A heavy-duty milling head for high-efficiency machining of grooves

Abstract

This utility model discloses a heavy-duty milling head for high-efficiency machining of grooves, specifically relating to the field of machine tool processing technology. It includes a housing and a bevel gear shaft and a main spindle housed within the housing. The main spindle is connected to a three-sided cutting head. A bearing assembly abuts between the main spindle and the housing. The bearing assembly includes a cylindrical roller bearing and a double-direction thrust angular contact ball bearing near the three-sided cutting head, and a first bearing away from the three-sided cutting head. A bevel gear is fitted onto the main spindle. The bevel gear shaft is fixed in the upper middle part of the housing, and the bevel gear is engaged with the bevel gear shaft. The rotation direction of the bevel gear shaft is perpendicular to the output direction of the bevel gear, thereby driving the main spindle to rotate. This utility model transmits power to the main spindle through the perpendicular engagement of the bevel gear shaft and the bevel gear. Simultaneously, the specifically configured bearing assembly provides stable support to the main spindle, ensuring that the main spindle driving the three-sided cutting head maintains high-precision rotation even under heavy cutting loads, thus achieving high-efficiency machining of grooves.

Description

Technical Field

[0001] This utility model belongs to the field of machine tool processing technology, and specifically relates to a heavy-duty milling head for high-efficiency machining of grooves. Background Technology

[0002] In the field of large CNC machine tool machining, the machining of T-slots, rectangular slots, and other shaped groove structures in key components such as worktables and beds has long faced the dual challenges of efficiency and accuracy. Traditional shaped groove machining often uses end mills or bar mills. Limited by tool rigidity and cutting load, it requires process parameters with small feed rates and low feed speeds, resulting in low metal removal rates. This is especially problematic for machining large-sized, high-volume shaped grooves, leading to lengthy production cycles and severely impacting machining efficiency. To improve machining efficiency, the industry currently uses heavy-duty milling heads paired with large-diameter three-sided cutting head cutters. This solution, by increasing the cutting width and depth, can significantly increase the metal removal per pass, greatly improving machining efficiency.

[0003] However, large-diameter cutter heads generate enormous radial cutting forces and axial impact forces when rotating at high speeds, accompanied by high-frequency vibrations. The spindle bearing assembly of traditional milling heads is unable to withstand the combined loads, which can easily lead to accuracy drift and poor stability, thus affecting the machining accuracy and efficiency of the grooves.

[0004] Therefore, this utility model proposes a heavy-duty milling head for high-efficiency machining of grooves to solve the above problems. Utility Model Content

[0005] This invention provides a heavy-duty milling head for high-efficiency machining of grooves, in order to solve at least one of the above-mentioned technical problems.

[0006] The technical solution adopted by this utility model is as follows: a heavy-duty milling head for high-efficiency machining of grooves, comprising a housing and a bevel gear shaft and a main shaft disposed within the housing. The main shaft is connected to a three-sided cutting head. A bearing assembly abuts between the main shaft and the housing. The bearing assembly includes a cylindrical roller bearing and a double-direction thrust angular contact ball bearing near one end of the three-sided cutting head, and a first bearing away from the three-sided cutting head. A bevel gear is sleeved on the main shaft. The bevel gear shaft is fixed in the upper middle part of the housing. The bevel gear is engaged with the bevel gear shaft. The rotation direction of the bevel gear shaft is perpendicular to the output direction of the bevel gear, so as to drive the main shaft to rotate through the bevel gear shaft.

[0007] In a preferred embodiment, the cylindrical roller bearing and the double-direction thrust angular contact ball bearing are arranged sequentially along the spindle axis, and the outer side wall of the double-direction thrust angular contact ball bearing is interference-fitted with the inner wall of the housing, while its inner side wall is clearance-fitted with the outer wall of the spindle.

[0008] In a preferred embodiment, the first bearing consists of two symmetrically arranged single-row angular contact ball bearings, with the wider end faces of the two single-row angular contact ball bearings facing each other.

[0009] In a preferred embodiment, magnetic blocks are respectively provided on opposite sides of the single-row angular contact ball bearing, and the magnetic poles on opposite sides of the magnetic blocks are of the same polarity.

