a T-shaped bevel gear box. The eccentric block assembly comprises a fixed eccentric block and a movable eccentric block connected with a sliding sleeve through a helical spline. The driving adjustment assembly uses a presser foot rod to lift with the material thickness, pushes a shift block to move horizontally through a ladder-shaped wedge, and drives the sliding sleeve to axially displace to change the phase difference between the movable and fixed eccentric blocks, so that the present application can realize stepless adjustment of the amplitude with the material thickness, reduce resonance caused by centrifugal force, and improve cutting precision and adaptability.

Description

Technical Field

[0001] This invention belongs to the field of cutting blade technology, and particularly relates to a vibration blade amplitude compensation system. Background Technology

[0002] In the use of vibrating cutters on cutting tables, amplitude is one of the key parameters that determines the cutting effect. In actual production, different materials and thicknesses have different requirements for amplitude. For example, when cutting thick materials such as felt and sponge, a larger amplitude is needed to ensure the penetration power of the blade, while when cutting thin materials such as carbon fiber prepreg and fiberglass cloth, a smaller amplitude is needed to reduce material delamination and burrs.

[0003] Existing standard vibratory cutters typically employ a fixed amplitude design, meaning a fixed amplitude value is set at the factory and cannot be adjusted according to actual needs during use. Some existing technologies utilize mechanical or electronic amplitude-changing mechanisms, such as adjusting the relative position of eccentric blocks or changing the motor speed to adjust the output amplitude. These solutions achieve amplitude adjustability to some extent, enabling the equipment to handle materials of uniform thickness. However, when dealing with composite materials with varying thicknesses or overlapping areas, a single amplitude is insufficient to match the dynamic changes in material thickness in real time. This can cause the blade to bend due to insufficient kinetic energy when cutting into thicker areas, or to pierce the bottom pad due to excessive amplitude when cutting into thinner areas.

[0004] Therefore, the existing technology still has at least the following shortcomings in actual use, which are the problems that the present invention aims to solve: 1. The problem of unsuitable amplitude in the variable thickness transition zone; 2. The problem of lag in electronic control adjustment response.

[0005] In conclusion, it is necessary to develop a cutting blade amplitude compensation structure that can adapt to thickness fluctuations during the cutting process to solve this problem. Summary of the Invention

[0006] This invention provides a vibrating knife amplitude compensation system, including a head housing fixed to the cutting bed beam, and a vibration component, an eccentric block assembly, and a drive adjustment component disposed therein. The vibration component includes a U-shaped vibration base made of a leaf spring and a bidirectional counter-rotating driven shaft driven by a T-shaped bevel gearbox. The eccentric block assembly includes a fixed eccentric block and a moving eccentric block connected to a sliding sleeve via a helical spline. The drive adjustment component uses a pressure foot rod to rise and fall with the material thickness, and pushes a dial block to move laterally through a trapezoidal wedge, thereby causing the sliding sleeve to move axially to change the phase difference between the moving and fixed eccentric blocks. Thus, this invention can achieve stepless amplitude adjustment with material thickness, reduce resonance caused by centrifugal force, and improve cutting accuracy and adaptability.

[0007] This invention overcomes the shortcomings of existing technologies and provides a vibrating knife amplitude compensation system, comprising: a machine head housing, fixedly mounted on a cutting bed crossbeam; a vibration assembly, including a U-shaped vibration base disposed on the inner top surface of the machine head housing, a drive motor disposed on the inner top surface of the machine head housing and arranged vertically downward, a T-shaped bevel gearbox disposed on the output shaft of the drive motor and connected at its lower end to the vibration base, two driven shafts respectively disposed on the output ends of the T-shaped bevel gearbox and passing through the side plate of the vibration base via bearings, a cutting knife component mounted on the lower surface of the vibration base, and the vibration base being made of a leaf spring; an eccentric block assembly, including a fixed eccentric block fixedly disposed on the driven shaft, a helical spline disposed in the middle section of the driven shaft, a sliding sleeve screwed onto the helical spline, and a moving eccentric block fixedly disposed on the sliding sleeve; and a drive adjustment assembly, including a thrust release bearing disposed on the surface of the sliding sleeve at a position avoiding the moving eccentric block, two annular grooves disposed on the surface of the thrust release bearing, and vertically disposed on the machine head housing. The inner side has a first linear guide rail, a lifting slider that is slidably mounted on the first linear guide rail and whose lower end is used to install the presser foot rod, a trapezoidal wedge block that is mounted on the upper end of the lifting slider block, a first return spring that is sleeved on the presser foot rod and whose end is connected to the machine head housing, a second linear guide rail that is horizontally mounted above the first linear guide rail, two levers that are symmetrically slidably mounted on the second linear guide rail and whose lower ends are both connected to the annular groove, and a second return spring whose two ends are respectively connected to the levers and the inner end of the second linear guide rail. The levers have a slope on their opposite sides that cooperates with the trapezoidal wedge block.

