Machining head and machining tool

Abstract

The invention provides a machining head and a machining machine tool, the machining head comprises a main shaft assembly, a driving mechanism and a transmission mechanism, the transmission mechanism comprises a belt transmission assembly, a gear transmission assembly and an anti-backlash assembly, the gear transmission assembly comprises an input gear, a transmission gear and an output gear, and the input gear comprises a first input gear and a second input gear; the transmission gear comprises a first transmission gear chain and a second transmission gear chain, the anti-backlash assembly comprises an adjusting disc, a supporting block and an adjusting bolt, the adjusting disc and the supporting block are arranged on one side of the driven belt wheel, the adjusting bolt is rotatably arranged on the supporting block, and the tail end of the adjusting bolt abuts against the adjusting disc. By the adoption of the machining head, it can be achieved that no matter the driving mechanism drives in the forward direction or in the reverse direction, it can be guaranteed that at least one set of transmission gear chains and the output gear drive almost without gaps all the time through gear transmission, idling caused by gear backlash is remarkably reduced, and input power can be converted into high-torque and high-precision output step by step.

Description

Technical Field

[0001] This application relates to the field of machine tools, and more specifically, to a machining head and a machining machine tool. Background Art

[0002] With the rapid development of industries such as aerospace, automotive, and energy, five-axis machining machine tools have become the core equipment for industrial machining, and their performance directly affects the quality and production efficiency of industrial products. As the core component of a five-axis machining machine tool, the machining head undertakes the core functions of transmitting power and controlling the movement of the spindle, and the performance of its transmission mechanism becomes a key factor affecting the machining performance of the machine tool.

[0003] When current five-axis machining machine tools perform heavy cutting machining, a large-torque swing head is required. The direct drive method will occupy a large amount of space, and there are backlash problems in traditional mechanical large-torque transmission mechanisms, which affect machining accuracy. Existing technologies mostly use servo closed-loop control to detect position deviation in real time through an encoder and drive the motor to compensate for the gap in the reverse direction. However, since servo control depends on the accuracy of sensors, electromagnetic interference or signal delay may cause oscillations, resulting in poor accuracy, and direct drive by a torque motor may result in a small torque, which is not suitable for high-precision and heavy-cutting machining requirements such as aerospace. Summary of the Invention

[0004] The embodiments of this application aim to solve at least one of the problems in the existing technologies. The embodiments of this application provide a machining head and a machining machine tool, which can achieve the purpose of eliminating or reducing the backlash in the gear transmission process whether the driving mechanism is driving forward or backward, and realize the step-by-step conversion of the input power into a high-torque and high-precision output. To achieve the above purpose, the related technical solutions of the embodiments of this application are as follows:

[0005] On the one hand, the embodiments of this application provide a machining head, including a spindle assembly, a driving mechanism, and a transmission mechanism. The transmission mechanism includes a belt transmission assembly and a gear transmission assembly. The belt transmission assembly includes a driving pulley and a driven pulley connected by a transmission belt. The gear transmission assembly includes an input gear and an output gear. The driving pulley is connected to the output end of the driving mechanism, the driven pulley is connected to the input gear, and the output gear is connected to the spindle assembly;

[0006] The gear transmission assembly also includes a transmission gear, the input gear includes a first input gear and a second input gear arranged coaxially, the transmission gear includes a first transmission gear chain and a second transmission gear chain, the first input gear is meshed with the output gear through the first transmission gear chain, and the second input gear is meshed with the output gear through the second transmission gear chain; the first input gear is fixedly connected to the driven pulley, and the central axis of the second input gear is rotatably disposed in the first input gear and the driven pulley;

[0007] Wherein, the transmission mechanism also includes an anti-backlash component, which includes an adjustment disk, a tightening block and an adjusting bolt. The adjustment disk and the tightening block are arranged on the side of the driven pulley away from the first input gear. The adjustment disk is fixedly connected to the central axis of the second input gear, and the tightening block is fixedly connected to the driven pulley. The adjusting bolt is rotatably arranged on the tightening block, and the end of the adjusting bolt abuts against the adjustment disk.

[0008] In some embodiments, the first transmission gear chain includes a first forward gear, a second forward gear, a third forward gear, a fourth forward gear, a fifth forward gear and a sixth forward gear, the first forward gear is coaxial with the second forward gear and is fixedly arranged, the third forward gear and the fourth forward gear are coaxial with each other and are fixedly arranged, the fifth forward gear and the sixth forward gear are coaxial with each other and are fixedly arranged, the second forward gear is meshed with the third forward gear, the fourth forward gear is meshed with the fifth forward gear, the first forward gear is meshed with the first input gear, and the sixth forward gear is meshed with the output gear.

