Dual-spindle milling head and machine tool having the same

Abstract

The application discloses a double-spindle milling head and a machine tool with the same. The double-spindle milling head comprises a first mounting part, a second mounting part, a first spindle and a second spindle. The second mounting part is mounted on the first mounting part and can rotate relative to the first mounting part; the first spindle is arranged on the first mounting part and can rotate around its own axis; and the second spindle is arranged on the second mounting part and can rotate around its own axis. The application can at least solve the problem that the included angle of the two spindles of the double-spindle milling head in the prior art is fixed, thereby causing poor machining adaptability of the milling head.

Description

Technical Field

[0001] This application relates to the field of milling technology, and more specifically, to a dual-spindle milling head and a machine tool having therein. Background Technology

[0002] In the field of CNC milling, automatic universal milling heads and twin-spindle milling heads are mainly used to achieve high-efficiency machining in two angular directions. However, automatic universal milling heads are costly to manufacture in order to achieve automatic spindle axis angle conversion; moreover, automatic universal milling heads are only equipped with one spindle, and each angle conversion requires a spindle angle direction conversion, which affects machining efficiency. Twin-spindle milling heads, on the other hand, usually have a fixed angle between the two spindles, and can only perform machining in two fixed angular directions, thus limiting their application range. Summary of the Invention

[0003] The main objective of this application is to provide a dual-spindle milling head and a machine tool having the same, so as to solve the problem that the fixed angle between the two spindles in the existing dual-spindle milling head leads to poor adaptability of the milling head.

[0004] According to one aspect of this application, a dual-spindle milling head is provided, comprising: First Installation Department; A second mounting part is mounted on the first mounting part and is rotatable relative to the first mounting part; A first spindle is disposed on the first mounting part and can rotate about its own axis; The second spindle is disposed in the second mounting part and can rotate about its own axis.

[0005] Furthermore, when the second mounting part rotates relative to the first mounting part, the axis of the second spindle moves in a first plane, and the axis of the first spindle is parallel to the first plane; and / or, the first mounting part is provided with a mounting hole, and the second mounting part is provided with a plug-in part, the plug-in part being at least partially inserted into the mounting hole and rotatable relative to the mounting hole; the dual-spindle milling head also includes a locking member, the locking member being at least partially loosely and securely disposed on the second mounting part, so as to lock the second mounting part to the first mounting part when the second mounting part rotates to the position relative to the first mounting part.

[0006] Furthermore, the first mounting portion is provided with an annular groove, which is coaxially arranged with the mounting hole; the locking component includes a plurality of locking members, which pass through the second mounting portion and can move circumferentially along the annular groove as the second mounting portion rotates; and / or, The dual-spindle milling head also includes a sealing ring, which is disposed in the gap between the insertion part and the mounting hole.

[0007] Furthermore, the dual-spindle milling head also includes: A drive mechanism is disposed in the first mounting part and can be selectively connected to the first spindle and the second spindle to drive the first spindle to rotate or drive the second spindle to rotate.

[0008] Furthermore, the drive mechanism includes: A drive shaft, on which a drive component is provided that can move along the axial direction of the drive shaft; A first transmission component is connected to the first main shaft to transmit power from the transmission shaft to the first main shaft to drive the first main shaft to rotate. The second transmission component is connected to the second main shaft to transmit the power of the transmission shaft to the second main shaft to drive the second main shaft to rotate. A toggle component is disposed on the first mounting portion to drive the drive member to move along the axial direction of the transmission shaft and selectively connect with the first transmission member or with the second transmission member.

[0009] Furthermore, the actuating component includes: A drive cylinder, which is mounted on the first mounting portion; A shift fork is connected between the drive cylinder and the drive member, and under the drive of the drive cylinder, it drives the drive member to move along the axial direction of the transmission shaft.

[0010] Furthermore, the shift fork is connected to the drive member and can rotate relative to the drive shaft about the axis of the drive shaft; The drive cylinder includes a piston rod, and the actuating component includes a guide rod. Both the piston rod and the guide rod are arranged parallel to the transmission shaft. The piston rod and the guide rod are respectively connected to the shift fork at a predetermined distance. Under the drive of the drive cylinder, the guide rod reciprocates synchronously with the piston rod along the axial direction of the transmission shaft.

[0011] Furthermore, the axis of the transmission shaft is parallel to the axis of the first main shaft; The driving component includes a first spur gear; The first transmission component includes a second spur gear, which is fixedly sleeved on the first main shaft for meshing with the first spur gear.

[0012] Furthermore, the second transmission component includes: The first bevel gear includes a first mounting shaft and a first bevel gear body fixedly connected to the first mounting shaft. The first mounting shaft is parallel to the transmission shaft and rotatably mounted on the first mounting part. The third spur gear is fixedly sleeved on the first mounting shaft for meshing with the first spur gear; A reversing gear set is disposed between the first bevel gear and the second main shaft to transmit power from the drive shaft to the second main shaft.

[0013] Furthermore, the reversing gear set includes: The second bevel gear includes a second mounting shaft, a second bevel gear body and a third bevel gear body respectively fixedly disposed at both ends of the second mounting shaft, the second mounting shaft being perpendicular to the first mounting shaft, and the second bevel gear body meshing with the first bevel gear body; The third bevel gear is fixedly mounted on the second main shaft and meshes with the body of the third bevel gear.

[0014] Furthermore, the first mounting portion includes a first housing component, which surrounds and forms a first mounting cavity; The second mounting part includes a second housing component, which is connected to the first housing component and can rotate relative to the first housing component. The second housing component surrounds a second mounting cavity, which communicates with the first mounting cavity to form a receiving cavity. The driving member, the first transmission member, and the second transmission member are all disposed in the receiving cavity.

[0015] Furthermore, the accommodating cavity is provided with lubricating oil; The dual-spindle milling head also includes an oil splashing component, which is disposed on the drive shaft and, driven by the drive shaft, splashes the lubricating oil to lubricate at least the drive component and / or the first transmission component and / or the second transmission component within the accommodating cavity.

[0016] Furthermore, the first mounting portion is provided with a first shaft hole, which extends axially along the first main shaft. The first main shaft is mounted in the first shaft hole at least by a first bearing. A first shaft spacer is sleeved on the first main shaft, and a first-hole spacer is provided between the first shaft spacer and the first shaft hole. The first shaft spacer has a first groove facing the first-hole spacer. The first-hole spacer is at least partially embedded in the first groove and has a first gap between it and the inner wall and top of the first groove; and / or, The second mounting part is provided with a second shaft hole, which extends along the axial direction of the second main shaft. The second main shaft is mounted in the second shaft hole at least through a second bearing. A second shaft spacer is sleeved on the second main shaft. A second hole spacer is provided between the second shaft spacer and the second shaft hole. The second shaft spacer is provided with a second groove facing the second hole spacer. The second hole spacer is at least partially embedded in the second groove and has a second gap between it and the inner wall and top of the second groove.