[0008] A further preferred technical solution is that the mass of the moving eccentric block is less than the mass of the fixed eccentric block.

[0009] A further preferred technical solution is that the lever includes an end block slidably connected within the second linear guide rail, a lever disposed below the end block, a lever fork disposed below the lever, and a cylindrical pin disposed on the fork corner and connected to the annular groove.

[0010] A further preferred technical solution is that the depth of the annular groove is not less than the maximum single amplitude.

[0011] A further preferred technical solution is that: ball bearings are provided on the mating surfaces of the end block and the trapezoidal wedge block.

[0012] A further preferred technical solution is that the T-type bevel gearbox includes a housing, a main input shaft connected to the output shaft of the drive motor via a flexible coupling, a main gear disposed at the lower end of the main input shaft, a driven gear meshing with both sides of the main gear and connected to the driven shaft, and an oil-sealed bearing disposed in the housing for passing through the main input shaft and the driven shaft.

[0013] A further preferred technical solution is that the housing and the vibration base are integrally formed.

[0014] A further preferred technical solution is that the mass ratio of the fixed eccentric block to the moving eccentric block is 1.3 to 1.8.

[0015] A further preferred technical solution is that the included angle of the inclined plane of the trapezoidal wedge is 15°~30°.

[0016] The beneficial effects of this invention are at least as follows: 1. By employing a mechanical feedback adjustment mechanism, the change in material thickness is converted into the axial displacement of the sliding sleeve through the mechanical linkage of the pressure foot, wedge, and shift fork, thereby changing the phase difference of the eccentric block and achieving adaptive adjustment of the amplitude; 2. By using a T-shaped bevel gear to achieve rotation in opposite directions at the same speed, the centrifugal force in the horizontal direction is offset, minimizing the resonance problem of the entire machine; 3. By employing a spiral spline sliding sleeve mechanism to achieve stepless adjustment of the amplitude, the adjustment range is continuously variable from the minimum amplitude to the maximum amplitude, which can accurately adapt to the cutting needs of materials of different thicknesses. Moreover, the spiral spline mechanism has a self-locking characteristic, which can maintain a stable phase difference under vibration environment, ensuring the stability of the amplitude. Attached Figure Description

[0017] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a three-dimensional schematic diagram of the present invention; Figure 2 This is a front view of the present invention; Figure 3 This is a schematic diagram of the vibration assembly and eccentric block assembly of the present invention; Figure 4 This is a schematic diagram of the internal structure of the machine head of the present invention; Figure 5 This is a schematic diagram of the drive adjustment component of the present invention; Figure 6 This is a partial schematic diagram of the drive adjustment component of the present invention; Figure 7 This is a schematic diagram of the eccentric block assembly of the present invention under different phases; Figure 8 This is a cross-sectional view of the T-type bevel gearbox of the present invention.

[0019] The meanings of the various reference numerals in the figure are as follows: 1. Head housing; 2. Vibration assembly; 3. Eccentric block assembly; 4. Drive adjustment assembly; Vibration base 21, drive motor 22, T-type bevel gearbox 23, driven shaft 24, cutting blade 25, fixed eccentric block 31, spiral spline 32, sliding sleeve 33, moving eccentric block 34, thrust separation bearing 41, annular groove 42, first linear guide rail 43, presser foot rod 44, lifting slider 45, trapezoidal wedge block 46, first return spring 47, second linear guide rail 48, lever block 49, second return spring 410; 231 housing, 232 main input shaft, 233 main gear, 234 driven gear, 235 oil seal bearing, 491 end block, 492 lever, 493 shift fork, 494 cylindrical pin. Detailed Implementation

[0020] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following description is only a preferred embodiment of the present invention and is not intended to limit the scope of the present invention.

