A milling machine with convenient rotary fixing for pelletizer processing

Abstract

This invention discloses a milling machine for granulation machining that facilitates rotational fixation, relating to the field of milling machine technology. It includes a base with a rotary worktable on its top outer wall, and further includes a locking mechanism located on one outer wall of the rotary worktable. The locking mechanism comprises a worm gear, a connecting bracket, a mounting cylinder, a tapered sleeve, an elastic sleeve, a guide cylinder, a guide rod, a locking ring, a return spring, a connecting cylinder, a fixed disc, and a limiting groove. The locking mechanism is used for axial positioning and locking of the worm gear. The mounting cylinder and the connecting bracket are connected by bearings. This invention discloses a milling machine for granulation machining that facilitates rotational fixation, which can center and tighten the worm gear when it becomes loose due to long-term operation, thereby ensuring the positioning accuracy and long-term operational stability of the rotary worktable under all working conditions.

Description

Technical Field

[0001] This invention relates to the field of milling machine technology, and more particularly to a milling machine for granulation machining that is easy to rotate and fix. Background Technology

[0002] In the rotary table of CNC milling machines, boring machines and other machine tools, the axial positioning of the worm gear is usually achieved by a lock nut and washer structure. In order to prevent the lock nut from loosening during working vibration, the existing technology generally adopts an open lock nut structure. By opening several grooves in the diameter direction of the nut, the set screw is screwed in during assembly, which forces the nut to produce elastic deformation in the grooved part. The additional friction of the thread pair generated by the deformation is used to prevent loosening.

[0003] However, in practical applications, although the locking nut appears to be locked, it does not actually generate effective anti-loosening friction. When the rotary table frequently rotates in both forward and reverse directions during processing, the nut gradually loosens under alternating impact loads, causing the worm to move axially. This can lead to rotary table vibration, inability to synchronize with the servo motor, loss of control when returning to the reference point, and abnormally increased meshing clearance between the worm wheel and the worm. Impact collisions may occur during forward and reverse switching, damaging the transmission pair surface and accelerating the decline in accuracy. Summary of the Invention

[0004] This invention discloses a milling machine for easy rotation and fixation in granulation processing. It aims to solve the technical problem that, in practical applications, the locking nut appears to be locked, but in reality, it does not generate effective anti-loosening friction. When the rotary table frequently rotates forward and reverse during processing, the nut gradually loosens under alternating impact loads, causing the worm gear to move axially. This can lead to rotary table vibration, inability to synchronize with the servo motor, loss of control when returning to the reference point, and an abnormally increased meshing clearance between the worm wheel and worm gear. Impact collisions may occur during forward and reverse switching, damaging the transmission pair surface and accelerating the decline in accuracy.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] A milling machine for granulation processing that facilitates rotation and fixation includes a base, a rotary worktable provided on the top outer wall of the base, and further includes:

[0007] Locking mechanism: Located on one outer wall of the rotary table; the locking mechanism includes a worm gear, connecting bracket, mounting cylinder, tapered sleeve, elastic sleeve, guide cylinder, guide rod, locking ring, return spring, connecting cylinder, fixed plate, and limiting groove. The locking mechanism is used for axial positioning and locking of the worm gear. The mounting cylinder and the connecting bracket are connected by bearings. The elastic sleeve is coaxially disposed inside the mounting cylinder. The mounting cylinder is fixedly installed on the fixed plate. One end of the elastic sleeve has a tapered inner hole for fitting and gripping the outer wall of the tapered sleeve. Several axial slots are opened along the circumferential direction on the cylinder wall of the elastic sleeve. The guide rod... A guide rod is coaxially inserted inside the guide cylinder. One end of the guide rod is fixedly connected to the tapered sleeve, and the other end of the guide rod extends outside the guide cylinder. A locking ring is threaded to the outer wall of the guide rod and connected to the guide cylinder via a bearing. The outer wall of the guide cylinder is fixedly connected to the elastic sleeve. A return spring is fitted onto the guide rod, with one end abutting against the inner end face of the guide cylinder and the other end abutting against the tapered sleeve. The connecting cylinder is fixedly connected to the locking ring. A limiting groove is formed on the fixed plate, and the limiting groove is used to limit the axial displacement stroke of the elastic sleeve.

[0008] Anti-loosening mechanism: Located on one side of the locking mechanism, used to prevent the locking mechanism from loosening during working vibration;

[0009] Axial preload mechanism: located inside the rotary table.

