Milling head for milling machine tool

Abstract

The invention relates to a milling head for a milling machine tool, and relates to the technical field of milling heads, the milling head comprises a milling head shell, a vertical driving assembly is rotatably mounted in the milling head shell, a transverse driving assembly is rotatably mounted in the milling head shell, the vertical driving assembly is connected with the milling machine tool, and the vertical driving assembly drives the transverse driving assembly to rotate; a milling cutter head is detachably mounted on the transverse driving assembly, a vertical cooling cavity is formed in the milling head shell, a transverse cooling cavity is formed in the milling head shell, a cooling liquid channel is formed in the inner side between the vertical cooling cavity and the transverse cooling cavity, and cooling liquid circulating pipes are arranged on the outer sides of the vertical cooling cavity and the transverse cooling cavity; a vertical cooling liquid pushing assembly is installed on the vertical driving assembly, and a transverse cooling liquid pushing assembly is installed on the transverse driving assembly. The problems of cooling lag, local overheating and complex structure of a traditional milling head are solved, and the beneficial effects of reducing the temperature rise of the main shaft, restraining thermal deformation and improving the machining precision stability are achieved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of milling head, in particular to a milling head for milling machine. BACKGROUND

[0002] The milling machine is the core equipment for high-precision and high-efficiency metal cutting in modern manufacturing industry. The core executive component of the milling machine is the milling head, which is usually composed of a shell, a spindle driving mechanism, a tool mounting interface and a cooling and lubricating system. In the prior art, the mainstream milling head adopts an external independent cooling pump to circulate the cooling liquid through the pipeline, or relies on the cooling system of the machine tool to supply liquid to the milling head shell interlayer or tool handle passage through an external hose. Some high-end milling heads integrate a spiral groove flow guide structure inside the spindle to assist the axial delivery of the cooling liquid, but this structure only acts on the spindle in a single direction and requires an additional sealing partition and pressure source. Such milling heads generally separate the driving transmission system and the cooling system physically, and the cooling liquid flow relies on external power, which has problems such as pipeline redundancy, response lag, multiple sealing points and complex maintenance.

[0003] However, the above-mentioned milling head lacks a coordinated, active and compact heat dissipation capability for the double heat sources of the vertical driving assembly (such as the worm-turbine reduction mechanism) and the horizontal driving assembly (such as the orthogonal worm-turbine pair) during long-time high-load continuous machining, resulting in significant temperature rise of the key transmission parts, cumulative thermal deformation, and decreased meshing accuracy, which further causes tool vibration, increased machining surface roughness, abnormal tool wear and even sudden failure, seriously affecting the machining stability and equipment life. SUMMARY

[0004] The present application provides a milling head for a milling machine, which can solve the technical problems of overheating, tool wear and decreased machining accuracy caused by the lack of an effective cooling system in the conventional milling head during long-time high-load machining.

[0005] The milling head for a milling machine provided by the present application adopts the following technical solution: a milling head for a milling machine, comprising a milling head shell, a vertical driving assembly rotatably installed in the milling head shell, a horizontal driving assembly rotatably installed in the milling head shell, the vertical driving assembly being connected to the milling machine, the vertical driving assembly driving the horizontal driving assembly to rotate, a milling cutter head being detachably installed on the horizontal driving assembly, a vertical cooling cavity being provided in the milling head shell, a horizontal cooling cavity being provided in the milling head shell, a cooling liquid channel being provided between the inner sides of the vertical cooling cavity and the horizontal cooling cavity, a cooling liquid circulation pipe being provided on the outer sides of the vertical cooling cavity and the horizontal cooling cavity, a vertical cooling liquid pushing assembly being installed on the vertical driving assembly, and a horizontal cooling liquid pushing assembly being installed on the horizontal driving assembly.

[0006] Optionally, the vertical driving assembly comprises a driving connecting piece for connecting with the electric spindle of the milling machine tool, a vertical worm is installed on the driving connecting piece, a vertical turbine is installed on the vertical worm, and the vertical worm is connected with the vertical cooling cavity through a sealing bearing.

[0007] Optionally, the horizontal driving assembly comprises a horizontal worm, a horizontal turbine is installed on the horizontal worm, the horizontal turbine is engaged with the vertical turbine, and the horizontal worm is connected with the horizontal cooling cavity through a sealing bearing.

[0008] Optionally, the vertical cooling liquid pushing assembly comprises a vertical spiral pushing plate fixed on the vertical worm, a first balance counterweight ring is fixed at both ends of the vertical spiral pushing plate, the horizontal cooling liquid pushing assembly comprises a horizontal spiral pushing plate, and a second balance counterweight ring is fixed at both ends of the horizontal spiral pushing plate; the horizontal spiral pushing plate has a T-shaped structure in cross section, and the second balance counterweight ring and the outer edge of the horizontal spiral pushing plate are in close contact with the inner wall of the horizontal cooling cavity. Optionally, a plurality of fan-shaped counterweight blocks are installed on the first balance counterweight ring, an axial sliding block is arranged on the lower side of the fan-shaped counterweight block, an axial threaded rod is threadedly installed on the axial sliding block, axial springs are arranged on both sides of the axial sliding block, the axial springs are sleeved on the axial threaded rod, a sliding groove is formed in the first balance counterweight ring, the axial threaded rod passes through the sliding groove, the axial threaded rod is used for adjusting the position of the fan-shaped counterweight block, one end of the axial spring is in abutment with the axial sliding block, and the other end of the axial spring is in abutment with the sliding groove.

[0009] Optionally, a flow guide groove is formed in the inner wall of the horizontal cooling cavity, the flow guide groove extends to the side of the sealing bearing close to the milling cutter head, and the flow guide groove is used for making the cooling liquid flow back.

[0010] Optionally, a heat dissipation grid piece is installed in the vertical cooling cavity, the heat dissipation grid piece comprises a pair of flange plates fixed in the vertical cooling cavity, a support ring is installed on the flange plate, a positioning strip is fixed on the outer side of the support ring, a limiting groove is formed in the flange plate, the positioning strip is clamped with the limiting groove, and the sealing bearing is clamped with the inner wall of the support ring.

[0011] Optionally, a vertical cutting fluid cavity and a horizontal cutting fluid cavity are arranged in the milling head shell, a cutting fluid inlet pipe is fixed at the upper end of the vertical cutting fluid cavity, and a cutting fluid spraying pipe is fixed at the end of the horizontal cutting fluid cavity close to the milling cutter head.

[0012] Optionally, a cooling liquid discharge pipe is installed on the lower side of the milling head shell, and a cooling liquid addition pipe is installed on the upper end of the milling head shell.

[0013] Optionally, one end of the cooling liquid circulating pipe is in communication with the upper end of the vertical cooling cavity, and the other end of the cooling liquid circulating pipe is in communication with the end of the horizontal cooling cavity close to the milling cutter head.

[0014] In summary, the present application includes at least one of the following beneficial technical effects: The present application provides a milling head for a milling machine, by integrating a vertical driving assembly and a horizontal driving assembly in the milling head shell, and respectively installing a vertical cooling liquid pushing assembly and a horizontal cooling liquid pushing assembly thereon, using the driving assembly itself to directly push the cooling liquid to actively circulate in the vertical cooling cavity, the horizontal cooling cavity and the inner and outer cooling channels; since the cooling liquid pushing assembly rotates synchronously with the driving shaft, it can realize efficient and low-power "flow promotion by motion" cooling without external pump body; since the vertical cooling cavity and the horizontal cooling cavity are connected by double paths of the inner cooling liquid channel and the outer cooling liquid circulation pipe, and the cooling liquid circulation pipe adopts a high-temperature preferential flow direction design of "vertical cavity upper end→horizontal cavity cutter head side", the coverage and response speed of key heat sources such as the meshing area of the worm and the worm gear, the sealed bearing and the cutter installation end are significantly improved; since the horizontal spiral pushing plate adopts a T-shaped cross section and closely fits the cavity wall, combined with the flow guide groove and the heat dissipation grid piece, the flow sealing property and heat exchange efficiency are further strengthened; thereby solving the problems of traditional milling head cooling lag, local overheating and complex structure, achieving the beneficial effects of reducing spindle temperature rise, inhibiting thermal deformation, prolonging the service life of the transmission pair and improving the stability of machining precision. BRIEF DESCRIPTION OF DRAWINGS

[0015] Figure 1 is a schematic diagram of the overall structure of the embodiment of the present application; Figure 2 is a schematic diagram of the cross-sectional structure of the embodiment of the present application; Figure 3 is a schematic diagram of the structure of the vertical driving assembly and the horizontal driving assembly of the embodiment of the present application; Figure 4 is a schematic diagram of the structure of the milling head shell of the embodiment of the present application; Figure 5 is a schematic diagram of the cross-sectional structure of the milling head shell of the embodiment of the present application; Figure 6 is a schematic diagram of the structure of the first balance weight ring of the embodiment of the present application; Figure 7 is a schematic diagram of the structure of the first balance weight ring of the embodiment of the present application.