[0021] The directional terms such as up, down, left, right, front, back, front, back, top, bottom, etc., mentioned or possibly mentioned in this specification are defined relative to the structure shown in the accompanying drawings. The terms "inner" and "outer" refer to the direction toward or away from the geometric center of a specific component, respectively. These are relative concepts and may therefore vary depending on their location and usage. Therefore, these or other directional terms should not be interpreted as restrictive terms.

[0022] As attached Figures 1-8As shown, a vibrating knife amplitude compensation system includes a head housing 1, fixedly mounted on a cutting bed crossbeam; a vibration assembly 2, including a U-shaped vibration base 21 disposed on the inner top surface of the head housing 1, a drive motor 22 disposed on the inner top surface of the head housing 1 and arranged vertically downward, a T-shaped bevel gearbox 23 disposed on the output shaft of the drive motor 22 and connected at its lower end to the vibration base 21, two driven shafts 24 respectively disposed on the output ends of the T-shaped bevel gearbox 23 and passing through the side plate of the vibration base 21 via bearings, a cutting knife 25 mounted on the lower surface of the vibration base 21, and the vibration base 21 being made of leaf springs; an eccentric block assembly 3, including a fixed eccentric block 31 fixedly disposed on the driven shaft 24, a helical spline 32 disposed in the middle section of the driven shaft 24, a sliding sleeve 33 screwed onto the helical spline 32, and a moving eccentric block 34 fixedly disposed on the sliding sleeve 33; and a drive adjustment group. Component 4 includes a thrust release bearing 41 disposed on the surface of the sliding sleeve 33 at a position that avoids the moving eccentric block 34, two annular grooves 42 disposed on the surface of the thrust release bearing 41, a first linear guide rail 43 vertically disposed on the inner side of the head housing 1, a lifting slider 45 slidably disposed on the first linear guide rail 43 and whose lower end is used to install the presser foot rod 44, a trapezoidal wedge block 46 disposed on the upper end of the lifting slider 45, a first return spring 47 sleeved on the presser foot rod 44 and whose end is connected to the head housing 1, a second linear guide rail 48 horizontally disposed above the first linear guide rail 43, two lever blocks 49 symmetrically slidably disposed on the second linear guide rail 48 and whose lower ends are both connected to the annular grooves 42, and a second return spring 410 whose two ends are respectively connected to the lever blocks and the inner end of the second linear guide rail, wherein the lever blocks 49 have a slope on opposite sides that cooperates with the trapezoidal wedge block 46.

[0023] In this embodiment, the machine head housing 1 is directly bolted to the Z-axis base plate of the CNC cutting machine. It has an internal mounting cavity and a through hole or an open bottom for the presser foot to extend. Its material can be cast iron, aluminum alloy, or high-strength engineering plastic, etc., and this embodiment does not impose any special limitations on this. The machine head housing 1 and the vibration base 21 in the vibration assembly 2 form a dynamic-static separation structure, confining the vibration energy within the internal components and preventing it from being transmitted to the cutting machine gantry and causing resonance.

