Five-axis machining center with hydraulic clamping and damping control

Abstract

The present application relates to the technical field of machine tools, and particularly relates to a five-axis machining center heavy cutting swing milling head with hydraulic clamping and damping control, wherein the front clamping disc and the rear clamping disc can be axially elastically deformed, so that the damping locking assembly selectively enters a damping state or a clamping state; in the damping state, the front clamping disc can press the rotating disc through the damping disc, so as to adapt to the heavy cutting working condition when the milling head has swing machining demand; in the clamping state, the rear clamping disc can press the front clamping disc through the locking disc, so as to adapt to the heavy cutting working condition when the milling head has no swing machining demand. The beneficial effect is that the copying error in heavy feed heavy cutting or high-precision machining is fundamentally eliminated. And the strong rigid support and vibration control allow more aggressive cutting parameters to be used, which improves the process range and machining efficiency.

Description

Technical Field

[0001] This invention relates to the technical field of machine tools, and more particularly to a heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control. Background Technology

[0002] Existing technologies face several significant technical challenges when machining complex curved surface parts, especially when applying five-axis CNC machine tools in fields such as aerospace and energy equipment:

[0003] First, for five-axis machine tools, the large torque caused by the cutting force during roughing and semi-finishing processes can easily cause vibration, resulting in relatively weak structural rigidity, which in turn affects the surface quality, tool life, and machining efficiency.

[0004] Currently available five-axis machine tools generally lack active vibration suppression capabilities. This means that chatter generated during heavy cutting can only be mitigated by passively increasing structural rigidity or optimizing cutting parameters. These methods not only have limited effectiveness but also sacrifice machining efficiency and cannot fundamentally solve the problems of decreased workpiece surface quality, reduced dimensional accuracy, and accelerated tool wear caused by vibration. Summary of the Invention

[0005] Technical problems to be solved

[0006] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a heavy-cutting oscillating milling head for a five-axis machining center with hydraulic clamping and damping control. It solves the problem that existing five-axis machine tools generally lack active vibration suppression functions. Chatter generated during heavy cutting can only be alleviated by passively increasing structural rigidity or optimizing cutting parameters. These methods are not only limited in effect, but also sacrifice machining efficiency and cannot fundamentally solve the technical problems of decreased workpiece surface quality, reduced dimensional accuracy and accelerated tool wear caused by vibration.

[0007] Technical solution

[0008] To achieve the above objectives, the main technical solutions adopted by the present invention include:

[0009] In a first aspect, the present invention provides a heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control, comprising a housing, a milling head, and a damping locking assembly; the milling head is self-lockingly hinged within the housing along a horizontal axis; the damping locking assembly comprises, in sequence, a coaxial rotating disk, a damping disk, a front clamping disk, a locking disk, and a rear clamping disk along an axial direction away from the milling head; both the damping disk and the locking disk are fixed relative to the milling head; the rotating disk, the front clamping disk, and the rear clamping disk are fixed relative to the housing; the damping disk is located between the rotating disk and the front clamping disk. Within the axial clearance of the clamping disc, the locking disc is located within the axial clearance of the front and rear clamping discs; both the front and rear clamping discs are capable of axial elastic deformation, allowing the damping locking assembly to selectively enter either a damped or clamped state; in the damped state, the front clamping disc can press the rotating disc against the damping disc to accommodate heavy cutting conditions when the milling head requires oscillation; in the clamped state, the rear clamping disc can press the front clamping disc against the locking disc to accommodate heavy cutting conditions when the milling head does not require oscillation.

[0010] In one technical solution of the present invention, the damping locking components are all hydraulically controlled; a first oil chamber and a second oil chamber are respectively provided in the front clamping plate and the rear clamping plate; the side wall of the first oil chamber near the rotating plate is a first deformation part capable of axial elastic deformation, and the side wall of the second oil chamber near the front clamping plate is a second deformation part capable of axial elastic deformation; the end face of the damping plate facing the first deformation part is a first pressure-bearing part, and the end face of the front clamping plate facing the second deformation part is a second pressure-bearing part; when the pressure in the corresponding first oil chamber and the corresponding second oil chamber reaches the corresponding threshold, the first deformation part and the second deformation part can selectively enter the damping state or the clamping state by axially squeezing the corresponding first pressure-bearing part or the second pressure-bearing part.

[0011] In one technical solution of the present invention, a drive wheel is fixedly connected to the milling head and whose axis coincides with the horizontal axis, and a rotating disk is fixedly connected to the drive wheel.

[0012] In one technical solution of the present invention, the driving wheel is a worm wheel; it also includes a worm rotatably connected to the housing, the worm meshing with the worm wheel, and power being transmitted unidirectionally from the worm to the worm wheel.

[0013] In one technical solution of the present invention, the milling head is fixedly connected to one axial end of the rotating shaft, and the milling head is self-lockingly hinged in the housing along the horizontal axis of the rotating shaft. The worm gear is fixedly connected to the rotating shaft. The rotating shaft extends axially to form a connecting section. The axial end face of the front clamping plate extends away from the milling head to form a stepped portion. The end face of the rear clamping plate facing the front clamping plate forms an annular groove that abuts against the stepped portion. Both the front and rear clamping plates are sleeved on the rotating shaft. The damping plate includes an axially extending sleeve and a radially extending first spring piece. The sleeve is fixed outside the rotating shaft. The first spring piece is fixedly connected to the radial outer wall of the sleeve and extends between the rotating plate and the front clamping plate. The rotating plate is sleeved outside the sleeve and fixedly connected to the front clamping plate. The locking plate includes a connecting ring and a second spring piece. The connecting ring is fixedly connected to the worm gear. The second spring piece is fixedly connected to the axial end of the connecting ring and extends between the front and rear clamping plates. The second spring piece is located circumferentially outside the stepped portion.

[0014] In one technical solution of the present invention, an intermediate sleeve is also included, and the front clamping plate and the rear clamping plate are both sleeved on the rotating shaft through the intermediate sleeve; the end of the intermediate sleeve away from the milling head forms an outwardly radially extending end flange, and the circumferential space between the end flange and the worm gear forms an assembly area for the damping locking assembly; the intermediate sleeve is rotatably connected to the rotating shaft, fixedly connected to the front clamping plate and the rear clamping plate, and fixedly connected to the housing.

[0015] In one technical solution of the present invention, both the front clamping plate and the rear clamping plate are provided with oil passages that communicate with the corresponding first oil chamber and second oil chamber, and the oil passages are connected to the hydraulic system.

[0016] In one technical solution of the present invention, a torque transmission component is further included. The torque transmission component includes a first bevel gear assembly, a cylindrical gear assembly, a second bevel gear, and a milling head bevel gear, all rotatably connected within the housing. The driving gear of the first bevel gear assembly, the second bevel gear, and the rotation axis of the milling head during milling are coaxial. The cylindrical gear assembly is used to drive the driven gear of the first bevel gear assembly and the driving gear of the second bevel gear. The second bevel gear meshes with the milling head bevel gear, and when the milling head swings along the horizontal axis, the second bevel gear rotates axially around the milling head bevel gear.