[0010] The above technical solution enables centering and tightening of the worm gear when it becomes loose due to long-term operation, thus ensuring the positioning accuracy and long-term operational stability of the rotary table under all working conditions. Specifically, during operation, the axial preload mechanism built into the rotary table is always in operation, continuously applying an axial thrust towards the free end of the worm gear. This thrust eliminates the inherent tooth backlash between the worm gear and the worm wheel, improving transmission rigidity. When the rotary table needs to be fixed at a certain angle for milling, the locking mechanism intervenes. The control system (a servo motor or stepper motor is installed on the machine tool, with a small gear meshing with the first gear on its output shaft, and the CNC system sends pulse signals to control the motor's rotation) drives the first gear fixedly connected to the connecting cylinder to rotate. This causes the connecting cylinder to drive the locking ring to rotate synchronously. Because the locking ring and the guide rod are threaded together, and the rotation of the locking ring forces the guide cylinder to move axially along the guide rod, it simultaneously pushes the end of the elastic sleeve. The tapered inner hole gradually wedges into the outer tapered surface of the tapered sleeve. Due to the axial groove on its cylinder wall, the elastic sleeve has radial contraction elasticity, and its axial displacement is limited within a predetermined stroke by the limiting groove on the fixed plate. Therefore, the wedging action of the tapered sleeve forces the elastic sleeve to contract radially inward evenly, thereby tightly gripping the fixed plate and the corresponding worm shaft section. Thus, even if the clearance at the rear end of the worm increases due to long-term operation, the locking action can recenter and grip this section, achieving simultaneous locking of axial displacement and rotational freedom. After locking, the anti-loosening mechanism dynamically self-locks and prevents loosening when the locking ring stops rotating, ensuring that the locking state does not loosen due to vibration under long-term heavy-load cutting conditions. When the angle needs to be changed, the first gear is rotated in the opposite direction, the locking ring reverses, and the return spring fitted on the guide rod releases the compressive potential energy, actively pushing the elastic sleeve away from the tapered sleeve. The elastic sleeve then relies on its own elasticity to restore the radial dimension to loosen the tapered sleeve and the fixed plate, and the rotary table returns to the free indexing state.

[0011] In a preferred embodiment, the anti-loosening mechanism includes a mounting plate, which is fixedly connected to the connecting bracket. A second gear, a second connecting rod, and a ratchet are provided on one outer wall of the mounting plate. Both the second gear and the ratchet are connected to the mounting plate via bearings. The second gear meshes with the first gear. A first connecting rod is movably connected to the eccentric portion of the second gear. The second connecting rod is movably connected to the mounting plate. One end of the first connecting rod and one end of the second connecting rod are hinged together. The second connecting rod is also provided with a first pawl and a second pawl, which respectively cooperate with the ratchet.

[0012] In this scheme, when the system drives the first gear to rotate, since the first gear and the second gear are distributed vertically and mesh with each other, the rotation of the first gear will synchronously and in the opposite direction drive the second gear to rotate. The first gear directly drives the locking ring through the connecting cylinder to achieve the clamping of the worm. The circumferential rotation of the second gear is transmitted through the first connecting rod movably connected to it. One end of the first connecting rod and one end of the second connecting rod are hinged to each other, and the second connecting rod is movably connected to the mounting plate, thereby converting the continuous rotation of the second gear into the reciprocating swing motion of the second connecting rod around its hinge point on the mounting plate.

[0013] When the first gear drives the locking ring to rotate in the clamping direction, the second connecting rod swings accordingly. At this time, the shorter second pawl will slide over the tooth tip of the ratchet without causing anti-reverse interference, allowing the ratchet to rotate normally, thus ensuring that the locking action is completed without any obstruction. When the alternating impact load attempts to force the first gear to rotate slightly in the loosening direction, the first gear will drive the second gear in the opposite direction, thereby causing the second connecting rod to swing in the opposite direction through the first connecting rod. At this time, the longer first pawl will be more firmly engaged in the corresponding tooth groove of the ratchet due to the larger swing amplitude, generating mechanical rigid anti-reverse, completely locking the rotational freedom of the second gear. Since the second gear and the first gear are always meshed, locking the second gear is equivalent to locking the first gear, thus completely suppressing the loosening tendency of the locking ring through the connecting cylinder. That is, the greater the impact torque, the tighter the first pawl and the second pawl wedge in, and the stronger the anti-loosening effect.

[0014] In a preferred embodiment, the axial preload mechanism includes a fixed cylinder and an end cap. The fixed cylinder is fixed inside the rotary table. A locking block is provided inside the fixed cylinder and is fixedly connected to the end cap. The end cap is fixedly connected to the fixed plate. A first bearing is also provided inside the fixed cylinder. A shoulder is provided on the optical axis section of the worm gear. A disc spring assembly is provided between the first bearing and the shoulder. A disc spring sleeve is provided on the optical axis section of the worm gear, and a sliding bearing is provided between the disc spring sleeve and the optical axis section of the worm gear. One end of the disc spring sleeve is in contact with the end face of the disc spring assembly, and the other end of the disc spring sleeve abuts against the shoulder.