[0024] The vibration base 21 is a suspended frame that supports the core transmission and eccentric mechanism. Its shape can be U-shaped, frame-shaped, or other geometric shapes that can form a semi-enclosed space. The vibration base 21 is made of leaf springs, that is, its main structure is made of spring steel sheets with high elastic modulus bent or welded. The high rigidity of the leaf spring in the horizontal plane is used to lock the internal components to prevent swaying. At the same time, its elastic deformation capability in the vertical direction allows high-frequency up and down vibration. Its upper part is fixedly connected to the machine head housing 1 or connected through elastic elements, and its lower part drives the cutting blade 25 to move. The drive motor 22 is an actuator that provides rotational power. It can be a servo motor, stepper motor, or AC asynchronous motor, etc. The drive motor 22 is arranged vertically downward on the inner top surface of the head housing 1, that is, its stator is fixed on the stationary head housing 1, while its rotor output shaft extends downward along the direction of gravity. The power input direction and the expected vibration output direction are spatially orthogonal to the rotation plane of the driven shaft 24, which facilitates power splitting through the T-type bevel gearbox 23. The end of the output shaft of the drive motor 22 is connected to the input shaft of the T-type bevel gear through a flexible coupling. The flexible coupling allows the bottom input shaft to slide relative to each other within a few millimeters to accommodate the high-frequency oscillation of the vibration base. The T-type bevel gearbox 23 is a transmission mechanism used to change the direction of power transmission and realize power distribution. It contains a set of meshing bevel gears. The main body of the T-type bevel gearbox 23 is fixed on the vibration base 21 and vibrates at high frequency with the vibration base 21. Its input shaft is connected to the output shaft of the stationary drive motor 22 through a flexible coupling to absorb the relative displacement between the two. The function of the T-type bevel gearbox 23 is to convert the vertical rotational motion input from the drive motor 22 into two horizontal rotational motions, which are then transmitted to the driven shafts 24 on both sides. The T-type bevel gearbox 23 has a symmetrical structure design, ensuring that the two driven shafts 24 always maintain absolute same speed and opposite rotation, thereby counteracting the generated horizontal centrifugal force and preventing the machine head from producing violent lateral sway. The driven shafts 24 are the rotating shafts that transmit rotational torque and support the eccentric block assembly 3. They are made of tempered alloy steel, and the surface can be hardened to improve wear resistance. They are respectively set on the output ends of the T-type bevel gearbox 23 and pass through the side plate of the vibration base 21 through bearings, allowing them to rotate freely relative to the vibration base 21. The fixed eccentric block 31 and the moving eccentric block 34 installed on them generate a vertical centrifugal force component when rotating, which, when superimposed, forms the excitation force that drives the vibration base 21 to move up and down. The cutting blade 25 is a cutting tool component that directly performs the cutting operation. It is installed on the lower surface of the vibration base 21 and is preferably fixed by a spring clip or a pin to lock the blade clip, so that the cutting blade 25 can perform high-frequency up-and-down reciprocating motion together with the vibration base 21. During the vibration process, the cutting blade 25 uses the cutting edge and vertical impact force to cut the material fibers. The magnitude of its amplitude directly determines the cutting depth capability and the adaptability to materials.

[0025] On the left and right driven shafts, a set of perfectly mirrored eccentric block assemblies 3 are connected in series. The fixed eccentric block 31 is a counterweight fixed to the driven shaft 24 and whose position cannot move axially. Its mass can be designed according to the base amplitude required by the system. It is usually located at the outer end of the driven shaft 24 and is rigidly connected to the driven shaft 24 by means of flat key, interference fit or welding, etc., to provide a constant base centrifugal force vector. The helical spline 32 is a toothed structure with a helical helix angle machined on the middle section surface of the driven shaft 24. Its tooth profile can be trapezoidal, rectangular or involute. Its function is to convert the axial linear motion of the sliding sleeve 33 into rotational motion and to convert the rotational constraint of the sliding sleeve 33 into axial displacement. When the sliding sleeve 33 moves along the helical spline 32, due to the existence of the helical helix angle, the sliding sleeve 33 will be forced to deflect angularly relative to the driven shaft 24, thereby driving the moving eccentric block 34 fixed on it to change the phase angle. The sliding sleeve 33 is a sleeve fitted outside the driven shaft 24, capable of sliding axially and rotating slightly. Its interior is machined with helical grooves that match the helical spline 32. The sliding sleeve 33 is screwed onto the helical spline 32, and its outer surface is used to mount the moving eccentric block 34 and the thrust release bearing 41. A small change in its axial position can be amplified by the helical spline 32 into a significant phase angle change in the moving eccentric block 34, thereby achieving fine adjustment of the amplitude. The moving eccentric block 34 is a counterweight fixed to the sliding sleeve 33, moving and rotating with it. Its mass is typically less than that of the fixed eccentric block 31 to create a mass difference and optimize dynamic balance. The moving eccentric block 34 and the fixed eccentric block 31 work together. When their phase difference is 180°, most of the centrifugal forces cancel each other out, and the system is in a small amplitude state. When their phase difference approaches 0°, the centrifugal forces superimpose, and the system is in a large amplitude state.