[0016] 1, milling head shell; 11, vertical cutting fluid cavity; 12, horizontal cutting fluid cavity; 13, cutting fluid inlet pipe; 14, cutting fluid spraying pipe; 15, cooling liquid discharge pipe; 16, cooling liquid addition pipe; 2, vertical driving assembly; 21, driving connecting piece; 22, vertical worm; 23, vertical turbine; 24, vertical spiral push plate; 25, first balance weight ring; 251, fan-shaped weight block; 252, axial sliding block; 253, axial threaded rod; 254, axial spring; 255, sliding groove; 3, horizontal driving assembly; 31, horizontal worm; 32, horizontal turbine; 4, milling cutter head; 5, vertical cooling cavity; 51, sealing bearing; 52, heat dissipation grid piece; 53, flange plate; 54, support ring; 55, positioning strip; 56, limiting groove; 6, horizontal cooling cavity; 61, flow guide groove; 7, cooling liquid channel; 8, cooling liquid circulation pipe; 9, vertical cooling liquid pushing assembly; 10, horizontal cooling liquid pushing assembly; 101, horizontal spiral push plate; 102, second balance weight ring. DETAILED DESCRIPTION

[0017] The following description will be made in conjunction with the accompanying drawings. Figure 1 - the accompanying drawings Figure 7 The application will be further described in detail.

[0018] Reference will be made to Figure 1 , Figure 2 A milling head for a milling machine, comprising a milling head shell 1, a vertical driving assembly 2 is rotatably installed in the milling head shell 1, a horizontal driving assembly 3 is rotatably installed in the milling head shell 1, the vertical driving assembly 2 is connected with the milling machine, the vertical driving assembly 2 drives the horizontal driving assembly 3 to rotate, a milling cutter head 4 is detachably installed on the horizontal driving assembly 3, a vertical cooling cavity 5 is arranged in the milling head shell 1, a horizontal cooling cavity 6 is arranged in the milling head shell 1, a cooling liquid channel 7 is arranged between the vertical cooling cavity 5 and the horizontal cooling cavity 6, a cooling liquid circulation pipe 8 is arranged outside the vertical cooling cavity 5 and the horizontal cooling cavity 6, a vertical cooling liquid pushing assembly 9 is installed on the vertical driving assembly 2, and a horizontal cooling liquid pushing assembly 10 is installed on the horizontal driving assembly 3.

[0019] The embodiment provides a kind of integrated double-shaft drive and self-driven collaborative cooling milling head structure.The core is that power transmission path and heat management path are deeply coupled: through vertical drive assembly, machine tool motor shaft input power is received, and horizontal drive assembly is simultaneously driven to realize tool space posture adjustment;At the same time, rotary motion is directly converted into cooling liquid delivery kinetic energy, so that the cooling system can form active circulation without independent pump source;Vertical cooling cavity and horizontal cooling cavity correspond to the heat source distribution characteristics of main drive shaft system and end cutting shaft system respectively, they are independent partition and form double-path communication structure by inside cooling liquid channel 7 and outside cooling liquid circulation pipe 8, and response speed and flow stability are considered;Detachable milling cutter head 4 uses standard interface such as HSK-A63, BT40 or CAT40 taper shank structure, supports quick tool changing and multi-type tool adaptation;The entire system is packaged in rigid milling head shell 1, and the shell material can be high-strength aluminum alloy such as 7075-T6 or nodular cast iron QT600-3, and light weight and thermal inertia buffering are considered.

[0020] The milling head shell 1 is a closed shell integrally cast or split machined and precisely assembled, which is internally provided with coaxial / orthogonal bearing seat cavities for mounting vertical driving assembly 2 and horizontal driving assembly 3, the inner wall of which is honed to ensure the roundness and roughness Ra≤0.8 μm of the mounting surface of the sealed bearing 51; the vertical driving assembly 2 is a power input unit rotating around the vertical direction of the machine tool Z, the input end of which is rigidly coupled with the output flange of the electric spindle of the milling machine tool through the driving connecting piece 21, the connection form including keyway + end face tooth meshing or interference fit + radial locking screw, to ensure that the torque transmission has no slip and the axial positioning is reliable; the horizontal driving assembly 3 is an output unit rotating around the horizontal direction X or Y, the axis of which is arranged at 90° to the axis of the vertical driving assembly 2, and the two are connected through a worm and gear pair to realize large reduction ratio, high rigidity and self-locking power transmission; the milling cutter head 4 is detachably fixed to the output end of the horizontal driving assembly 3 through the three-positioning mode of draw pin + conical surface + end face, the interface is compatible with ISO 7388-1 or DIN 69871 standard, and can also be replaced with a quick-change modular tool holder such as Capto C4 interface; the vertical cooling cavity 5 extends axially along the vertical driving assembly 2, and is annular or spiral groove-shaped and enveloped around the periphery of the vertical worm 22, the volume ratio being 18%-25% of the total volume of the internal cavity of the milling head shell 1, the cavity surface can be additionally provided with a micro-texture such as a laser-textured pit array with a diameter of 50-100 μm and a depth of 10-20 μm to enhance the liquid film adhesion and heat transfer coefficient; the horizontal cooling cavity 6 extends axially along the horizontal driving assembly 3, and is arranged around the horizontal worm 31 and the horizontal turbine 32, the cross section of which is oblate oval to adapt to the horizontal space constraint, and the inner wall maintains a dynamic gap of 0.1-0.3 mm with the outer edge of the horizontal spiral push plate 101; the cooling liquid channel 7 is a radial hole or inclined flow channel penetrating the inner side wall of the vertical cooling cavity 5 and the horizontal cooling cavity 6, the hole diameter is Φ2-Φ5 mm, the number is 3-6, and the axis is at an angle of 15°-30° to the center line of the two cavities to optimize the liquid flow impact direction; the cooling liquid circulating pipe 8 is an external flexible metal hose such as 316L stainless steel bellows or a hard alloy pipe, the two ends of which are connected to the upper end of the vertical cooling cavity 5 and the end close to the milling cutter head 4 of the horizontal cooling cavity 6 respectively through quick connectors, the inner diameter of the pipe is Φ6-Φ10 mm, and the total length is controlled within 300-600 mm to reduce the along-the-way loss; the vertical cooling liquid pushing assembly 9 is fixed on the body of the vertical worm 22 and rotates synchronously with it to generate axial thrust to drive the cooling liquid to flow upward or downward in one direction; the horizontal cooling liquid pushing assembly 10 is fixed on the body of the horizontal worm 31 and rotates synchronously with it to generate a combined effect of circumferential shearing and axial extrusion, thereby strengthening the liquid flow disturbance and boundary layer renewal in the horizontal cooling cavity 6.

[0021] The spatial layout relationship of the vertical driving assembly 2 and the transverse driving assembly 3 determines the kinematic characteristics of the whole machine: the rotation axes of the two are strictly orthogonal and intersect near the theoretical cutting point of the milling cutter head 4, with an error of ≤0.05 mm, thereby ensuring the unity of dynamic decoupling and thermal deformation compensation reference; the vertical cooling cavity 5 and the transverse cooling cavity 6 are not simply connected in series, but realize pressure coupling high-pressure area→low-pressure area short-path flow guiding through the cooling liquid channel 7, and realize flow coupling steady-state large-flow circulation through the cooling liquid circulation pipe 8, and the two cooperate to avoid local dry burning and air resistance; the vertical cooling liquid pushing assembly 9 and the transverse cooling liquid pushing assembly 10 are both driven by the rotating body itself, without introducing additional energy consumption, and the pumping capacity and the speed of the two are approximately in a square relationship Q ∝ n², and in the typical machining speed range of 500-6000 rpm, the cooling liquid flow rate can be maintained at 0.3-2.5 m / s, which meets the targeted cooling needs of bearings, gear meshing areas and tool clamping sections; the detachability of the milling cutter head 4 not only embodies the convenience of mechanical connection, but also lies in its thermal interface design - a heat-conducting silicone grease layer or a copper foil gasket with a thickness of 0.05-0.1 mm is arranged between the tool shank and the output end of the transverse driving assembly 3, which ensures that the cutting heat energy is efficiently introduced into the transverse cooling cavity 6 for dissipation.

[0022] Through the above technical scheme, the application realizes that during the operation of the milling machine, when the vertical driving assembly 2 is rotated by the electric spindle, on the one hand, the power is transmitted to the transverse driving assembly 3 through the meshing of the vertical turbine 23 and the transverse turbine 32, driving the milling cutter head 4 to complete horizontal direction feeding cutting; on the other hand, the vertical cooling liquid pushing assembly 9 rotates synchronously with the vertical worm 22, forming an axial pressure gradient in the vertical cooling cavity 5, pushing the cooling liquid to enter the transverse cooling cavity 6 through the inner cooling liquid channel 7, and part of the cooling liquid flows into the transverse cooling cavity 6 through the outer cooling liquid circulation pipe 8; the cooling liquid entering the transverse cooling cavity 6 is accelerated under the action of the transverse cooling liquid pushing assembly 10 and flushes the surface of the transverse worm 31, the transverse turbine 32 and the clamping section of the milling cutter head 4, and after absorbing heat, the high-temperature cooling liquid returns to the area adjacent to the sealed bearing 51 along the flow guide groove 61, and then returns to the vertical cooling cavity 5 through the cooling liquid channel 7 or the circulation pipe 8 for secondary heat dissipation. Since the vertical cooling cavity 5 has a large heat capacity and surface area, and is provided with a built-in heat dissipation grid 52, it can effectively buffer the transient thermal load; and the transverse cooling cavity 6 is close to the core area of the heat source, realizing rapid thermal response. Therefore, this structure fundamentally solves the technical problems of high temperature rise, large thermal drift and short tool life of the spindle system caused by the passive cooling and path fragmentation of the traditional milling head, and significantly improves the machining precision retention, system operation stability and multi-task adaptability under high-speed milling conditions.

[0023] Referring to Figure 2 , Figure 3The vertical driving assembly 2 comprises a driving connecting piece 21 for connecting with an electric spindle of the milling machine tool, a vertical worm 22 is installed on the driving connecting piece 21, and a vertical worm wheel 23 is installed on the vertical worm 22, and the vertical worm 22 is connected with the vertical cooling cavity 5 through a sealing bearing 51.