[0010] In a preferred embodiment, the bevel gear is a spiral bevel gear, and a spline structure is provided at the engagement connection between the bevel gear and the main shaft, wherein the spline structure adopts an involute tooth profile.

[0011] In a preferred embodiment, a sealing structure is provided at one end of the spindle near the three-sided cutting disc. The sealing structure includes a locking component and a sealing cavity, and the sealing cavity is provided with lubricating oil.

[0012] In a preferred embodiment, the engagement assembly includes a locking tooth disposed on the main shaft and a check ring disposed on the housing, wherein the check ring is provided with ratchet teeth that engage with the locking tooth.

[0013] In a preferred embodiment, the housing includes an inner box and an outer box, the inner box and the outer box are connected by screws and pins, and a buffer pad is provided between the inner box and the outer box.

[0014] In a preferred embodiment, the connection end between the spindle and the three-sided cutting disc is provided with a positioning stop and a tension bolt assembly, the tension bolt assembly including a positioning bolt and a limiting bolt.

[0015] Due to the adoption of the above technical solution, the beneficial effects achieved by this utility model are as follows: 1. In a preferred embodiment of this utility model, the externally input power is transmitted to the spindle through the vertical engagement of the bevel gear shaft and the conical gear. Simultaneously, a specially configured bearing assembly provides stable support to the spindle, ensuring that the spindle, driving the three-sided cutting head, maintains high-precision rotation even under heavy cutting loads, thereby achieving efficient and precise machining of workpiece grooves. Specifically, the cylindrical roller bearing primarily bears the radial cutting force generated during machining, while the double-direction thrust angular contact ball bearing is responsible for balancing the axial impact force. The combination of these two effectively suppresses radial and axial movement of the spindle. The first bearing further enhances the overall support rigidity of the spindle, ensuring good coaxiality and stability during high-speed rotation and under heavy loads.

[0016] 2. In a preferred embodiment of this utility model, the cylindrical roller bearings and the double-direction thrust angular contact ball bearings are arranged sequentially along the spindle axis, which can more accurately distribute the force. The outer wall of the double-direction thrust angular contact ball bearing is interference-fitted with the inner wall of the housing, which can stably transmit the axial force to the housing and avoid the bearing displacement affecting the support effect. The inner wall of the bearing is clearance-fitted with the outer wall of the spindle, which can reduce the frictional resistance between the spindle and the bearing when the spindle rotates, reduce energy loss, and at the same time reserve space for the thermal expansion and contraction of the spindle to prevent jamming caused by temperature changes.

[0017] 3. As a preferred embodiment of this utility model, two single-row angular contact ball bearings are arranged with their wider end faces facing each other to form a back-to-back installation. In this arrangement, the contact angles of the two bearings point outwards respectively, forming a symmetrical mechanical layout. This makes the contact angles of the two bearings point in opposite directions, resulting in a larger distance between the support points. This can effectively resist the overturning moment caused by the imbalance of forces at both ends of the spindle, thereby enhancing the rigidity and stability of the spindle.

[0018] Furthermore, by using magnetic blocks installed on the single-row angular contact ball bearings, a stable repulsive force is generated between the bearings using the principle of magnetic repulsion. Simultaneously, when an impact causes the two bearings to tend to move closer together, the distance between the magnetic blocks decreases, the repulsive force increases, forming a reverse buffer force to offset part of the impact energy; when an impact causes the bearings to tend to move away from each other, the distance between the magnetic blocks increases, the repulsive force decreases, and this avoids a sudden increase in bearing load caused by excessive preload, thus playing a dynamic buffering role.

[0019] 4. As a preferred embodiment of this utility model, the spiral bevel gear has a spiral tooth surface and a progressive contact during meshing. It features a high degree of overlap, smooth transmission, and strong load-bearing capacity, effectively reducing impact and vibration during power transmission. Simultaneously, the engagement connection between the bevel gear and the spindle employs an involute spline structure, which has self-centering characteristics. This ensures that the bevel gear and spindle maintain coaxiality during rotation, reducing vibration and additional stress caused by eccentricity. Furthermore, multiple teeth of the involute spline engage simultaneously, resulting in uniform load distribution among the teeth. This allows it to withstand large radial and axial loads, ensuring efficient and stable power transmission from the bevel gear shaft to the spindle, thereby providing stable cutting power for the three-sided cutting head.