[0026] The drive adjustment component is used to drive the eccentric block assembly to change the phase difference, thereby adjusting the amplitude. The thrust release bearing 41 is a bearing assembly that can withstand axial thrust and allow relative rotation of the inner and outer rings. Its type can be a planar thrust bearing, an angular contact ball bearing, or a dedicated release bearing. It is set on the surface of the sliding sleeve 33 to avoid the moving eccentric block 34. The inner ring rotates at high speed with the sliding sleeve 33 and the driven shaft 24, while its outer ring remains stationary or is restricted from rotation, only receiving axial thrust. It transmits the stationary axial thrust generated by the drive adjustment component 4 to the rotating sliding sleeve 33, while isolating rotational friction, ensuring that the adjustment process is smooth and does not interfere with the normal rotation of the driven shaft 24. The annular groove 42 is an annular groove formed on the outer ring surface of the thrust release bearing 41. Its depth is not less than the maximum single amplitude to ensure that it does not dislodge during vibration. The two annular grooves 42 are used to connect with the lower end of the lever 49, providing a force application point for the lever 49. This allows the lever 49 to push the thrust release bearing 41 in the axial direction while allowing the thrust release bearing 41 to vibrate in the vertical direction. The first linear guide rail 43 is a vertical guide mechanism installed on the inner side of the head housing 1. It is used to limit the movement trajectory of the lifting slider 45, i.e., the presser foot rod 44, to only the vertical direction, ensuring that the presser foot rod 44 can sense the change in material thickness and convert it into a vertical displacement signal. The lifting slider 45 is a connector that is slidably mounted on the first linear guide rail 43. Its lower end is used to install the presser foot rod 44. The lifting slider 45 slides along the first linear guide rail 43 as the presser foot rod 44 moves up and down. Its upper end carries the trapezoidal wedge 46 and transmits the material thickness change (vertical displacement) detected by the presser foot rod 44 to the trapezoidal wedge 46, thereby triggering the subsequent amplitude adjustment action. The trapezoidal wedge 46 is a wedge-shaped block with inclined sides. The included angle of its inclined surface can be set according to actual needs and matches the slope surface of the two levers 49. When the lifting slider 45 moves upward, the wider part of the trapezoidal wedge 46 inserts between the two levers 49, forcing the levers 49 to separate horizontally to both sides; when the lifting slider 45 moves downward, under the action of the second return spring 410, the levers 49 move towards the center, and the trapezoidal wedge 46 descends accordingly. The first return spring 47 and the second return spring 410 are elastic elements that provide return spring force, and their types can be helical compression springs, disc springs, or rubber springs, etc. At least one extension plate extends from the inner side of the machine head housing 1 for the presser foot rod 44 to pass through. The first return spring 47 is sleeved on the presser foot rod 44, with one end connected to the extension plate and the other end connected to the presser foot rod. The second linear guide rail 48 is a guide mechanism that is horizontally arranged above the first linear guide rail 43. It is used to limit the movement trajectory of the toggle block 49 to only the horizontal direction. The second linear guide rail 48 is arranged perpendicularly to the first linear guide rail 43 to form a cross.The shift block 49 refers to the transmission component that is symmetrically slidably arranged on the second linear guide rail 48. There are two of them, located on both sides of the trapezoidal wedge block 46. The lower end of the shift block 49 is connected to the annular groove 42, and the upper end or side has a slope that matches the trapezoidal wedge block 46. It transmits the horizontal component of the trapezoidal wedge block 46 to the thrust release bearing 41, driving the sliding sleeve 33 to move axially.