[0024] The vertical driving assembly 2 is a core transmission unit for realizing active power input and vertical motion transmission, and the overall structure is designed with the design targets of high rigidity, low vibration and dynamic sealing. The driving connecting piece 21 is a hollow cylindrical flange structure, the outer periphery is provided with a key groove matched with the output end of the electric spindle and a radial positioning stop, and the inner hole is provided with a threaded hole or a tapered surface matching section for rigidly connecting with the output shaft of the electric spindle; the material of the driving connecting piece 21 can be selected from 40CrNiMoA quenched and tempered steel, and the surface is subjected to nitriding treatment to improve wear resistance and torsional stiffness. The driving connecting piece 21 not only bears the torque transmission function, but also serves as the installation base and axial positioning reference of the vertical worm 22.

[0025] The vertical worm 22 is a single-head or double-head involute worm, the module is 2.5-4 mm, the helix angle is 15°-25°, the tooth surface is subjected to carburizing quenching and grinding processing, and the surface hardness reaches HRC58-62; one end of the vertical worm 22 is axially fixed on the inner extension shaft section of the driving connecting piece 21 through interference fit or locking nut, the other end is suspended into the interior of the vertical cooling cavity 5, and the rotation support and cavity isolation are realized through the sealing bearing 51. The vertical worm wheel 23 is a whole-circle worm wheel made of ZCuSn10P1 cast tin bronze, the tooth width is matched with the length of the meshing section of the worm, the tooth profile is a modified Archimedes worm pair tooth profile which is conjugate with the worm, and the vertical worm wheel 23 is installed on the input end shaft of the transverse driving assembly 3, that is, the specific embodiment 3, and the torque output is realized through key connection; the vertical worm wheel 23 and the vertical worm 22 form a worm-worm wheel transmission pair with a reduction ratio of 15:1 to 30:1, and have self-locking capability, which can prevent the transverse driving assembly 3 from accidentally rotating due to gravity or cutting reaction force in the case of power failure or sudden stop.

[0026] The sealing bearing 51 is a double-row angular contact ball bearing or a deep groove ball bearing with a double-lip sealing structure, the inner ring is interference-fitted with the shaft neck of the vertical worm 22, and the outer ring is transition-fitted with the bearing seat hole of the vertical cooling cavity 5; the sealing lip of the sealing bearing 51 faces the interior of the cooling cavity, is made of fluororubber FKM, can resist immersion in cooling liquid and short-term temperature rise of 120°C, and has three functions of radial load, axial thrust and dynamic sealing; the sealing bearing 51 ensures that the cooling liquid does not penetrate into the side of the driving connecting piece 21 along the axial direction under the condition that the vertical worm 22 rotates at a high speed with a rated speed of ≤3000 r / min, and prevents external oil mist or cutting debris from entering the vertical cooling cavity 5.

[0027] The above components work together: the drive connecting piece 21 stably guides the power output by the electric spindle into the vertical worm 22; the vertical worm 22 meshes with the vertical turbine 23, converts the high-speed low-torque input into low-speed high-torque output, and drives the subsequent horizontal transmission chain; the sealing bearing 51 ensures the reliable rotation of the vertical worm 22 while forming a physical isolation barrier between the cooling cavity and the external driving area. The three together constitute an integrated vertical drive subsystem that integrates power input, mechanical transmission, and boundary control of thermal management.

[0028] Through the above technical solution, the application achieves: when the milling machine tool electric spindle starts and outputs rotary power, the power is transmitted to the vertical worm 22 through the drive connecting piece 21, which drives the vertical turbine 23 to rotate synchronously, thereby driving the horizontal drive assembly 3 to act; In this process, the sealing bearing 51 continuously maintains the airtight state of the vertical cooling cavity 5, avoiding the migration of cooling liquid along the vertical worm 22 to the driving connecting piece 21 and the electric spindle connection interface, which not only prevents the cooling liquid from polluting the electric spindle lubrication system, but also avoids the reverse intrusion of external impurities into the cooling cavity, which causes the heat dissipation efficiency to decrease; At the same time, the self-locking characteristic of the worm-turbine mechanism improves the operation safety of the system under emergency stop, power failure or heavy load cutting. The structure solves the technical problems of unreliable dynamic sealing between the vertical drive components and the cooling cavity, insufficient transmission stability, and uncontrolled displacement of the horizontal assembly in the stop state in the background technology, significantly improving the reliability and life of the milling head in the multi-axis linkage and high-precision continuous cutting working condition.

[0029] Referring to Figure 2 , Figure 3 The horizontal drive assembly 3 includes a horizontal worm 31, a horizontal turbine 32 is installed on the horizontal worm 31, the horizontal turbine 32 is meshed between the vertical turbine 23, and the horizontal worm 31 is connected with the horizontal cooling cavity 6 through the sealing bearing 51.

[0030] The transverse driving assembly 3 is the core transmission unit for realizing the conversion of the milling direction from the vertical main driving force to the transverse cutting output. Its structural design needs to consider the power transmission efficiency, axial space constraint, rotary sealing reliability and thermal management adaptability. The transverse worm 31 is used as the rotating main shaft, which bears the radial load and torque output of the milling cutter head 4. The transverse turbine 32 is rigidly connected to the transverse worm 31, forming an integrated turbine-worm pair, receiving the rotary motion from the vertical turbine 23 through the tooth surface engagement, and converting the torque into the rotation of the transverse worm 31, thereby driving the milling cutter head 4 to perform transverse feeding or deflection cutting operation. The transverse worm 31 is supported at both ends in the inner wall of the milling head housing 1, one end of which penetrates into the transverse cooling cavity 6, and the rotary support and cavity isolation are realized through the sealing bearing 51. The sealing bearing 51 adopts a double-lip structure fluororubber sealing ring + stainless steel skeleton composite radial sealing bearing. The inner ring is interference fitted on the shaft neck of the transverse worm 31, and the outer ring is pressed into the bearing seat hole of the corresponding end cover of the transverse cooling cavity 6, which ensures that the cooling liquid does not leak into the transmission mechanism along the axial direction, and allows the transverse worm 31 to rotate stably at a rated speed of ≤1200 r / min. The engagement relationship between the transverse turbine 32 and the vertical turbine 23 is a worm gear with a vertical shaft intersection angle of 90°, a module of 2.5 mm, a pressure angle of 20°, a worm head number of 1, and a turbine tooth number of 40. This parameter combination ensures the transmission ratio i=40:1, suppresses the risk of reverse self-locking, and reduces the sliding speed to reduce heat generation; the transverse turbine 32 can be machined after integral casting of tin bronze ZCuSn10P1, or replaced by a 20CrMnTi alloy steel gear ring with surface nitriding treatment, to improve wear resistance and anti-gluing ability; the transverse worm 31 can be made of 40Cr quenched and tempered + surface high-frequency hardened with a hardness of HRC52-56, or replaced by a ceramic matrix composite such as Si3N4 reinforced Al2O3 hollow shaft structure, which reduces the weight by 35% under the same stiffness, reduces the moment of inertia, and improves the dynamic response characteristics.

[0031] The transverse worm 31 is the rotation reference axis of the transverse driving assembly 3, and its axis is parallel and coplanar with the rotation axis of the milling cutter head 4, and is used for directly or indirectly transmitting the cutting torque; the transverse turbine 32 is a force receiving component at the power input end, and the rim thereof is provided with an annular oil groove and a radial oil guide hole, and during the engagement of the transverse turbine 32 and the vertical turbine 23, the lubricating oil is thrown into the engagement area through the oil guide hole by centrifugal force to form a continuous oil film; the engagement position of the transverse turbine 32 and the vertical turbine 23 is located in the area where the axes of the two are orthogonal, so as to ensure that the force flow path is the shortest and the contact stiffness is the highest; the sealing bearing 51 not only bears the radial load, but also compensates the axial displacement caused by thermal expansion through pre-tightening structures such as spring pre-tightening or gasket adjustment, so as to maintain the long-term sealing integrity of the transverse cooling cavity 6. The mechanical connection between the transverse worm 31 and the transverse cooling cavity 6 is established through the sealing bearing 51, and the connection simultaneously realizes three functions: one is a rotation motion transmission path, the second is a cooling medium static isolation barrier, and the third is a vibration transmission blocking interface - when the transverse worm 31 produces a micro axial displacement due to cutting impact, the elastic sealing lip of the sealing bearing 51 is deformed controllably to absorb the displacement without damaging the seal, so as to avoid the axial leakage of the cooling liquid to the gear engagement area to cause lubrication failure.

[0032] The cooperation of each component is as follows: when the vertical turbine 23 continuously rotates, the tooth surface of the vertical turbine 23 pushes the tooth groove of the transverse turbine 32, so that the transverse turbine 32 drives the transverse worm 31 to rotate synchronously; the transverse worm 31 stably rotates around its own axis under the constraint of the sealing bearing 51, and the milling cutter head 4 connected to the output end of the transverse worm 31 obtains transverse cutting motion; at the same time, the cooling liquid in the transverse cooling cavity 6 flows along the inner wall of the cavity in the circumferential direction under the driving of the transverse spiral push plate 101, and the sealing bearing 51 is located at the key section of the cooling liquid flow channel - the integrated guide slope of the outer bearing seat of the sealing bearing 51 guides part of the cooling liquid to the end surface of the bearing friction pair, so as to realize the double cooling and lubrication of the sealing lip and the rolling body, and significantly prolong the sealing life. The connection between the transverse worm 31 and the transverse cooling cavity 6 is no longer a static supporting relationship, but a functional integrated node of “rotating shaft-sealing interface-cooling flow channel”.