[0017] On the other hand, this application also provides a machine tool including the aforementioned dual-spindle milling head.

[0018] In this application, by setting the first spindle on the first mounting part and the second spindle on the second mounting part, and making the second mounting part rotatable relative to the first mounting part, the included angle between the second spindle and the first spindle can be adjusted according to actual machining requirements. This overcomes the shortcomings of existing dual-spindle milling heads, which suffer from poor machining adaptability and limited application range due to the fixed included angle of the two spindles. Furthermore, this configuration eliminates the need for frequent spindle angle direction changes during actual machining, unlike single-spindle structures, thus improving machining efficiency. In addition, this dual-spindle milling head achieves angle adjustment simply by allowing the second mounting part to rotate relative to the first mounting part, eliminating the need for a complex automatic universal conversion mechanism, resulting in a simple structure and low manufacturing cost. Attached Figure Description

[0019] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, are illustrative and descriptive, serving to explain this application and do not constitute an undue limitation thereof. In the drawings: Figure 1 This is a schematic diagram of a dual-spindle milling head disclosed in an embodiment of this application from a first-view perspective; Figure 2 This is a schematic diagram of a dual-spindle milling head disclosed in an embodiment of this application from a second perspective; Figure 3 This is a schematic diagram of a dual-spindle milling head disclosed in an embodiment of this application from a third-person perspective; Figure 4 for Figure 3 Sectional view of AA; Figure 5 for Figure 4 A magnified view of a portion of region A in the middle; Figure 6 for Figure 4 A magnified view of a portion of region B in the middle; Figure 7 for Figure 3 Sectional view of BB; Figure 8 for Figure 4 Sectional view of CC; Figure 9 This is a schematic diagram showing the rotation of the second mounting portion relative to the first mounting portion by a predetermined angle in a dual-spindle milling head disclosed in an embodiment of this application.

[0020] The above figures include the following reference numerals: 10. First mounting part; 11. Mounting hole; 12. Annular groove; 13. First housing component; 131. First mounting cavity; 14. First shaft hole; 20. Second mounting part; 21. Insertion part; 22. Second housing component; 221. Second mounting cavity; 23. Second shaft hole; 24. Oil guide hole; 30. First spindle; 40. Second spindle; 50. Locking component; 51. Locking element; 52. Locking nut; 60. Sealing ring; 70. Drive mechanism; 71. Transmission shaft; 72. Drive element 721. First spur gear; 73. First transmission component; 731. Second spur gear; 74. Second transmission component; 741. First bevel gear; 7411. First mounting shaft; 7412. First bevel gear body; 742. Third spur gear; 743. Reversing gear set; 7431. Second bevel gear; 74311. Second mounting shaft; 74312. Second bevel gear body; 74313. Third bevel gear body; 7432. Third bevel gear; 75. Actuating component; 751. Drive 7511 Piston rod; 752 Shift fork; 753 Guide rod; 80 Detection assembly; 81 Detection switch; 82 Detection block; 90 Accommodating cavity; 100 Lubricating oil; 110 Oil splashing component; 111 Fourth bevel gear; 112 Fifth bevel gear; 113 Impeller; 120 Support frame; 130 First bearing; 140 First shaft spacer; 141 First groove; 150 First hole spacer; 160 First clearance; 170 Second bearing; 180 Second Shaft spacer; 181, second groove; 190, second hole spacer; 191, second gap; 192, third groove; 200, first tool release cylinder; 210, second tool release cylinder; 220, third bearing; 230, fourth bearing; 240, first mounting sleeve; 250, fifth bearing; 260, sixth bearing; 270, input transmission component; 280, seventh bearing; 290, second mounting sleeve; 300, eighth bearing; 310, ninth bearing; 320, guide sleeve; 330, tenth bearing. Detailed Implementation

[0021] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0022] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0023] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0024] As described in the background section, in related technologies, twin-spindle milling heads typically have a fixed angle between the two spindles, limiting their application to machining in only two fixed angular directions. Therefore, this application provides a novel twin-spindle milling head where one spindle can be angle-adjusted relative to the other, enabling machining in two angles with a single workpiece clamping. The twin-spindle milling head of this application will be described below with reference to the accompanying drawings.

[0025] See Figures 1 to 9 As shown in the figure, this application embodiment provides a dual-spindle milling head. The dual-spindle milling head includes a first mounting part 10, a second mounting part 20, a first spindle 30, and a second spindle 40.

[0026] Specifically, the second mounting part 20 is mounted on the first mounting part 10 and can rotate relative to the first mounting part 10; the first spindle 30 is disposed on the first mounting part 10 and can rotate about its own axis; the second spindle 40 is disposed on the second mounting part 20 and can rotate about its own axis.

[0027] In this application, by mounting the second mounting part 20 to the first mounting part 10 and allowing it to rotate relative to the first mounting part 10, the included angle θ between the first spindle 30 and the second spindle 40 can be adjusted according to actual machining requirements. This overcomes the limitation of existing dual-spindle milling heads that can only perform machining at fixed angles, thus significantly improving the adaptability of the dual-spindle milling head to machining complex features such as inclined planes with different angles and structural shapes. Simultaneously, the dual-spindle milling head adopts a parallel arrangement of the two spindles, eliminating the need for complex spindle direction adjustments at each angle change, as required by single-spindle milling heads. This effectively reduces auxiliary time during machining and improves overall machining efficiency. Furthermore, the spindle angle adjustment is achieved through a mechanical rotating structure of the second mounting part 20. Compared to the complex automatic reversing mechanism of an automatic universal milling head, the overall structure is simpler, the manufacturing cost is lower, and maintenance is more convenient. Moreover, both the first spindle 30 and the second spindle 40 can rotate independently around their own axes, ensuring that both spindles maintain stable cutting capabilities and machining performance after angle adjustment.

[0028] Furthermore, in this application, the first spindle 30 is fixedly disposed within the first mounting portion 10, while angle adjustment only involves the second mounting portion 20 and the second spindle 40 mounted within the second mounting portion 20, resulting in a smaller moment of inertia. This arrangement not only improves the sensitivity of rotational response but also makes it easier to ensure the accuracy and reliability of angle positioning. Simultaneously, based on the adjustable angle characteristic of the second spindle 40, the workpiece can be continuously processed in different orientations after a single clamping, effectively avoiding secondary positioning errors caused by repeated clamping. This further enhances the overall processing efficiency of the machine tool while ensuring processing accuracy.