[0020] 5. As a preferred embodiment of this utility model, the sealing structure ensures the long-term stable operation of the milling head; wherein, the engaging assembly achieves radial contact through clearance fit, reducing the clearance space and preventing impurities such as chips, coolant, and dust generated by external milling from radially invading the bearing assembly inside the spindle; the lubricating oil in the sealing cavity can lubricate the contact area between the spindle and the sealing structure as well as the edge of the nearby bearing assembly, reducing friction and wear during rotation. At the same time, the lubricating oil can also enhance the sealing effect, forming an oil film barrier, further blocking the intrusion of impurities and extending the service life of the milling head.

[0021] In addition, the unidirectional meshing of the locking teeth on the spindle and the ratchet teeth on the backstop ring of the housing allows the spindle to rotate smoothly during normal operation, while preventing it from rotating in the opposite direction when the external load changes suddenly or the machine stops, thus avoiding impact damage to the transmission system and bearing assembly caused by reverse rotation.

[0022] 6. In a preferred embodiment of this utility model, the inner box and the outer box are connected by screws and pins, which are firm and reliable and easy to disassemble and maintain; wherein, the inner box provides a precise positioning reference for the internal core components, while the outer box plays an external protection role, and the buffer pad absorbs vibration energy through its own elastic deformation, reducing the transmission of vibration to the outside and avoiding loosening of components, increased wear or decreased processing accuracy caused by vibration. 7. As a preferred embodiment of this utility model, the connection structure between the spindle and the three-sided cutting head ensures stable output of cutting power; the positioning stop achieves coaxial positioning of the spindle and the three-sided cutting head through precise dimensional matching, ensuring that the rotation center of the cutting head is consistent with the rotation center of the spindle, avoiding cutting vibration and groove machining accuracy errors caused by positioning deviation; in the tension bolt group, the positioning bolt is used to initially fix the cutting head on the spindle, ensuring that the cutting head and the spindle fit tightly, while the limiting bolt further enhances the tightness of the connection, preventing the cutting head from loosening or displacing when rotating at high speed and bearing heavy cutting loads, ensuring that the cutting head and the spindle rotate synchronously, and ensuring stable transmission of cutting force. Attached Figure Description

[0023] The accompanying drawings, which are provided to further illustrate the present invention and constitute a part of the present invention, illustrate exemplary embodiments of the present invention and are used to explain the present invention, but do not constitute an undue limitation of the present invention.

[0024] In the attached diagram: Figure 1 This is a schematic diagram of the heavy-duty milling head for high-efficiency machining of grooves according to this utility model; Figure 2 This is a schematic diagram of a single-row angular contact ball bearing. Figure 3 A schematic diagram of a spiral bevel gear and spline structure; Figure 4 This is a schematic diagram of the sealed structure; Figure 5 This is a schematic diagram of the cushioning pad structure; Figure label: 1. Shell; 11. Inner casing; 12. Outer casing; 13. Screws and pins; 14. Buffer pad; 2. Main spindle; 21. Bevel gear shaft; 22. Three-sided cutting head; 23. Positioning stop; 24. Tensioner bolt assembly; 241. Positioning bolt; 242. Limit bolt; 3. Bearing assembly; 31. Cylindrical roller bearing; 32. Double-direction thrust angular contact ball bearing; 33. Bevel gear; 34. Spline structure; 4. First bearing; 41. Single-row angular contact ball bearing; 411. Magnetic block; 5. Sealing structure; 51. Engaging assembly; 511. Engaging teeth; 512. Check ring; 513. Ratchet; 52. Sealing cavity. Detailed Implementation

[0025] To more clearly illustrate the overall concept of this utility model, a detailed description will be provided below with reference to the accompanying drawings.