[0015] In this design, during use, a disc spring assembly fitted onto the worm shaft section transmits elastic force to the worm shoulder via a disc spring sleeve, applying a continuous and constant axial thrust to the worm. This actively eliminates the tooth backlash between the worm and worm wheel and provides a reference preload for subsequent locking. During this process, the disc spring sleeve engages with the worm shaft section through a sliding bearing within its inner bore, allowing the disc spring sleeve to slide axially without rotating with the worm. This separates the axial thrust transmission from the rotational motion, ensuring stable preload application and preventing fatigue from rotational friction. When the worm is subjected to a reverse axial load or axial movement occurs due to long-term wear of the rear bearing, the worm shoulder... When the disc spring assembly is compressed by the disc spring sheath, the disc spring assembly automatically extends or retracts to dynamically compensate for displacement and maintain a constant preload. At the same time, the connecting block fixed to the end of the disc spring assembly near the shoulder extends out of the cylinder through the observation groove on the outer wall of the fixed cylinder. When the disc spring assembly is compressed or rebounds, the connecting block drives the pointer to slide synchronously along the axial direction of the observation groove. This allows the operator to obtain the current compression deformation of the disc spring assembly in real time and quantitatively by reading the pointer position on the scale plate on the outer wall of the fixed cylinder. This indirectly determines the magnitude of the preload and the degree of bearing wear. By comparing the difference in pointer readings before and after locking, the axial elastic relief of the worm gear under the locking force can also be accurately determined, providing data for machining compensation parameters.

[0016] In a preferred embodiment, two axially extending observation slots are provided on the outer wall of the fixed cylinder, and two connecting blocks are provided at one end of the disc spring assembly near the shoulder. The connecting blocks extend out of the fixed cylinder through the observation slots, and a pointer is provided on the connecting blocks. A scale plate is provided on the outer wall of the fixed cylinder corresponding to the position of the pointer, and the pointer is used in conjunction with the scale plate.

[0017] In this design, when the worm shaft shoulder pushes the disc spring assembly to compress axially, the two connecting blocks slide simultaneously along the observation groove, effectively limiting the radial wobble or tilt of the disc spring assembly end face during compression. This ensures that the compression movement of the disc spring assembly always proceeds along the axis of the fixed cylinder, avoiding jamming or abnormal wear caused by disc spring misalignment. Compared to traditional disc spring preload mechanisms where the compression state of the disc spring assembly is enclosed inside the fixed cylinder during operation, making it impossible for operators to know the actual compression amount without disassembling the machine, or to determine whether the preload has weakened or the bearings are worn, this design can directly convert the axial compression amount of the internal disc spring assembly into the visible displacement of the external pointer on the scale plate, achieving real-time, visual, and accurate measurement of the disc spring assembly compression amount.

[0018] The beneficial effects of this invention are:

[0019] 1. Compared with the traditional locking method of pressing the end of the nut against the fixed end of the worm, the present invention adopts the wedge-shaped fit of the tapered sleeve and the elastic sleeve, and locks the worm shaft section by radially contracting the elastic sleeve. This fundamentally avoids tooth surface crushing, deformation or pitting caused by locking stress, and effectively protects the precision and life of the transmission pair.

[0020] 2. This invention uses a ratchet in conjunction with a first pawl and a second pawl. Compared with friction-based anti-loosening methods such as spring washers and end face teeth, its anti-loosening effect does not depend on the stability of the friction coefficient. Once the first pawl is engaged in the ratchet tooth groove, a mechanical rigid interlock is formed. Any tendency of the locking ring to loosen or rotate is instantly cut off, avoiding the situation where traditional locking methods gradually loosen due to the decrease in the friction coefficient under alternating impact loads. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of a milling machine for granulation processing that is easy to rotate and fix, as proposed in this invention.

[0022] Figure 2 This is a cross-sectional view of a milling machine for granulation processing that is easy to rotate and fix, as proposed in this invention.

[0023] Figure 3 This is a schematic diagram of the worm gear and worm shaft structure of a milling machine for easy rotation and fixation in granulation processing, as proposed in this invention.

[0024] Figure 4 for Figure 3 Enlarged schematic diagram of the structure at point A and schematic diagram of the anti-loosening mechanism.

[0025] Figure 5 This is a cross-sectional view of the locking mechanism structure of a milling machine for easy rotation and fixation in granulation processing, as proposed in this invention.

[0026] Figure 6 This is a schematic diagram of the guide cylinder structure of a milling machine for easy rotation and fixation in granulation processing, as proposed in this invention.

[0027] Figure 7 This is a schematic diagram of an elastic sleeve structure for a milling machine that is easy to rotate and fix in granulation, as proposed in this invention.

[0028] Figure 8 This is a schematic diagram of the fixed cylinder structure of a milling machine for granulation processing that is easy to rotate and fix, as proposed in this invention.

[0029] Figure 9 for Figure 8 Enlarged schematic diagram of the structure at point B.

[0030] Figure 10This is a schematic diagram of the axial preload mechanism of a milling machine for easy rotation and fixation in granulation processing, as proposed in this invention.