[0029] In other words, in this application, by setting the first spindle 30 on the first mounting part 10 and the second spindle 40 on the second mounting part 20, and making the second mounting part 20 rotatable relative to the first mounting part 10, the included angle between the second spindle 40 and the first spindle 30 can be adjusted according to actual processing requirements, thereby overcoming the defects of existing dual-spindle milling heads that have poor processing adaptability and limited application range due to the fixed included angle between the two spindles.

[0030] Furthermore, when the second mounting part 20 rotates relative to the first mounting part 10, the axis of the second spindle 40 moves within the first plane (not shown in the figure), and the axis of the first spindle 30 is parallel to the first plane. This configuration, by constraining the rotational movement of the second spindle 40 within the first plane and ensuring the axis of the first spindle 30 is parallel to this first plane, ensures that the relative positional relationship between the two spindles remains in a controllable parallel plane state. This effectively avoids the risk of mechanical interference between the second spindle 40 and the first spindle 30 due to arbitrary rotation in three-dimensional space during angle adjustment. Simultaneously, this first plane constraint establishes a clear safety motion envelope between the two spindles. Only a reasonable setting of the rotation angle range and spindle spacing within the two-dimensional plane is needed to ensure that the two spindles do not collide, significantly simplifying the anti-interference structure design and motion control logic, and improving the operational safety and reliability of the dual-spindle milling head during angle adjustment.

[0031] like Figure 4 As shown, the first mounting part 10 is provided with a mounting hole 11, and the second mounting part 20 is provided with a plug-in part 21. The plug-in part 21 is at least partially inserted into the mounting hole 11 and can rotate relative to the mounting hole 11. The locking member 50 is at least partially loosely and tightly disposed on the second mounting part 20 so as to lock the second mounting part 20 to the first mounting part 10 when the second mounting part 20 is rotated to the position relative to the first mounting part 10.

[0032] It is understood that in this application, the engagement of the plug-in portion 21 and the mounting hole 11 achieves centering and guidance of the second mounting portion 20 relative to the first mounting portion 10, ensuring the coaxiality and rotational accuracy of the rotation axis of the second mounting portion 20 relative to the first mounting portion 10. The locking component 50, at least partially (here referring to the locking nut 52), is adjustable to provide reliable axial and circumferential fixing forces, ensuring that the second mounting portion 20 will not shift or loosen under cutting loads, thus balancing the convenience of angle adjustment with the rigidity of the working state. Exemplarily, in this application, the plug-in portion 21 is a positioning convex frustum.

[0033] See you again Figure 4 As shown, the first mounting part 10 is provided with an annular groove 12, which is coaxially arranged with the mounting hole 11; the locking component 50 includes a plurality of locking members 51, which are inserted through the second mounting part 20 and can move circumferentially along the annular groove 12 as the second mounting part 20 rotates.

[0034] It is understood that in this application, the annular groove 12 is an annular T-groove, and the locking member 51 includes a T-bolt. The locking component 50 also includes a locking nut 52. The T-bolt is embedded in the annular T-groove and passes through the second mounting part 20, so that after the second mounting part 20 is rotated around the mounting hole 11 to any target angle, the T-bolt can move circumferentially along the annular T-groove to the corresponding position without the need for additional adapter components or alignment holes. This achieves stepless angle locking within a predetermined angle range (the maximum angle is determined according to the limit state that prevents lubricating oil from flowing into the main bearing of the second spindle 40), greatly improving the flexibility of angle adjustment and the arbitrariness of the locking position. After the second mounting part 20 is rotated into position, the second mounting part 20 is locked onto the first mounting part 10 by using the locking nut 52 and the locking member 51.

[0035] Meanwhile, a stable surface contact fit is formed between the T-bolt and the annular T-groove, which can generate a uniform and strong axial clamping force after locking. Multiple locking parts 51 are inserted into the second mounting part 20 and distributed axially along the annular groove 12. They can provide a multi-point uniform locking force to the second mounting part 20 after it is rotated into place, so as to firmly press the second mounting part 20 onto the first mounting part 10. This can effectively resist the large-value cutting force and high-frequency vibration generated during the machining process, and ensure that the angle positioning of the second spindle 40 does not shift under long-term heavy-load cutting conditions, which significantly improves the locking rigidity and machining stability.

[0036] In addition, the locking element 51 is inserted through the second mounting part 20 and rotates synchronously with it, so that the operator can directly perform the locking operation without realigning after adjusting the angle, which simplifies the angle switching process and improves work efficiency. The annular T-slot is machined at the end of the first mounting part 10 and the T-bolt is a standardized fastener. The combination of the two not only makes the structure compact and occupies little space, but also reduces the number of parts and makes it easy to assemble and disassemble, which helps to reduce manufacturing costs and facilitates later maintenance and replacement.

[0037] Furthermore, the dual-spindle milling head also includes a sealing ring 60, which is disposed within the gap between the insertion part 21 and the mounting hole 11. With this configuration, this application effectively seals the mating gap between the insertion part 21 and the mounting hole 11 using the sealing ring 60, effectively preventing lubricant leakage or loss along the gap, ensuring that the mating surfaces maintain good lubrication over a long period, and further reducing maintenance frequency. Simultaneously, the sealing ring 60 creates a uniform elastic preload in the mating gap, helping to absorb minor radial runout caused by machining vibrations or impact loads, thereby enhancing the vibration resistance and dynamic rigidity of the rotating pair, making the second mounting part 20 more stable during rotation adjustment and locking.

[0038] like Figures 1 to 8As shown, the dual-spindle milling head also includes a drive mechanism 70. This drive mechanism 70 is disposed in the first mounting portion 10 and can be selectively connected to the first spindle 30 and the second spindle 40 to drive either the first spindle 30 or the second spindle 40 to rotate. Specifically, in this application, by integrating the selectively connectable drive mechanism 70, the power source can be allocated to the first spindle 30 and the second spindle 40 on demand. When one spindle needs to work, the power transmission to the other spindle can be cut off, avoiding idling wear and energy consumption of the non-working spindle. Compared to traditional dual-spindle milling heads, this significantly reduces operating costs and the risk of spindle thermal deformation.

[0039] Meanwhile, in this application, only one drive mechanism 70 is needed to provide rotational power to the first spindle 30 and the second spindle 40 respectively, eliminating the need for separate drive units for the first spindle 30 and the second spindle 40. This simplifies the overall structure of the milling head, reduces its size and weight, and lowers the overall manufacturing cost. Furthermore, since the drive mechanism 70 is mounted on the first mounting part 10, and the first mounting part 10 remains relatively fixed during angle adjustment, the drive mechanism 70 will not rotate with the second mounting part 20. This avoids pipe entanglement and transmission interference problems caused by the drive mechanism 70 rotating with the second mounting part 20, thus improving transmission reliability.