[0017] In one technical solution of the present invention, a control module and a vibration sensor are interconnected; the vibration sensor is adapted to detect the vibration parameters of the milling head during milling operations and transmit the measured vibration parameters to the control module; the control module uses the vibration parameters combined with a preset algorithm to determine the damping force required by the damping component, and controls the hydraulic system to input the required pressure of hydraulic oil into the first oil chamber according to the damping force.

[0018] Beneficial effects

[0019] The beneficial effects of this invention are: under heavy cutting conditions where the milling head requires oscillation, the damping locking component can enter a damping state, thereby absorbing the vibration of the machining process during heavy cutting, thus ensuring that the milling head maintains good machining stability and machining accuracy.

[0020] Damping provides controllable and smooth resistance to suppress vibration, prevent shocks, and improve motion smoothness. Hydraulic damping is used in "dynamic" conditions, with the core objective of improving motion smoothness, suppressing vibration and shocks, and ensuring dynamic accuracy and surface quality. It can be applied in five-axis linkage machining operations.

[0021] In heavy cutting conditions where the milling head does not require oscillation, the damping locking assembly enters a clamping state. In conjunction with the self-locking characteristics of the milling head, it further fixes the oscillation angle of the milling head, improves its positional stability, and thus improves machining stability and accuracy.

[0022] Furthermore, in heavy cutting conditions where the milling head does not require oscillation, the damping locking assembly in its clamped state provides a huge rigid locking force, eliminating any possible minor movement or vibration. In other words, hydraulic locking is used for "static" conditions, with the core objective of providing extreme rigidity against external forces to ensure positioning accuracy, specifically for three-axis milling and heavy cutting conditions. The milling head can be locked at any oscillation angle, thus reducing the load on the self-locking components during roughing.

[0023] This technical solution solves the problem of milling head vibration under heavy cutting conditions. When the damping locking assembly is in the clamping state, it eliminates force-induced deformation, removes backlash and elastic deformation in the transmission chain, and provides a rigid foundation for finishing beyond mechanical locking. In the damped state, it suppresses vibration, making high-precision five-axis simultaneous machining possible on a five-axis machine tool under heavy cutting conditions, resulting in a revolutionary improvement in machining accuracy and surface quality. The damped and clamping states fundamentally eliminate copying errors during heavy cutting with large feed rates or high-precision machining. Furthermore, the strong rigid support and vibration control allow for more aggressive cutting parameters, such as large depth of cut and large feed rates, while the large swing angle capability expands the machine tool's machining range, improving process range and machining efficiency.

[0024] Because the damping locking component is arranged coaxially with the milling head, it ensures the shortest path for force transmission, resulting in a compact structure, maximized rigidity, no additional bending moment, and rapid response. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of the heavy-cutting oscillating milling head of the five-axis machining center with hydraulic clamping and damping control according to the present invention;

[0026] Figure 2 This is one of the structural schematic diagrams showing the location of the damping locking component of the present invention;

[0027] Figure 3 This is a second structural schematic diagram showing the location of the damping locking component of the present invention;

[0028] Figure 4 This is a schematic diagram of the damping disc of the present invention;

[0029] Figure 5 This is a schematic diagram of the locking disc of the present invention;

[0030] Figure 6 For the present invention Figure 1 A magnified schematic diagram of the local structure at point A;

[0031] Figure 7 This is a schematic diagram of the damping feedback control algorithm of the present invention.

[0032] Explanation of reference numerals in the attached figures

[0033] 1. Shell;

[0034] 2. Milling head;

[0035] 3. Damping locking assembly;

[0036] 31. Rotating disc;

[0037] 32. Damping disc; 321. Sleeve; 322. First spring; 320. First pressure-bearing part;

[0038] 33. Front clamping plate; 331. First oil cavity; 3311. First deformation section; 332. Second pressure-bearing section; 3313. Stepped section;

[0039] 34. Locking disc; 341. Connecting ring; 342. Second spring;

[0040] 35. Rear clamping plate; 351. Second oil cavity; 3511. Second deformation section; 3512. Annular groove;

[0041] 4. Worm gear;

[0042] 5. Worm gear;

[0043] 6. Shaft;

[0044] 7. Intermediate sleeve; 71. End flange;

[0045] 8. Torque transmission components;

[0046] 81. First bevel gear assembly; 82. Cylindrical gear assembly; 83. Second bevel gear; 84. Milling head bevel gear. Detailed Implementation

[0047] To better explain and facilitate understanding of this invention, the following description is provided in conjunction with the appendix. Figures 1-7 The present invention will be described in detail through specific embodiments. In this document, directional terms such as "upper" and "lower" are used interchangeably with other directional terms. Figure 1 The orientation is used as a reference.

[0048] Example 1:

[0049] Reference Figures 1-7 The present invention provides a heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control, including a housing 1, a milling head 2, and a damping locking assembly 3;

[0050] The milling head 2 is self-lockingly hinged in the housing 1 along the horizontal axis; the damping locking assembly 3 includes, in sequence, a coaxial rotating disk 31, a damping disk 32, a front clamping disk 33, a locking disk 34 and a rear clamping disk 35 along the axial direction away from the milling head 2.

[0051] Both the damping disc 32 and the locking disc 34 are fixed relative to the milling head 2; the rotating disc 31, the front clamping disc 33 and the rear clamping disc 35 are fixed relative to the housing 1; the damping disc 32 is located within the axial gap between the rotating disc 31 and the front clamping disc 33, and the locking disc 34 is located within the axial gap between the front clamping disc 33 and the rear clamping disc 35.

[0052] Both the front clamping plate 33 and the rear clamping plate 35 are capable of axial elastic deformation, allowing the damping locking assembly 3 to selectively enter either a damping state or a clamping state. In the damping state, the front clamping plate 33 can press the rotating plate 31 against the damping plate 32 to adapt to the heavy cutting conditions when the milling head 2 has a swinging machining requirement. In the clamping state, the rear clamping plate 35 can press the front clamping plate 33 against the locking plate 34 to adapt to the heavy cutting conditions when the milling head 2 does not have a swinging machining requirement.

[0053] In this embodiment, the dynamic response control of the milling head 2 under different working conditions is achieved through the cleverly arranged damping locking assembly 3. Specifically, the milling head 2 is hinged to the housing 1 via a horizontal axis, that is, hinged around axis A, giving it the ability to swing around this axis to adapt to the machining requirements of complex curved or inclined surfaces. The damping locking assembly 3, which is arranged around this swing axis, includes a rotating disk 31, a damping disk 32, a front clamping disk 33, a locking disk 34, and a rear clamping disk 35 arranged sequentially along the axial direction, with each component forming a precise fit.

