Machining head and machining machine 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, and the transmission mechanism comprises a belt transmission mechanism, a gear transmission mechanism, an anti-backlash mechanism and a tensioning mechanism; the belt transmission mechanism comprises a driving belt wheel, a first driven belt wheel and a second driven belt wheel which are arranged in a triangular shape and are in transmission connection through a transmission belt. The clearance eliminating mechanism comprises a clearance adjusting wheel and a clearance adjusting support, the clearance adjusting wheel abuts against the outer side of the portion, between the first driven belt wheel and the second driven belt wheel, of the transmission belt, and the tensioning mechanism comprises a tensioning wheel and a tensioning support. The tensioning wheel abuts against the outer side of the transmission belt between the driving belt wheel and the first driven belt wheel or the outer side of the transmission belt between the driving belt wheel and the second driven belt wheel. By the adoption of the machining head, the expected values of the tensioning amount of the transmission belt and the backlash amount of the gear can be achieved with few adjustment times.

Description

Technical Field

[0001] The present application relates to the technical field of machine tools, and particularly to a machining head and a machining machine tool. Background Art

[0002] As a core component of a numerically controlled machine tool (especially a five-axis linkage machining center), the performance of the machining head directly affects the accuracy, stability, and machining efficiency of the entire machine tool. The machining head of a numerically controlled machine tool usually adopts transmission methods such as belt drive and gear drive. When using the belt drive method, the transmission belt must be tensioned, and when using the gear drive method, the backlash must be reduced.

[0003] Currently, for the transmission mechanism with the above two transmission methods, the following solutions are usually adopted for the two requirements of tensioning and clearance adjustment: (1) The tensioning mechanism also serves as the clearance adjustment mechanism (for example, Chinese Patent Document CN111922739A). There is often a large gap between the required tension of the transmission belt and the required backlash of the gear. If one of them is satisfied, the other will surely not reach the ideal adjustment amount. In addition, when the transmission belt is not tensioned, adjusting the clearance according to the calculated backlash adjustment amount will result in a large deviation between the actual effect and the expected value calculated theoretically; (2) The tensioning mechanism still uses a tensioning wheel for pressing against the transmission belt, and the clearance adjustment mechanism applies different torques to two gears respectively based on the principle of double-gear backlash elimination and locks them (for example, Chinese Patent Document CN116906550B). However, this solution must be tensioned at least twice. In fact, although it is tensioned twice, the amount of backlash still changes unexpectedly (that is, the tension amount is satisfied, but the amount of backlash is not the expected value).

[0004] The machining head of a numerically controlled machine tool must reach the expected values in both aspects of the tensioning of the transmission belt and the adjustment of the backlash as much as possible. Therefore, the current machining head needs to be improved. Summary of the Invention

[0005] The embodiments of the present application aim to solve at least one of the problems in the prior art. The embodiments of the present application provide a machining head and a machining machine tool, which can achieve the expected values of both the tension amount of the transmission belt and the backlash amount of the gear with fewer adjustment times.

[0006] The related technical solutions of the embodiments of the present application are as follows:

[0007] The first aspect of the embodiments of the present application provides a machining head, including:

[0008] A spindle assembly, including a spindle box and a spindle installed in the spindle box;

[0009] A driving mechanism, including a motor;

[0010] The transmission mechanism includes a belt transmission mechanism, a gear transmission mechanism, a backlash elimination mechanism, a tensioning mechanism, and a rotating base. The belt transmission mechanism is in transmission connection with the output end of the motor. The gear transmission mechanism is in transmission connection with the belt transmission mechanism. The input end of the rotating base is in transmission connection with the gear transmission mechanism. The rotating base is used to drive the headstock to rotate.

[0011] Among them, the belt transmission mechanism includes a driving pulley, a first driven pulley, and a second driven pulley that are connected by a transmission belt. The driving pulley, the first driven pulley, and the second driven pulley are arranged in a triangle. The backlash elimination mechanism includes an adjusting wheel and an adjusting bracket for installing the adjusting wheel. The adjusting wheel abuts against the outer side of the transmission belt between the first driven pulley and the second driven pulley. The tensioning mechanism includes a tensioning wheel and a tensioning bracket for installing the tensioning wheel. The tensioning wheel abuts against the outer side of the transmission belt between the driving pulley and the first driven pulley or between the driving pulley and the second driven pulley.