[0009] In some embodiments, the second transmission gear chain includes a first reverse gear, a second reverse gear, a third reverse gear, a fourth reverse gear, a fifth reverse gear and a sixth reverse gear, the first reverse gear is coaxial with the second reverse gear and fixedly arranged, the third reverse gear and the fourth reverse gear are coaxial with each other and fixedly arranged, the fifth reverse gear and the sixth reverse gear are coaxial with each other and fixedly arranged, the second reverse gear is meshed with the third reverse gear, the fourth reverse gear is meshed with the fifth reverse gear, the first reverse gear is meshed with the second input gear, and the sixth reverse gear is meshed with the output gear;

[0010] Among them, the number of teeth of the first reverse gear, the second reverse gear, the third reverse gear, the fourth reverse gear, the fifth reverse gear, and the sixth reverse gear is respectively the same as that of the first forward gear, the second forward gear, the third forward gear, the fourth forward gear, the fifth forward gear, and the sixth forward gear; the rotation axes of the first reverse gear and the second reverse gear are parallel to the rotation axes of the first forward gear and the second forward gear; the rotation axes of the third reverse gear and the fourth reverse gear are parallel to the rotation axes of the third forward gear and the fourth forward gear; the rotation axes of the fifth reverse gear and the sixth reverse gear are parallel to the rotation axes of the fifth forward gear and the sixth forward gear.

[0011] In some embodiments, the belt drive assembly is a synchronous belt drive assembly, the diameter of the driving pulley is smaller than the diameter of the driven pulley, the diameter of the first forward gear is larger than the diameter of the first input gear, the diameter of the third forward gear is larger than the diameter of the second forward gear, the diameter of the fifth forward gear is larger than the diameter of the fourth gear, and the diameter of the output gear is larger than the diameter of the sixth forward gear; the diameter of the first reverse gear is larger than the diameter of the second input gear, the diameter of the third reverse gear is larger than the diameter of the second reverse gear, the diameter of the fifth reverse gear is larger than the diameter of the fourth reverse gear, and the diameter of the output gear is larger than the diameter of the sixth reverse gear.

[0012] In some embodiments, the first input gear extends upward with a protruding shaft, and a first groove adapted to the protruding shaft is provided on a surface of the driven pulley close to the first input gear, and the protruding shaft is fixed in the first groove.

[0013] In some embodiments, a central hole adapted to the central shaft is provided in the middle of the protruding shaft and the middle of the driven pulley, the central shaft is rotatably inserted into the central hole, and one end of the central shaft passes through the central hole and is fixedly connected to the adjustment disc.

[0014] In some embodiments, the second input gear is integrally formed with the central shaft, and a second groove adapted to one end of the central shaft is provided at the bottom of the adjustment disc, and one end of the central shaft is fixed in the second groove.

[0015] In some embodiments, the first groove is located in the middle of the driven pulley, and the second groove is located in the middle of the adjustment disc; the cross sections of the first groove and the second groove are polygonal.

[0016] In some embodiments, the adjustment disc has a cross shape structure and has four arms, the four arms extend along the radial direction of the driven pulley, and the adjusting bolt is arranged on one side of the arm along the clockwise or counterclockwise direction.

[0017] On the other hand, the present application provides a processing machine tool, including the processing head in one of the foregoing embodiments, and the processing head is disposed on the machine tool body.

[0018] The technical solution of the processing head in the embodiments of the present application has at least the following technical effects: The processing head provided in the embodiments of the present application adopts a mechanical large-torque transmission mechanism, and through the precise cooperation of multiple gears of two transmission gear chains, the output gear is jointly output. At the same time, by using a backlash elimination component, no matter whether the driving mechanism is in the forward driving or reverse driving process, the gear transmission always ensures that there is almost no clearance between the teeth of at least one set of transmission gear chains and the output gear, which can significantly reduce the idling caused by the side clearance of the teeth, achieve the purpose of eliminating or reducing the side clearance of the teeth, and further realize the step-by-step conversion of the input power into a high-torque and high-precision output. It is not difficult to understand that the relevant technical solutions of the processing machine tool in the embodiments of the present application at least also have the corresponding technical effects of the technical solutions of the processing head, which will not be elaborated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The present application will be further described below in conjunction with the drawings and embodiments. In the drawings:

[0020] Figure 1 is a schematic structural diagram of the processing head in the embodiment of the present application;

[0021] Figure 2 is a schematic structural diagram of the driving mechanism and the transmission mechanism in the processing head in the embodiment of the present application;

[0022] Figure 3 is a schematic structural diagram of the driven pulley, the input gear and the backlash elimination component in the processing head in the embodiment of the present application;

[0023] Figure 4 is Figure 3 a sectional view of;

[0024] Figure 5 is Figure 3 a top view of;

[0025] Figure 6 is a schematic structural diagram of the driving mechanism, the belt transmission component, the input gear, the first transmission gear chain and the output gear in the processing head in the embodiment of the present application.