[0054] In this design, the damping disc 32 and the locking disc 34 move synchronously with the milling head 2, while the rotating disc 31, the front clamping disc 33, and the rear clamping disc 35 remain stationary relative to the housing 1. This separation of dynamic and static components allows the entire system to generate controllable friction or clamping force through relative displacement without interfering with the swing freedom. The damping disc 32 is positioned in the axial gap between the rotating disc 31 and the front clamping disc 33, while the locking disc 34 is located in the axial gap between the front clamping disc 33 and the rear clamping disc 35. This not only effectively utilizes the limited space but also provides a structural basis for subsequent elastic deformation and force transmission.

[0055] Thus, under heavy cutting conditions where the milling head 2 requires oscillating machining, the damping locking component 3 can enter the damping state, thereby absorbing the vibration of the machining process during heavy cutting, and ensuring that the milling head 2 maintains good machining stability and machining accuracy.

[0056] Damping provides controllable and smooth resistance to suppress vibration, prevent shocks, and improve motion smoothness. Hydraulic damping is used in "dynamic" conditions, with the core objective of improving motion smoothness, suppressing vibration and shocks, and ensuring dynamic accuracy and surface quality. It can be applied in five-axis linkage machining operations.

[0057] In heavy cutting conditions where the milling head 2 does not require oscillation, the damping locking component 3 enters a clamping state. In conjunction with the self-locking characteristics of the milling head 2, it further fixes the oscillation angle of the milling head 2, improves its positional stability, and thus improves machining stability and accuracy.

[0058] Furthermore, under heavy cutting conditions where the milling head 2 does not require oscillation, the damping locking assembly 3, in its clamped state, provides a huge rigid locking force, eliminating any possible minor movement or vibration. In other words, hydraulic locking is used for "static" conditions, with the core objective of providing extreme rigidity against external forces to ensure positioning accuracy, specifically for three-axis milling and heavy cutting conditions. The milling head 2 can be locked at any oscillation angle, thus reducing the load on the self-locking components during roughing.

[0059] This technical solution solves the vibration problem of the milling head 2 under heavy cutting conditions. When the damping locking component 3 is in the clamping state, it eliminates force-induced deformation, removes backlash and elastic deformation in the transmission chain, and provides a rigid foundation for finishing that surpasses mechanical locking. In the damping state, it suppresses vibration, making it possible for five-axis machine tools to perform high-precision five-axis linkage machining under heavy cutting conditions, resulting in a revolutionary improvement in machining accuracy and surface quality. The damping and clamping states fundamentally eliminate copying errors during heavy cutting with large feed rates or high-precision machining. Furthermore, the strong rigid support and vibration control allow for more aggressive cutting parameters, such as large depth of cut and large feed rates, while the large swing angle capability expands the machining range of the machine tool, improving the process range and machining efficiency.

[0060] Because the damping locking component 3 is arranged coaxially with the milling head 2, it ensures the shortest path for force transmission, resulting in a compact structure, maximized rigidity, no additional bending moment, and rapid response.

[0061] Furthermore, in the undamped and unclamped state, the damping disc 32 is disengaged from the rotating disc 31 and the front clamping disc 33, and the locking disc 34 is disengaged from the front clamping disc 33 and the rear clamping disc 35, so as to ensure the smooth swing of the milling head 2.

[0062] Example 2:

[0063] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0064] All damping locking components 3 are hydraulically controlled; the front clamping plate 33 and the rear clamping plate 35 are respectively provided with a first oil cavity 331 and a second oil cavity 351; the side wall of the first oil cavity 331 near the rotating plate 31 is a first deformation part 3311 capable of axial elastic deformation, and the side wall of the second oil cavity 351 near the front clamping plate 33 is a second deformation part 3511 capable of axial elastic deformation; the end face of the rotating plate 31 facing the first deformation part 3311 is a first pressure-bearing part 320, and the end face of the front clamping plate 33 facing the second deformation part 3511 is a second pressure-bearing part 332; when the pressure in the corresponding first oil cavity 331 and the second oil cavity 351 reaches the corresponding threshold, the first deformation part 3311 and the second deformation part 3511 can selectively enter the damping state or the clamping state by axially pressing the corresponding first pressure-bearing part 320 or the second pressure-bearing part 332.

[0065] In this embodiment, both the front clamping plate 33 and the rear clamping plate 35 have independent hydraulic chambers, namely the first oil chamber 331 and the second oil chamber 351. The two chambers directly drive structural deformation through changes in hydraulic pressure, thereby achieving dynamic control of the working state of the milling head 2.

[0066] The side wall of the first oil chamber 331 near the rotating disk 31 is designed as a first deformation part 3311 with axial elastic deformation capability, while the side of the second oil chamber 351 near the front clamping disk 33 is provided with a second deformation part 3511 that also has axial elasticity. Correspondingly, the end face of the damping disk 32 facing the first oil chamber 331 constitutes a first pressure-bearing part 320, and the end face of the front clamping disk 33 facing the second oil chamber 351 constitutes a second pressure-bearing part 332. This pairing relationship of "compression part - pressure-bearing part" constitutes two independent but cooperative hydraulic actuation interfaces.

[0067] When the system needs to enter a damped state, the hydraulic system injects hydraulic oil at a set pressure into the first oil chamber 331, causing the pressure inside the chamber to gradually increase. Once a preset first threshold is reached, the first deformation part 3311 undergoes controllable axial elastic deformation towards the first pressure-bearing part 320 under hydraulic action, thereby establishing a moderate positive pressure between the rotating disk 31 and the front clamping disk 33. The frictional force generated by this pressure is sufficient to suppress the shaking during heavy cutting when the milling head 2 has a swing requirement, improve the surface quality of the machined surface, and protect the spindle system.

[0068] When clamping is required, the hydraulic pressure in the second oil chamber 351 rises to the second threshold, causing the second deformation part 3511 to deform towards the second pressure-bearing part 332, firmly pressing the front clamping plate 33 onto the rear clamping plate 35. This action not only enhances the rigidity of the entire clamping chain but also completely locks the milling head 2 at the target angle position through a multi-stage clamping structure, eliminating possible angular displacement and improving the geometric accuracy and structural stability of the milling head 2 when there is no need for oscillation, thus adapting to high-precision machining conditions.

[0069] Since the entire control logic is driven by the hydraulic system, it not only simplifies the structural layout but also significantly improves response speed and reliability.

[0070] Example 3:

[0071] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0072] The heavy-cutting oscillating milling head of the five-axis machining center with hydraulic clamping and damping control also includes a drive wheel fixedly connected to the milling head 2, with its axis coinciding with the horizontal axis, and a rotating disk 31 fixedly connected to the drive wheel.

[0073] In this embodiment, the rotation axis of the drive wheel is strictly coincident with the horizontal hinge axis around which the milling head 2 is wound, ensuring that the drive wheel will not introduce additional eccentric loads or additional bending moments when transmitting driving torque, and also providing a guarantee for the motion synchronization and structural compactness of the entire swing system.

[0074] The rotating disk 31 is directly fixed on the drive wheel, thus forming a completely synchronized motion relationship with the milling head 2. Regardless of whether the milling head 2 is in a free swing, damped state, or clamped state, the rotating disk 31 always moves with it, ensuring the certainty and controllability of the relative displacement relationship between the moving and stationary interfaces in the damping clamping assembly.