[0012] Optionally, the processing head further includes a processing head base. The driving mechanism is arranged on the processing head base. The adjusting bracket is connected to the processing head base.

[0013] Among them, the tensioning mechanism further includes a tensioning wheel shaft, a spring, and a sliding member. The tensioning wheel is rotatably connected to the sliding member through the tensioning wheel shaft. The sliding member is used to drive the tensioning wheel shaft to approach or move away from the transmission belt. One end of the tensioning bracket is fixedly connected to the processing head base. The other end of the tensioning bracket is connected to the sliding member through the spring. A partial area of the tensioning bracket overlaps with the sliding member. The overlapping area of the tensioning bracket and the sliding member is matched with a locking element through a plurality of through holes. The sliding member is slidably connected relative to the tensioning bracket. The locking element is used to lock the sliding member and the tensioning bracket at a specific position.

[0014] Optionally, one end of the tensioning bracket is fixedly connected to the processing head base through the adjusting bracket. The other end of the tensioning bracket is provided with a first spring mounting seat. The sliding member is provided with a second spring mounting seat. A plurality of the springs are arranged side by side, and both ends of the plurality of springs respectively abut against the first spring mounting seat and the second spring mounting seat.

[0015] One of the tensioning bracket and the sliding member is provided with a plurality of through holes at equal intervals along the sliding direction of the sliding member in the overlapping area. The other is provided with a waist-shaped hole in the overlapping area. The waist-shaped hole can be aligned with at least one of the plurality of through holes for the locking element to pass through for locking.

[0016] Optionally, an installation hole is provided at one end of the sliding member close to the tensioning wheel. The sliding member is further fixedly connected with a tensioning wheel shaft mounting seat. A clamping hole is provided at a position of the tensioning wheel shaft mounting seat corresponding to the installation hole. The tensioning wheel shaft sequentially passes through the installation hole and the clamping hole. The tensioning wheel is mounted between the installation hole and the clamping hole. The clamping hole has an opening in the circumferential direction. One side of the tensioning wheel shaft mounting seat is separated by the opening into a first locking portion and a second locking portion which are spaced apart and oppositely arranged. The first locking portion and the second locking portion are respectively connected to the inner walls at the opening of the clamping hole. The first locking portion and the second locking portion are respectively provided with locking holes that are aligned with each other. A locking bolt is inserted into the locking hole for locking the tensioning wheel shaft.

[0017] Optionally, the tensioning mechanism further includes a tensioning wheel bearing and a guide rod. The tensioning wheel is sleeved on the tensioning wheel shaft through the tensioning wheel bearing; a guide hole is provided on the first spring mounting seat. One end of the guide rod is fixedly connected with the second spring mounting seat. The other end of the guide rod slidably passes through the guide hole. The spring is sleeved on the guide rod.

[0018] Optionally, the gear transmission mechanism includes a driven gear and a first driving gear and a second driving gear that are respectively meshed with the driven gear; a first speed reducer is used for drivingly connecting the first driven belt pulley and the first driving gear, and a second speed reducer is used for drivingly connecting the second driven belt pulley and the second driving gear; the transmission belt is a synchronous belt.

[0019] Optionally, the backlash elimination mechanism further includes a spiral adjusting member, an adjusting wheel shaft and a pushing block. The adjusting wheel is rotatably arranged on the adjusting bracket through the adjusting wheel shaft. The adjusting wheel shaft is located between the spiral adjusting member and the transmission belt. A threaded hole adapted to the spiral adjusting member is provided on the adjusting bracket. The spiral adjusting member passes through the threaded hole to drive the adjusting wheel shaft to approach or move away from the transmission belt; the pushing block is fixedly connected with the adjusting wheel shaft. A through groove is provided on the pushing block. A notch is formed on the surface of the through groove perpendicular to the extending direction of the spiral adjusting member. An annular groove is provided on the circumferential surface of the spiral adjusting member. The spiral adjusting member cooperates with the two side walls of the through groove through the annular groove.