[0040] Further, the drive mechanism 70 includes: a drive shaft 71, a first transmission component 73, a second transmission component 74, and a toggle component 75. The drive shaft 71 is provided with a drive member 72 that can move along the axial direction of the drive shaft 71; the first transmission component 73 is connected to the first main shaft 30 to transmit power from the drive shaft 71 to the first main shaft 30 to drive the first main shaft 30 to rotate; the second transmission component 74 is connected to the second main shaft 40 to transmit power from the drive shaft 71 to the second main shaft 40 to drive the second main shaft 40 to rotate; the toggle component 75 is disposed on the first mounting portion 10 to drive the drive member 72 to move along the axial direction of the drive shaft 71 and selectively connect to the first transmission component 73 or the second transmission component 74.

[0041] Specifically, in this application, a drive element 72 that slides axially along the drive shaft 71 is used as a power switching element. Its position on the drive shaft 71 is controlled by a toggle component 75 to achieve engagement or disengagement with the first transmission component 73 or the second transmission component 74. This mechanical clutch structure offers rapid response, high load-bearing capacity, a short power transmission path, and high efficiency. It maintains stable shifting performance even in harsh machining environments, ensuring the reliability of the start-stop and switching of the first spindle 30 and the second spindle 40.

[0042] Furthermore, in this application, the drive component 72 is slidably mounted in the middle of the transmission shaft 71 using a keyed connection (such as a spline). This configuration, with the keyed connection serving as circumferential positioning and torque transmission, ensures reliable circumferential fixation between the drive component 72 and the transmission shaft 71, enabling the transmission of larger cutting torques. It also provides stable guidance for the axial sliding of the drive component 72, ensuring smooth reciprocating movement under the drive of the actuating component 75, preventing jamming or misalignment, and providing strong load-bearing capacity. Simultaneously, by positioning the drive component 72 in the middle of the transmission shaft 71, sufficient axial space is reserved on both sides, facilitating the arrangement of meshing positions with the first transmission component 73 and the second transmission component 74 on its left and right sides respectively. This ensures that the stroke of the actuating component 75 driving the drive component 72 to shift gears to both sides is symmetrical and minimized, avoiding the increased bending moment and localized wear problems of the transmission shaft 71 caused by the drive component 72 being offset to one side. This effectively improves the rotational balance of the transmission shaft 71 and the bearing life, and reduces vibration and noise in the transmission system.

[0043] Furthermore, in this application, the drive shaft 71 is mounted on the first mounting portion 10 via the sixth bearing 260 and the seventh bearing 280. The drive shaft 71 is connected to the power unit on the machine tool via an input transmission component 270 (such as a coupling, pulley, etc.). This configuration provides stable radial and axial positioning of the drive shaft 71 on the first mounting portion 10, effectively withstanding the high-speed rotational torque from the machine tool's power unit and the radial cutting force and axial impact load generated during machining. This significantly improves the rigidity and vibration resistance of the transmission system, ensuring smooth power transmission and precision retention. Simultaneously, the input transmission component 270, acting as a connecting bridge between the drive shaft 71 and the machine tool's power unit, allows for flexible selection of couplings, pulleys, or other standard transmission elements based on the specific machine tool's interface type. This improves the adaptability and versatility of the milling head with different machine tool models and facilitates installation, debugging, and subsequent maintenance. Furthermore, in this application, the input transmission component 270 is disposed at the outer end of the transmission shaft 71, so that the main motion power of the machine tool can be introduced into the interior of the dual-spindle milling head in the most direct and shortest path, reducing energy loss and accumulated error in the intermediate transition links, which is beneficial to improving transmission efficiency and response speed.

[0044] Furthermore, the actuating component 75 includes a drive cylinder 751 and a shift fork 752. The drive cylinder 751 is mounted on the first mounting portion 10; the shift fork 752 connects the drive cylinder 751 and the drive member 72, and, driven by the drive cylinder 751, moves the drive member 72 along the axis of the transmission shaft 71. With this configuration, by employing a clutch-operated method combining the drive cylinder 751 and the shift fork 752, the drive cylinder 751, as a standardized actuator, can directly obtain a stable and adjustable driving force through hydraulic or pneumatic control. Its mounting on the fixed first mounting portion 10 results in a simple piping layout and convenient maintenance.

[0045] In this application, the drive cylinder 751 is preferably hydraulically driven. The hydraulic system can provide a stable and strong driving force within a compact space, ensuring that the shift fork 752 pushes the drive member 72 to overcome the resistance during transmission engagement and reliably completes the engagement and disengagement actions with the first transmission component 73 or the second transmission component 74. At the same time, the shift fork 752 accurately transmits the linear reciprocating motion of the drive cylinder 751 to the circumference of the drive member 72, avoiding jamming or uneven wear caused by unilateral force, and extending the service life of the drive member 72.

[0046] Furthermore, in this application, the shift fork 752 and the drive component 72 are connected by a ninth bearing 310, which can effectively eliminate the additional frictional torque caused by gravity or vibration, reduce motion resistance, and improve switching sensitivity and service life.

[0047] like Figure 4 and Figure 7 As shown, the shift fork 752 is connected to the drive member 72 and can rotate relative to the drive shaft 71 around the axis of the drive shaft 71; the drive cylinder 751 includes a piston rod 7511, and the actuating component 75 also includes a guide rod 753. Both the piston rod 7511 and the guide rod 753 are arranged parallel to the drive shaft 71. The piston rod 7511 and the guide rod 753 are respectively connected to the shift fork 752 at a predetermined distance. Under the drive of the drive cylinder 751, the guide rod 753 moves synchronously with the piston rod 7511 along the axial direction of the drive shaft 71.

[0048] Understandably, the guide rod 753 enhances the guiding effect on the shift fork 752, effectively counteracting the lateral torque generated during the movement of the shift fork 752, and improving the straightness and smoothness of the shifting action. At the same time, the design of the shift fork 752 being able to rotate relative to the drive shaft 71 around the axis of the drive shaft 71 allows it to follow the circumferential position changes of the drive component 72, ensuring the continuity of power transmission.

[0049] Furthermore, in some embodiments, the guide rod 753 can be mounted on the first mounting portion 10 via the guide sleeve 320; in other embodiments, the guide rod 753 can also be directly and slidably mounted on the first mounting portion 10.