[0075] This layout, which integrates the rotating disk 31 onto the drive wheel, cleverly merges the power transmission path and the state control path into the same axis system, avoiding the problems of accumulated backlash or motion lag caused by multiple components connected in series in traditional solutions. Simultaneously, since the drive wheel is integrally fixed to the milling head 2, its own rigidity can effectively support the reaction force borne by the rotating disk 31 during high-pressure clamping, preventing local deformation from affecting clamping accuracy. Furthermore, when the hydraulic system is activated, the clamping force generated by the first oil chamber 331 acts on the first pressure-bearing part 320 of the rotating disk 31 through the first deformation part 3311, and this force is ultimately evenly transmitted to the entire milling head 2 structure via the drive wheel, making the clamping force distribution more symmetrical and stable, significantly improving the torsional resistance and angle holding accuracy under clamping conditions.

[0076] Example 4:

[0077] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0078] The drive wheel is a worm gear 4; it also includes a worm 5 rotatably connected to the housing 1, the worm 5 meshing with the worm gear 4, and power can be transmitted unidirectionally from the worm 5 to the worm gear 4.

[0079] In this embodiment, the worm gear 4 and the worm 5 mounted on the housing 1 form a precision meshing worm gear 4-worm 5 transmission pair. This transmission pair not only undertakes the angle adjustment function of the milling head 2, but also further enhances the positioning and holding capability and safety of the entire system through its inherent self-locking characteristics.

[0080] The worm 5 can be driven by an external servo motor or hydraulic motor. Its rotational motion is transmitted to the worm wheel 4 via the helical tooth surface, thereby driving the milling head 2 to rotate precisely around the horizontal axis to the target angular position. Because the worm wheel 4 and worm 5 mechanism has a unidirectional power transmission characteristic, that is, power can be efficiently transmitted from the worm 5 to the worm wheel 4, while the reverse direction is difficult to drive because the helix angle is smaller than the friction angle. Therefore, even if the hydraulic clamping system is not fully activated or is accidentally depressurized, the milling head 2 can still maintain its current position by mechanical self-locking, effectively preventing unexpected rotation caused by gravity, cutting reaction force or vibration.

[0081] This embodiment combines mechanical self-locking with hydraulic active control. The system relies on the self-locking foundation of the worm gear 4 and worm 5 to provide basic positioning, while the first oil chamber 331 applies appropriate pressure to achieve flexible damping. When it is necessary to lock the milling head 2, the second oil chamber 351 is activated, and the second deformation part 3511 presses the front clamping plate 33, so that the entire clamping assembly forms a rigid connection. At this time, the hydraulic locking and mechanical self-locking work together to greatly improve the anti-overturning moment and impact resistance.

[0082] The worm gear 5 is supported on the housing 1, and its bearing preload and lubrication can be optimized independently without being affected by the hydraulic cavity inside the milling head 2, which is beneficial to improving transmission accuracy and long-term operational reliability.

[0083] In summary, the introduction of a worm gear 4-worm 5-drive system not only achieves precise angle control at high reduction ratios but also provides reliable mechanical redundancy for the hydraulic control system by leveraging its inherent unidirectional transmission and self-locking capabilities. While ensuring dynamic response flexibility, it significantly enhances the robustness of static positioning, making it particularly suitable for high-end manufacturing scenarios with extremely high requirements for angular accuracy, rigidity, and safety margins, such as aerospace structural components and mold cavities.

[0084] Example 5:

[0085] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0086] The heavy-cutting oscillating milling head of the five-axis machining center with hydraulic clamping and damping control also includes a rotating shaft 6. The milling head 2 is fixedly connected to one end of the rotating shaft 6 in the axial direction. The milling head 2 is self-lockingly hinged in the housing 1 along the horizontal axis through the rotating shaft 6. The worm gear 4 is fixedly connected to the rotating shaft 6.

[0087] The axial extension of the pivot 6 forms a connecting section;

[0088] The rotating disk 31 is fitted over the sleeve 321 and is fixedly connected to the front clamping disk 33;

[0089] The axial end face of the front clamping plate 33 extends away from the milling head 2 to form a stepped portion 3313, and the end face of the rear clamping plate 35 facing the front clamping plate 33 forms an annular groove 3512 that abuts against the stepped portion 3313.

[0090] The damping disc 32 includes an axially extending sleeve 321 and a radially extending first spring piece 322. The sleeve 321 is fixed outside the rotating shaft 6, and the first spring piece 322 is fixedly connected to the radial outer wall of the sleeve 321. The first spring piece 322 extends between the rotating disc 31 and the front clamping disc 33.

[0091] The locking disc 34 includes a connecting ring 341 and a second spring 342. The connecting ring 341 is fixedly connected to the worm gear 4, and the second spring 342 is fixedly connected to the axial end of the connecting ring 341 and extends between the front clamping disc 33 and the rear clamping disc 35. The second spring 342 is located on the circumferential outside of the stepped portion 3313.

[0092] In this embodiment, the milling head 2 further integrates mechanical transmission, hydraulic control and elastic compensation functions into the same axis system through the integrated design of the rotating shaft 6, which significantly improves the structural compactness, motion synchronization and reliability of state switching.

[0093] One end of the rotating shaft 6 is rigidly connected to the milling head 2, while the other end is supported in the housing 1 by a bearing, forming a stable rotating pair. The worm gear 4 is fixedly installed on the rotating shaft 6, so that when the external worm 5 is driven, the power is efficiently transmitted through the path of worm gear 4-rotating shaft 6-milling head 2, ensuring the accuracy of angle adjustment and the consistency of response.

[0094] The connecting section is used to support the moving parts in the damping clamping assembly. The rotating disk 31 is sleeved on the outer periphery of the connecting section and is rigidly connected to the front clamping disk, thereby ensuring that it is always fixed relative to the housing 1, simplifying the assembly process, and ensuring the coaxiality and uniform force distribution among the components during high-pressure clamping.

[0095] Regarding the fixed-side structure, the front clamping disc 33 extends an axial stepped portion 3313 in a direction away from the milling head 2, while the rear clamping disc 35 has a matching annular groove 3512 on its end face facing the front clamping disc 33. The stepped portion 3313 and the annular groove 3512 abut against each other, forming a rigid force transmission path, effectively preventing the rear clamping disc 35 from tilting or warping under high pressure, thereby ensuring the structural integrity and torsional stiffness of the entire clamping chain in the clamping state.

[0096] The damping disc 32 includes a sleeve 321 and a first spring plate 322. The sleeve 321 is fixedly fitted onto the outer wall of the rotating shaft 6, serving as a structural base. The first spring plate 322 extends axially from the radially outer side of the sleeve 321, precisely inserting into the axial gap between the rotating disc 31 and the front clamping disc 33. This spring plate combines flexibility and strength, remaining in a relaxed state when the first oil chamber 331 is not pressurized, allowing the milling head 2 to adjust freely. When entering the damping state, the first deformation part 3311 pushes the first spring plate 322 to produce controllable deformation under hydraulic action, transmitting clamping force and absorbing high-frequency vibrations through material elasticity, achieving "soft contact" type dynamic damping.