[0033] By the technical scheme, the following is achieved: under the premise of keeping the vertical main driving force source unchanged, the vertical rotary motion is efficiently converted into lateral rotary output through orthogonal meshing of the lateral worm 31, the lateral turbine 32 and the vertical turbine 23; the sealing bearing 51 synchronously undertakes three tasks of rotary supporting, cooling cavity isolation and local flow field guiding, so that the lateral driving assembly 3 still maintains transmission precision and cooling system reliability under high-load cutting conditions. Because the lateral turbine 32 and the vertical turbine 23 are directly meshed, the intermediate coupling or transition gear set is omitted, the length of the transmission chain and the cumulative error are reduced, and the technical problems of complex structure of the lateral output shaft system, redundant axial size and easy invasion of the cooling medium into the transmission pair in the traditional multi-axis milling head are solved; and because the lateral worm 31 is directly connected to the lateral cooling cavity 6 through the sealing bearing 51, the additional independent cooling pipeline wall-penetrating structure is avoided, and the leakage risk and local heat accumulation caused thereby are eliminated, so that the environmental adaptability and long-term operation stability of the milling head as a whole are improved.

[0034] With reference to Figure 2 , Figure 3 The vertical cooling liquid pushing assembly 9 comprises a vertical spiral pushing plate 24 fixed on the vertical worm 22, and the vertical spiral pushing plate 24 is fixed with a first balance weight ring 25 at both ends; the lateral cooling liquid pushing assembly 10 comprises a lateral spiral pushing plate 101, and the lateral spiral pushing plate 101 is fixed with a second balance weight ring 102 at both ends; the lateral spiral pushing plate 101 has a T-shaped structure in cross section, and the second balance weight ring 102 and the lateral spiral pushing plate 101 are in close contact with the inner wall of the lateral cooling cavity 6.

[0035] The embodiment proposes an integrated cooling liquid pushing structure based on direct driving of cooling liquid circulation by rotary motion of a driving shaft, and the core is that the spiral pushing plate is rigidly fixed on the rotary driving part, the rotational kinetic energy of the shaft system is converted into the directional axial conveying force of the cooling liquid, the dynamic balance under high-speed working conditions is realized through the balance weight ring, and the effective sealed flow channel is formed through the close cooperation of the T-shaped cross section and the cavity wall, so that the collaborative circulation of the cooling liquid between the vertical and lateral cooling cavities is completed without relying on external pumping devices. The scheme discards the complex cooling driving system which needs to additionally configure a motor, a pipeline valve and an independent sealing cavity, and significantly reduces the size, assembly difficulty and fault point number of the whole machine.

[0036] The vertical helical push plate 24 is a thin-walled metal plate structure extending in a helix along the vertical worm 22 in the axial direction, with a helix angle of 12°-20°, and a helix angle of 15° can be selected. The material is high-strength aluminum alloy such as 7075-T6 or stainless steel such as SUS304, which is fixed circumferentially on the outer cylindrical surface of the vertical worm 22 by interference fit or radial screw fastening, to ensure that there is no relative slip when transmitting torque. Its function is to continuously push the cooling liquid in the vertical cooling cavity 5 to flow upward or downward along the axial direction when the vertical worm 22 rotates, forming a one-way pulsating propulsion flow field. As an optional embodiment, the vertical helical push plate 24 can also adopt a double-head helical structure, that is, two groups of helical blades are arranged on the same worm in opposite directions to offset part of the axial thrust; or it can be replaced by a variable-pitch helical structure with a gradually changing pitch to adapt to the dynamic needs of cooling liquid flow rate at different axial positions in the cavity.

[0037] The first balance weight ring 25 is an annular member, which is segmented as a whole and consists of a plurality of circumferentially distributed sector-shaped weight blocks 251. Each sector-shaped weight block 251 is connected to the end flange of the vertical helical push plate 24 through a radial sliding groove and is fixed by a locking screw. The mass distribution is designed initially, allowing dynamic balance calibration by adjusting the radial position of each sector-shaped weight block 251 after assembly is completed, with a calibration accuracy of G2.5 level ISO 1940-1 standard. The material is high-density alloy steel such as 40CrNiMoA or tungsten alloy, to provide sufficient inertial compensation in limited space. As an optional embodiment, the first balance weight ring 25 can also adopt an integral annular weight structure, with a plurality of axial adjustment grooves on the outer circumference, and the mass can be adjusted by adding or removing embedded weight blocks; or it can be replaced by a magnetic adjustable weight module, which uses the attractive force between the permanent magnet array and the magnetically conductive base to achieve non-mechanical contact weight adjustment.

[0038] The horizontal helical push plate 101 is an axial helical member mounted on the horizontal worm 31, with a T-shaped cross section. The flange part of the T-shaped structure forms a face-contacting fit with the inner wall of the horizontal cooling cavity 6, with a fit gap of ≤0.05 mm, ensuring that the flange part is always tightly attached to the cavity wall during the rotation of the horizontal worm 31, and forming a closed helical conveying flow channel with the inner wall of the cavity. The material is wear-resistant engineering plastic such as PEEK or alloy steel such as 20CrMnTi with surface nitriding treatment, to balance low friction and structural strength. As an optional embodiment, the T-shaped cross section of the horizontal helical push plate 101 can also be replaced by an inverted L-shaped or dovetail-shaped cross section, as long as it can ensure that the protruding part forms a continuous, stable, and low-leakage radial sealing band with the cavity wall; its installation method can also be changed from integral hot mounting to split buckle connection, which is convenient for disassembly and maintenance.

[0039] The second balance weight ring 102 is a ring-shaped weight structure symmetrically arranged at both ends of the transverse spiral push plate 101. The inner hole of the second balance weight ring 102 is in transition fit with the transverse worm 31, and the outer edge contour is concentric with the inner wall of the transverse cooling cavity 6. The maximum outer diameter is smaller than the inner diameter of the cavity by 0.1-0.3 mm. The second balance weight ring 102 functions to offset the mass eccentricity of the transverse spiral push plate 101 caused by the T-shaped cross section and the imbalance of the rotational centrifugal force, and suppress the vibration amplification effect of the transverse driving assembly 3 at high speed. The material of the second balance weight ring 102 is the same as or matched with the first balance weight ring 25 to ensure that the thermal expansion coefficients are similar. As an optional implementation, the second balance weight ring 102 can also be integrated into the body of the transverse spiral push plate 101, that is, the T-shaped main plate part is directly thickened and extended to form a ring-shaped weight section at both ends, realizing structural integration. Alternatively, a liquid dynamic balance cavity structure can be used to encapsulate a freely flowing inert liquid medium in the ring-shaped cavity, and the liquid center of gravity is automatically migrated to compensate for the unbalance in real time.

[0040] There is a certain mechanical coupling relationship between the above-mentioned components: the rotational movement of the vertical worm 22 directly drives the synchronous rotation of the vertical spiral push plate 24, which in turn pushes the cooling liquid in the vertical cooling cavity 5 to flow axially. After the cooling liquid passes through the cooling liquid channel 7 and enters the transverse cooling cavity 6, the transverse spiral push plate 101 is rotated by the transverse worm 31. The T-shaped flange part and the cavity wall form a sealed spiral flow channel to force the cooling liquid to be pushed to the proximal end of the milling cutter head 4 along the transverse worm 31. The first balance weight ring 25 and the second balance weight ring 102 constrain the mass centers of the vertical and transverse rotation systems, respectively, so that both of them maintain low-amplitude stable operation within their respective speed ranges. The T-shaped structure of the transverse spiral push plate 101 not only provides fluid thrust, but also directly affects the fitting state of the flange part and the cavity wall, which is directly affected by the rotation accuracy and support stiffness of the transverse worm 31. Therefore, the coaxiality of the installation of the sealing bearing 51 and the cylindricity of the inner hole of the transverse cooling cavity 6 together constitute the key constraint conditions of the cooling liquid delivery efficiency.

[0041] By the technical scheme, when the electric spindle of the milling machine drives the vertical driving assembly 2 to operate, the vertical worm 22 rotates to drive the vertical spiral push plate 24 to work, and pushes the cooling liquid upward from the bottom of the vertical cooling cavity 5; after the cooling liquid flows into the horizontal cooling cavity 6 through the inner cooling liquid channel 7, the horizontal worm 31 rotates synchronously under the meshing transmission of the vertical turbine 23-horizontal turbine 32, drives the horizontal spiral push plate 101 to make spiral conveying movement in the closed flow channel formed by the T-shaped section and the cavity wall, and continuously pressurizes the cooling liquid to the end close to the milling cutter head 4; in this process, the first balance weight ring 25 and the second balance weight ring 102 respectively implement dynamic balance compensation for the vertical and horizontal rotating systems, inhibit high-frequency vibration caused by uneven mass distribution of the spiral push plate, and guarantee the stability and continuity of the cooling liquid conveying flow field. Because the external cooling liquid pump and its supporting pipeline and control system are cancelled, the problems of redundant structure, response lag, poor sealing reliability and high maintenance cost of the existing milling head cooling system are solved, so that the technical effects of high integration of cooling and driving, strong controllability of cooling liquid flow field, high stability of the whole machine operation and significant reduction of system failure rate are achieved.