[0027] The working principle of this embodiment is as follows: After the system starts, the drive motor 22 drives the T-shaped bevel gearbox 23 to rotate, which in turn drives the two driven shafts 24 to rotate in opposite directions at the same speed. At this time, the fixed eccentric block 31 and the moving eccentric block 34 generate centrifugal force as they rotate with the shaft. In the initial state, the presser foot rod 44 is in a low position under the action of the first return spring 47, the trapezoidal wedge block 46 is located at the narrowest point, and the two lever blocks 49 are pulled inward under the action of the spring, pushing the thrust separation bearing 41 and the sliding sleeve 33 to a certain axial position, so that the phase difference between the moving eccentric block 34 and the fixed eccentric block 31 is close to 180°, and most of their centrifugal forces cancel each other out, leaving only a small resultant vector. The vibration base 21 drives the cutting blade 25 to perform small-amplitude high-frequency vibration. When encountering thick materials, the presser foot rod 44 is relatively lifted by the material obstruction, driving the lifting slider 45 and the trapezoidal wedge block 46 to rotate in opposite directions. As the trapezoidal wedge 46 rises, the inclined surface of the trapezoidal wedge 46 presses the push block 49 to slide horizontally outward. The push block 49 pulls the thrust separation bearing 41 and the sliding sleeve 33 to move axially along the driven shaft 24 through the annular groove 42. The movement of the sliding sleeve 33 forces the moving eccentric block 34 to twist relative to the driven shaft 24 through the helical spline 32, reducing the phase difference between the moving eccentric block 34 and the fixed eccentric block 31. As the phase difference decreases, the sum of the centrifugal forces of the two gradually increases, and the amplitude of the vibration base 21 increases accordingly, thus adapting to the cutting requirements of thick materials. Conversely, when the material becomes thinner, the process is reversed, and the amplitude automatically decreases.

[0028] In a preferred embodiment, the mass of the moving eccentric block 34 is less than the mass of the fixed eccentric block 31; the mass ratio of the fixed eccentric block 31 to the moving eccentric block 34 is 1.3 to 1.8.

[0029] In this embodiment, if the mass difference is too small, the minimum amplitude will be too large, which may lead to overcutting when cutting thin materials; if the mass difference is too large, the vibration will not be stable enough, and the effective utilization rate of the adjustment range will be reduced.

[0030] In a preferred embodiment, the lever 49 includes an end block 491 slidably connected within the second linear guide rail 48, a lever 492 disposed below the end block 491, a lever fork 493 disposed below the lever 492, and a cylindrical pin 494 disposed on the fork corner of the lever fork 493 and connected to the annular groove 42; the depth of the annular groove 42 is not less than the maximum single amplitude.

[0031] In this embodiment, the end block 491 is slidably mounted on the second linear guide rail 48 as a connection between the shift block 49 and the horizontal guide mechanism in the drive adjustment assembly. The shape of the end block 491 can be set according to actual conditions, such as a rectangular block. The shift lever 492 is a transmission component connecting the end block 491 and the shift fork 493, transmitting the horizontal movement of the end block 491 to the shift fork 493. The material of the shift lever 492 can be high-strength alloy steel or heat-treated carbon steel to ensure that no plastic deformation occurs during high-frequency reciprocating motion. The connection between the shift lever 492 and the end block 491 and the shift fork 493... The mechanism is integrally molded; the shift fork 493 is an actuator with a forked structure located at the lower end of the shift lever 492, and its fork angle is designed to accommodate and drive the cylindrical pin 494; the cylindrical pin 494 is a columnar connector fixed on the fork angle of the shift fork 493 and embedded in the annular groove 42. Its outer diameter and the groove width of the annular groove 42 can adopt a transition fit or a small clearance fit to ensure that there is no idle stroke when transmitting thrust in the axial direction, while retaining the necessary movement margin in the vibration direction. The cylindrical pin 494 can be made of wear-resistant bearing steel, and the surface can be quenched or carburized to improve wear resistance. Since there is a maximum single amplitude displacement during vibration, the depth of the annular groove 42 must be sufficient to cover this displacement to ensure that when the vibration base 21 reaches the upper and lower limit positions, the cylindrical pin 494 can still slide within the internal space of the annular groove 42 and will not come out of the groove.

[0032] As a preferred embodiment, ball bearings are provided on the mating surfaces of the end block 491 and the trapezoidal wedge block 46.