[0026] Figure 7 is a schematic structural diagram of the driving mechanism, the belt transmission component, the input gear, the second transmission gear chain and the output gear in the processing head in the embodiment of the present application.

[0027] Among them, the reference numerals are:

[0028] 10 - Spindle assembly, 20 - Driving mechanism, 30 - Transmission mechanism, 31 - Belt drive assembly, 32 - Gear drive group, 33 - Backlash elimination assembly

[0029] 311 - Driving pulley, 312 - Driven pulley, 313 - Transmission belt, 321 - Input gear, 322 - Transmission gear, 323 - Output gear, 331 - Adjusting disc, 332 - Tightening block, 333 - Adjusting bolt

[0030] 321a - First input gear, 321b - Second input gear, 322a - First transmission gear chain, 322b - Second transmission gear chain, 3121 - First groove, 3311 - Second groove, 3312 - Support arm

[0031] 3221a - First forward gear, 3222a - Second forward gear, 3223a - Third forward gear, 3224a - Fourth forward gear, 3225a - Fifth forward gear, 3226a - Sixth forward gear, 3221b - First reverse gear, 3222b - Second reverse gear, 3223b - Third reverse gear, 3224b - Fourth reverse gear, 3225b - Fifth reverse gear, 3226b - Sixth reverse gear, 3211a - Protruding shaft, 3211b - Central shaft Detailed implementation mode

[0032] In order to enable those skilled in the art to better understand the solution of this application, the technical solutions in the embodiments of this application will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of this application. Obviously, the described embodiments are only a part of the embodiments of this application, rather than all the embodiments. Based on the embodiments in this application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of this application.

[0033] It should be noted that in the description of this application, the orientation descriptions involved, such as up, down, front, back, left, right, etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing this application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to this application.

[0034] In the description of this application, the meaning of several is one or more, the meaning of multiple is more than two, understand greater than, less than, exceeding, etc. as not including the number itself, and understand above, below, within, etc. as including the number itself. If the first and second are described only for the purpose of distinguishing technical features, they cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence relationship of the indicated technical features.

[0035] In addition, terms such as "first", "second", etc. are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more features.

[0036] In the description of the present application, it should be noted that unless otherwise clearly specified and defined, the term "connection" should be understood in a broad sense. For example, it may be a fixed connection or a movable connection, or a detachable connection or a non-detachable connection, or an integral connection; it may be a mechanical connection, an electrical connection or a connection that can communicate with each other; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components, indirect communication or the interaction relationship between two components.

[0037] Numerous different embodiments or examples are provided below to implement different solutions of the present application.

[0038] As Figures 1 to 7 shown, the first aspect of the embodiment of the present application provides a machining head for a machining tool. As Figures 1 to 3 shown, the machining head includes a spindle assembly 10, a driving mechanism 20, and a transmission mechanism 30. Among them, the spindle assembly 10 is the core part for performing machining operations, the driving mechanism 20 provides a power source for the entire machining head, and the transmission mechanism 30 transmits the power of the driving mechanism to the spindle assembly. The transmission mechanism 30 includes a belt transmission assembly 31 and a gear transmission assembly 32. The belt transmission assembly 31 includes a driving pulley 311 and a driven pulley 312 that are transmission-connected through a transmission belt 313. The gear transmission assembly 32 includes an input gear 321 and an output gear 323. The driving pulley 311 is connected to the output end of the driving mechanism 20, the driven pulley 312 is connected to the input gear 321, and the output gear 323 is connected to the spindle assembly 10. The driving mechanism 20 drives the driving pulley 311 to rotate, the driving pulley 311 drives the driven pulley 312 to rotate through the transmission belt 313, the rotation of the driven pulley 312 then drives the input gear to rotate, the input gear 321 drives the output gear 323 to rotate through gear transmission, and the power transmission and torque conversion are achieved during the gear transmission process. Finally, the output gear 323 drives the spindle assembly 10 to rotate to realize the machining of the machining head.