[0042] With reference to Figure 3 , Figure 6 , Figure 7 A plurality of fan-shaped weight blocks 251 are installed on the first balance weight ring 25, the lower side of the fan-shaped weight block 251 is provided with an axial sliding block 252, an axial threaded rod 253 is threadedly installed on the axial sliding block 252, axial springs 254 are arranged on both sides of the axial sliding block 252, the axial springs 254 are sleeved on the axial threaded rod 253, a sliding groove 255 is formed in the first balance weight ring 25, the axial threaded rod 253 passes through the sliding groove 255, the axial threaded rod 253 is used for adjusting the position of the fan-shaped weight block 251, and one end of the axial spring 254 abuts against the axial sliding block 252 and the other end abuts against the sliding groove 255.

[0043] The first balance weight ring 25 is a non-continuous weight block array, and the first balance weight ring 25 is uniformly distributed with fan-shaped weight blocks 251 along the circumference, and each group is composed of a radial adjustable sliding block.

[0044] Wherein, the "non-continuous counterweight block array" refers to the first balance counterweight ring 25 does not adopt the overall ring structure, but is composed of a plurality of independent counterweight units separated from each other and not connected to each other; each unit is arranged at equal angles along the circumferential direction of the vertical screw push plate 24, forming a discrete mass distribution pattern; this structure avoids the problem that the traditional whole ring counterweight must be replaced or machined due to local mass deviation leading to global imbalance, and at the same time provides a physical basis for single-point mass adjustment; the number of units in the array is 6-12, and the corresponding circumferentially distributed angle is 30°-60°, which ensures the adjustment resolution and takes into account the structural stiffness and assembly space constraints; the radial cross section of each fan-shaped counterweight block 251 is in the form of a fan ring, the inner arc surface is attached to the mounting base surface of the end of the vertical screw push plate 24, and the outer arc surface profile matches the curvature of the inner wall of the vertical cooling cavity 5, in order to maintain the symmetry of rotational inertia; the material is selected from high-density alloy steel, tungsten alloy or sintered hard alloy, with a density range of 7.8 g / cm³-19.3 g / cm³, to adapt to the centrifugal force load under different speed conditions.

[0045] Wherein, the "fan-shaped counterweight block 251" is the basic functional unit that constitutes the non-continuous array, and its geometric form is defined by the central angle, radial thickness and axial height; the central angle is 20°-45°; the radial thickness is 8 mm-25 mm; the axial height is consistent with the flange thickness of the end of the vertical screw push plate 24, which is 12 mm-30 mm; each fan-shaped counterweight block 251 is slidably connected to the corresponding guide rail on the end surface of the vertical screw push plate 24 through the sliding groove 255 provided on the back, and is axially limited by the axial spring 254, to ensure that it does not move axially during operation.

[0046] Wherein, "each group is composed of a radially adjustable slider" means that each fan-shaped counterweight block 251 itself integrates an independent radial displacement adjustment mechanism; the slider is an embedded structure, arranged along the radial center line of the fan-shaped counterweight block 251, and the axial slider 252 is embedded in the sliding groove 255 of the fan-shaped counterweight block 251; the axial slider 252 is provided with a fine adjustment threaded hole and is threadedly connected with the axial threaded rod 253; rotating the axial threaded rod 253 can drive the axial slider 252 to move a small amount in the radial direction, thereby performing targeted mass compensation on the rotating subsystem composed of the vertical screw push plate 24 and the vertical worm 22 rigidly connected thereto; this adjustment mechanism does not rely on disassembly or replacement of parts, and only needs to obtain the unbalance amplitude and phase through a dynamic balance tester after the static assembly of the milling head is completed, and then distribute the radial displacement instructions to each fan-shaped counterweight block 251 according to the vector decomposition principle, to complete the closed-loop calibration.

[0047] Through the above technical solution, this application achieves the following: without changing the original structural layout and transmission path of the vertical drive assembly 2, the first balance counterweight ring 25 is decoupled into independently adjustable discrete mass units, and each unit is given radial displacement capability with millimeter-level precision. Because the first balance counterweight ring 25 adopts a non-continuous counterweight block array, and each sector counterweight block 251 is composed of radially adjustable sliders, it can target and correct the local mass asymmetry generated when the vertical spiral push plate 24 rotates at high speed, overcoming the technical defects of traditional integral counterweight rings that cannot be locally adjusted and cannot meet the microgram-level dynamic balance precision requirements at high speeds. In turn, it effectively suppresses the peak vibration acceleration of the vertical drive assembly 2 under operating conditions above 3000 r / min, reduces the dynamic contact stress of the meshing pair between the sealed bearing 51 and the vertical turbine 23, delays the pressure pulsation during the coolant propulsion process, ensures the stability of the coolant flow field in the vertical cooling chamber 5, and ultimately improves the overall running stability and long-term machining reliability of the milling head.

[0048] (The structure and principle of the second counterweight ring 102 are the same as those of the first counterweight ring 25, and will not be described in detail here.)

[0049] Reference Figure 2 , Figure 5 A guide groove 61 is provided on the inner wall of the transverse cooling chamber 6. The guide groove 61 extends to the side of the sealed bearing 51 near the milling cutter head 4. The guide groove 61 is used to allow the coolant to flow back.

[0050] This embodiment achieves active diversion of coolant in the area adjacent to the sealed bearing by setting a directional extending guide groove 61 on the inner wall of the transverse cooling chamber 6. This significantly improves the problem of coolant stagnation and poor return in this local area, thereby ensuring the continuity of the coolant circulation path and pressure stability, and indirectly improving the lubrication conditions and thermal management reliability of the sealed bearing 51.

[0051] Wherein, the transverse cooling cavity 6 is a ring-shaped or approximately ring-shaped closed cavity arranged axially along the transverse driving assembly 3 inside the milling head shell 1, the inner wall of which is a smooth curved surface matched with the outer edge of the transverse spiral push plate 101 and the second balance weight ring 102 to form a dynamic seal; the flow guide groove 61 is a groove structure formed axially or spirally along the inner wall, with a rectangular, trapezoidal or circular arc cross section, a depth of 0.3 mm-1.2 mm, a width of 1.5 mm-4.0 mm, and a length extending continuously from the main section of the transverse cooling cavity 6 to the boundary of the radial projection of the sealing bearing 51 installation position, and the terminal end thereof is located in the axial end face projection area of the outer ring of the sealing bearing 51 near the milling cutter head 4 side; the arrangement ensures that the flow guide groove 61 can effectively cover the low flow area where the cooling liquid is easily accumulated in front of the bearing after being pushed by the transverse spiral push plate 101. As an optional embodiment, the flow guide groove 61 can be provided as a single axial straight groove, or as two or more axially distributed grooves, or as a continuous spiral groove with a spiral angle of 5°-15° spirally rising along the inner wall to adapt to the liquid film distribution characteristics under different rotating speed conditions; the groove surface is polished with a roughness Ra≤0.8 μm to reduce the flow resistance.

[0052] Wherein, the sealing bearing 51 is an angular contact ball bearing or a double-row cylindrical roller bearing, the outer ring of which is fitted into the bearing seat hole at the end of the transverse cooling cavity 6 with interference fit, and the inner ring is interference fitted with the transverse worm 31; the terminal position of the flow guide groove 61 is strictly limited to the extension projection range of the axial end face of the outer ring of the sealing bearing 51 towards the milling cutter head 4 side, i.e. the axial distance from the terminal end of the flow guide groove 61 to the axial end face of the outer ring of the sealing bearing 51 on this side is not greater than 0.5 mm, thereby ensuring that the cooling liquid is guided out of the high-pressure retention area before entering the bearing sealing lip; this positioning relationship is independent of the bearing pre-tightening force or assembly tolerance, and is only guaranteed by a one-time boring and milling process during the machining of the milling head shell 1, which has process robustness.

[0053] Wherein, "for making the cooling liquid backflow" does not mean forming a complete loop independently, but means locally forming a low-resistance reverse channel inside the transverse cooling cavity 6, so that the cooling liquid pushed by the transverse spiral push plate 101 along the cavity wall, and tends to settle due to the weakening of the centrifugal effect in front of the sealing bearing 51, under the combined action of gravity and the cavity pressure difference, flows along the flow guide groove 61 in the axial or spiral direction to the communication port of the cooling liquid circulation pipe 8 or the low-position outlet of the transverse cooling cavity 6; this function does not change the main circulation direction of the cooling liquid, i.e. from the vertical cooling cavity 5→the cooling liquid channel 7→the transverse cooling cavity 6→the cooling liquid circulation pipe 8, but is used to eliminate the local dead zone. As a variant, the terminal end of the flow guide groove 61 can be connected to a pre-set liquid collection pit at the bottom of the transverse cooling cavity 6, and then introduced into the cooling liquid discharge pipe 15 branch through a micropore with a diameter of Φ0.6 mm-Φ1.0 mm, to form an auxiliary backflow sub-path.

[0054] The cooperation of each structure is embodied as follows: the transverse spiral push plate 101 rotates to push the cooling liquid to move circumferentially along the transverse cooling cavity 6, and the outer edge thereof is attached to the cavity wall to form a dynamic positive pressure area; when the cooling liquid travels to the vicinity of the sealing bearing 51, the flow rate is reduced and the static pressure is increased due to the structural mutation and the flow channel contraction, so that vortex flow and liquid film accumulation are easily formed; at this time, the flow guide groove 61 provides a radial-axial composite pressure relief path for the high static pressure area due to the axial through property and the terminal precise positioning thereof, so that part of the cooling liquid preferentially flows along the groove body to the downstream area of the cavity with lower pressure, thereby breaking the local pressure balance, inhibiting bubble residence and liquid phase separation, and maintaining the uniform coverage of the cooling liquid in the transverse cooling cavity 6.