[0050] See you again Figure 4 and Figure 7 As shown, the drive member 72 has a first position connected to the first transmission member 73, a second position connected to the second transmission member 74, and a third position away from the first transmission member 73 and the second transmission member 74; the dual spindle milling head also includes a detection component 80, which is disposed between the guide rod 753 and the first mounting part 10 to detect the position of the drive member 72.

[0051] Specifically, in this application, the detection component 80 includes a detection switch 81 and a detection block 82. Specifically, the detection switch 81 is disposed between the guide rod 753 and the first mounting portion 10, and the detection block 82 is fixedly mounted on the outer end of the guide rod 753. The detection block 82 comprises three blocks, corresponding to the first position, the second position, and the third position, respectively. With this configuration, this application includes three clearly defined work positions, including neutral. Through the cooperation of the detection switch 81 and the detection block 82 of the detection component 80, the actual position of the drive component 72 is fed back in real time, enabling precise closed-loop control of the dual-spindle motion selection. This ensures rapid and reliable power switching under different machining conditions, further improving the automation level and ease of operation of the equipment. This closed-loop detection mechanism allows the control system to accurately determine the current power transmission status, preventing misoperation or starting the spindle before fully engaging the gear, thus improving the safety of the dual-spindle milling head operation and the accuracy of automated control.

[0052] like Figure 4 As shown, the axis of the drive shaft 71 is parallel to the axis of the first spindle 30; the drive component 72 includes a first spur gear 721; the first transmission component 73 includes a second spur gear 731, which is fixedly sleeved on the first spindle 30 for meshing with the first spur gear 721. In this application, through the parallel shaft layout and spur gear meshing transmission method, the power of the drive shaft 71 can be directly transmitted to the first spindle 30 through the meshing of the first spur gear 721 and the second spur gear 731. The transmission path is short and direct, and the structure is compact. There is no need to add intermediate transition gears or reversing elements, which not only reduces the cumulative error and energy loss of the transmission chain and improves the transmission efficiency and accuracy, but also simplifies the assembly and maintenance difficulty. At the same time, the parallel layout of the drive shaft 71 and the first spindle 30 optimizes the internal space utilization of the first mounting part 10, making the overall structure more compact, which is beneficial to reducing the size of the milling head and improving its passability on the machine tool. Furthermore, in this application, the drive component 72 adopts a first spur gear 721 that can move axially along the transmission shaft 71, which cooperates with the aforementioned toggle component 75 and detection component 80, so that when the power is switched, the first spur gear 721 can reliably approach or move away from the second spur gear 731 axially, realizing smooth gear engagement and disengagement, further enhancing the flexibility and reliability of dual spindle motion selection.

[0053] like Figure 4As shown, the second transmission component 74 includes a first bevel gear 741, a third spur gear 742, and a reversing gear set 743. The first bevel gear 741 includes a first mounting shaft 7411 and a first bevel gear body 7412 fixedly connected to the first mounting shaft 7411. The first mounting shaft 7411 is parallel to the transmission shaft 71 and rotatably mounted on the first mounting portion 10. The third spur gear 742 is fixedly sleeved on the first mounting shaft 7411 for meshing with the first spur gear 721. The reversing gear set 743 is disposed between the first bevel gear 741 and the second main shaft 40 for transmitting power from the transmission shaft 71 to the second main shaft 40.

[0054] Understandably, in this application, a multi-stage gear combination is used to achieve the transmission and reversal of power from the drive shaft 71 to the second main shaft 40. The design of the first mounting shaft 7411 of the first bevel gear 741 being parallel to the drive shaft 71 facilitates the arrangement of the transmission chain within the same housing, reducing the assembly difficulty caused by the cross shaft system. The introduction of the reversing gear set 743 provides the necessary kinematic interface for the subsequent connection of the rotatable second mounting part 20, ensuring the decoupling of power transmission and angle adjustment functions. Specifically, when the drive member 72 moves axially along the drive shaft 71 to mesh with the third spur gear 742, power is transmitted sequentially to the second main shaft 40 via the first spur gear 721, the third spur gear 742, the first mounting shaft 7411, the first bevel gear body 7412, and the reversing gear set 743. The spur gear portion of the transmission chain is used to realize the power transmission between parallel shafts, while the bevel gear portion is used to realize the reversal in the 90° direction, so as to meet the transmission requirements of the second main shaft 40 being arranged at an angle relative to the first main shaft 30.

[0055] Furthermore, in some embodiments, the first bevel gear 741, together with the third spur gear 742, is mounted in the hole of the first mounting sleeve 240 via the fifth bearing 250, and the first mounting sleeve 240 is fixedly mounted on the first mounting part 10. In other embodiments, the first bevel gear 741 can be directly mounted on the first mounting part 10 via the fifth bearing 250.

[0056] Furthermore, in this application, along the axial direction of the first main shaft 30, the first spur gear 721 is disposed between the second spur gear 731 and the third spur gear 742. The driving member 72 (i.e., the first spur gear 721) only needs to make a small range of axial movement on the transmission shaft 71 between the second spur gear 731 and the third spur gear 742 to realize the power switching with the first main shaft 30 or the second main shaft 40, effectively shortening the shifting stroke of the shifting member 75, reducing the stroke requirement and response time of the drive cylinder 751, and helping to improve the shifting speed and operational flexibility.

[0057] Furthermore, in this application, the reversing gear set 743 includes a second bevel gear 7431 and a third bevel gear 7432. The second bevel gear 7431 includes a second mounting shaft 74311, a second bevel gear body 74312 and a third bevel gear body 74313 respectively fixedly disposed at both ends of the second mounting shaft 74311. The second mounting shaft 74311 is perpendicular to the first mounting shaft 7411, and the second bevel gear body 74312 meshes with the first bevel gear body 7412. The third bevel gear 7432 is fixedly mounted on the second main shaft 40, and meshes with the third bevel gear body 74313.

[0058] Specifically, in this application, the power transmitted from the first bevel gear 741 is then transmitted to the second main shaft 40 via the second bevel gear 7431 and the third bevel gear 7432, thereby driving the second main shaft 40 to rotate. This structure enables power reversal within a compact space and can adapt to the transmission requirements when the second main shaft 40 and the first main shaft 30 are arranged at an angle. Simultaneously, since the axis of the second mounting shaft 74311 is coaxial with the rotation axis of the second mounting part 20, the relative position and meshing state of the second bevel gear 7431 and the third bevel gear 7432 remain unchanged when the second mounting part 20 rotates around its rotation axis to adjust the angle. This ensures the integrity and stability of the power transmission path after the angle of the second main shaft 40 is adjusted, and reliable transmission under stepless angle adjustment can be achieved without the need for additional compensation mechanisms. In addition, the second bevel gear body 74312 and the third bevel gear body 74313 are coaxially arranged at both ends of the same mounting shaft, with a highly integrated structure. This reduces the number of intermediate transmission links and parts, which not only improves transmission rigidity and efficiency but also reduces manufacturing and assembly difficulty, thus enhancing the overall reliability of the equipment.