[0020] Optionally, a first guiding structure is provided on the gap adjusting bracket, and a second guiding structure adapted to the first guiding structure is provided on the gap adjusting wheel shaft. One of the first guiding structure and the second guiding structure is a chute structure and the other is a convex block structure. The opening width of the chute structure is greater than the bottom width of the chute structure, and / or the width of the protruding end of the convex block structure is less than the width of the root of the convex block structure.

[0021] Optionally, the rotation axis of the rotating base forms a 45° angle with the axis of the main shaft. The main shaft box is fixedly connected to the rotating base, and the outer peripheries of the rotating base and the processing head base are hermetically connected by a fixed sealing ring and a rotating sealing ring.

[0022] In a second aspect of the embodiments of the present application, a processing machine tool is provided. The processing machine tool includes the processing head in one of the foregoing embodiments.

[0023] The technical solution of the processing head in the embodiments of the present application has at least the following technical effects: The processing head in the embodiments of the present application has a backlash elimination mechanism and a tensioning mechanism. Among them, the gap adjusting wheel of the backlash elimination mechanism abuts against the outer side of the transmission belt between the first driven pulley and the second driven pulley, and the tensioning wheel of the tensioning mechanism abuts against the outer side of the transmission belt between the driving pulley and the first driven pulley or between the driving pulley and the second driven pulley. After tensioning a section of the transmission belt (i.e., the transmission belt between the driving pulley and the first driven pulley or between the driving pulley and the second driven pulley) by using the tensioning wheel to abut against it inward, then use the gap adjusting wheel to abut against other sections of the transmission belt (i.e., the transmission belt between the first driven pulley and the second driven pulley) inward for gap adjustment. Since the adjustment amounts of the tensioning mechanism and the gap adjustment mechanism are both displacement amounts toward the inner side of the transmission belt, the influence of the tensioning amount on the gap adjustment amount or the influence of the gap adjustment amount on the tensioning amount can be directly offset or compensated when calculating, thereby simplifying the calculation of the adjustment amount. After the calculation of the adjustment amount is simplified, only adjusting the tensioning amount once can basically meet both the tensioning amount and the gap adjustment amount.

[0024] It is not difficult to understand that the related 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.

[0025] Additional aspects and advantages of the embodiments of the present application will be given in part in the following description. Thus, part of them will become obvious from the following description, or be learned through the practice of the present application. Description of the Drawings

[0026] FIG. 1(a) is a schematic structural view of the processing head in the embodiments of the present application;

[0027] FIG. 1(b) is a cross-sectional view of the processing head in the embodiments of the present application;

[0028] Figure 2(a) is a schematic structural diagram of the tensioning mechanism in the processing head in the embodiment of the present application;

[0029] Figure 2(b) is a schematic structural diagram of the tensioning bracket and the sliding member in the tensioning mechanism in the embodiment of the present application;

[0030] Figure 2(c) is an exploded schematic diagram of some components in the tensioning mechanism in the embodiment of the present application;

[0031] Figure 2(d) is an exploded schematic diagram of the tensioning wheel shaft mounting seat and the locking bolt in the tensioning mechanism in the embodiment of the present application;

[0032] Figure 3(a) is a schematic structural diagram of the belt drive mechanism, the backlash elimination mechanism, the tensioning mechanism, etc. in the processing head in the embodiment of the present application;

[0033] Figure 3(b) is a schematic diagram of another perspective of Figure 3(a) (the viewing direction is from bottom to top);

[0034] Figure 4 is a schematic structural diagram of the main transmission components of the transmission mechanism of the processing head in the embodiment of the present application;

[0035] Figure 5 is a schematic diagram of the backlash elimination principle of the backlash elimination mechanism in some embodiments of the present application;

[0036] Figure 6 is an exploded schematic diagram of the backlash elimination mechanism of the processing head in the embodiment of the present application;

[0037] Figure 7(a) is an assembly schematic diagram of the backlash elimination bracket, the backlash elimination wheel shaft, and the stop block in the embodiment of the present application;

[0038] Figure 7(b) is an assembly schematic diagram of the screw transmission member, the backlash elimination wheel shaft, and the stop block in the embodiment of the present application;

[0039] Figure 7(c) is an assembly schematic diagram of the screw transmission member and the stop block in the embodiment of the present application;

[0040] Figure 7(d) is a schematic structural diagram of the backlash elimination bracket in the embodiment of the present application;

[0041] Figure 7(e) is a schematic structural diagram of the backlash elimination wheel shaft in the embodiment of the present application.