[0039] As Figures 2 to 4As shown, the gear transmission assembly 32 also includes a transmission gear 322, which transmits power between the input gear 321 and the output gear 323, so that the power is effectively transmitted from the input gear 321 to the output gear 323, and the rotation speed and torque are changed. The input gear 321 includes a first input gear 321a and a second input gear 321b arranged coaxially, and the transmission gear 322 includes a first transmission gear chain 322a and a second transmission gear chain 322b. The first input gear 321a is meshed with the output gear 323 through the first transmission gear chain 322a, and the second input gear 321b is meshed with the output gear 323 through the second transmission gear chain 322b. The first input gear 321a and the second input gear 321b drive the output gear 323 to rotate together through the first transmission gear chain 322a and the second transmission gear chain 322b respectively. The first input gear 321a is fixedly connected to the driven pulley 312, and the central axis 3211b of the second input gear 321b is rotatably disposed in the first input gear 321a and the driven pulley 312, so that there can be a certain deviation between the tooth positions of the first input gear 321a and the second input gear 321b.

[0040] like Figure 4 and Figure 5 As shown, the transmission mechanism 30 also includes an anti-backlash assembly 33, which includes an adjusting disk 331, a tightening block 332 and an adjusting bolt 333. The adjusting disk 331 and the tightening block 332 are arranged on the side of the driven pulley 312 away from the first input gear 321a, the adjusting disk 331 is fixedly connected to the central axis 3211b of the second input gear 321b, the tightening block 332 is fixedly connected to the driven pulley 312, and the driven pulley 312 is fixedly connected to the first input gear 321a. The adjusting bolt 333 is rotatably disposed on the supporting block 332, and the end of the adjusting bolt 333 abuts against the adjusting disk 331. Due to the action of the anti-backlash assembly 33, the first input gear 321a and the second input gear 321b can be fixed at a specific position, so that the first driven pulley 312 can drive the first input gear 321a and the second input gear 321b to rotate, and the rotation directions of the three are the same, but there may be deviations in the tooth position of the first input gear 321a and the second input gear 321b.

[0041] When the adjusting bolt 333 is rotated so that the end of the adjusting bolt 333 abuts against the adjusting disk 331, the adjusting bolt 333 will generate a moment of force M1 acting on the adjusting disk 331. Since the adjusting disk 331 is fixedly connected to the central axis 3211b of the second input gear 321b, that is, the second input gear 321b will be subjected to the same action as the moment of force M1. At the same time, since the adjusting bolt 333 is rotatably arranged on the supporting block 332, the supporting block 332 will be subjected to a reaction moment M2 with the same magnitude but opposite in direction to the moment of force M1. The moment of force M1 and the reaction moment M2 are a pair of moments of force and reaction moments with opposite directions and the same magnitude. Since the supporting block 332 is fixedly connected to the driven pulley 312 and the driven pulley 312 is fixedly connected to the first input gear 321a, that is, the first input gear 321a will be subjected to the same action as the moment of force M2. Therefore, the first input gear 321a and the second input gear 321b are respectively subjected to moments of force with the same magnitude and opposite directions.

[0042] The moments of force with opposite directions and the same magnitude received by the first input gear 321a and the second input gear 321b are respectively transmitted to the output gear 323 through the first transmission gear chain 322a and the second transmission gear chain 322b. Finally, the teeth in the meshing state of the first transmission gear chain 322a and the second transmission gear chain 322b respectively abut against the opposite meshing surfaces of the corresponding two teeth of the output gear 323. In this case, during the process of the drive mechanism 20 performing reverse drive, there is almost no clearance in the gear transmission, which can significantly reduce the idling caused by the side clearance of the teeth, thereby achieving the purpose of eliminating or reducing the side clearance of the teeth.

[0043] Furthermore, in some embodiments of the present application, as Figure 6 shown, the first transmission gear chain 322a includes a first forward gear 3221a, a second forward gear 3222a, a third forward gear 3223a, a fourth forward gear 3224a, a fifth forward gear 3225a and a sixth forward gear 3226a. The first forward gear 3221a and the second forward gear 3222a are coaxially and fixedly arranged, the third forward gear 3223a and the fourth forward gear 3224a are coaxially and fixedly arranged, the fifth forward gear 3225a and the sixth forward gear 3226a are coaxially and fixedly arranged. The second forward gear 3222a meshes with the third forward gear 3223a, the fourth forward gear 3224a meshes with the fifth forward gear 3225a, the first forward gear 3221a meshes with the first input gear 321a, and the sixth forward gear 3226a meshes with the output gear 323.