[0031] In the diagram: 1. Base; 2. Rotary worktable; 3. Motor; 4. Fixing frame; 5. Worm gear; 6. Worm; 7. Fixing cylinder; 8. Connecting bracket; 9. Mounting plate; 10. Ratchet; 11. Mounting cylinder; 12. First gear; 13. Second gear; 14. First connecting rod; 15. First pawl; 16. Second connecting rod; 17. Second pawl; 18. Return spring; 19. Guide cylinder; 20. Guide rod; 21. Elastic sleeve; 22. Connecting cylinder; 23. Fixing plate; 24. Limiting groove; 25. Locking ring; 26. End cap; 27. Observation groove; 28. Scale plate; 29. ​​Pointer; 31. Locking pressure block; 32. Disc spring sleeve; 33. Disc spring assembly; 34. Shoulder; 35. First bearing; 36. Washer; 37. Tapered sleeve. Detailed Implementation

[0032] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0033] Reference Figure 1 , Figure 2 , Figure 3 , Figure 5 , Figure 6 and Figure 7 A milling machine for easy rotation and fixation in granulation processing includes a base 1, a rotary worktable 2 provided on the top outer wall of the base 1, and further includes:

[0034] Locking mechanism: Located on one outer wall of the rotary table 2; the locking mechanism includes a worm gear 6, a connecting bracket 8, a mounting cylinder 11, a tapered sleeve 37, an elastic sleeve 21, a guide cylinder 19, a guide rod 20, a locking ring 25, a return spring 18, a connecting cylinder 22, a fixed plate 23, and a limiting groove 24. The locking mechanism is used for axial positioning and locking of the worm gear 6. The mounting cylinder 11 and the connecting bracket 8 are connected by bearings. The elastic sleeve 21 is coaxially arranged inside the mounting cylinder 11. The mounting cylinder 11 is fixedly installed on the fixed plate 23. One end of the elastic sleeve 21 is provided with a tapered inner hole, which is used to fit and hold the outer wall of the tapered sleeve 37. Several axial grooves are opened along the circumferential direction on the cylinder wall of the elastic sleeve 21. The guide rod 20 is coaxially inserted inside the guide cylinder 19. One end of the guide rod 20 is fixedly connected to the tapered sleeve 37, and the other end of the guide rod 20 extends out of the guide cylinder 19. The locking ring 25 is threadedly connected to the outer wall of the guide rod 20. The locking ring 25 is connected to the guide cylinder 19 through a bearing. The outer wall of the guide cylinder 19 is fixedly connected to the elastic sleeve 21. The return spring 18 is fitted on the guide rod 20, and one end of the return spring 18 abuts against the inner end face of the guide cylinder 19. The other end of the return spring 18 abuts against the tapered sleeve 37. The connecting cylinder 22 is fixedly connected to the locking ring 25. The limiting groove 24 is opened on the fixed plate 23. The limiting groove 24 is used to limit the axial displacement stroke of the elastic sleeve 21.

[0035] Anti-loosening mechanism: Located on one side of the locking mechanism, it is used to prevent the locking mechanism from loosening during working vibrations;

[0036] Axial preload mechanism: located inside the rotary table 2.

[0037] The rotary table 2 has a motor 3 on its outer wall away from the locking mechanism. The free end of the worm gear 6 is fixedly connected to the output shaft of the motor 3. The limiting groove 24 is an elongated through groove extending along the axial direction of the mounting cylinder 11. The limiting groove 24 is used to limit the maximum axial displacement of the elastic sleeve 21. By cooperating with the elastic sleeve 21, the limiting groove 24 strictly defines the maximum axial advance stroke of the elastic sleeve 21, ensuring that it always works within the elastic deformation zone. This ensures the reliable reuse of the locking mechanism in several operation cycles and avoids equipment damage due to misoperation.

[0038] In the specific implementation process, a connecting cylinder 22 is fixedly connected to the outer wall of the locking ring 25 away from the guide cylinder 19. A first gear 12 is fixedly installed at the end of the connecting cylinder 22 away from the locking ring 25. The operator can drive the first gear 12 without having to insert the tool into the narrow space inside the rotary table 2, which reduces the difficulty of operation and safety hazards, and also provides more operating space for daily inspection, lubrication and maintenance.

[0039] The rotary table 2 has a fixed frame 4 inside, and a worm wheel 5 is connected to the fixed frame 4 through a bearing. The worm wheel 5 works in conjunction with the worm 6.

[0040] Specifically, during the operation, the axial preload mechanism built into the rotary table 2 is always in operation, continuously applying an axial thrust to the worm 6 pointing towards the free end. This thrust can eliminate the inherent tooth backlash between the worm 6 and the worm wheel 5, thereby improving the transmission rigidity.