[0042] In the figure:

[0043] 10 - Spindle assembly, 12 - Spindle box; 20 - Driving mechanism, 21 - Motor, 22 - Motor mounting base; 30 - Transmission mechanism, 31 - Belt transmission mechanism, 311 - First driven pulley, 312 - Second driven pulley, 313 - Driving pulley, 314 - Transmission belt, 32 - Reducer assembly, 321 - First reducer, 322 - Second reducer, 33 - Gear transmission mechanism, 331 - First driving gear, 332 - Second driving gear, 333 - Driven gear, 34 - Backlash elimination mechanism, 341 - Adjusting wheel, 342 - Spiral adjusting member, 343 - Adjusting bracket, 3431 - First guiding structure, 344 - Adjusting wheel shaft, 3441 - Second guiding structure, 345 - Stopper, 346 - Pushing block, 3461 - Through groove, 347 - Adjusting wheel bearing, 35 - Tensioning mechanism, 351 - Tensioning pulley, 352 - Tensioning pulley shaft, 353 - Spring, 354 - Tensioning bracket, 3541 - First spring mounting seat, 3542 - Kidney-shaped hole, 3543 - Reinforcing rib plate, 3544 - Bracket mounting portion, 355 - Sliding member, 3551 - Second spring mounting seat, 3552 - Mounting hole, 3553 - Sliding guiding portion, 356 - Locking element, 357 - Tensioning pulley shaft mounting seat, 3571 - First locking portion, 3572 - Second locking portion, 3573 - Clamping hole, 3574 - Locking bolt, 358 - Tensioning pulley bearing, 359 - Guide rod, 36 - Rotating base; 40 - Machining head base. Detailed implementation manner

[0044] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for the description of the embodiments of the present application or the prior art.

[0045] Obviously, the drawings in the following description are only some embodiments of the present application. For those of ordinary skill in the art, without creative efforts, other drawings of embodiments can also be obtained according to the technical solutions shown in these drawings.

[0046] It should be understood that the "multiple" mentioned herein refers to two or more. In the description of the present application, unless otherwise specified, " / " means "or", for example, "A / B" means A or B; the "and / or" herein is only a description of the association relationship of associated objects, and it means that there can be three relationships, for example, "A and / or B" can mean: A exists alone, A and B exist simultaneously, and B exists alone, etc. The above three situations.

[0047] In addition, for the sake of clearly describing the technical solutions of the embodiments of the present application, in the embodiments of the present application, expressions such as "first" or "second" are used to distinguish identical or similar items with basically the same functions and roles. Those skilled in the art can understand that expressions such as "first" and "second" do not limit the quantity and execution order, and the expressions such as "first" and "second" do not necessarily limit differences.

[0048] The "installation", "connection", and "setting" mentioned in the embodiments of the present application include direct installation / connection / setting and also include indirect installation / connection / setting; include detachable installation / connection / setting and also include non-detachable installation / connection / setting; include fixed installation / connection / setting and also include movable installation / connection / setting. The "fixed connection" mentioned in the embodiments of the present application includes detachable fixed connection, also includes non-detachable fixed connection, and also includes an integrally formed structure.

[0049] Please refer to Figures 1(a) to 7(e) , the first aspect of the embodiments of the present application provides a processing head for a processing machine tool. As shown in FIGS. 1(a) and 1(b), the processing head includes a spindle assembly 10, a driving mechanism 20, a transmission mechanism 30, and a processing head base 40.