[0097] The locking disc 34 adopts a combination of a connecting ring 341 and a second spring 342: the connecting ring 341 is fixedly connected to the worm gear 4 to ensure that it moves synchronously with the milling head 2; the second spring 342 extends from the axial end of the connecting ring 341, is located in the axial gap between the front clamping disc 33 and the rear clamping disc 35, and is specifically arranged on the circumferential outer side of the stepped portion 3313. This positional design allows the second spring 342 to effectively fill the space around the mating area of ​​the stepped portion 3313 and the annular groove 3512 when the second oil chamber 351 is pressurized, enhancing the overall clamping uniformity while compensating for minor gaps caused by manufacturing tolerances or thermal expansion, and preventing local stress concentration. The flexible characteristics of the second spring 342 can provide buffering under heavy cutting impact, avoiding structural damage or failure caused by rigid collisions.

[0098] In summary, this embodiment provides a layout scheme for a compact damping locking component 3, thereby reducing its encroachment on the interior space of the housing 1 and reducing the overall size of the milling head 2.

[0099] It also includes an intermediate sleeve 7, and the front clamping plate 33 and the rear clamping plate 35 are both sleeved on the rotating shaft 6 through the intermediate sleeve 7;

[0100] The end of the intermediate sleeve 7 away from the milling head 2 forms an outwardly radially extending end flange 71, and the circumferential space between the end flange 71 and the worm gear 4 forms the assembly area of ​​the damping locking assembly 3.

[0101] The intermediate sleeve 7 is rotatably connected to the rotating shaft 6, fixedly connected to the front clamping plate 33 and the rear clamping plate 35, and fixedly connected to the housing 1.

[0102] In this embodiment, the intermediate sleeve 7 is integrally fitted around the outer periphery of the rotating shaft 6. Its inner wall is rotatably connected to the rotating shaft 6 through a precision bearing or a low-friction sliding pair, ensuring that the rotating shaft 6 and its connected milling head 2, worm gear 4, and rotating disk 31 can swing freely around the horizontal axis without constraint. At the same time, the outer periphery of the intermediate sleeve 7 is firmly fixed to the front clamping disk 33 and the rear clamping disk 35, forming a complete stationary assembly. The intermediate sleeve 7 is also rigidly connected to the housing 1 through the end flange 71, thereby reliably anchoring the entire fixed side structure, i.e., the clamping disk, to the housing reference, eliminating floating or displacement caused by the reaction of clamping force.

[0103] The intermediate sleeve 7 has an outwardly radially extending end flange 71 at the end furthest from the milling head 2. This flange not only significantly improves the bending and torsional stiffness of the intermediate sleeve 7 itself, but also encloses an annular circumferential clearance space between itself and the outer edge of the adjacent worm gear 4. This space is specifically designed as the assembly area for the damping locking assembly 3. Since this area is located between the rotating component, i.e., the worm gear 4, and the stationary component, i.e., the flange of the intermediate sleeve 7, a clear motion boundary is naturally formed, which effectively prevents rotational interference and provides controlled degrees of freedom for the axial and circumferential deformation of the elastic element, ensuring that it can respond accurately according to the design path under hydraulic excitation.

[0104] The front clamping plate 33, the rear clamping plate 35, and related compensation elements can be pre-integrated with the intermediate sleeve 7 into an independent sub-assembly, and then installed into the housing 1 as a whole, which greatly simplifies the on-site assembly process and improves the coaxiality control accuracy. If it is necessary to replace worn parts or upgrade the hardware configuration corresponding to the damping algorithm in the future, the sub-assembly can also be quickly disassembled without dismantling the entire swing mechanism.

[0105] Both the front clamping plate 33 and the rear clamping plate 35 are provided with oil passages that communicate with the corresponding first oil chamber 331 and second oil chamber 351. The oil passages are connected to the hydraulic system. Since the front clamping plate 33 and the rear clamping plate 35 are fixed, the arrangement of the hydraulic oil passages is very easy, and there is no need to consider the problem of rotational interference, which further reduces the application cost of this solution.

[0106] Furthermore, the front clamping plate 33 and the rear clamping plate 35 can be forged from high-strength alloy steel, such as 42CrMo or 30CrMnSiA. Their first deformation part 3311 and second deformation part 3511 undergo special heat treatment processes to give them extremely high yield strength and high fatigue life, ensuring that no plastic deformation or fatigue cracking occurs during repeated hydraulic tightening-recovery processes.

[0107] The friction surfaces of the rotating disk 31 and the front clamping disk 33 also require extremely high flatness and are usually coated or welded with wear-resistant materials, such as copper-based alloys or special friction materials, to provide a stable contact surface with a high coefficient of friction.

[0108] Specifically, refer to Figure 3 The rotating disk 31 is fixedly connected to the rear clamping disk 35 by bolts. The rear clamping disk 35 is fixedly connected to the front clamping disk 33 by bolts. The front clamping disk 33 is fixedly connected to the housing 1 by bolts. In this way, the rotating disk 31, the rear clamping disk 35, the front clamping disk 33 and the housing 1 are fixed.

[0109] The damping disc 32 oscillates synchronously with the milling head 2 and can be fixedly connected to the outside of the rotating shaft 6, such as by limiting the relative rotational freedom of the two through a key or a limit block. The locking disc 34 is fixedly connected to the worm gear 4 by bolts.

[0110] Example 6:

[0111] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0112] The heavy-cutting oscillating milling head of the five-axis machining center with hydraulic clamping and damping control also includes a torque transmission assembly 8. The torque transmission assembly 8 includes a first bevel gear assembly 81, a cylindrical gear assembly 82, a second bevel gear 83, and a milling head bevel gear 84, all rotatably connected within the housing 1. The driving gear of the first bevel gear assembly 81, the second bevel gear 83, and the rotation axis of the milling head 2 during milling are coaxial. The cylindrical gear assembly 82 is used to drive the driven gear of the first bevel gear assembly 81 and the driving gear of the second bevel gear 83. The second bevel gear 83 meshes with the milling head bevel gear 84.

[0113] In this embodiment, the milling head 2 further incorporates a torque transmission component 8 to solve the technical problem of power transmission interruption or transmission path misalignment in the traditional milling head 2 under large-angle yaw conditions, ensuring efficient and stable power transmission even under complex spatial constraints.

[0114] Specifically, the design of the entire torque transmission chain revolves around the core logic of "constant power input - adaptive angle following - stable output to the main shaft".

[0115] In this system, the driving gear of the first bevel gear assembly 81 is coaxially connected to the machine tool spindle or an external power source, and its rotation axis coincides with the main rotation axis of the milling head 2 during milling operations, ensuring the direct input of the original driving torque. The cylindrical gear assembly 82 acts as an intermediate bridge: it not only translates the power from the output end of the first bevel gear assembly 81 to the input end of the second bevel gear 83, but also, due to its parallel shaft transmission characteristics, effectively isolates the installation errors and thermal deformation effects between the two stages of bevel gears, improving the robustness of the transmission system.