[0041] When the rotary table 2 needs to be fixed at a certain angle for milling, the locking mechanism intervenes. The control system (a servo motor 3 or stepper motor 3 is installed on the machine tool, and a small gear meshing with the first gear 12 is installed on its output shaft. The CNC system sends pulse signals to control the rotation of the motor 3) drives the first gear 12, which is fixedly connected to the connecting cylinder 22, to rotate. As a result, the connecting cylinder 22 drives the locking ring 25 to rotate synchronously. Since the locking ring 25 and the guide rod 20 are threaded together, and the rotation of the locking ring 25 forces the guide cylinder 19 to move axially along the guide rod 20, it pushes the tapered inner hole at the end of the elastic sleeve 21 to gradually wedge into the outer tapered surface of the tapered sleeve 37. Because the elastic sleeve 21 has radial contraction elasticity due to the axial groove on its cylinder wall, and its axial displacement is limited within a predetermined stroke by the limiting groove 24 on the fixed plate 23, the wedging action of the tapered sleeve 37 forces the elastic sleeve 21 to contract radially inward evenly, thereby tightly gripping the fixed plate 23 and... The corresponding worm gear 6 optical shaft section is connected, so even if the clearance at the rear end of the worm gear 6 increases due to long-term operation, the locking action can recenter and tighten this section, achieving simultaneous locking of axial displacement and rotational freedom. After locking, the anti-loosening mechanism dynamically self-locks and prevents loosening when the locking ring 25 stops rotating, ensuring that the locking state will not loosen due to vibration under long-term heavy-load cutting conditions. When the angle needs to be changed, the first gear 12 is rotated in the opposite direction, the locking ring 25 is reversed, and the return spring 18 fitted on the guide rod 20 releases the compressive potential energy, actively pushing the elastic sleeve 21 away from the tapered sleeve 37. The elastic sleeve 21 then relies on its own elasticity to restore the radial dimension to loosen the tapered sleeve 37 and the fixed plate 23, and the rotary table 2 returns to the free indexing state. In summary, this device can center and tighten the worm gear 6 when it becomes loose due to long-term operation, thereby ensuring the positioning accuracy and long-term operational stability of the rotary table 2 under all working conditions.

[0042] Reference Figure 3 and Figure 4In a preferred embodiment, the anti-loosening mechanism includes a mounting plate 9, which is fixedly connected to a connecting bracket 8. A second gear 13, a second connecting rod 16, and a ratchet 10 are provided on one outer wall of the mounting plate 9. The second gear 13 and the ratchet 10 are both connected to the mounting plate 9 through bearings. The second gear 13 meshes with the first gear 12. A first connecting rod 14 is movably connected to the eccentric part of the second gear 13. The second connecting rod 16 is movably connected to the mounting plate 9. One end of the first connecting rod 14 is hinged to one end of the second connecting rod 16. The second connecting rod 16 is also provided with a first pawl 15 and a second pawl 17. The first pawl 15 and the second pawl 17 are respectively used in conjunction with the ratchet 10.

[0043] The first gear 12 and the second gear 13 are arranged vertically, which makes full use of the vertical space. When the first gear 12 and the second gear 13 mesh, the meshing area is located on the side or below the two gears. Excess cutting fluid and small chips can drip off naturally under the action of gravity and are not easy to accumulate in the tooth groove.

[0044] It should be noted that the vertical distribution of the first gear 12 and the second gear 13 is based on the vertical direction of the rotary table 2, that is, the axes of the first gear 12 and the second gear 13 are parallel to the horizontal plane, and the two are arranged vertically along the direction of gravity.

[0045] It is particularly important to note that the length of the second pawl 17 is less than that of the first pawl 15, and the first pawl 15 and the second pawl 17 respectively engage with different tooth positions of the ratchet 10. The shorter second pawl 17, due to its limited length, can only touch the sliding surface of the tooth top of the ratchet 10 when it swings with the second connecting rod 16. This allows the ratchet 10 to rotate freely with the second gear 13 without any jamming. The longer first pawl 15, due to its greater extension distance, can have its tip pass over the tooth top and firmly engage with the tooth root of the ratchet 10 when swinging in the opposite direction. Since the first pawl 15 and the second pawl 17 correspond to different tooth positions, the tooth position into which the second pawl 17 engages is offset from the tooth position through which the first pawl 15 slides. This forms a double anti-reverse constraint with different phases on the circumference of the ratchet 10. Once the first pawl 15 locks into the tooth groove, the reverse rotation is instantly and rigidly cut off, completely preventing any micro-loosening of the locking ring 25 under alternating impact load.

[0046] Specifically, when the system drives the first gear 12 to rotate, since the first gear 12 and the second gear 13 are distributed vertically and mesh with each other, the rotation of the first gear 12 will synchronously and in the opposite direction drive the second gear 13 to rotate. The first gear 12 directly drives the locking ring 25 through the connecting cylinder 22 to clamp the worm 6. The circumferential rotation of the second gear 13 is transmitted through the first connecting rod 14 movably connected to it. One end of the first connecting rod 14 is hinged to one end of the second connecting rod 16, and the second connecting rod 16 is movably connected to the mounting plate 9, thereby converting the continuous rotation of the second gear 13 into the reciprocating swing motion of the second connecting rod 16 around its hinge point on the mounting plate 9.