[0044] When the first input gear 321a rotates, the first forward gear 3221a meshing with it will rotate accordingly. Since the first forward gear 3221a and the second forward gear 3222a are coaxial and fixed, the second forward gear 3222a will rotate synchronously at the same angular velocity. The rotation of the second forward gear 3222a drives the third forward gear 3223a meshing with it, and the third forward gear 3223a drives the fourth forward gear 3224a coaxial with it. The fourth forward gear 3224a drives the fifth forward gear 3225a meshing with it, and the fifth forward gear 3225a drives the sixth forward gear 3226a coaxial with it. Finally, the rotation of the sixth forward gear 3226a drives the output gear 323 meshing with it, thereby transmitting the power from the first input gear 321a to the output gear 323. Each pair of coaxial and fixed gears, such as the first forward gear 3221a and the second forward gear 3222a, forms a rotation unit, and their rotational speeds and directions are exactly the same. Since the second forward gear 3222a meshes with the third forward gear 3223a, the fourth forward gear 3224a meshes with the fifth forward gear 3225a, the first forward gear 3221a meshes with the first input gear 321a, and the sixth forward gear 3226a meshes with the output gear 323, through the meshing relationship between the gears, each rotation unit is connected in sequence to form a continuous power transmission chain. Based on the basic principle of gear transmission, the transmission ratio of the first transmission gear chain 322a is determined by the number of teeth of each gear. For example, the transmission ratio of the first forward gear 3221a to the first input gear 321a is equal to the number of teeth of the first input gear 321a divided by the number of teeth of the first forward gear 3221a. By reasonably designing the number of teeth of each gear, different transmission ratios can be achieved to meet the requirements of the processing head for rotational speed and torque.

[0045] Furthermore, in some embodiments of the present application, such as Figure 7As shown, the second transmission gear chain 322b includes a first reverse gear 3221b, a second reverse gear 3222b, a third reverse gear 3223b, a fourth reverse gear 3224b, a fifth reverse gear 3225b, and a sixth reverse gear 3226b. The first reverse gear 3221b and the second reverse gear 3222b are coaxially and fixedly arranged. The third reverse gear 3223b and the fourth reverse gear 3224b are coaxially and fixedly arranged. The fifth reverse gear 3225b and the sixth reverse gear 3226b are coaxially and fixedly arranged. The second reverse gear 3222b meshes with the third reverse gear 3223b. The fourth reverse gear 3224b meshes with the fifth reverse gear 3225b. The first reverse gear 3221b meshes with the second input gear 321b. The sixth reverse gear 3226b meshes with the output gear 323. Similarly, each pair of coaxially and fixedly arranged gears, such as the first reverse gear 3221 and the second reverse gear 3222b, forms a rotating unit, and their rotational speeds and directions are exactly the same. Based on the basic principle of gear transmission, the transmission ratio of the second transmission gear chain 322b is determined by the number of teeth of each gear. For example, the transmission ratio of the first reverse gear 3221b meshing with the second input gear 321b is equal to the number of teeth of the second input gear 321b divided by the number of teeth of the first reverse gear 3221b meshing with it.

[0046] Among them, the number of teeth of the first reverse gear 3221b, the second reverse gear 3222b, the third reverse gear 3223b, the fourth reverse gear 3224b, the fifth reverse gear 3225b, and the sixth reverse gear 3226b are respectively the same as the number of teeth of the first forward gear 3221a, the second forward gear 3222a, the third forward gear 3223a, the fourth forward gear 3224a, the fifth forward gear 3225a, and the sixth forward gear 3226a, so that the transmission ratio when the first input gear 321a is transmitted through the first transmission gear chain 322a is the same as the transmission ratio when the second transmission gear chain 322b is transmitted through the second transmission gear chain 322b, and the driving mechanism 20 can flexibly switch the transmission direction and achieve the purpose of eliminating or reducing the gear side clearance.

[0047] The rotation axes of the first reverse gear 3221b and the second reverse gear 3222b are parallel to the rotation axes of the first forward gear 3221a and the second forward gear 3222a; the rotation axes of the third reverse gear 3223b and the fourth reverse gear 3224b are parallel to the rotation axes of the third forward gear 3223a and the fourth forward gear 3224a; the rotation axes of the fifth reverse gear 3225b and the sixth reverse gear 3226b are parallel to the rotation axes of the fifth forward gear 3223a and the sixth forward gear 3224a. The rotation axes of each reverse gear and the corresponding forward gear are parallel. For example, the rotation axes of the first reverse gear 3221b and the second reverse gear 3222b are parallel to the rotation axes of the first forward gear 3221a and the second forward gear 3222a, which ensures the relative positional relationship in space between the first transmission gear chain 322a and the second transmission gear chain 322b. By using parallel rotation axes and through a reasonable gear meshing layout, forward or reverse power transmission is achieved, and the rotational speed and torque of the output shaft are precisely controlled according to the tooth number ratio of the gears.