[0116] The second bevel gear 83 meshes with the milling head bevel gear 84 fixed on the main shaft inside the milling head 2, forming the final power output stage. Regardless of the tilt angle of the milling head 2, power can be continuously and uninterruptedly transmitted to the cutting tool through the path of "first bevel gear, spur gear, second bevel gear, milling head bevel gear 84", completely avoiding the problems of speed fluctuation, torque loss or vibration noise caused by traditional universal joints or flexible couplings at large angles.

[0117] Furthermore, the torque transmission component 8 is highly coordinated with the aforementioned hydraulic clamping and worm gear 4 and worm 5 system in physical space: the worm gear 4 and worm 5 are responsible for controlling the swing angle and providing mechanical self-locking, the hydraulic damping component is responsible for suppressing dynamic disturbances during the swing process and achieving rigid locking, while the gear transmission chain focuses on high-precision, high-rigidity cutting power transmission. The three components complement each other and do not interfere with each other, jointly constructing an integrated swing milling unit that is "adjustable in angle, stable in power, and controllable in state".

[0118] Furthermore, since all gears are enclosed within housing 1 and employ forced or grease lubrication, the lifespan of transmission components is extended, and maintenance requirements are significantly reduced. Simultaneously, the high overlap meshing characteristics of bevel gears inherently possess a certain vibration absorption capacity, forming a dual vibration reduction mechanism with the hydraulic damping system, further enhancing the surface finish during high-speed, heavy-load cutting.

[0119] Specifically, the torque transmission component 8 enables a maximum swing range of 180° on the heavy-duty milling head; at the same time, the hydraulic clamping mechanism integrated with it on the same axis can provide extremely high locking rigidity at any angle instantly, completely solving the contradiction between large swing angle and high rigidity.

[0120] In summary, this torque transmission component 8, through the spatial coupling and motion decoupling design of multi-stage gears, successfully achieves continuous and high rigidity power transmission of the milling head 2 across the entire angular range, resolving the core contradiction in high-end five-axis machining: "flexible oscillation and powerful cutting." Combined with hydraulic adaptive damping control and the self-locking mechanism of the worm gear 4, the entire system achieves advanced levels in dynamic response, static stiffness, process adaptability, and operational reliability, providing solid technical support for efficient and precision milling of complex curved surfaces, deep cavity structures, and difficult-to-machine materials.

[0121] Example 7:

[0122] Reference Figures 1-7 In addition to possessing all the technical solutions of the above embodiments, the embodiments of the present invention further possess the following technical solutions:

[0123] The heavy-duty oscillating milling head of the five-axis machining center with hydraulic clamping and damping control also includes an interconnected control module and a vibration sensor; the vibration sensor is suitable for detecting the vibration parameters of the milling head 2 during milling operations and transmitting the measured vibration parameters to the control module; the control module uses the vibration parameters combined with a preset algorithm to determine the damping force required by the damping component, and controls the hydraulic system to input the required pressure of hydraulic oil into the first oil chamber 331 according to the damping force.

[0124] In this embodiment, vibration sensors are strategically positioned on the milling head 2 body or its adjacent structure, enabling highly sensitive acquisition of multidimensional vibration parameters generated during the milling process, including but not limited to vibration acceleration, frequency spectrum characteristics, and amplitude variations. These raw signals are transmitted to the control module in real time via a high-speed data channel.

[0125] The control module has a built-in intelligent algorithm model that quickly analyzes the current vibration state, determines whether the cutting process is in a stable range, and calculates the optimal damping force required to suppress harmful vibrations. Subsequently, the control module converts this target damping force into a corresponding hydraulic control command, precisely adjusting the servo proportional valve or electro-hydraulic pressure regulating device to input hydraulic oil at a specific pressure into the first oil chamber 331. With the dynamic adjustment of the pressure within the first oil chamber 331, the first deformation part 3311 undergoes a corresponding degree of axial elastic deformation, thereby changing its clamping force on the first pressure-bearing part 320 of the rotating disk 31, ultimately achieving continuous and stepless control of the damping characteristics of the milling head 2.

[0126] Because the control logic is fully coupled with the hydraulic actuator and requires no additional mechanical intervention, the entire adjustment process is smooth and shock-free, avoiding processing interruptions or transient disturbances caused by traditional discrete gear switching. Simultaneously, the vibration sensor and control module can be deeply integrated with the machine tool's CNC system, uploading information such as damping status and vibration level to a higher-level monitoring platform, supporting advanced functions such as process optimization, tool health assessment, and preventative maintenance.

[0127] With the action of vibration sensors, the system can sense the cutting state in real time and dynamically and accurately adjust the damping force through proportional valves, realizing a fundamental transformation from "passively bearing vibration" to "actively and intelligently suppressing vibration", providing core guarantee for high stability in heavy cutting and realizing stable five-axis linkage machining under relatively heavy cutting conditions.

[0128] The large swing angle avoids multiple clamping operations, and the closed-loop vibration suppression ensures process stability. It enables five-axis linkage machining under large cutting parameters, thereby fundamentally eliminating "copying errors" and precision degradation caused by vibration, and ensuring the final precision of the workpiece is stable.

[0129] Specifically, the processed vibration signal is compared with an internally set value. The control algorithm (such as fuzzy PID) calculates and outputs a corresponding control voltage signal in real time based on the amplitude and frequency components of the vibration signal.

[0130] The hydraulic system includes a high-pressure hydraulic pump station, a solenoid directional valve, a relief valve for setting the maximum clamping pressure, an accumulator, and a hydraulic rotary joint that leads oil from the stationary pipeline to the rotating clamping disc. The accumulator plays a crucial role; it can instantly provide a large flow of high-pressure oil for rapid clamping when the pump station is not continuously operating, and maintain stable system pressure during locking, compensating for possible minor leaks, thus achieving energy saving and pressure maintenance.

[0131] When clamping is required, the hydraulic system introduces high-pressure oil into the second oil chamber 351, typically at 15-25 MPa. Under hydraulic pressure, the rear clamping plate 35 undergoes controllable elastic deformation, forcing the second deformation part 3511 to produce precise and controllable elastic deformation, similar to the "drumstick" effect. This causes its friction end face to expand outward along the axial direction by a small displacement, typically 0.1-0.3 mm. This generates an extremely large end-face friction torque with the front clamping plate 33, reaching tens of thousands of N·m, thereby completely locking the worm gear 4 and the entire housing 1. This eliminates backlash and elastic deformation in the transmission chain, providing a rigid foundation for precision machining that surpasses mechanical locking. After machining is completed, the pressure is released, the rear clamping plate 35 returns to its original shape, and the locking is released.

[0132] Specifically, in the clamped state, the hydraulic system operates as follows:

[0133] S1 Lock Command: When the CNC system determines that the milling head 2 needs to be locked, it issues a command.