[0047] When the first gear 12 drives the locking ring 25 to rotate in the clamping direction, the second connecting rod 16 swings accordingly. At this time, the shorter first pawl 15 will slide over the tooth tip of the ratchet 10 without generating anti-reverse interference, allowing the ratchet 10 to rotate normally, thus ensuring that the locking action is completed without any obstruction. When the alternating impact load attempts to force the first gear 12 to produce a micro-rotation in the loosening direction, the first gear 12 will drive the second gear 13 in the opposite direction, thereby driving the second connecting rod 16 to swing in the opposite direction through the first connecting rod 14. When the ratchet 17 moves, the longer second pawl 17 will be more vibrating and will be more firmly engaged in the corresponding tooth groove of the ratchet 10 in advance, generating mechanical rigidity to prevent backlash and completely locking the rotational freedom of the second gear 13. Since the second gear 13 is always meshed with the first gear 12, locking the second gear 13 is equivalent to locking the first gear 12. In turn, the loosening tendency of the locking ring 25 is completely suppressed by the connecting cylinder 22. That is, the greater the impact torque, the tighter the first pawl 15 and the second pawl 17 are wedged in, and the stronger the anti-loosening effect.

[0048] Reference Figure 3 , Figure 8 , Figure 9 and Figure 10 In a preferred embodiment, the axial preload mechanism includes a fixed cylinder 7 and an end cap 26. The fixed cylinder 7 is fixed inside the rotary table 2. A locking block 31 is provided inside the fixed cylinder 7. The locking block 31 is fixedly connected to the end cap 26. The end cap 26 is fixedly connected to the fixed plate 23. A first bearing 35 is also provided inside the fixed cylinder 7. A shoulder 34 is provided on the optical axis section of the worm gear 6. A disc spring assembly 33 is provided between the first bearing 35 and the shoulder 34. A disc spring sleeve 32 is provided on the optical axis section of the worm gear 6. A sliding bearing is provided between the disc spring sleeve 32 and the optical axis section of the worm gear 6. One end of the disc spring sleeve 32 is in contact with the end face of the disc spring assembly 33, and the other end of the disc spring sleeve 32 abuts against the shoulder 34.

[0049] Among them, a washer 36 is provided between the locking block 31 and the first bearing 35. A fixing groove is provided on the locking block 31, and the worm gear 6 is rotatably inserted into the fixing groove. The washer 36 between the locking block 31 and the first bearing 35 buffers the axial impact and compensates for the dimensional chain tolerance, ensuring that the first bearing 35 maintains axial stability when the preload fluctuates. At the same time, the fixing groove on the locking block 31 provides a rotation avoidance channel for the worm gear 6.

[0050] In the specific implementation process, two axially extending observation slots 27 are opened on the outer wall of the fixed cylinder 7. Two connecting blocks are provided at the end of the disc spring assembly 33 near the shoulder 34. The connecting blocks extend out of the fixed cylinder 7 through the observation slots 27. A pointer 29 is provided on the connecting blocks. A scale plate 28 is provided on the outer wall of the fixed cylinder 7 at the position corresponding to the pointer 29. The pointer 29 and the scale plate 28 are used in conjunction. When the shoulder 34 of the worm gear 6 pushes the disc spring assembly 33 to compress axially, the two connecting blocks slide along the observation slots 27 at the same time, which effectively limits the radial wobble of the end face of the disc spring assembly 33 during the compression process. The mechanism can be tilted to ensure that the compression movement of the disc spring assembly 33 always follows the axis of the fixed cylinder 7, avoiding jamming or abnormal wear caused by the tilt of the disc spring. Compared with the traditional disc spring preload mechanism, where the compression state of the disc spring assembly 33 is enclosed inside the fixed cylinder 7 during operation, and the operator cannot know its actual compression without disassembling the machine, and cannot judge whether the preload has weakened or whether the bearing is worn, this mechanism can directly convert the axial compression of the internal disc spring assembly 33 into the visible displacement of the external pointer 29 on the scale plate 28, realizing real-time visual and accurate measurement of the compression of the disc spring assembly 33.

[0051] It should be noted that the axial length of the observation slot 27 should not be less than the maximum working stroke of the disc spring assembly 33.

[0052] In addition, it should be clarified that the elastic sleeve 21 of the locking mechanism does not directly grip the worm 6. Since the end cover 26 of the axial preload mechanism is fixedly connected to the fixed plate 23 of the locking mechanism, when the locking mechanism is activated, the elastic sleeve 21 contracts radially and grips the fixed plate 23. After the rotational freedom of the fixed plate 23 is constrained, the braking effect is transmitted to the disc spring assembly 33 inside the axial preload mechanism and the shoulder 34 of the worm 6 through the end cover 26 and the locking pressure block 31, so that the axial movement of the worm 6 is locked. Since the rotational movement of the worm 6 in the worm wheel 5 is inevitably accompanied by axial force, the axial locking is equivalent to the indirect constraint of the rotational freedom, thus achieving reliable locking of the rotational freedom of the worm 6.