[0026] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0027] Furthermore, it should be understood in the description of this utility model that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0028] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0029] In this invention, unless otherwise expressly specified and limited, the first feature "on" or "below" the second feature may be in direct contact with the first and second features, or indirect contact through an intermediate medium. In the description of this specification, references to terms such as "implementation," "example," "aspect," or "specific example" indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0030] Example 1 A preferred embodiment, such as Figure 1 As shown, a heavy-duty milling head for high-efficiency machining of grooves includes a housing 1 and a bevel gear shaft 21 and a spindle 2 disposed within the housing 1. The spindle 2 is connected to a three-sided cutting head 22. A bearing assembly 3 abuts between the spindle 2 and the housing 1. When the equipment is started, an external power source transmits rotational power to the bevel gear shaft 21, which is fixed in the upper middle part of the housing 1, causing the bevel gear shaft 21 to rotate around its own axis at a set speed. At this time, the bevel gear shaft 21 acts as a power input component, introducing external energy into the internal transmission system of the milling head. The bevel gear 33, mounted on the main shaft 2, is engaged, and their rotation directions are perpendicular. The rotation of the bevel gear shaft 21 drives the bevel gear 33 to rotate through gear meshing. During this process, the power transmission direction changes by 90°. The rotation direction of the bevel gear shaft 21 is converted by the bevel gear 33 and then transmitted to the main shaft 2, achieving a vertical conversion of the power transmission direction. This ensures that power can be accurately and efficiently transmitted from the bevel gear shaft 21 to the main shaft 2. The rotation of the bevel gear 33 directly drives the main shaft 2 connected to it to rotate. During the rotation of the main shaft 2, it is precisely supported by the bearing assembly 3. The rotation of the main shaft 2 drives the connected three-sided cutting head 22 to rotate synchronously. When the rotating three-sided cutting head 22 contacts the groove machining part of the workpiece, the cutting head cuts the workpiece material under the drive of the external feed mechanism. Because the main shaft 2 maintains high-precision rotation under the support of the bearing assembly 3 and the power transmission is stable, the three-sided cutting head 22 can cut the workpiece according to the preset trajectory and parameters, ultimately machining a groove that meets the precision requirements. Throughout the machining process, the bearing assembly 3 continuously provides support, ensuring the stable operation of the spindle 2 and the cutter head. The stable meshing of the bevel gear shaft 21 and the bevel gear 33 ensures the continuous and efficient transmission of power, together achieving efficient machining of the groove.

[0031] Example 2 like Figure 1 and Figure 2As shown, a heavy-duty milling head for high-efficiency machining of grooves differs from Embodiment 1. Cylindrical roller bearings 31 and double-direction thrust angular contact ball bearings 32 are arranged sequentially along the axial direction of the main shaft 2. The outer ring of the double-direction thrust angular contact ball bearing 32 is fixed to the housing 1 by an interference fit, and the inner ring maintains a gap with the main shaft 2. When the spindle 2 starts to rotate under power drive, the inner ring of the cylindrical roller bearing 31 rotates synchronously with the spindle 2, while the outer ring is fixed on the housing 1. The rollers roll between the inner and outer rings, providing low-friction support for the radial direction. The inner ring of the double-direction thrust angular contact ball bearing 32 rotates freely with the spindle 2. Due to the unobstructed clearance fit, the outer ring remains stationary, and the rolling elements are in a state of waiting to be stressed between the inner and outer rings. When the three-sided cutting head 22 contacts the workpiece for cutting, it generates a radial cutting force. This force is transmitted to the cylindrical roller bearing 31 through the spindle 2. After the rollers are stressed, they distribute the force to the outer ring, which is ultimately borne by the housing 1, limiting the radial runout of the spindle 2 and ensuring accurate cutting position. At the same time, the axial cutting force, the thrust during feed, or the tool reaction force generated are transmitted to the inner ring of the double-direction thrust angular contact ball bearing 32 through the spindle 2. The inner ring transmits the axial force to the fixed outer ring through the rolling elements, which is then absorbed by the housing 1, effectively preventing the spindle 2 from moving axially and ensuring stable tool feed depth. Throughout the entire groove machining process, as the spindle 2 continues to rotate and the workpiece is fed relative to it, radial and axial loads act alternately or simultaneously. The two types of bearings consistently and stably perform their respective functions: the cylindrical roller bearing 31 maintains radial accuracy, and the double-direction thrust angular contact ball bearing 32 maintains axial accuracy. Their cooperation ensures that the spindle 2 maintains a stable rotational state, reducing vibration and errors. Simultaneously, two single-row angular contact ball bearings 41, symmetrically positioned at the end away from the three-sided cutting head 22, are arranged with their wider end faces facing each other. When the single-row angular contact ball bearings 41 are configured back-to-back, the inner rings face each other while the outer rings are separated, increasing the bearing span and enhancing the system's resistance to overturning moment. This further strengthens the support stability of the spindle 2. They can jointly withstand radial and double-direction axial forces, effectively coping with the complex loads generated during machining, counteracting the reverse forces, and enabling the spindle 2 to rotate at a stable speed and with high precision.