[0134] S2 Pressure Locking: The solenoid directional valve is energized and reversed, allowing high-pressure oil to enter the second oil chamber 351 through the rotary joint and internal oil passage. The oil pressure causes the second deformation part 3511 to undergo elastic deformation, pressing it against the front clamping plate 33.

[0135] S3 Pressure Holding Monitoring: The system pressure sensor monitors the oil pressure in real time. Once the pressure reaches the set value, the pump station stops working, and the pressure is maintained by the accumulator. The entire locking process can be completed within hundreds of milliseconds.

[0136] S4 Pressure Relief: After machining is completed, the CNC issues a release command. The solenoid directional valve resets, and the pressurized oil in the second oil chamber 351 is discharged back to the oil tank through the valve body. The rear clamping plate 35 returns to its original shape by relying on the elastic restoring force of its own material, completely disengaging from the front clamping plate 33, maintaining a small gap between the friction surfaces, ensuring that the milling head axis 2 can swing freely and without friction.

[0137] The hydraulic system also includes:

[0138] The pressure servo valve, also known as a high-response-frequency electro-hydraulic servo valve or proportional valve, receives current signals from the controller and precisely and quickly regulates the hydraulic oil pressure output to the first oil chamber 331. Its response speed is much faster than ordinary on / off valves or pressure reducing valves, meeting the requirements for real-time vibration suppression.

[0139] The pressure sensor is directly installed in the oil circuit of the oil chamber to monitor and feed back the actual pressure value in the oil chamber to the controller in real time, forming a closed-loop control circuit to ensure that the damping pressure output by the system is highly consistent with the command value.

[0140] Vibration sensor: Typically an accelerometer, it is mounted directly on the housing 1 or milling head 2 as close as possible to the vibration source. It is responsible for acquiring vibration signals (acceleration values) during the machining process in real time and converting them into electrical signals for transmission to the controller.

[0141] The goal of the system is to apply a damping torque that is opposite to the vibration trend in real time. The specific working process is as follows.

[0142] S1 Sensing (Vibration Detection): The vibration sensor continuously monitors the vibration intensity of the milling head 2 system, typically expressed in acceleration values ​​(m / s²). During heavy cutting processes in roughing and semi-finishing, the cutting force changes drastically, easily triggering chatter, and the sensor immediately captures these minute vibration signals.

[0143] S2 Decision (Intelligent Control Algorithm): The monitored vibration signal is sent to a numerical control system (CNC) or a dedicated adaptive controller. The controller has a preset control algorithm. The algorithm compares and calculates the vibration amplitude and frequency with the set thresholds.

[0144] If the vibration exceeds the safety threshold, the algorithm will immediately generate a control command: "Damping force needs to be increased."

[0145] This instruction is converted into a specific current signal sent to the servo valve.

[0146] S3 Execution (Pressure Regulation and Damping Generation):

[0147] The servo valve increases the hydraulic oil pressure leading to the first oil chamber 331 proportionally based on the received current signal.

[0148] The pressure sensor monitors the oil pressure synchronously to ensure that the pressure accurately reaches the target value.

[0149] The damping torque acts on the rotating disk 31 through the first deformation part 3311, effectively absorbing and dissipating vibration energy, just like "applying brakes" to the vibrating milling head 2, thereby quickly suppressing chatter.

[0150] Specifically, heavy cutting conditions requiring oscillating machining mainly include the following conditions:

[0151] Heavy cutting roughing:

[0152] Features: Large cutting depth, fast feed rate, extremely large cutting force and full of impact, which is the stage where chatter is most likely to occur.

[0153] The damping strategy system is set to high-sensitivity mode. The vibration threshold is set low, and the controller algorithm is more "aggressive." Once a vibration trend is detected, a large damping pressure is immediately applied to forcefully and quickly suppress the vibration, protecting the machine tool structure and cutting tools, and allowing the machine tool to operate at a higher metal removal rate.

[0154] Semi-finishing under heavy cutting:

[0155] Features: Cutting parameters are slightly slower than in roughing, but attention is now focused on surface quality and allowing for finishing. Vibration can cause shape errors and deterioration of surface texture.

[0156] Damping strategy: The system is set to precision control mode. The vibration threshold can be appropriately increased, and the control algorithm focuses more on smoothness and precision. The goal is to "iron" out subtle vibrations, rather than "violently" suppress them. This ensures surface quality while avoiding unnecessary energy loss and heat generation caused by excessive damping force.

[0157] Finishing and high-speed light cutting:

[0158] Features: It has very low cutting force and is extremely sensitive to vibration, but it has extremely high requirements for surface finish and dimensional accuracy.

[0159] Damping strategy: The system is typically off or maintains extremely low reference damping pressure. This is because high damping force at this point could introduce additional friction and "stick-slip" phenomena, affecting the positioning accuracy and smoothness of the milling head 2. The system only acts as a monitoring device, intervening only minimally unless abnormal vibration occurs.

[0160] Workflow and control logic (closed-loop feedback control):

[0161] This system constitutes a typical closed-loop negative feedback control system, as detailed below:

[0162] S1 Signal Acquisition and Processing: The vibration sensor transmits the acquired raw signal to the CNC control module. The signal is first filtered (low-pass filtering to remove high-frequency noise) and integrated (converting the acceleration signal into a displacement signal).

[0163] S2 Control Decision: The processed vibration signal is compared with the internally set value. The control algorithm (such as fuzzy PID) calculates and outputs a corresponding control voltage signal in real time based on the amplitude and frequency components of the vibration signal.

[0164] Advantages of fuzzy PID: Compared to traditional PID, it is better able to adapt to the nonlinear and time-varying characteristics of the cutting process. For example, the system can be set with rules: if the vibration amplitude is large and the vibration frequency is low to medium, then a larger control voltage is output; if the vibration amplitude is small and the frequency is high, then a medium control voltage is output.

[0165] S3 Pressure Regulation: The electro-hydraulic proportional valve receives voltage commands from the CNC and outputs the corresponding hydraulic pressure to the second oil chamber 351 accurately and quickly.

[0166] S4 Damping Force Generation: The hydraulic pressure acts on the rotating disk 31, causing it to generate a frictional force proportional to the hydraulic pressure. This force is the controllable damping force that suppresses vibration.

[0167] S5 Feedback and Correction: The pressure sensor feeds back the actual pressure value inside the damping disc to the CNC control module, compares it with the target pressure value calculated by the algorithm, and forms a closed-loop control to ensure the accurate application of damping force and compensate for interference such as internal system leakage.

[0168] Preferably, locking and damping share a single hydraulic power source, but are controlled by their respective independent valve groups to achieve precise and coordinated functions. The system can fine-tune the variation coefficient according to different cutting tools, and automatically memorize this information. In subsequent production, it can perform adaptive damping control on any workpiece, fully utilizing the machine tool's potential, optimizing the cutting load caused by vibration, and ensuring uniform tool wear, thus effectively extending tool life.

[0169] An adaptive damping control system based on multi-sensor feedback (vibration + pressure) is applied to milling head damping. The system can sense the cutting state in real time and dynamically and precisely adjust the damping force through a proportional valve, realizing a fundamental shift from "passively bearing vibration" to "actively and intelligently suppressing it," providing a core guarantee for high stability in heavy cutting and achieving stable five-axis linkage machining under relatively heavy cutting conditions.