[0055] Through the above technical solution, the present application realizes that the flow guide groove 61 extending to the side of the sealing bearing 51 close to the milling cutter head 4 is arranged on the inner wall of the transverse cooling cavity 6, so that the cooling liquid pushed to the sealing bearing adjacent area by the transverse spiral push plate 101 can timely escape from the residence area through the low-resistance channel provided by the flow guide groove 61 and flow back to the downstream of the cooling system; because the structural form, size parameters and terminal space positioning of the flow guide groove 61 are designed in adaptation to the natural accumulation law of the cooling liquid in the sealing bearing 51 front side of the transverse cooling cavity 6, the problem of poor backflow and local accumulation of the cooling liquid in this area is effectively alleviated, and the phenomena of insufficient lubrication, abnormal temperature rise and uneven cooling heat exchange of the sealing bearing 51 caused thereby are avoided, and the thermal stability and operation reliability of the milling head under the condition of continuous high load milling are improved.

[0056] Referring to Figure 2 , Figure 3 , Figure 5 The vertical cooling cavity 5 is provided with a heat dissipation grid piece 52, the heat dissipation grid piece 52 comprises a pair of flange plates 53 fixed in the vertical cooling cavity 5, a support ring 54 is arranged on the flange plate 53, a positioning strip 55 is fixed outside the support ring 54, a limiting groove 56 is formed on the flange plate 53, the positioning strip 55 is clamped with the limiting groove 56, and the sealing bearing 51 is clamped with the inner wall of the support ring 54.

[0057] The embodiment significantly enhances the heat exchange efficiency and flow stability of the cooling liquid in the cavity by integrating a modular heat dissipation grid 52 inside the vertical cooling cavity 5 without increasing the external cooling power source. The flange plate 53 is rigidly fixed to the inner walls of the axial ends of the vertical cooling cavity 5 by interference fit or bolt fastening as the basic load-bearing structure, ensuring the anti-vibration performance and positional accuracy of the overall structure under high-speed rotating conditions. The support ring 54 is a hollow ring-shaped member with a radial cross-section in the shape of a rectangle or trapezoid, made of aluminum alloy such as 6061-T6 or copper alloy such as H62 brass with a thermal conductivity not less than 150 W / (m·K), which not only serves as a cooling liquid flow channel separation function but also as an efficient heat conduction path to quickly spread the heat conducted by the vertical drive assembly 2 through the sealed bearing 51 to the cavity to the milling head housing 1. The positioning strips 55 are distributed in axial symmetry along the outer periphery of the support ring 54, with a number of 3-6, and their cross-section is in the shape of a convex or swallowtail, forming a radial + axial double-constrained mechanical clamping with the corresponding limiting groove 56 provided on the flange plate 53. This clamping structure allows the support ring 54 to be adjusted in the circumferential angle along the flange plate 53 plane during assembly to adapt to the installation eccentricity of the sealed bearing 51, and also supports the later replacement without disassembly. The limiting groove 56 is a full-length straight groove or a segmented arc-shaped groove, with a groove width tolerance controlled within ±0.05 mm and a depth of 1.2-2.0 mm, ensuring that there is no loose gap after the positioning strip 55 is inserted. The outer ring of the sealed bearing 51 and the inner wall of the support ring 54 adopt a transition fit H7 / k6, and the inner ring is interference fit with the vertical worm 22, so that the support ring 54 simultaneously constitutes the axial positioning reference and the heat conduction interface of the bearing. This design breaks through the limitation of traditional natural heat exchange relying on the cavity wall, forcibly divides the originally single flow channel laminar cooling liquid into multiple spiral turbulent flow paths, prolongs the effective heat exchange distance, and improves the turbulent intensity of the unit volume of cooling liquid.

[0058] The flange plate 53 can be replaced by a ring-shaped steel plate with a central through hole and welded to the end of the vertical cooling cavity 5, or an integrated cast structure can be used to omit the assembly process. The support ring 54 can also be made of two half-type split rings, with the split surface positioned by a stopper and locked by screws, to facilitate installation in a small cavity. The clamping form of the positioning strip 55 and the limiting groove 56 can also be replaced by a flexible clamping structure such as a cantilever plastic clamping hook embedded in a metal groove, a magnetic positioning structure with a neodymium iron boron magnet embedded in the positioning strip 55, a magnetic steel sheet provided at the bottom of the limiting groove 56, or filling the limiting groove 56 with curable silicone to achieve flexible limiting and vibration reduction. The inner wall surface of the support ring 54 can be additionally provided with a 0.1-0.3 mm deep spiral heat conduction pattern, or sprayed with an aluminum nitride ceramic coating with a thickness of 15-30 μm to further improve the interface heat conduction density. The clamping relationship between the sealed bearing 51 and the inner wall of the support ring 54 can also be achieved by providing an axial groove in the inner wall of the support ring 54 and embedding an elastic O-ring in the groove to realize a pre-tightening flexible clamping, which takes into account the thermal expansion compensation and vibration isolation.

[0059] The cooperation of each component is embodied as follows: the flange plate 53 provides a static installation reference, the support ring 54 becomes a main heat transfer channel due to its structural rigidity and high thermal conductivity, the positioning strip 55 and the limiting groove 56 jointly ensure the spatial posture stability of the support ring 54 under dynamic load, and the direct contact between the sealing bearing 51 and the support ring 54 opens up an efficient longitudinal heat conduction link of “vertical worm 22→sealing bearing 51→support ring 54→flange plate 53→milling head housing 1”; when the cooling liquid flows through the annular gap channel formed by the support ring 54, the flow state is changed from laminar flow to turbulent flow due to the disturbance of the edge of the positioning strip 55 and the surface roughness of the support ring 54, the Nusselt number Nu is increased by 20%-35%, and the equivalent heat exchange area is increased by more than 1.8 times.

[0060] Through the above technical solutions, the following is achieved: an integrated heat dissipation grid piece 52 with the functions of structural support, heat conduction enhancement and flow field regulation is constructed in the vertical cooling cavity 5; after the cooling liquid enters the vertical cooling cavity 5, it is divided into multiple sub-flow channels that spiral along the circumference by the support ring 54, the flow velocity distribution is more uniform, and local stagnation and heat accumulation are avoided; because the support ring 54 is directly connected with the sealing bearing 51, the friction heat generated during the operation of the vertical driving assembly 2 is quickly introduced into the support ring 54 through the bearing outer ring, and then radiated to the milling head housing 1 through the flange plate 53, greatly reducing the temperature rise in the meshing area of the vertical worm 22 and the vertical turbine 23; because the positioning strip 55 and the limiting groove 56 constitute a precise connection that can be repeatedly disassembled and assembled, the heat dissipation grid piece 52 can be replaced or cleaned without disassembling the entire milling head housing 1, and the maintenance cycle is shortened by more than 40%; finally, without adding pumps and valves, without changing the cooling liquid formula, and without increasing the circulating pressure, the average temperature drop of the vertical cooling cavity 5 reaches 8-12℃, effectively alleviating the problem of transmission error accumulation of the vertical driving assembly 2 caused by thermal deformation, and improving the size repeatability precision of milling.

[0061] Referring to Figure 1 , Figure 2 , Figure 3 , the milling head housing 1 is provided with a vertical cutting fluid cavity 11 and a horizontal cutting fluid cavity 12, the vertical cutting fluid cavity 11 is fixed with a cutting fluid inlet pipe 13 at the upper end, and the horizontal cutting fluid cavity 12 is fixed with a cutting fluid spraying pipe 14 at one end close to the milling cutter head 4.

[0062] The milling head shell 1 is a rigid shell integrally cast or separately machined, made of high-strength aluminum alloy or nodular cast iron, and has a cavity structure formed by precision boring and numerical control milling, which is isolated and functionally divided. The vertical cutting fluid cavity 11 is arranged along the axial direction of the milling head shell 1, and has a cylindrical or rectangular cross-section, the axis of which coincides with the rotation center line of the vertical driving assembly 2, and is used for receiving and temporarily storing the cutting fluid supplied from the outside. The horizontal cutting fluid cavity 12 extends along the horizontal direction of the milling head shell 1, and has an axis perpendicular to the axis of the vertical cutting fluid cavity 11 and parallel to the rotation center line of the horizontal driving assembly 3, and the cross-section of the cavity is elliptical or rectangular with rounded corners, so as to adapt to the spatial layout of the horizontal worm 31 and the peripheral support structure. The two cavities are connected through an internal flow guide channel, which is part of the milling head shell 1 body structure, and is arranged between the lower side wall of the vertical cutting fluid cavity 11 and the starting end of the horizontal cutting fluid cavity 12. The channel has an inner diameter of Φ6-Φ12 mm and a surface roughness Ra≤1.6 μm, which ensures low resistance and directional delivery of the cutting fluid.