[0048] It should be noted that the first reverse gear 3221b, the second reverse gear 3222b, the third reverse gear 3223b, the fourth reverse gear 3224b, the fifth reverse gear 3225b, the sixth reverse gear 3226b, the first forward gear 3221a, the second forward gear 3222a, the third forward gear 3223a, the fourth forward gear 3224a, the fifth forward gear 3225a, and the sixth forward gear 3226a are provided to increase the transmission ratio and enhance the output torque of the processing head. On the premise of no conflict, the number of transmission gears in the first transmission gear chain 322a and the second transmission gear chain 322b can be reduced, thereby simplifying the transmission structure. For example, the fifth forward gear 3225a, the sixth forward gear 3226a, the fifth reverse gear 3225b, and the sixth reverse gear 3226b can be cancelled, so that the fourth forward gear 3224a and the fourth reverse gear 3224b are directly meshed with the output gear 323. Of course, the third forward gear 3223a, the fourth forward gear 3224a, the third reverse gear 3223b, and the fourth reverse gear 3224b can be further cancelled, so that the second forward gear 3222a and the second reverse gear 3222b are directly meshed with the output gear 323.

[0049] Furthermore, in some embodiments of the present application, such as Figure 2 、 Figure 6 and Figure 7As shown, the belt drive assembly 31 is a synchronous belt drive assembly to achieve a more precise transmission ratio. The diameter of the driving pulley 311 is smaller than that of the driven pulley 312, that is, the rotational speed of the driven pulley 312 will be lower than that of the driving pulley 311, realizing the first reduction of the transmission mechanism 20. The diameter of the first forward gear 3221a is larger than that of the first input gear 321a, the diameter of the third forward gear 3223a is larger than that of the second forward gear 3222a, the diameter of the fifth forward gear 3225a is larger than that of the fourth gear 3224a, and the diameter of the output gear 323 is larger than that of the sixth forward gear 3226a; the diameter of the first reverse gear 3221b is larger than that of the second input gear 321b, the diameter of the third reverse gear 3223b is larger than that of the second reverse gear 3222b, the diameter of the fifth reverse gear 3225b is larger than that of the fourth reverse gear 3224b, and the diameter of the output gear 323 is larger than that of the sixth reverse gear 3226b. The driven pulley 312 drives the first input gear 321a to rotate, and the rotation is transmitted through the meshing gears in the first transmission gear chain 322a. Due to the different diameters of the gears, the rotational speed will change. For example, since the diameter of the first forward gear 3221a is larger than that of the first input gear 321a, the rotational speed of the first forward gear 3221a will decrease and the torque will increase. Similarly, through a series of gear meshing transmissions, the power is finally transmitted to the output gear 323, achieving the deceleration and torque increase effects of the output gear 323. Similarly, the driven pulley 312 also drives the second input gear 321b to rotate, and the rotation is transmitted through the meshing gears in the second transmission gear chain 322b. Finally, the power is transmitted to the output gear 323, achieving the deceleration and torque increase effects of the output gear 323.

[0050] Further, in some embodiments of the present application, as Figure 4 shown, the first input gear 321a extends upward with a protruding shaft 3211a, and a first groove 3121 adapted to the protruding shaft 3211a is provided on the surface of the driven pulley 312 close to the first input gear 321a. The protruding shaft 3211a is fixed in the first groove 3121, so that the driven pulley 312 and the first input gear 321a are tightly connected in space, improving the reliability of power transmission. When the driving pulley 311 drives the driven pulley 311 to rotate through the transmission belt 313, since the protruding shaft 3211a is fixed in the first groove 3121, the rotation of the driven pulley 311 will be transmitted to the first input gear 321a through the protruding shaft 3211a, thereby driving the first input gear 321a to rotate. Therefore, the rotations of the driven pulley 311 and the first input gear 321a are synchronized and have the same rotational speed, realizing the effective connection between the belt drive and the gear drive.

[0051] Further, in some embodiments of the present application, as Figure 4As shown, a central hole adapted to the central shaft 3211b is provided in the middle of the protruding shaft 3211a and the middle of the driven pulley 312. The central shaft 3211b is rotatably inserted into the central hole. One end of the central shaft 3211b passes through the central hole and is fixedly connected to the adjustment disc 331, so that the central shaft 3211b can move synchronously with the adjustment disc 331. At the same time, during the process of gear backlash elimination, the central shaft 3211b can effectively transmit the acting torque received by the adjustment disc 331 to the second input gear 321b, achieving the purpose of eliminating or reducing the gear tooth side clearance of the second input gear 321b, the second transmission gear chain 322b, and the output gear.

[0052] Furthermore, in some embodiments of the present application, as Figure 3 and Figure 4 shown, the second input gear 321b is integrally formed with the central shaft 3211b, ensuring the connection strength and transmission accuracy between the second input gear 321b and the central shaft 3211b, and reducing the assembly error and energy loss between the two. A second groove 3311 adapted to one end of the central shaft 3211b is provided at the bottom of the adjustment disc 331. One end of the central shaft 3211b is fixed in the second groove 3311, so that during the process of gear backlash elimination, the acting torque received by the adjustment disc 331 can be more accurately transmitted to the central shaft 3211b, achieving a more precise adjustment.