[0050] The spindle assembly 10 includes a spindle box 12 and a spindle installed in the spindle box 12.

[0051] The driving mechanism 20 includes a motor 21. Specifically, the motor 21 can be a servo motor.

[0052] The transmission mechanism 30 includes a belt transmission mechanism 31, a gear transmission mechanism 33, a backlash elimination mechanism 34, a tensioning mechanism 35, and a rotating base 36. The belt transmission mechanism 31 is in transmission connection with the output end of the motor 21, the gear transmission mechanism 33 is in transmission connection with the belt transmission mechanism 31, the input end of the rotating base 36 is in transmission connection with the gear transmission mechanism 33, and the rotating base 36 is used to drive the spindle box 12 to rotate. The rotating base 36 can be a bearing seat. The rotating base 36 is used to drive the spindle box 12 to rotate. Specifically, the housing of the spindle box 12 is fixedly connected circumferentially to the bearing seat serving as the rotating base 36, so that the spindle box 12 rotates following the rotating base 36. The spindle is installed in the spindle box 12, so that the spindle can revolve around the rotation center axis of the rotating base 36.

[0053] As Figures 1(a) to 4As shown in the figure, the belt transmission mechanism 31 includes a driving pulley 313, a first driven pulley 311, and a second driven pulley 312 that are drivingly connected through a transmission belt 314. The driving pulley 313, the first driven pulley 311, and the second driven pulley 312 are arranged in a triangle; the backlash elimination mechanism 34 includes an adjustment pulley 341 and an adjustment bracket 343 for mounting the adjustment pulley 341. The adjustment pulley 341 abuts against the outer side of the transmission belt 314 between the first driven pulley 311 and the second driven pulley 312. The tensioning mechanism 35 includes a tensioning pulley 351 and a tensioning bracket 354 for mounting the tensioning pulley 351. The tensioning pulley 351 abuts against the outer side of the transmission belt 314 between the driving pulley 313 and the first driven pulley 311 or between the driving pulley 313 and the second driven pulley 312. As mentioned above, in the embodiments of the present application, "mounting" includes indirectly mounting.

[0054] In the processing head in the embodiments of the present application, there is a backlash elimination mechanism 34 and a tensioning mechanism 35. Among them, the adjustment pulley 341 of the backlash elimination mechanism 34 abuts against the outer side of the transmission belt 314 between the first driven pulley 311 and the second driven pulley 312, while the tensioning pulley 351 of the tensioning mechanism 35 abuts against the outer side of the transmission belt 314 between the driving pulley 313 and the first driven pulley 311 or between the driving pulley 313 and the second driven pulley 312. After tensioning by using the tensioning pulley 351 to abut against a section of the transmission belt 314 (i.e., the transmission belt 314 between the driving pulley 313 and the first driven pulley 311 or between the driving pulley 313 and the second driven pulley 312) towards the inside, then use the adjustment pulley 341 to abut against other sections of the transmission belt 314 (i.e., the transmission belt 314 between the first driven pulley 311 and the second driven pulley 312) towards the inside for backlash adjustment. Since the adjustment amounts of both the tensioning mechanism 35 and the backlash adjustment mechanism 34 are displacement amounts towards the inside of the transmission belt 314, when calculating the influence of the tensioning amount on the backlash adjustment amount or the influence of the backlash adjustment amount on the tensioning amount, they can be directly offset or compensated, thus simplifying the calculation of the adjustment amount.

[0055] On the contrary, in the traditional technical solution, the parameter quantity adjusted by the backlash elimination mechanism 34 (for example, the torque value applied by a torque wrench) is different from the parameter quantity adjusted by the tensioning mechanism 35 (for example, the displacement amount towards the inside of the transmission belt 314), and the expected value of the tensioning amount and the expected value of the flank clearance amount affect each other, so that in order to balance the requirements of both, repeated trial adjustments are necessary. By adopting the technical solution of the embodiments of the present application, the calculation formulas for both the tensioning amount and the flank clearance amount can be simplified. After the calculation of the adjustment amount is simplified, only adjusting the tensioning amount once can basically meet the requirements of both the tensioning amount and the backlash adjustment amount.