[0063] The cutting fluid inlet pipe 13 is a stainless steel hard pipe or an enhanced polytetrafluoroethylene soft pipe, and has an outer diameter of Φ8-Φ15 mm. One end of the cutting fluid inlet pipe 13 is fixed to the center of the top of the vertical cutting fluid cavity 11 through a threaded sealing joint such as NPT 1 / 4" or G3 / 8", and the other end is connected to the central cutting fluid supply system of the machine tool. The axis of the cutting fluid inlet pipe 13 is collinear with the axis of the vertical cutting fluid cavity 11, and the inlet end is provided with a one-way valve and a pressure buffer section, which can prevent backflow and pressure impact. The cutting fluid spraying pipe 14 is a micro nozzle made of copper alloy or corrosion-resistant stainless steel, and has an outer diameter of Φ3-Φ6 mm. The cutting fluid spraying pipe 14 is fixed to the side wall at the end of the horizontal cutting fluid cavity 12, and the outlet end thereof faces the installation position of the cutting edge of the milling cutter head 4. The included angle between the nozzle axis and the rotation plane of the cutter head is 15°-45°. The nozzle is integrated with a micro fan-shaped nozzle or a double-hole symmetrical nozzle, and the spraying coverage width is 1.2-1.8 times the diameter of the cutter. The O-ring + sleeve type compression sealing structure is used between the cutting fluid spraying pipe 14 and the horizontal cutting fluid cavity 12, and the integrity of the cavity is not damaged when disassembled.

[0064] The vertical cutting fluid cavity 11 and the horizontal cutting fluid cavity 12 are physically isolated cavities in the milling head shell 1, there is no direct through opening between the two, and only one-way fluid communication is realized through the aforementioned built-in flow guide channel; this design avoids the disorderly diffusion or stagnation of cutting fluid in the cavity, ensures controllable flow and clear path; as an optional implementation, a throttle orifice plate with a thickness of 1-2 mm and a center opening of Φ2-Φ4 mm throttle hole can be added in the horizontal cutting fluid cavity 12, which is used to adjust the flow and pressure of the cutting fluid spraying pipe 14; the cutting fluid inlet pipe 13 can also be replaced by an integrated interface module with a solenoid valve to realize on-demand liquid supply control triggered by the CNC program; in addition, the cutting fluid spraying pipe 14 can be replaced by a ring-shaped spraying seat, that is, 3-6 micro-nozzles are evenly distributed around the output flange of the horizontal driving assembly 3, and are arranged around the milling cutter head 4 base to improve the uniformity of cooling.

[0065] The cooperation of each component is as follows: after the cutting fluid is injected into the vertical cutting fluid cavity 11 through the cutting fluid inlet pipe 13, it flows stably into the horizontal cutting fluid cavity 12 under the dual action of gravity and system pressure along the built-in flow guide channel; due to the limited axial length of the horizontal cutting fluid cavity 12 and the narrowing of the end, the fluid is accelerated and maintains a certain dynamic pressure, and finally is accurately delivered to the contact area between the milling cutter head 4 and the workpiece in the form of atomization or jet through the cutting fluid spraying pipe 14. This path design makes the cutting fluid complete pressure stabilization and impurity preliminary settlement before entering the spraying link, significantly reducing the risk of nozzle blockage; at the same time, because the vertical and horizontal cutting fluid cavities 12 are independently formed and directionally guided, they completely avoid cross-mixing with the circulating cooling liquid in the vertical and horizontal cooling cavities 5 and 6, ensuring that the cutting fluid is pure and stable in concentration, meeting the compatible needs of various process media such as emulsion, extreme pressure oil or micro-lubrication MQL.

[0066] Through the above technical scheme, a compact, clear, responsive and dedicated cutting fluid supply subsystem is constructed without interfering with the operation of the main cooling system; because the vertical cutting fluid cavity 11 and the horizontal cutting fluid cavity 12 are independently arranged in the milling head shell 1 and are respectively provided with dedicated inlet and outlet interfaces, the problem of lack of in-situ, directional and controllable cutting fluid supply capability of existing milling heads is solved; because the cutting fluid inlet pipe 13 is located at the top of the cavity, the cutting fluid spraying pipe 14 is arranged close to the milling cutter head 4, and there is no sharp corner in the flow channel, the cutting fluid can reach the cutting area in time, thereby improving the chip removal efficiency, suppressing the temperature rise in the cutting area, and improving the roughness Ra value of the machined surface to 0.2-0.8 μm; this system can be adapted to various milling cutter heads 4 such as high-speed steel, hard alloy and PCD, and can also be compatible with dry, wet and hybrid processing modes, and has good process adaptability and equipment compatibility.

[0067] Reference Figure 1 , Figure 2The lower side of the milling head shell 1 is provided with a cooling liquid discharge pipe 15, and the upper end of the milling head shell 1 is provided with a cooling liquid addition pipe 16.

[0068] In this embodiment, the cooling liquid discharge pipe 15 and the cooling liquid addition pipe 16 constitute a basic fluid interface system, the core of which is to realize directional filling and gravity-driven emptying of the cooling liquid through vertical separation of the spatial position, thereby solving the maintenance problems such as poor liquid addition, residual liquid retention, and incomplete liquid replacement caused by the convergence of the cooling liquid addition port and the discharge port and the unreasonable layout of the traditional milling head. The structure can complete the cooling liquid renewal operation under normal working conditions without relying on external pumping or vacuum assistance, thereby significantly reducing the complexity and time cost of daily maintenance operations.

[0069] The cooling liquid discharge pipe 15 is arranged on the lower side of the milling head shell 1, i.e., at the position of the lowest potential energy point of the cooling circuit in the installed state of the whole machine; its axis extends vertically downward, and the pipe opening end face is flush with or slightly lower than the bottom surface profile of the milling head shell 1, so as to ensure that the cooling liquid can be naturally collected and completely flowed out by gravity in the static state; the pipe body is made of corrosion-resistant metal material such as 304 stainless steel or aluminum alloy with surface anodic oxidation treatment, the inner diameter is Φ8 mm-Φ12 mm, the wall thickness is ≥1.0 mm, and the end part is provided with a standard threaded interface such as G1 / 4” internal thread or a quick plug connector, so as to be connected with an external waste liquid collection container or a circulating filter device. (As an optional implementation manner, the cooling liquid discharge pipe 15 can be integrated with a manual ball valve or an electromagnetic shut-off valve, but it is a conventional adaptation means in the art and is used for controlling the start and stop of liquid discharge; a transparent liquid viewing section can also be added in the middle of the pipeline, so as to observe the liquid discharge state and whether the residual liquid is completely discharged.) The cooling liquid addition pipe 16 is arranged on the upper end of the milling head shell 1, i.e., at the position of the highest potential energy point of the cooling system in the installed state of the whole machine; its axis is vertically upward or upwardly inclined at an angle ≤30°, and the pipe opening is higher than the top liquid level design upper limit of the vertical cooling cavity 5 by at least 20 mm, so as to reserve a safety air gap and prevent overflow; the pipe body material is consistent with the cooling liquid discharge pipe 15, the inner diameter is Φ6 mm-Φ10 mm, and the end part is provided with an injection port structure with a sealing cover or a compatible pressure injection connector such as a DIN 4760 standard quick-change interface; in the non-liquid addition state, the pipe opening is closed by an elastic silica gel sealing plug or a screw-in plug with an O-ring, so as to ensure the sealing and dustproof and waterproof performance of the cooling cavity. As an optional implementation manner, the cooling liquid addition pipe 16 can be extended to the outside of the milling head shell 1 and provided with a liquid level scale mark, or used in cooperation with a liquid level sensor such as a capacitive liquid level switch, to realize the visualization and automatic control of the liquid addition process; such an extension does not change the basic structure of this embodiment and conforms to the technical evolution path that can be reasonably predicted by those skilled in the art based on the interface position.

[0070] The relative spatial relationship of the cooling liquid discharge pipe 15 and the cooling liquid addition pipe 16 on the milling head shell 1 constitutes a pair of functionally complementary fluid channels: the axes thereof are arranged in approximate vertical opposition, with a vertical height difference ≥ 150 mm, which ensures sufficient driving head to overcome the flow resistance along the path and local resistance when the cooling liquid flows in the internal cavities including the vertical cooling cavity 5, the transverse cooling cavity 6 and the cooling liquid channel 7; at the same time, the height difference also provides natural siphon starting conditions for the cooling liquid circulation pipe 8, which is beneficial to improving the active heat exchange efficiency between the vertical and transverse cavities after the initial liquid injection of the system is completed. Both pipes penetrate the wall of the milling head shell 1 and are sealed by welding, screwing, sealing glue or O-ring compression, with a sealing level not lower than IP54, meeting the long-term reliability requirements in the oil mist and cutting fluid splashing environment of the machine tool processing site.

[0071] Through the above technical scheme, the application realizes the upper and lower split type fluid interface layout of arranging the cooling liquid discharge pipe 15 at the lower side of the milling head shell 1 and arranging the cooling liquid addition pipe 16 at the upper end. Since the cooling liquid discharge pipe 15 is located at the lowest point and the cooling liquid addition pipe 16 is located at the highest point, the cooling liquid can fill the entire cooling cavity system from top to bottom when injected, avoiding air resistance and cavities; when the machine is stopped and the liquid is discharged, the residual liquid automatically flows under the action of gravity and is completely discharged through the cooling liquid discharge pipe 15, without low-liquid accumulation dead angle. Therefore, the structure effectively alleviates the low daily maintenance efficiency problem caused by inconvenient cooling liquid injection and incomplete waste liquid discharge in the background art, and improves the equipment maintenance convenience, cooling system cleanliness and long-term operation stability.

[0072] With reference to Figure 1 , one end of the cooling liquid circulation pipe 8 is in communication with the upper end of the vertical cooling cavity 5, and the other end is in communication with the end of the transverse cooling cavity 6 close to the milling cutter head 4.