[0059] In some embodiments, the second bevel gear 7431 may include a second mounting shaft 74311, a second bevel gear body 74312 and a third bevel gear body 74313 respectively fixedly disposed at both ends of the second mounting shaft 74311. In other embodiments, the second bevel gear 7431 may also be formed by two bevel gears fixedly fitted together. Figure 4 The diagram shows that the second bevel gear 7431 is formed by a fixed assembly of two bevel gears. For example, the two bevel gears can be connected by a key, interference fit, or fasteners to ensure that the two bevel gears rotate synchronously.

[0060] Furthermore, in some embodiments, the second bevel gear 7431 is mounted in the hole of the second mounting sleeve 290 via the eighth bearing 300, and the second mounting sleeve 290 is fixedly mounted in the hole of the insertion portion 21 of the second mounting part 20. In other embodiments, the second bevel gear 7431 can also be directly mounted in the hole of the insertion portion 21 of the second mounting part 20 via the eighth bearing 300.

[0061] Furthermore, such as Figure 4 As shown, the first mounting part 10 includes a first housing component 13, which surrounds and forms a first mounting cavity 131; the second mounting part 20 includes a second housing component 22, which is connected to the first housing component 13 and can rotate relative to the first housing component 13. The second housing component 22 surrounds and forms a second mounting cavity 221, which communicates with the first mounting cavity 131 to form a receiving cavity 90. The driving member 72, the first transmission member 73, and the second transmission member 74 are all disposed in the receiving cavity 90.

[0062] Understandably, in this application, the first mounting part 10 and the second mounting part 20 adopt a layout in which a shell surrounds and forms a closed accommodating cavity 90. Firstly, the first transmission component 73 and the second transmission component 74 are integrated into a unified, sealed space. This effectively prevents external impurities such as chips, dust, and coolant generated during processing from entering the working area of ​​the transmission components, significantly reducing the risk of wear and failure of the gear meshing surfaces and bearings due to foreign object intrusion, and extending the service life of the transmission system. Simultaneously, the first mounting cavity 131 and the second mounting cavity 221 are interconnected, ensuring that when the second mounting part 20 rotates relative to the first mounting part 10 to adjust its included angle, the first transmission component 73 and the second transmission component 74 located within the first mounting cavity 131 and the second mounting cavity 221 remain within the same lubrication and protection system. This eliminates the need for additional complex dynamic sealing structures at the rotating joint surfaces, simplifying the overall machine design.

[0063] Furthermore, this application centrally arranges all transmission components within the housing cavity, effectively reducing the external profile dimensions of the milling head, making the structure more compact, facilitating layout within a limited space, and improving the overall rigidity and vibration resistance of the machine. In addition, the drive component 72, the first transmission component 73, and the second transmission component 74 are all installed within the accommodating cavity 90, ensuring the power transmission path is completely enclosed within the housing protection, avoiding safety hazards caused by accidental contact with exposed transmission components, and further enhancing the safety of equipment operation.

[0064] like Figure 4 , Figure 7 and Figure 8 As shown, lubricating oil 100 is provided in the accommodating cavity 90; the dual spindle milling head also includes an oil splashing component 110, which is disposed on the drive shaft 71 and causes the lubricating oil 100 to splash under the drive of the drive shaft 71 to lubricate at least the drive component 72 and / or the first transmission component 73 and / or the second transmission component 74 in the accommodating cavity 90.

[0065] Specifically, the enclosed cavity 90 provides an ideal sealed environment for the splash lubrication system, allowing the lubricating oil 100 to circulate within the cavity without leakage. This ensures sufficient lubrication for each transmission pair and prevents lubricating oil 100 leakage from contaminating the workpiece or machine tool environment. Furthermore, in this application, the splash lubrication component 110 is driven by the rotational power of the transmission shaft 71 itself, achieving self-powered lubrication. The splash lubrication method eliminates the need for an additional oil pump and complex piping, resulting in a simple and reliable structure. It can also evenly distribute the lubricating oil 100 to each meshing tooth surface and bearing area, solving the problems of poor heat dissipation, easy drying and poor performance of traditional grease lubrication, as well as the complexity and easy leakage of external oil circuits.

[0066] Furthermore, the drive shaft 71 extends along the height direction of the accommodating cavity 90, and the oil splashing component 110 includes a fourth bevel gear 111 and a fifth bevel gear 112. The fourth bevel gear 111 is fixedly sleeved on the bottom end of the drive shaft 71; the fifth bevel gear 112 is rotatably mounted within the accommodating cavity 90 and meshes with the fourth bevel gear 111. Driven by the fourth bevel gear 111, the fifth bevel gear 112 drives the lubricating oil 100 to splash, thereby lubricating the drive component 72 and / or the first transmission component 73 and / or the second transmission component 74.

[0067] It is understood that in this application, through the reversing transmission layout of the fourth bevel gear 111 and the fifth bevel gear 112, the rotational motion of the transmission shaft 71 is transmitted through the fourth bevel gear 111 to the fifth bevel gear 112 that meshes with it perpendicularly, realizing a 90° reversal of the power transmission direction. This allows the fifth bevel gear 112 to rotate on a horizontal axis at the lower part of the accommodating cavity 90, thereby effectively agitating the lubricating oil 100 deposited at the bottom of the cavity and producing a sufficient splashing effect, ensuring that the lubricating oil 100 can reach the working area of ​​each transmission component in the accommodating cavity 90.

[0068] Meanwhile, since the fourth bevel gear 111 is directly mounted on the bottom end of the drive shaft 71, there is no need for an additional independent drive shaft or transmission mechanism, simplifying the structure and saving installation space. The meshing position of the fifth bevel gear 112 and the fourth bevel gear 111 is close to the bottom of the receiving cavity 90, so that the teeth of the fifth bevel gear 112 or the impeller 113 connected to it can always be immersed in the lubricating oil 100. Even if the level of the lubricating oil 100 drops during long-term use, a reliable splash lubrication effect can be guaranteed. In addition, this bevel gear splash structure uses the existing rotational motion of the drive shaft 71 as a power source, eliminating the need for an external oil pump or independent drive components, reducing energy consumption and failure rate. Moreover, it operates automatically with the start and stop of the main shaft during operation, requiring no additional control logic, further improving the reliability and ease of use of the lubrication system.

[0069] Furthermore, in this application, a support frame 120 is fixedly disposed in the first mounting cavity 131, and the fifth bevel gear 112 is mounted on the support frame 120 through the tenth bearing 330.