[0056] Optionally, in some embodiments of the present application, please refer to Figures 2(a) to 2(d), the processing head further includes a processing head base 40, the driving mechanism 20 is arranged on the processing head base 40, and the clearance adjusting bracket 343 is connected to the processing head base 40; the tensioning mechanism 35 further includes a tensioning wheel shaft 352, a spring 353 and a sliding member 355. The tensioning wheel 351 is rotatably connected to the sliding member 355 through the tensioning wheel shaft 352. The sliding member 355 is used to drive the tensioning wheel shaft 352 to approach or move away from the transmission belt 314. One end of the tensioning bracket 354 is fixedly connected to the processing head base 40, and the other end of the tensioning bracket 354 is connected to the sliding member 355 through the spring 353. A partial area of the tensioning bracket 354 overlaps with the sliding member 355. The overlapping area of the tensioning bracket 354 and the sliding member 355 is matched with a locking element 356 through a plurality of through holes. The sliding member 355 is slidably connected relative to the tensioning bracket 354, and the locking element 356 is used to lock the sliding member 355 and the tensioning bracket 354 at a specific position.

[0057] The processing head base 40 can be a part of the housing of the processing head, and a part of the housing is used as the installation base for the components of the processing head. The spring 353 can be a compression spring.

[0058] In the embodiment of the present application, the locking element 356 can lock the relative positions of the two through the through holes on the tensioning bracket 354 and the sliding member 355. The spring 353 also abuts between the tensioning bracket 354 and the sliding member 355. Therefore, the spring 353 is in a compressed deformation state under the locked state. When the locking element 356 is removed, the sliding member 355 will be in an unlocked state. The spring mounting seat on the tensioning bracket 354 is indirectly fixed on the processing head base 40. Under the action of the elastic restoring force, the sliding member 355 has a tendency to recover from the compressed deformation state to the natural length state, that is, the sliding member 355 in the unlocked state will move towards the transmission belt 314 until it abuts against the transmission belt 314. Since there are a plurality of through holes in the overlapping area of the tensioning bracket 354 and the sliding member 355, the sliding member 355 can be locked at different positions on the tensioning bracket 354, that is, the degree of compression (i.e., the amount of deformation) of the spring 353 can be adjusted as needed, so that the magnitude of the elastic restoring force released by the spring 353 is also different. That is to say, the magnitude of the tensioning force of the tensioning wheel 351 against the transmission belt 314 can be adjusted as needed. In addition, in the embodiment of the present application, the two components (i.e., the tensioning bracket 354 and the sliding member 355) used to adjust the magnitude of the tensioning force overlap in a partial area rather than being axially connected in series with each other. Therefore, the structure of the entire tensioning mechanism 35 and even the entire processing head can be more compact.

[0059] As shown in FIG. 2( a) and FIG. 2( b), in one embodiment of the present application, the tension bracket 354 includes a tension bracket body extending in the same direction as the sliding direction of the sliding member 355, a first spring mounting seat 3541, a bracket mounting portion 3544, and a reinforcing rib 3543. The bracket mounting portion 3544 is provided with a plurality of through holes, and the tension bracket 354 is fixedly mounted on the processing head base 40 through the cooperation of the plurality of through holes on the bracket mounting portion 3544 and the locking element 356. The first spring mounting seat 3541 is provided at one end of the tension bracket 354 away from the transmission belt 314. The first spring mounting seat 3541 is an integral structure with the tension bracket body, and is fixedly connected in an undetachable manner or in a detachable manner. The reinforcing rib 3543 connects the tension bracket body with two side edges of the bracket mounting portion 3544, thereby improving the mechanical properties of the entire tension bracket 354.