[0053] Specifically, in use, the disc spring assembly 33, which is sleeved on the optical shaft section of the worm 6, transmits the elastic force to the shoulder 34 of the worm 6 through the disc spring sleeve 32, applying a continuous and constant axial thrust to the worm 6. This actively eliminates the tooth backlash between the worm 6 and the worm wheel 5 and provides a reference preload for subsequent locking. During this process, the disc spring sleeve 32 cooperates with the optical shaft section of the worm 6 through the sliding bearing set in its inner hole, so that the disc spring sleeve 32 only slides axially and does not rotate with the worm 6. This achieves the separation of axial thrust transmission and rotational motion, which not only ensures the stable application of preload but also avoids the disc spring assembly 33 from overheating and fatigue due to rotational friction.

[0054] When the worm 6 is subjected to a reverse axial load or axial movement occurs due to long-term wear of the rear bearing, the shoulder 34 of the worm 6 compresses the disc spring assembly 33 through the disc spring sleeve 32. The disc spring assembly 33 automatically extends or retracts to dynamically compensate for the displacement and maintain a constant preload. At the same time, the connecting block fixed to the end of the disc spring assembly 33 near the shoulder 34 extends out of the cylinder through the observation groove 27 on the outer wall of the fixed cylinder 7. When the disc spring assembly 33 is compressed or rebounds, the connecting block drives the pointer 29 to slide synchronously axially along the observation groove 27. This allows the operator to obtain the current compression deformation of the disc spring assembly 33 in real time and quantitatively by reading the position of the pointer 29 on the scale plate 28 on the outer wall of the fixed cylinder 7. This indirectly determines the magnitude of the preload and the degree of bearing wear. By comparing the difference in the readings of the pointer 29 before and after locking, the axial elastic relief of the worm 6 under the action of the locking force can also be accurately obtained, providing data for processing compensation parameters.

[0055] Working principle: When the rotary table 2 needs to be fixed at a certain angle for milling, the locking mechanism intervenes. The control system installs a servo motor 3 or stepper motor 3 on the machine tool, and a small gear meshing with the first gear 12 is installed on its output shaft. The CNC system sends pulse signals to control the rotation of the motor 3, which drives the first gear 12, which is fixedly connected to the connecting cylinder 22, to rotate. As a result, the connecting cylinder 22 drives the locking ring 25 to rotate synchronously. Since the locking ring 25 and the guide rod 20 are threaded together, and the rotation of the locking ring 25 forces the guide cylinder 19 to move axially along the guide rod 20, it pushes the tapered inner hole at the end of the elastic sleeve 21 to gradually wedge into the outer tapered surface of the tapered sleeve 37. Because the elastic sleeve 21 has radial contraction elasticity due to the axial groove on its cylinder wall, and its axial displacement is limited within a predetermined stroke by the limiting groove 24 on the fixed plate 23, the tapered sleeve 37... The wedging action forces the elastic sleeve 21 to contract radially inward evenly, thereby tightly gripping the fixed disk 23 and the corresponding worm gear 6 shaft section. Therefore, even if the clearance at the rear end of the worm gear 6 increases due to long-term operation, the locking action can recenter and grip this section, achieving simultaneous locking of axial displacement and rotational freedom. After locking, the anti-loosening mechanism dynamically self-locks and prevents loosening when the locking ring 25 stops rotating, ensuring that the locking state will not loosen due to vibration under long-term heavy-load cutting conditions. When the angle needs to be changed, the first gear 12 is rotated in the opposite direction, the locking ring 25 is reversed, and the return spring 18 fitted on the guide rod 20 releases the compressive potential energy, actively pushing the elastic sleeve 21 away from the tapered sleeve 37. The elastic sleeve 21 then relies on its own elasticity to restore the radial dimension to loosen the tapered sleeve 37 and the fixed disk 23, and the rotary table 2 returns to the free indexing state.

[0056] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A milling machine for easy rotation fixation for pelletizer processing comprising a base (1), characterized in that, The base (1) has a rotary worktable (2) on its top outer wall, and also includes: Locking mechanism: Located on one outer wall of the rotary table (2); the locking mechanism includes a worm gear (6), a connecting bracket (8), a mounting cylinder (11), a cone sleeve (37), an elastic sleeve (21), a guide cylinder (19), a guide rod (20), a locking ring (25), a return spring (18), a connecting cylinder (22), a fixed plate (23), and a limiting groove (24). The locking mechanism is used for axial positioning and locking of the worm gear (6). The mounting cylinder (11) is connected to the connecting bracket (8) by a bearing. The elastic sleeve (21) is coaxially arranged inside the mounting cylinder (11). The mounting cylinder (11) is fixedly installed on the fixed plate (23). One end of the elastic sleeve (21) is provided with a tapered inner hole. The tapered inner hole is used to fit and hold the outer wall of the cone sleeve (37). Several axial slots are opened along the circumferential direction on the cylinder wall of the elastic sleeve (21). The guide rod (20) is coaxially arranged with the connecting bracket (8) and the connecting bracket (8). The shaft passes through the inside of the guide cylinder (19). One end of the guide rod (20) is fixedly connected to the tapered sleeve (37), and the other end of the guide rod (20) extends out of the outside of the guide cylinder (19). The locking ring (25) is threadedly connected to the outer wall of the guide rod (20). The locking ring (25) is connected to the guide cylinder (19) through a bearing. The outer wall of the guide cylinder (19) is fixedly connected to the elastic sleeve (21). The return spring (18) is fitted on the guide rod (20), and one end of the return spring (18) abuts against the inner end face of the guide cylinder (19). The other end of the return spring (18) abuts against the tapered sleeve (37). The connecting cylinder (22) is fixedly connected to the locking ring (25). The limiting groove (24) is opened on the fixed plate (23). The limiting groove (24) is used to limit the axial displacement stroke of the elastic sleeve (21). Anti-loosening mechanism: Located on one side of the locking mechanism, used to prevent the locking mechanism from loosening during working vibration; Axial preload mechanism: located inside the rotary table (2).