[0053] Furthermore, in some embodiments of the present application, as Figure 4 shown, the first groove 3121 is located in the middle of the driven pulley 312, and the second groove 3311 is located in the middle of the adjustment disc 331, ensuring the coaxiality and stability when the driven pulley 312 is connected to the protruding shaft 3211a of the first input gear 321a and the adjustment disc 331 is connected to the second input gear 321b. At the same time, it also ensures the uniform distribution of force, reducing stress concentration and vibration caused by eccentricity. The cross-sections of the first groove 3121 and the second groove 3311 are polygonal, increasing the connection reliability, and effectively preventing the protruding shaft 3211a and the central shaft 3211b from rotating relative to each other in the first groove 3121 and the second groove 3311 respectively, ensuring the accuracy and stability of power transmission.

[0054] Furthermore, in some embodiments of the present application, as Figure 5As shown, the adjustment disk 331 has a cross structure, with good stability and symmetry. Moreover, the adjustment disk 331 has four support arms 3312, enabling the adjustment disk 331 to more evenly bear the acting moment of the adjusting bolt 333 and facilitating the arrangement of the adjusting bolt 333. The four support arms 3312 extend along the radial direction of the driven pulley 312, and the adjusting bolt 333 is arranged on one side of the support arm 3312 in the clockwise or counterclockwise direction, making the acting moment exerted by the adjusting bolt 333 on the adjustment disk 331 more uniform and stable, achieving a better purpose of eliminating or reducing the backlash.

[0055] Another aspect of the embodiment of the present application further provides a processing machine tool. In some embodiments of the present application, the processing machine tool includes the processing head described in one of the foregoing embodiments, and the processing head is arranged on the machine tool body. Since the processing machine tool has the foregoing processing head, it also correspondingly has the effects of the machine tool body, which will not be elaborated here.

[0056] Although the embodiments of the present application have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and purposes of the present application. The scope of the present application is defined by the claims and their equivalents.

Claims

1. A processing head, comprising a main shaft assembly (10), a driving mechanism (20) and a transmission mechanism (30), wherein the transmission mechanism (30) comprises a belt transmission assembly (31) and a gear transmission assembly (32), the belt transmission assembly (31) comprises a driving pulley (311) and a driven pulley (312) which are in transmission connection through a transmission belt (313), the gear transmission assembly (32) comprises an input gear (321) and an output gear (323), the driving pulley (311) is connected to the output end of the driving mechanism (20), the driven pulley (312) is connected to the input gear (321), and the output gear (323) is connected to the main shaft assembly (10), characterized in that, the gear transmission assembly (32) further comprises a transmission gear (322), the input gear (321) comprises a first input gear (321a) and a second input gear (321b) arranged coaxially, the transmission gear (322) comprises a first transmission gear chain (322a) and a second transmission gear chain (322b), the first input gear (321a) meshes with the output gear (323) through the first transmission gear chain (322a), and the second input gear (321b) meshes with the output gear (323) through the second transmission gear chain (322b); the first input gear (321a) is fixedly connected to the driven pulley (312), and the central axis (3211b) of the second input gear (321b) is rotatably arranged in the first input gear (321a) and the driven pulley (312); wherein, the transmission mechanism (30) further comprises a backlash elimination assembly (33), the backlash elimination assembly (33) comprises an adjustment disc (331), a supporting block (332) and an adjusting bolt (333), the adjustment disc (331) and the supporting block (332) are arranged on a side of the driven pulley (312) away from the first input gear (321a), the adjustment disc (331) is fixedly connected to the central axis (3211b) of the second input gear (321b), the supporting block (332) is fixedly connected to the driven pulley (312), the adjusting bolt (333) is rotatably arranged on the supporting block (332), and the end of the adjusting bolt (333) abuts against the adjustment disc (331).

2. The processing head according to claim 1, characterized in that, The first transmission gear chain (322a) includes a first forward gear (3221a), a second forward gear (3222a), a third forward gear (3223a), a fourth forward gear (3224a), a fifth forward gear (3225a), and a sixth forward gear (3226a). The first forward gear (3221a) and the second forward gear (3222a) are coaxially and fixedly arranged. The third forward gear (3223a) and the fourth forward gear (3224a) are coaxially and fixedly arranged. The fifth forward gear (3225a) and the sixth forward gear (3226a) are coaxially and fixedly arranged. The second forward gear (3222a) meshes with the third forward gear (3223a). The fourth forward gear (3224a) meshes with the fifth forward gear (3225a). The first forward gear (3221a) meshes with the first input gear (321a). The sixth forward gear (3226a) meshes with the output gear (323).