[0033] In this embodiment, the ball bearing is a rolling friction element disposed between the inclined surfaces of the end block 491 and the trapezoidal wedge block 46 in contact with each other. During the amplitude adjustment process, the end block 491 and the trapezoidal wedge block 46 experience continuous relative sliding, and the ball bearing converts the sliding friction between the contact surfaces into rolling friction. The ball bearing can be made of high-hardness bearing steel, ceramic, or other wear-resistant materials. Its diameter and number can be set according to the actual load requirements and space dimensions. It can be arranged in a single row or in multiple rows in a staggered arrangement, effectively ensuring the uniformity of driving force transmission and avoiding jamming or jumping phenomena caused by friction fluctuations.

[0034] In a preferred embodiment, the T-type bevel gearbox 23 includes a housing 231, a main input shaft 232 connected to the output shaft of the drive motor 22 via a flexible coupling, a main gear 233 disposed at the lower end of the main input shaft 232, a driven gear 234 meshing with both sides of the main gear 233 and connected to the driven shaft 24, and an oil-sealed bearing 235 disposed in the housing 231 for passing through the main input shaft 232 and the driven shaft 24.

[0035] In this embodiment, the housing 231 is an outer shell structure that houses the gear transmission mechanism. Its material can be high-strength aluminum alloy or cast iron, or other metal materials with sufficient rigidity and shock absorption performance. It cooperates with the vibration base 21 to jointly constitute the core transmission cavity of the vibration system. Figure 8 As shown, the housing 231 has bearing housing holes inside for mounting the main input shaft 232 and the driven shaft 24. The upper end of the main input shaft 232 is connected to the output shaft of the drive motor 22 via a flexible coupling. This flexible coupling can be a plum blossom-shaped flexible coupling, a diaphragm coupling, or a tire coupling, etc. The lower end of the main input shaft 232 is fixedly equipped with a main gear 233, which can be a straight bevel gear or a spiral bevel gear. Its tooth surface is hardened to withstand high-frequency alternating loads. The main gear 233 meshes with two driven gears 234 simultaneously, forming a symmetrical transmission structure. This matching relationship ensures that the driven shafts 24 on the left and right sides can obtain absolutely the same speed and opposite rotational power, thereby counteracting the centrifugal force in the horizontal direction and preventing the machine head from resonating. The driven gears 234 are connected to the driven shafts 24 by means of flat keys, splines, or interference fits. After receiving torque from the main gears 233, the driven gears 234 drive the driven shafts 24 to rotate, thereby driving the eccentric block assembly 3 to work. The oil seal bearing 235 is installed in the bearing housing hole to pass through the main input shaft 232 and the driven shaft 24. It contains rolling elements to support the high-speed rotation of the shaft and has an integrated lip seal ring to prevent the lubricating oil inside the housing from leaking and external dust from entering. In high-frequency vibration environment, the oil seal bearing 235 can effectively maintain the stability of the lubrication environment and extend the service life of the gearbox.

[0036] As a preferred embodiment, the housing 231 and the vibration base 21 are integrally formed.

[0037] In this embodiment, the one-piece molding design ensures that the lower surface of the housing 231 and the upper surface of the vibration base 21 are continuously connected in terms of material, forming a rigid overall frame. This structural design allows the rotational power transmitted from the drive motor 22 to the driven shaft 24 via the T-shaped bevel gearbox 23 to be directly converted into the vertical vibration of the vibration base 21 through this integral structure, avoiding energy loss or delay caused by separate connections.

[0038] As a preferred embodiment, the included angle of the inclined surface of the trapezoidal wedge 46 is 15°~30°.

[0039] In this embodiment, the specific value of the included angle of the inclined surface of the trapezoidal wedge block 46 can be set according to the actual application scenario. However, if the included angle of the inclined surface is too small, although it can provide a large horizontal thrust amplification factor, it will result in a significant reduction in the effective adjustment stroke, which may not be able to cover the entire axial displacement of the sliding sleeve 33 required from the minimum amplitude to the maximum amplitude. In extreme cases, it is easy to generate mechanical self-locking due to the friction angle being greater than the wedge angle, causing the dial block 49 to be unable to retract smoothly under the action of the return spring. If the included angle of the inclined surface is too large, although a longer linear adjustment stroke can be obtained, it will greatly reduce the force transmission efficiency, resulting in the need for a large pressure foot lifting force to drive the dial block 49 to overcome resistance and move. This increases the requirements of the system on the stiffness of the first return spring 47 and the drive load, and may reduce the response sensitivity of the amplitude adjustment.