[0070] Furthermore, in this application, a through hole extending axially along the second mounting shaft 74311 of the second bevel gear 7431 is provided inside the second mounting shaft 74311, and a plurality of oil guide holes 24 distributed at predetermined intervals in the circumferential direction are provided on the side of the second mounting part 20 near the first mounting part 10. When the oil splashing component 110 is working, the splashed oil lubricates the meshing part of the second bevel gear 7431 and the third bevel gear 7432 through the through hole, and the lubricated oil flows back through the oil guide holes 24 and mixes with the lubricating oil 100 provided in the accommodating cavity 90.

[0071] like Figure 4 and Figure 5 As shown, a first shaft hole 14 is provided on the first mounting part 10. The first shaft hole 14 extends along the axial direction of the first main shaft 30. The first main shaft 30 is installed in the first shaft hole 14 at least through a first bearing 130. A first shaft sleeve 140 is sleeved on the first main shaft 30. A first hole sleeve 150 is provided between the first shaft sleeve 140 and the first shaft hole 14. A first groove 141 is provided on the first shaft sleeve 140 facing the first hole sleeve 150. The first hole sleeve 150 is at least partially embedded in the first groove 141 and has a first gap 160 between it and the inner wall and top of the first groove 141.

[0072] Specifically, in this application, the first spindle 30 is mounted in the first shaft hole 14 via a first bearing 130 and a third bearing 220. The first bearing 130 is the main bearing of the first spindle 30. The first shaft spacer 140 corresponds to the inner ring of the first bearing 130, and the first hole spacer 150 corresponds to the outer ring of the first bearing 130. The nested spacer structure formed by the first shaft spacer 140 and the first hole spacer 150 allows the first shaft spacer 140 to rotate with the first spindle 30, while the first hole spacer 150 is fixed within the first shaft hole 14. A tortuous labyrinthine sealing path is formed between the two through the embedded engagement of the first groove 141 and the first hole spacer 150. The first gap 160 ensures that there is no contact friction between the rotating and fixed components, avoiding wear and heat generated by direct metal-to-metal friction. It also effectively prevents the lubricating oil 100 splashed within the accommodating cavity 90 from seeping along the first spindle 30 towards the bearing, preventing the lubricating oil 100 from intruding into the first bearing 130 and the machining area at the front end of the spindle. This ensures that the bearing lubrication is undisturbed and the machining area remains clean. Furthermore, in this application, a spacer is also provided at the third bearing 220 to prevent splashed lubricating oil 100 from affecting the accuracy of the third bearing 220.

[0073] like Figure 4and Figure 6 As shown, the second mounting part 20 is provided with a second shaft hole 23, which extends axially along the second main shaft 40. The second main shaft 40 is installed in the second shaft hole 23 at least through the second bearing 170. A second shaft spacer 180 is sleeved on the second main shaft 40. A second hole spacer 190 is provided between the second shaft spacer 180 and the second shaft hole 23. A second groove 181 is provided on the second shaft spacer 180 facing the second hole spacer 190. The second hole spacer 190 is at least partially embedded in the second groove 181 and has a second gap 191 between it and the inner wall and top of the second groove 181.

[0074] It is understood that in this application, the second spindle 40 is mounted in the second shaft hole 23 via the second bearing 170 and the fourth bearing 230, wherein the second bearing 170 is the main bearing of the second spindle 40. The functions of the second shaft spacer 180 and the second hole spacer 190 are the same as those of the first shaft spacer 140 and the first hole spacer 150 described above, and will not be repeated here. However, it is worth noting that in this application, the shape of the second shaft spacer 180 is adapted to the shape of the third bevel gear body 74313 of the second bevel gear 7431, so as to avoid interference between the second shaft spacer 180 and the second bevel gear 7431 during movement, thereby affecting its service life. At the same time, in this application, the second hole spacer 190 is provided with a third groove 192 near the second groove 181. When the second mounting part 20 rotates at a predetermined angle relative to the first mounting part 10, the third groove 192 can further block possible oil inflow, further preventing the lubricating oil 100 from adversely affecting the accuracy of the second spindle 40 and its service life.

[0075] Furthermore, in this application, the dual-spindle milling head also includes a first tool release cylinder 200 and a second tool release cylinder 210. The first tool release cylinder 200 is mounted on the first mounting part 10 at the rear of the first spindle 30, and the second tool release cylinder 210 is mounted on the second mounting part 20 at the rear of the second spindle 40, ensuring that the tool release action can be performed stably and reliably at any angle.

[0076] On the other hand, this application also provides a machine tool (not shown in the figure), which can be a CNC milling machine, a turning-milling composite machining center, etc. This machine tool includes the aforementioned dual-spindle milling head. Therefore, the machine tool provided in this embodiment includes all the technical effects of the aforementioned dual-spindle milling head. Since the technical effects of the dual-spindle milling head have been described in detail above, they will not be repeated here.

[0077] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects: (1) This application realizes the adjustment of the included angle between the second spindle and the first spindle by setting the second mounting part with the second spindle to be rotatable relative to the first mounting part with the first spindle. This adapts to the milling head adjustment and workpiece clamping at one time, and can perform machining in two angle directions. The two angle directions can be adjusted according to actual needs.

[0078] (2) This application enables the first spindle and the second spindle to be selected and operated independently through a drive mechanism, avoiding the phenomenon that one spindle is being processed while the other spindle needs to idle at the same time, thus reducing energy consumption.

[0079] (3) This application provides an oil splashing component, which is driven by a transmission shaft to splash lubricating oil, thereby achieving lubrication of at least the drive component, the first transmission component, and the second transmission component. At the same time, at the main bearings of the first and second main shafts, the hole spacer is at least partially embedded in the groove on the shaft spacer to form a labyrinth-type protective structure, which prevents lubricating oil from entering the first and second bearings.

[0080] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0081] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0082] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A dual-spindle milling head, characterized in that, include: First installation section (10); The second mounting part (20) is mounted on the first mounting part (10) and is rotatable relative to the first mounting part (10); The first spindle (30) is disposed on the first mounting part (10) and can rotate around its own axis; The second spindle (40) is disposed on the second mounting part (20) and can rotate about its own axis.

2. The dual-spindle milling head according to claim 1, characterized in that, When the second mounting part (20) rotates relative to the first mounting part (10), the axis of the second main shaft (40) moves in the first plane, and the axis of the first main shaft (30) is parallel to the first plane; and / or, The first mounting part (10) is provided with a mounting hole (11), and the second mounting part (20) is provided with a plug-in part (21). The plug-in part (21) is at least partially inserted into the mounting hole (11) and can rotate relative to the mounting hole (11). The dual spindle milling head also includes a locking member (50). The locking member (50) is at least partially loosely disposed on the second mounting part (20) to lock the second mounting part (20) to the first mounting part (10) when the second mounting part (20) rotates to the position relative to the first mounting part (10).