[0060] In FIG. 2(a) and FIG. 2(b), the surface of the sliding member 355 opposite to the tension bracket 354 (i.e., the sliding surface) is a flat surface, and the opposite side of the flat surface has a plurality of stepped surfaces, so that the thickness of the sliding member body at different positions thereof is different, wherein the thickness of the region where the mounting hole 3552 is located is relatively thin, so that the depth of the mounting hole 3552 is relatively shallow, which is convenient for the installation and positioning of the tension wheel shaft 352. The thickness of the sliding member body at the position where it is fixedly connected to the second spring mounting seat 3551 and the position where it is fixedly connected to the tension wheel mounting seat 357 is relatively thick. FIG. 2(b) also shows that one side of the sliding member 355 protrudes toward the tension bracket 354 to form a sliding guide portion 3553, and the extension direction of the sliding guide portion 3553 is the same as the sliding direction of the sliding member 355 itself. FIG2(c) shows that the tension wheel 351 can rotate around the tension wheel shaft 352 through the cooperation between the tension wheel bearing 358 and the tension wheel shaft 352, wherein the tension wheel shaft 352 is a stepped shaft with a shoulder, so as to facilitate the installation and positioning of other accessories. The tension wheel 351 can be set to a shape with larger diameters at both ends and smaller in the middle along its axial direction (its longitudinal section is an I-shaped shape), and the transmission belt 314 is just stuck in the concave part with a smaller diameter in the middle.

[0061] Further, in some embodiments of the present application, as shown in FIGS. 2(a) and 2(b), one of the tensioning bracket 354 and the sliding member 355 is provided with a plurality of through holes at equal intervals along the sliding direction of the sliding member 355 in the overlapping area therebetween, and the other is provided with a waist-shaped hole 3542 in the overlapping area therebetween. The waist-shaped hole 3542 can be aligned with at least one of the plurality of through holes for the locking element 356 to pass through for locking. The equal-spacing arrangement of the plurality of through holes enables the deformation amount of the spring 353 to be adjusted in different gears. In FIGS. 2(a) and 2(b), the waist-shaped hole 3542 is provided on the tensioning bracket 354, and a plurality of through holes are provided at equal intervals along its own sliding direction on the sliding member 355 directly below the tensioning bracket 354. It can be understood that the plurality of through holes can also be provided on the tensioning bracket 354, and the waist-shaped hole is provided on the sliding member 355. Optionally, in some embodiments of the present application, as shown in FIGS. 2(a) and 2(b), one end of the tensioning bracket 354 is fixedly connected to the processing head base 40 through the clearance adjusting bracket 343, the other end of the tensioning bracket 354 is provided with a first spring mounting seat 3541, the sliding member 355 is provided with a second spring mounting seat 3551, the plurality of springs 353 are arranged side by side, and both ends of the plurality of springs 353 respectively abut against the first spring mounting seat 3541 and the second spring mounting seat 3551.

[0062] The stiffness coefficient k of the elastic system composed of multiple parallel springs is the sum of the stiffness coefficients of the multiple springs, that is, k = k 1 + k 2 + … + k n , where k 1 , k 2 , …… k n are respectively the stiffness coefficients of the multiple parallel springs. In FIGS. 2(a) and 2(b), two springs 353 are in parallel. A plurality of guide rods 359 are provided between the first spring mounting seat 3541 and the second spring mounting seat 3551, and each spring 353 is respectively sleeved on a guide rod 359. It can be understood that more springs 353 can also be provided in parallel according to needs, and the number of guide rods 359 can also be set to be multiple. Therefore, in some embodiments of the present application, a plurality of parallel springs are provided, and the stiffness coefficient of the elastic system can also be adjusted according to needs. As is well known, the magnitude of the elastic restoring force is the product of the stiffness coefficient and the deformation amount. As described above, in the technical solutions of some embodiments of the present application, the deformation amount can be adjusted according to needs; and in some other embodiments of the present application, the stiffness coefficient can be further adjusted to further adjust the magnitude of the tensioning force.

[0063] Further, in some embodiments of the present application, as shown in FIGS. 2(a) and 2(b), one of the tensioning bracket 354 and the slider 355 is provided with a plurality of through holes at equal intervals along the sliding direction of the slider 355 in the overlapping area, and the other is provided with a waist-shaped hole 3542 in the overlapping area. The waist-shaped hole 3542 can be aligned with at least one of the plurality of through holes for the locking element 356 to pass through for locking.