3. The processing head according to claim 2, wherein, The second transmission gear chain (322b) includes a first reverse gear (3221b), a second reverse gear (3222b), a third reverse gear (3223b), a fourth reverse gear (3224b), a fifth reverse gear (3225b), and a sixth reverse gear (3226b). The first reverse gear (3221b) and the second reverse gear (3222b) are coaxially and fixedly arranged. The third reverse gear (3223b) and the fourth reverse gear (3224b) are coaxially and fixedly arranged. The fifth reverse gear (3225b) and the sixth reverse gear (3226b) are coaxially and fixedly arranged. The second reverse gear (3222b) meshes with the third reverse gear (3223b). The fourth reverse gear (3224b) meshes with the fifth reverse gear (3225b). The first reverse gear (3221b) meshes with the second input gear (321b). The sixth reverse gear (3226b) meshes with the output gear (323); Among them, the number of teeth of the first reverse gear (3221b), the second reverse gear (3222b), the third reverse gear (3223b), the fourth reverse gear (3224b), the fifth reverse gear (3225b), and the sixth reverse gear (3226b) is the same as that of the first forward gear (3221a), the second forward gear (3222a), the third forward gear (3223a), the fourth forward gear (3224a), the fifth forward gear (3225a), and the sixth forward gear (3226a) respectively; the rotation axes of the first reverse gear (3221b) and the second reverse gear (3222b) are parallel to the rotation axes of the first forward gear (3221a) and the second forward gear (3222a); the rotation axes of the third reverse gear (3223b) and the fourth reverse gear (3224b) are parallel to the rotation axes of the third forward gear (3223a) and the fourth forward gear (3224a); the rotation axes of the fifth reverse gear (3225b) and the sixth reverse gear (3226b) are parallel to the rotation axes of the fifth forward gear (3223a) and the sixth forward gear (3224a).

4. The processing head according to claim 3, characterized in that, The belt drive assembly (31) is a synchronous belt drive assembly. The diameter of the driving pulley (311) is smaller than the diameter of the driven pulley (312). The diameter of the first forward gear (3221a) is larger than the diameter of the first input gear (321a). The diameter of the third forward gear (3223a) is larger than the diameter of the second forward gear (3222a). The diameter of the fifth forward gear (3225a) is larger than the diameter of the fourth gear (3224a). The diameter of the output gear (323) is larger than the diameter of the sixth forward gear (3226a); the diameter of the first reverse gear (3221b) is larger than the diameter of the second input gear (321b). The diameter of the third reverse gear (3223b) is larger than the diameter of the second reverse gear (3222b). The diameter of the fifth reverse gear (3225b) is larger than the diameter of the fourth reverse gear (3224b). The diameter of the output gear (323) is larger than the diameter of the sixth reverse gear (3226b).

5. The processing head according to any one of claims 1-4, characterized in that, The first input gear (321a) extends upward with a protruding shaft (3211a). A first groove (3121) adapted to the protruding shaft (3211a) is provided on the surface of the driven pulley (312) close to the first input gear (321a). The protruding shaft (3211a) is fixed in the first groove (3121).

6. The processing head according to claim 5, characterized in that, A central hole adapted to the central shaft (3211b) is provided in the middle of the protruding shaft (3211a) and the middle of the driven pulley (312). The central shaft (3211b) is rotatably inserted through the central hole. One end of the central shaft (3211b) passes through the central hole and is fixedly connected to the adjustment disc (331).

7. The processing head according to claim 6, characterized in that, The second input gear (321b) is integrally formed with the central shaft (3211b), and a second groove (3311) adapted to one end of the central shaft (3211b) is provided at the bottom of the adjustment disc (331), and one end of the central shaft (3211b) is fixed in the second groove (3311).

8. The processing head according to claim 7, characterized in that, The first groove (3121) is located in the middle of the driven pulley (312), and the second groove (3311) is located in the middle of the adjustment disc (331); the cross-sections of the first groove (3121) and the second groove (3311) are polygonal.

9. The processing head according to any one of claims 1-4, characterized in that, The adjustment disc (331) has a cross structure and has four arms (3312), and the four arms (3312) extend along the radial direction of the driven pulley (312), and the adjusting bolt (333) is arranged on one side of the arm (3312) in the clockwise or counterclockwise direction.

10. A processing machine tool, comprising a machine tool body, characterized in that, It further includes a processing head according to any one of claims 1 to 9, and the processing head is arranged on the machine tool body.

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