3. The dual-spindle milling head according to claim 2, characterized in that, The first mounting portion (10) is provided with an annular groove (12), which is coaxially arranged with the mounting hole (11); the locking component (50) includes a plurality of locking elements (51), which pass through the second mounting portion (20) and can move circumferentially along the annular groove (12) as the second mounting portion (20) rotates; and / or, The dual-spindle milling head also includes a sealing ring (60), which is disposed in the gap between the insertion part (21) and the mounting hole (11).

4. The dual-spindle milling head according to claim 1, characterized in that, The dual-spindle milling head also includes: A drive mechanism (70) is disposed on the first mounting part (10) and can be selectively connected to the first spindle (30) and the second spindle (40) to drive the first spindle (30) to rotate or drive the second spindle (40) to rotate.

5. The dual-spindle milling head according to claim 4, characterized in that, The drive mechanism (70) includes: A drive shaft (71) is provided with a drive member (72) that can move along the axial direction of the drive shaft (71). A first transmission component (73) is connected to the first main shaft (30) to transmit the power of the transmission shaft (71) to the first main shaft (30) and drive the first main shaft (30) to rotate. The second transmission component (74) is connected to the second main shaft (40) to transmit the power of the transmission shaft (71) to the second main shaft (40) and drive the second main shaft (40) to rotate. A toggle member (75) is disposed on the first mounting portion (10) to drive the drive member (72) to move along the axial direction of the transmission shaft (71) and selectively connect to the first transmission member (73) or to the second transmission member (74).

6. The dual-spindle milling head according to claim 5, characterized in that, The actuating component (75) includes: Drive cylinder (751), which is mounted on the first mounting part (10); The shift fork (752) is connected between the drive cylinder (751) and the drive member (72), and under the drive of the drive cylinder (751), it drives the drive member (72) to move along the axial direction of the transmission shaft (71).

7. The dual-spindle milling head according to claim 6, characterized in that, The shift fork (752) is connected to the drive member (72) and can rotate relative to the drive shaft (71) about the axis of the drive shaft (71); The drive cylinder (751) includes a piston rod (7511), and the actuating component (75) also includes a guide rod (753). The piston rod (7511) and the guide rod (753) are both arranged parallel to the transmission shaft (71). The piston rod (7511) and the guide rod (753) are respectively connected to the shift fork (752) at a predetermined distance. Under the drive of the drive cylinder (751), the guide rod (753) moves synchronously with the piston rod (7511) along the axial direction of the transmission shaft (71).

8. The dual-spindle milling head according to claim 5, characterized in that, The axis of the drive shaft (71) is parallel to the axis of the first main shaft (30); The drive component (72) includes a first spur gear (721); The first transmission component (73) includes a second spur gear (731), which is fixedly sleeved on the first main shaft (30) for meshing with the first spur gear (721).

9. The dual-spindle milling head according to claim 8, characterized in that, The second transmission component (74) includes: The first bevel gear (741) includes a first mounting shaft (7411) and a first bevel gear body (7412) fixedly connected to the first mounting shaft (7411). The first mounting shaft (7411) is parallel to the transmission shaft (71) and rotatably mounted on the first mounting part (10). The third spur gear (742) is fixedly sleeved on the first mounting shaft (7411) for meshing with the first spur gear (721); A reversing gear set (743) is disposed between the first bevel gear (741) and the second main shaft (40) for transmitting power from the drive shaft (71) to the second main shaft (40).

10. The dual-spindle milling head according to claim 9, characterized in that, The reversing gear set (743) includes: The second bevel gear (7431) includes a second mounting shaft (74311), a second bevel gear body (74312) and a third bevel gear body (74313) respectively fixedly disposed at both ends of the second mounting shaft (74311). The second mounting shaft (74311) is perpendicular to the first mounting shaft (7411), and the second bevel gear body (74312) meshes with the first bevel gear body (7412). The third bevel gear (7432) is fixedly mounted on the second main shaft (40) and meshes with the third bevel gear body (74313).

11. The dual-spindle milling head according to claim 5, characterized in that, The first mounting part (10) includes a first housing component (13), which surrounds and forms a first mounting cavity (131). The second mounting part (20) includes a second housing component (22), which is connected to the first housing component (13) and can rotate relative to the first housing component (13). The second housing component (22) surrounds and forms a second mounting cavity (221), which communicates with the first mounting cavity (131) to form a receiving cavity (90). The driving member (72), the first transmission member (73), and the second transmission member (74) are all disposed in the receiving cavity (90).

12. The dual-spindle milling head according to claim 11, characterized in that, The cavity (90) is provided with lubricating oil (100); The dual-spindle milling head also includes an oil splashing component (110), which is disposed on the drive shaft (71) and, driven by the drive shaft (71), splashes the lubricating oil (100) to lubricate at least the drive member (72) and / or the first transmission member (73) and / or the second transmission member (74) within the accommodating cavity (90).

13. The dual-spindle milling head according to any one of claims 1 to 12, characterized in that, The first mounting part (10) is provided with a first shaft hole (14), the first shaft hole (14) extends axially along the first main shaft (30), and the first main shaft (30) is mounted in the first shaft hole (14) at least by a first bearing (130); wherein, a first shaft sleeve (140) is sleeved on the first main shaft (30), a first hole sleeve (150) is provided between the first shaft sleeve (140) and the first shaft hole (14), the first shaft sleeve (140) is provided with a first groove (141) facing the first hole sleeve (150), the first hole sleeve (150) is at least partially embedded in the first groove (141), and has a first gap (160) between itself and the inner wall and top of the first groove (141); and / or, The second mounting part (20) is provided with a second shaft hole (23), the second shaft hole (23) extends along the axial direction of the second main shaft (40), and the second main shaft (40) is installed in the second shaft hole (23) at least through a second bearing (170); wherein, a second shaft sleeve (180) is sleeved on the second main shaft (40), a second hole sleeve (190) is provided between the second shaft sleeve (180) and the second shaft hole (23), the second shaft sleeve (180) is provided with a second groove (181) facing the second hole sleeve (190), the second hole sleeve (190) is at least partially embedded in the second groove (181), and there is a second gap (191) between the second hole sleeve (191) and the inner wall and top of the second groove (181).

14. A machine tool, characterized in that, The machine tool includes a dual-spindle milling head as described in any one of claims 1 to 13.

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