[0032] In addition, magnetic blocks 411 are respectively provided on opposite sides of the single-row angular contact ball bearing 41. The magnetic poles of the opposite sides of the magnetic blocks 411 are the same. The magnetic blocks 411 with the same poles on opposite sides are fixed with the bearing. At the initial distance, a basic repulsive force is generated. When the radial and axial loads are stable, the axial position of the spindle 2 remains basically unchanged, the distance between the magnetic blocks 411 remains stable, and the repulsive force is balanced with the axial force generated by cutting and the bearing preload, forming a dynamic stable state. The bearing raceway is uniformly stressed, and the rotational accuracy remains stable. If the cutting feed causes the spindle 2 to bear a forward axial force, it will cause the front bearing to tend to move closer to the rear bearing. The distance between the two magnetic blocks 411 decreases, the repulsive force increases, and the repulsive force is transmitted to the housing 1 through the outer ring of the bearing to offset part of the axial force and avoid excessive load on the rear bearing. If the impact causes the distance between the magnetic blocks 411 to decrease suddenly, the repulsive force increases suddenly, and a reverse resistance is quickly formed to buffer the impact. If the impact causes the distance to increase suddenly, the repulsive force decreases suddenly, avoiding the gap vibration caused by the instantaneous disappearance of the bearing preload and protecting the bearing from impact damage.

[0033] Example 3 like Figure 3 As shown, a heavy-duty milling head for high-efficiency machining of grooves differs from Embodiment 1 in that the bevel gear 33 is a helical bevel gear 33. A spline structure 34 is provided at the engagement connection between the bevel gear 33 shaft and the main shaft 2, and the spline structure 34 adopts an involute tooth profile. When an external power source drives the bevel gear shaft 21 to rotate, the tooth surface of the bevel gear shaft 21 begins to contact the helical tooth surface of the helical bevel gear 33. Due to the progressive meshing characteristics of the helical teeth, the two first make partial contact, and gradually expand the contact area with rotation until they are fully meshed, achieving a smooth power connection. Subsequently, the rotational force of the bevel gear shaft 21 is transmitted to the helical bevel gear 33 through tooth surface meshing. The helix angle of the helical tooth surface converts the horizontal rotational force into the vertical rotational force, and the bevel gear 33 begins to rotate with the meshing motion, completing a 90° change in the direction of power. At the same time, the rotating bevel gear 33 engages with the main shaft 2 through the involute spline, and multiple tooth surfaces of the spline contact simultaneously, uniformly transmitting the torque of the bevel gear 33 to the main shaft 2. Due to the self-centering effect of the involute tooth profile, the bevel gear 33 and the main shaft 2 maintain strict coaxial rotation, avoiding additional forces and vibrations caused by eccentricity, and ensuring efficient power transmission to the main shaft 2.

[0034] During milling, the spindle 2 obtains stable rotational power and speed under the synergistic action of the spiral bevel gear 33 and spline structure 34, driving the three-sided cutting head 22 to perform milling operations. The spiral bevel gear 33 continuously bears the cutting reaction force, and its spiral tooth shape and large contact area ensure the stability of power transmission. The involute spline maintains connection rigidity under high load, avoiding connection loosening or tooth surface damage caused by vibration.