2. The milling machine for easy rotation and fixation in granulation processing according to claim 1, characterized in that, The rotary worktable (2) has a motor (3) on the outer wall away from the locking mechanism. The free end of the worm (6) is fixedly connected to the output shaft of the motor (3). The limiting groove (24) is an elongated through groove extending along the axial direction of the mounting cylinder (11). The limiting groove (24) is used to limit the maximum axial displacement of the elastic sleeve (21).

3. A milling machine for easy rotation and fixation in granulation processing according to claim 2, characterized in that, A connecting cylinder (22) is fixedly connected to the outer wall of the locking ring (25) away from the guide cylinder (19), and a first gear (12) is fixedly provided at the end of the connecting cylinder (22) away from the locking ring (25).

4. A milling machine for easy rotation and fixation in granulation processing according to claim 3, characterized in that, The rotary worktable (2) is equipped with a fixed frame (4) inside. A worm wheel (5) is connected to the fixed frame (4) through a bearing. The worm wheel (5) works in conjunction with the worm (6).

5. A milling machine for easy rotation and fixation in granulation processing according to claim 3, characterized in that, The anti-loosening mechanism includes a mounting plate (9), which is fixedly connected to the connecting bracket (8). A second gear (13), a second connecting rod (16), and a ratchet (10) are provided on one outer wall of the mounting plate (9). The second gear (13) and the ratchet (10) are both connected to the mounting plate (9) through bearings. The second gear (13) meshes with the first gear (12). A first connecting rod (14) is movably connected to the eccentric part of the second gear (13). The second connecting rod (16) is movably connected to the mounting plate (9). One end of the first connecting rod (14) is hinged to one end of the second connecting rod (16). The second connecting rod (16) is also provided with a first pawl (15) and a second pawl (17). The first pawl (15) and the second pawl (17) are respectively used in conjunction with the ratchet (10).

6. A milling machine for granulation machining that is easy to rotate and fix, as described in claim 5, characterized in that, The first gear (12) and the second gear (13) are arranged vertically in a vertical direction.

7. A milling machine for granulation machining that is easy to rotate and fix, as described in claim 6, characterized in that, The length of the second pawl (17) is less than the length of the first pawl (15), and the first pawl (15) and the second pawl (17) respectively engage with different teeth of the ratchet (10).

8. A milling machine for easy rotation and fixation in granulation processing according to claim 1, characterized in that, The axial preload mechanism includes a fixed cylinder (7) and an end cap (26). The fixed cylinder (7) is fixed inside the rotary table (2). The fixed cylinder (7) is provided with a locking block (31). The locking block (31) is fixedly connected to the end cap (26). The end cap (26) is fixedly connected to the fixed plate (23). The fixed cylinder (7) is also provided with a first bearing (35). The optical axis section of the worm gear (6) is provided with a shoulder (34). A disc spring assembly (33) is provided between the first bearing (35) and the shoulder (34). A disc spring sleeve (32) is provided on the optical axis section of the worm gear (6). A sliding bearing is provided between the disc spring sleeve (32) and the optical axis section of the worm gear (6). One end of the disc spring sleeve (32) is in contact with the end face of the disc spring assembly (33). The other end of the disc spring sleeve (32) abuts against the shoulder (34).

9. A milling machine for granulation processing that is easy to rotate and fix, as described in claim 8, characterized in that, A washer (36) is provided between the locking block (31) and the first bearing (35). A fixing groove is provided on the locking block (31), and the worm (6) is rotatably inserted into the fixing groove.

10. A milling machine for granulation machining that is easy to rotate and fix, as described in claim 9, characterized in that, Two observation slots (27) extending axially are provided on the outer wall of the fixed cylinder (7). Two connecting blocks are provided at one end of the disc spring assembly (33) near the shoulder (34). The connecting blocks extend out of the fixed cylinder (7) through the observation slots (27). A pointer (29) is provided on the connecting blocks. A scale plate (28) is provided on the outer wall of the fixed cylinder (7) corresponding to the position of the pointer (29). The pointer (29) and the scale plate (28) are used together.

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