[0073] The technical scheme defines the cooling liquid circulation path as a one-way forced flow layout from the upper end of the vertical cooling cavity to the external circulation pipe to the end of the transverse cooling cavity close to the milling cutter head, thereby constructing a cooling liquid external circulation channel with clear structure and controllable path. The core is to use the synergistic effect of gravity assistance and rotating kinetic energy of the driving assembly to preferentially deliver the cooling liquid to the area near the milling cutter head 4 with the highest heat load and the most urgent heat dissipation demand, thereby improving the local thermal response efficiency; at the same time, this arrangement completely avoids the problems of high machining difficulty, high sealing risk and easy flow channel blockage caused by drilling through cooling holes in the milling head shell 1, significantly enhancing the system reliability and manufacturability.

[0074] The coolant circulation pipe 8 is a flexible or rigid tubular component, made of pressure- and corrosion-resistant 304 stainless steel, polytetrafluoroethylene (PTFE), or reinforced nylon composite material. Its inner diameter ranges from Φ4mm to Φ12mm, and its wall thickness is not less than 0.8mm to balance flow requirements and mechanical strength. Both ends of the pipe are detachably and sealed to the upper interface of the vertical cooling chamber 5 and the front interface of the horizontal cooling chamber 6 via quick-connect fittings or O-ring sealed threaded fittings, facilitating future maintenance and replacement. In an optional embodiment, the coolant circulation pipe 8 adopts a double-jacketed structure, with an outer heat insulation layer to suppress the backflow of ambient heat into the coolant flow path and maintain low-temperature stability.

[0075] The upper end of the vertical cooling chamber 5 is provided with an axial outlet with internal threads. The centerline of this outlet coincides with the axis of the vertical cooling chamber 5, ensuring that the coolant is drawn out from the central area at the top of the chamber, avoiding increased turbulence of the liquid surface or the risk of cavitation due to eccentric suction. After the outlet is connected to the inlet end of the coolant circulation pipe 8, a dead-zone-free transition section is formed, with a minimum radius of curvature not less than three times the inner diameter of the pipe, to reduce local pressure loss. In an optional embodiment, a miniature check valve is integrated at the outlet to prevent coolant from flowing back into the vertical cooling chamber 5 and causing abnormal liquid level when the machine is stopped.

[0076] A radial inlet is provided at one end of the transverse cooling chamber 6 near the milling cutter head 4. This inlet is located within the first quarter of the axial length of the transverse cooling chamber 6, and its axis is perpendicular to the axis of the transverse cooling chamber 6 and inclined at 5° to 15° towards the milling cutter head 4. This guides the coolant to be injected tangentially along the inner wall of the transverse cooling chamber 6, enhancing the scouring and cooling effect on the outer edge of the transverse spiral pusher plate 101 and the second balance weight ring 102. The inlet is connected to the outlet end of the coolant circulation pipe 8 through a floating sealing flange, allowing for a certain amount of axial and angular assembly deviation. In an optional embodiment, the inlet is replaced by a porous distributor structure, consisting of 3 to 5 evenly distributed micropores with a single pore diameter of Φ0.6mm to Φ1.2mm, to achieve more uniform coolant distribution.

[0077] There are defined spatial and functional coupling relationships among the aforementioned components: the coolant circulation pipe 8, as a connecting medium independent of the main structural cavity, directly determines the starting and ending points of coolant energy transfer at its two end interfaces; the upper end of the vertical cooling chamber 5 serves as the high-level cold source output end, forming a potential energy difference driving basis with the front end of the horizontal cooling chamber 6 as the low-level heat sink input end; and the positioning of the front end of the horizontal cooling chamber 6 strictly corresponds to the mounting reference surface of the milling cutter head 4, ensuring that the coolant arrival position coincides with the spatial coordinates of the heat source. This layout does not rely on the internal flow channel connection of the vertical drive component 2 or the horizontal drive component 3, nor does it involve the opening and closing control of the coolant channel 7; the cooling strategy guidance is completed solely by defining the physical interface positions.

[0078] By the technical scheme, the application realizes that, under the premise of not changing the basic transmission structure of the milling head and the body design of the cooling cavity, by only adjusting the two-end connection position of the external cooling liquid circulating pipe 8, the cooling liquid delivery logic can be changed from the traditional "homogeneous circulation" to "targeted supply". Since the cooling liquid is led out from the upper end of the vertical cooling cavity 5, at this time, the liquid level is high, the static pressure is sufficient, and the flow stability is strong; and the fresh low-temperature cooling liquid is injected into the horizontal cooling cavity 6 close to one end of the milling cutter head 4, so that the fresh low-temperature cooling liquid covers the tool support area and the working condition area of the horizontal worm 31 end bearing at the first time, effectively inhibiting the local temperature rise mutation caused by the superposition of cutting heat conduction and friction heat; thereby, without increasing additional power elements, without introducing complex control logic, and without changing the original sealing structure, the cooling timeliness and temperature field uniformity of the key heat-sensitive area are significantly improved, and the machining precision drift problem caused by thermal deformation is relieved.

[0079] The embodiments of the specific embodiment are the preferred embodiments of the application, and are not intended to limit the protection scope of the application, wherein the same parts are denoted by the same reference numerals. Therefore: any equivalent changes made according to the structure, shape, principle of the application should be covered within the protection scope of the application.

Claims

1. A milling head for a milling machine, characterized in that, The milling head shell (1) is provided with a vertical driving assembly (2) and a transverse driving assembly (3), the vertical driving assembly (2) is connected with a milling machine, the vertical driving assembly (2) drives the transverse driving assembly (3) to rotate, the transverse driving assembly (3) is detachably provided with a milling cutter head (4), the milling head shell (1) is provided with a vertical cooling cavity (5) and a transverse cooling cavity (6), the vertical cooling cavity (5) and the transverse cooling cavity (6) are provided with a cooling liquid channel (7) and a cooling liquid circulation pipe (8), the vertical driving assembly (2) is provided with a vertical cooling liquid pushing assembly (9), and the transverse driving assembly (3) is provided with a transverse cooling liquid pushing assembly (10).

2. A milling head for a milling machine according to claim 1, characterized in that The vertical driving assembly (2) comprises a driving connecting piece (21), the driving connecting piece (21) is connected with an electric spindle of the milling machine, the driving connecting piece (21) is provided with a vertical worm (22), the vertical worm (22) is provided with a vertical turbine (23), and the vertical worm (22) is connected with the vertical cooling cavity (5) through a sealing bearing (51).

3. A milling head for a milling machine according to claim 2, characterized in that The transverse driving assembly (3) comprises a transverse worm (31), the transverse worm (31) is provided with a transverse turbine (32), the transverse turbine (32) is engaged with the vertical turbine (23), and the transverse worm (31) is connected with the transverse cooling cavity (6) through a sealing bearing (51).

4. A milling head for a milling machine according to claim 3, characterized in that The vertical cooling liquid pushing assembly (9) comprises a vertical spiral pushing plate (24) fixed on the vertical worm (22), the vertical spiral pushing plate (24) is provided with a first balance counterweight ring (25) at both ends, the transverse cooling liquid pushing assembly (10) comprises a transverse spiral pushing plate (101), the transverse spiral pushing plate (101) is provided with a second balance counterweight ring (102) at both ends, the transverse spiral pushing plate (101) is in T-shaped structure, and the second balance counterweight ring (102) and the transverse spiral pushing plate (101) are attached to the inner wall of the transverse cooling cavity (6).

5. A milling head for a milling machine according to claim 4, characterized in that The first balance counterweight ring (25) is provided with a plurality of fan-shaped counterweight blocks (251), the fan-shaped counterweight blocks (251) are provided with an axial sliding block (252) at the lower side, the axial sliding block (252) is provided with an axial threaded rod (253) in a threaded mode, the axial sliding block (252) is provided with an axial spring (254) at both sides, the axial spring (254) is sleeved on the axial threaded rod (253), the first balance counterweight ring (25) is provided with a sliding groove (255), the axial threaded rod (253) passes through the sliding groove (255), the axial threaded rod (253) is used for adjusting the position of the fan-shaped counterweight block (251), one end of the axial spring (254) is in abutment with the axial sliding block (252), and the other end is in abutment with the sliding groove (255).

6. A milling head for a milling machine according to claim 5, characterized in that The inner wall of the transverse cooling cavity (6) is provided with a flow guide groove (61), which extends to the side of the sealing bearing (51) close to the milling cutter head (4) and is used for backflow of the cooling liquid.

7. A milling head for a milling machine according to claim 6, characterized in that The vertical cooling cavity (5) is provided with a heat dissipation grid piece (52), which comprises a pair of flange plates (53) fixed in the vertical cooling cavity (5), a support ring (54) fixed on the flange plate (53), a positioning strip (55) fixed on the outer side of the support ring (54), a limiting groove (56) provided on the flange plate (53), and the positioning strip (55) and the limiting groove (56) are connected, and the sealing bearing (51) and the inner wall of the support ring (54) are connected.

8. A milling head for a milling machine according to claim 5, characterized in that, The milling head shell (1) is provided with a vertical cutting fluid cavity (11) and a transverse cutting fluid cavity (12), the upper end of the vertical cutting fluid cavity (11) is fixed with a cutting fluid inlet pipe (13), and the end of the transverse cutting fluid cavity (12) close to the milling cutter head (4) is fixed with a cutting fluid spraying pipe (14).

9. A milling head for a milling machine according to claim 5, characterized in that, The lower side of the milling head shell (1) is provided with a cooling liquid discharge pipe (15), and the upper end of the milling head shell (1) is provided with a cooling liquid addition pipe (16).

10. A milling head for a milling machine according to claim 6, characterized in that, One end of the cooling liquid circulating pipe (8) is communicated with the upper end of the vertical cooling cavity (5), and the other end is communicated with the end of the transverse cooling cavity (6) close to the milling cutter head (4).

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