[0035] Example 4 like Figure 4As shown, a heavy-duty milling head for high-efficiency machining of grooves, differing from Embodiment 1, has a sealing structure 5 at one end of the spindle 2 near the three-sided cutting head 22. The sealing structure 5 includes a locking assembly 51 and a sealing cavity 52, which contains lubricating oil. When the spindle 2 starts to rotate, the locking assembly 51 rotates synchronously with the spindle 2, and the lubricating oil in the sealing cavity 52 is radially distributed under centrifugal force, with the oil film thickness becoming uniform under rotational inertia. At this time, the mechanical engagement of the locking assembly 51 prevents large impurities from entering, while the lubricating oil film adheres to the contact surface through viscosity, forming a dynamic sealing barrier. During milling, the chips, splashed coolant, and dust generated by the cutting of the three-sided cutting head 22 diffuse towards the front end of the spindle 2, and are first blocked by the radial and axial structures of the locking assembly 51, preventing them from directly entering the inner side of the sealing cavity 52. ​​When a small amount of tiny impurities or liquid attempts to enter through the gap, they are intercepted by the oil film in the sealing cavity 52. ​​The viscous force of the oil film adsorbs the impurities or carries them back to the sealing cavity 52 with the flow of oil, preventing them from entering the bearing assembly 3.

[0036] Meanwhile, the engagement assembly 51 includes a locking tooth 511 on the main shaft 2 and a check ring 512 on the housing 1. The check ring 512 is provided with a ratchet 513 that engages with the locking tooth 511. When the main shaft 2 rotates in a set direction, the locking tooth 511 slides along the inclined tooth surface of the ratchet 513. The frictional force generated at the meshing point is small and does not hinder the rotation of the main shaft 2. At this time, the continuous meshing of the locking tooth 511 and the ratchet tooth 513 maintains the integrity of the mechanical barrier. The locking tooth 511, which rotates with the spindle 2, drives the lubricating oil to flow between the teeth, and the oil film evenly covers the tooth surface, which not only enhances the sealing but also achieves lubrication. If an accident occurs, such as the tool chipping or the workpiece suddenly jamming, causing the spindle 2 to rotate in the opposite direction, the vertical tooth back of the locking tooth 511 quickly and rigidly contacts the vertical tooth back of the ratchet tooth 513, preventing the spindle 2 from reversing through mechanical locking. At this time, the check ring 512 is fixed on the housing 1, transmitting the reverse impact force to the housing 1 and preventing the impact force from being transmitted to the bevel gear shaft 21, bevel gear 33 and other transmission components, thus preventing gear breakage, bearing damage and other failures. Example 5 like Figure 5As shown, a heavy-duty milling head for high-efficiency machining of grooves differs from Embodiment 1. A buffer pad 14 is located on the connecting surface between the inner housing 11 and the outer housing 12, positioned by pins to ensure precise alignment of the mounting holes in the inner and outer housings 12, guaranteeing consistent assembly references for the core components. Tightening the screws causes the inner and outer housings 12 to press the buffer pad 14 under preload. The buffer pad 14 undergoes elastic deformation due to compression, filling gaps and storing elastic potential energy, thus completing the overall assembly of the housing 1. The inner housing 11 serves as the mounting carrier for the core components. The spindle 2, bevel gear shaft 21, bearing assembly 3, etc., are fixed to the inner housing 11 through bearing seats, positioning holes, and other structures. The rigidity of the inner housing 11 ensures the relative positional accuracy of these components, such as the perpendicularity of the spindle 2 and bevel gear shaft 21, and the gear meshing clearance, meeting design requirements. The outer housing 12, through its connection with the inner housing 11, forms a closed space, protecting the internal components from external collisions and environmental influences. When internal components need maintenance, the separate structure facilitates component disassembly of the milling head.

[0037] Meanwhile, the buffer pad 14 acts as a shock absorber, reducing wear on the connecting surfaces of the inner and outer housings 12 and the tendency of screws to loosen; the rigid connection of the screw pins 13 ensures that the relative positional accuracy of the inner and outer housings 12 does not change, maintaining the stable assembly accuracy of the internal components; the sealing effect of the buffer pad 14 continuously prevents impurities from entering, protecting the inside of the housing 1 from being clean.