[0040] The drive motor, bevel gearbox, cutting tool, thrust release bearing, linear guide, flexible coupling, bearing, etc. in the above embodiments are common knowledge known to those skilled in the art, and therefore will not be described in detail.

[0041] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the present invention.

Claims

1. A vibration compensation system for a vibrating knife, characterized in that, include: The head housing (1) is fixedly installed on the crossbeam of the cutting bed; The vibration assembly (2) includes a vibration base (21) arranged in a U-shape on the inner top surface of the machine head housing (1), a drive motor (22) arranged vertically downward on the inner top surface of the machine head housing (1), a T-shaped bevel gearbox (23) arranged on the output shaft of the drive motor (22) and connected to the vibration base (21) at its lower end, two driven shafts (24) respectively arranged on the output ends of the T-shaped bevel gearbox (23) and passing through the side plate of the vibration base (21) via bearings, a cutter (25) is installed on the lower surface of the vibration base (21), and the vibration base (21) is made of leaf spring; The eccentric block assembly (3) includes a fixed eccentric block (31) fixedly disposed on the driven shaft (24), a spiral spline (32) disposed in the middle section of the driven shaft (24), a sliding sleeve (33) screwed onto the spiral spline (32), and a moving eccentric block (34) fixedly disposed on the sliding sleeve (33). The drive adjustment assembly (4) includes a thrust release bearing (41) disposed on the surface of the sliding sleeve (33) at a position that avoids the moving eccentric block (34), two annular grooves (42) disposed on the surface of the thrust release bearing (41), a first linear guide rail (43) vertically disposed on the inner side of the head housing (1), a lifting slider (45) slidably disposed on the first linear guide rail (43) and whose lower end is used to install the presser foot rod (44), and a trapezoidal wedge (46) disposed on the upper end of the lifting slider (45) and sleeved on the presser foot rod. (44) A first return spring (47) connected to the head housing (1) at the top and end, a second linear guide rail (48) horizontally arranged above the first linear guide rail (43), two slidable blocks (49) symmetrically arranged on the second linear guide rail (48) and connected at the bottom to the annular groove (42), and a second return spring (410) connected at both ends to the slidable block (49) and the inner end of the second linear guide rail (48) respectively. The slidable block (49) has a slope on the opposite side that cooperates with the trapezoidal wedge (46).

2. The vibration compensation system for a vibrating knife according to claim 1, characterized in that, The mass of the moving eccentric block (34) is less than the mass of the fixed eccentric block (31).

3. The vibration compensation system for a vibrating knife according to claim 2, characterized in that, The lever (49) includes an end block (491) slidably connected in the second linear guide (48), a lever (492) disposed below the end block (491), a lever fork (493) disposed below the lever (492), and a cylindrical pin (494) disposed on the fork corner of the lever fork (493) and connected to the annular groove (42).

4. The vibration compensation system for a vibrating knife according to claim 3, characterized in that, The depth of the annular groove (42) is not less than the maximum single amplitude.

5. The vibration compensation system for a vibrating knife according to claim 3, characterized in that, Ball bearings are provided on the mating surfaces of the end block (491) and the trapezoidal wedge block (46).

6. The vibration amplitude compensation system for a vibrating knife according to claim 1, characterized in that, The T-type bevel gearbox (23) includes a housing (231), a main input shaft (232) connected to the output shaft of the drive motor (22) via a flexible coupling, a main gear (233) located at the lower end of the main input shaft (232), a driven gear (234) meshing with both sides of the main gear (233) and connected to the driven shaft (24), and an oil-sealed bearing (235) located in the housing (231) for passing through the main input shaft (232) and the driven shaft (24).

7. The vibration compensation system for a vibrating knife according to claim 6, characterized in that, The housing (231) and the vibration base (21) are integrally formed.

8. The vibration amplitude compensation system for a vibrating knife according to claim 2, characterized in that, The mass ratio of the fixed eccentric block (31) to the moving eccentric block (34) is 1.3 to 1.

8.

9. The vibration amplitude compensation system for a vibrating knife according to claim 1, characterized in that, The included angle of the inclined plane of the trapezoidal wedge (46) is 15°~30°.

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