[0170] refer to Figure 6 The input variable is the calculated value of the vibration signal after conditioning and filtering, and the output variable is the milling head damping 2, that is, the rotational damping along the horizontal axis. The adjustment point 1 is when the load exceeds 50%, and the adjustment coefficient is 150%; the adjustment point 2 is when the load is less than 20%, and the adjustment coefficient is 100%.

[0171] It can be understood that, except for conflicting parts, the above embodiments 1-7 can be freely combined to form other embodiments of the present invention.

[0172] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0173] In this invention, 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 or an electrical 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 invention according to the specific circumstances.

[0174] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first and second features are in direct contact, or that they are in indirect contact through an intermediate medium. Furthermore, "above," "over," or "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," or "beneath" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0175] The term "comprising" or any other similar term is intended to cover non-exclusive inclusion, such that a process, article, or apparatus / device that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to those processes, articles, or apparatus / devices.

[0176] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control, characterized in that, Includes housing (1), milling head (2), and damping locking assembly (3); The milling head (2) is self-lockingly hinged in the housing (1) along the horizontal axis; the damping locking assembly (3) is arranged in sequence away from the milling head (2) along the axial direction, including a coaxial rotating disk (31), a damping disk (32), a front clamping disk (33), a locking disk (34) and a rear clamping disk (35). The damping disc (32) and the locking disc (34) are both fixed relative to the milling head (2); the rotating disc (31), the front clamping disc (33) and the rear clamping disc (35) are fixed relative to the housing (1); the damping disc (32) is located within the axial gap between the rotating disc (31) and the front clamping disc (33), and the locking disc (34) is located within the axial gap between the front clamping disc (33) and the rear clamping disc (35); Both the front clamping plate (33) and the rear clamping plate (35) are capable of axial elastic deformation, so that the damping locking assembly (3) can selectively enter the damping state or the clamping state. In the damping state, the front clamping plate (33) can press the rotating plate (31) with the damping plate (32) to adapt to the heavy cutting condition when the milling head (2) has a swinging machining requirement. In the clamping state, the rear clamping plate (35) can press the front clamping plate (33) with the locking plate (34) to adapt to the heavy cutting condition when the milling head (2) does not have a swinging machining requirement. The damping locking components (3) are all hydraulically controlled; The front clamping plate (33) and the rear clamping plate (35) are respectively provided with a first oil cavity (331) and a second oil cavity (351); The first oil chamber (331) has a first deformation part (3311) near the side wall of the rotating disk (31) that is capable of axial elastic deformation, and the second oil chamber (351) has a second deformation part (3511) near the side wall of the front clamping disk (33) that is capable of axial elastic deformation. The end face of the damping disc (32) facing the first deformation part (3311) is the first pressure-bearing part (320), and the end face of the front clamping disc (33) facing the second deformation part (3511) is the second pressure-bearing part (332). When the pressure in the corresponding first oil cavity (3311) and the second deformation part (3511) reaches the corresponding threshold, they can selectively enter the damped state or the clamping state by axially pressing the corresponding first pressure part (320) or the second pressure part (332).

2. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 1, characterized in that, It also includes a drive wheel that is fixedly connected to the milling head (2) and whose axis coincides with the horizontal axis, and a rotating disk (31) is fixedly connected to the drive wheel.

3. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 2, characterized in that, The drive wheel is a worm gear (4); It also includes a worm (5) rotatably connected to the housing (1), the worm (5) meshing with the worm wheel (4), and the power can be transmitted unidirectionally from the worm (5) to the worm wheel (4).

4. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 3, characterized in that, It also includes a rotating shaft (6), a milling head (2) is fixedly connected to one axial end of the rotating shaft (6), the milling head (2) is self-lockingly hinged in the housing (1) along the horizontal axis through the rotating shaft (6), and the worm gear (4) is fixedly connected to the rotating shaft (6); The rotating shaft (6) extends axially to form a connecting section; The axial end face of the front clamping plate (33) extends away from the milling head (2) to form a stepped portion (3313), and the end face of the rear clamping plate (35) facing the front clamping plate (33) forms an annular groove (3512) that abuts against the stepped portion (3313). Both the front clamping plate (33) and the rear clamping plate (35) are sleeved on the rotating shaft (6). The damping disc (32) includes an axially extending sleeve (321) and a radially extending first spring (322). The sleeve (321) is fixed outside the rotating shaft (6), and the first spring (322) is fixedly connected to the radial outer wall of the sleeve (321). The first spring (322) extends between the rotating disc (31) and the front clamping disc (33). The rotating disk (31) is fitted over the sleeve (321) and is fixedly connected to the front clamping disk (33); The locking disc (34) includes a connecting ring (341) and a second spring (342). The connecting ring (341) is fixedly connected to the worm gear (4). The second spring (342) is fixedly connected to the axial end of the connecting ring (341) and extends between the front clamping disc (33) and the rear clamping disc (35). The second spring (342) is located on the circumferential outside of the stepped portion (3313).

5. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 4, characterized in that, It also includes an intermediate sleeve (7), and the front clamping plate (33) and the rear clamping plate (35) are both sleeved on the rotating shaft (6) through the intermediate sleeve (7); The end of the intermediate sleeve (7) away from the milling head (2) forms an outwardly radially extending end flange (71), and the assembly area of ​​the damping locking assembly (3) is formed in the circumferential space between the end flange (71) and the worm gear (4). The intermediate sleeve (7) is rotatably connected to the rotating shaft (6) and fixedly connected to the front clamping plate (33) and the rear clamping plate (35).

6. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 1, characterized in that, Both the front clamping plate (33) and the rear clamping plate (35) are provided with oil passages that communicate with the corresponding first oil chamber (331) and second oil chamber (351), and the oil passages are connected to the hydraulic system.

7. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in claim 1, characterized in that, It also includes interconnected control modules and vibration sensors; The vibration sensor is suitable for detecting the vibration parameters of the milling head (2) during milling operations and transmitting the measured vibration parameters to the control module; The control module uses vibration parameters combined with a preset algorithm to determine the damping force required by the damping component, and controls the hydraulic system to input the required pressure of hydraulic oil into the first oil chamber (331) according to the damping force.

8. The heavy-duty oscillating milling head for a five-axis machining center with hydraulic clamping and damping control as described in any one of claims 1-7, characterized in that, It also includes a torque transmission assembly (8), which includes a first bevel gear assembly (81), a cylindrical gear assembly (82), a second bevel gear (83), and a milling head bevel gear (84), all rotatably connected within the housing (1). The drive gear of the first bevel gear assembly (81), the second bevel gear (83), and the rotation axis of the milling head (2) during milling are coaxial; The cylindrical gear assembly (82) is used to drive the driven gear of the first bevel gear assembly (81) and the driving gear of the second bevel gear (83); The second bevel gear (83) meshes with the milling head bevel gear (84).

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