[0038] Example 6 like Figure 1 As shown, a heavy-duty milling head for high-efficiency machining of grooves, differing from Embodiment 1, has a positioning stop 23 and a tension bolt assembly 24 at the connection end between the spindle 2 and the three-sided cutting head 22. The tension bolt assembly 24 includes a positioning bolt 241 and a limiting bolt 242. When installing the three-sided cutting head 22, first align the cutting head's retaining pin with the positioning stop 23 of the spindle 2, allowing the cutting head and spindle 2 to slowly engage until fully fitted. At this point, the positioning stop 23 restricts the axial position, and the cutting head initially achieves coaxial positioning with the spindle 2. When the positioning bolt 241 passes through the mounting hole of the cutting head and is screwed into the threaded hole of the spindle 2, it is gradually tightened in a symmetrical sequence to ensure even distribution of preload. As the bolts tighten, the cutting head and spindle 2 form a preliminary rigid connection. Subsequently, the limiting bolt 242 is installed, which, through cooperation with the cutting head's limiting structure, further restricts the circumferential rotation of the cutting head, completing the tightening loop.

[0039] When milling is in progress, the spindle 2 drives the cutter head to rotate at high speed. The radial fit of the positioning stop 23 prevents the cutter head from running radially due to centrifugal force, ensuring that the rotation axis of the cutter head is consistent with the spindle 2 and reducing the impact of vibration on the surface quality of the machined surface. When milling grooves, the friction of the positioning bolt 241 and the circumferential constraint of the limiting bolt 242 are used to balance and prevent relative sliding between the cutter head and the spindle 2.

[0040] For any parts not mentioned in this utility model, existing technologies can be used or referenced.

[0041] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0042] The above description is merely an embodiment of this utility model and is not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principle of this utility model should be included within the scope of the claims of this utility model.

Claims

1. A heavy-duty milling head for high-efficiency machining of grooves, comprising a housing (1) and a bevel gear shaft (21) and a spindle (2) disposed within the housing (1), wherein the spindle (2) is connected to a three-sided cutting head (22), characterized in that, A bearing assembly (3) abuts between the main shaft (2) and the housing (1). The bearing assembly (3) includes a cylindrical roller bearing (31) near one end of the three-sided cutting disc (22), a double-direction thrust angular contact ball bearing (32), and a first bearing (4) away from the three-sided cutting disc (22). The main shaft (2) is fitted with a bevel gear (33). The bevel gear shaft (21) is fixed in the upper middle part of the housing (1). The bevel gear (33) is engaged with the bevel gear shaft (21). The rotation direction of the bevel gear shaft (21) is perpendicular to the output direction of the bevel gear (33), so as to drive the main shaft (2) to rotate through the bevel gear shaft (21).

2. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The cylindrical roller bearing (31) and the double-direction thrust angular contact ball bearing (32) are arranged sequentially along the axial direction of the main shaft (2), and the outer side wall of the double-direction thrust angular contact ball bearing (32) is interference-fitted with the inner wall of the housing (1), and its inner side wall is clearance-fitted with the outer wall of the main shaft (2).

3. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The first bearing (4) consists of two symmetrically arranged single-row angular contact ball shafts (41), and the narrower end faces of the two single-row angular contact ball shafts (41) are arranged opposite each other.

4. The heavy-duty milling head for high-efficiency machining of grooves according to claim 3, characterized in that, The single-row angular contact ball bearing (41) has a magnetic block (411) on each side of its opposite side, and the magnetic poles of the opposite sides of the magnetic block (411) are the same.

5. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The bevel gear (33) is a spiral bevel gear, and a spline structure (34) is provided at the engagement connection between the bevel gear (33) and the main shaft (2), wherein the spline structure (34) adopts an involute tooth shape.

6. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The spindle (2) is provided with a sealing structure (5) at one end near the three-sided cutting disc (22). The sealing structure (5) includes a locking assembly (51) and a sealing cavity (52), and the sealing cavity (52) is provided with lubricating oil.

7. The heavy-duty milling head for high-efficiency machining of grooves according to claim 6, characterized in that, The engagement assembly (51) includes a locking tooth (511) on the main shaft (2) and a check ring (512) on the housing (1). The check ring (512) is provided with a ratchet (513) that engages with the locking tooth (511).

8. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The housing (1) includes an inner box (11) and an outer box (12), which are connected by screws and pins (13), and a buffer pad (14) is provided between the inner box (11) and the outer box (12).

9. The heavy-duty milling head for high-efficiency machining of grooves according to claim 1, characterized in that, The connection end between the main shaft (2) and the three-sided cutting disc (22) is provided with a positioning stop (23) and a tension bolt group (24), the tension bolt group (24) including a positioning bolt (241) and a limiting bolt (242).

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