[0064] The equal interval arrangement of the plurality of through holes enables the deformation amount of the spring 353 to be adjusted in different gears. In FIGS. 2(a) and 2(b), the waist-shaped hole 3542 is provided on the tensioning bracket 354, and a plurality of through holes are provided at equal intervals along the sliding direction of the slider 355 directly below the tensioning bracket 354. It can be understood that the plurality of through holes can also be provided on the tensioning bracket 354, and the waist-shaped hole is provided on the slider 355.

[0065] Optionally, in some embodiments of the present application, as shown in FIG. 2(b), an installation hole 3552 is formed at one end of the slider 355 close to the tensioning wheel 351. As shown in FIGS. 2(a), 2(c), and 2(d), the slider 355 is also fixedly connected with a tensioning wheel shaft mounting seat 357. The tensioning wheel shaft mounting seat 357 is provided with a clamping hole 3573 at a position directly opposite to the installation hole 3552. The tensioning wheel shaft 352 sequentially passes through the installation hole 3552 and the clamping hole 3573, and the tensioning wheel 351 is installed between the installation hole 3552 and the clamping hole 3573. As shown in FIG. 2(d), the clamping hole 3573 has an opening in the circumferential direction. One side of the tensioning wheel shaft mounting seat 357 is separated into a first locking portion 3571 and a second locking portion 3572 which are spaced apart and oppositely arranged by the opening. The first locking portion 3571 and the second locking portion 3572 are respectively connected to the inner walls at the opening of the clamping hole 3573. The first locking portion 3571 and the second locking portion 3572 are respectively provided with locking holes that are aligned with each other, and a locking bolt 3574 is inserted into the locking holes for locking the tensioning wheel shaft 352.

[0066] The technical solution of the embodiment of the present application adopts the tensioning wheel shaft mounting seat 357 to clamp the lower part of the tensioning wheel shaft 352 (it can also be set to clamp the upper part of the tensioning wheel shaft 352 as needed), and the upper part of the tensioning wheel shaft 352 is limited in directions other than the axial direction by the mounting hole 3552 on the sliding member 355, so as to reduce the possibility of rollover caused by only clamping the lower part of the tensioning wheel shaft 352. In addition, the tensioning wheel shaft mounting seat 357 adopts a structure similar to a clamp to clamp the tensioning wheel shaft 352, and its clamping is relatively firm, so that the movement of the tensioning wheel shaft mounting seat 357 can drive the movement of the tensioning wheel shaft 352. The tensioning wheel shaft mounting seat 357 is fixedly connected to the sliding member 355, so that the sliding of the sliding member 355 after unlocking can drive the movement of the tensioning wheel shaft 352.

[0067] Optionally, in some embodiments of the present application, please refer to Figures 2(a) to 2(d) The tensioning mechanism 35 further includes a tensioning wheel bearing 358 and a guide rod 359. The tensioning wheel 351 is sleeved on the tensioning wheel shaft 352 through the tensioning wheel bearing 358. A guide hole is provided on the first spring mounting seat 3541. One end of the guide rod 359 is fixedly connected to the second spring mounting seat 3551. The other end of the guide rod 359 is slidably penetrated in the guide hole. The spring 353 is sleeved on the guide rod 359. Specifically, the other end of the guide rod 359 passes through the guide hole and thus also passes through the entire first spring mounting seat 3541. The provision of the guide rod 359 can reduce the risk of instability of the spring 353.

[0068] Further, in some embodiments of the present application, please refer to Figure 4 The gear transmission mechanism 33 includes a driven gear 333 and a first driving gear 331 and a second driving gear 332 respectively meshing with the driven gear 333. The transmission mechanism 30 also includes a reducer assembly 32, and the reducer assembly 32 includes a first reducer 321 and a second reducer 322. The first driven pulley 311 and the first driving gear 331 are connected to each other through the first reducer 321, and the second driven pulley 312 and the second driving gear 332 are connected to each other through the second reducer 322. The transmission belt 314 is a synchronous belt, such as a trapezoidal tooth synchronous belt, a circular arc tooth synchronous belt, a parabolic tooth synchronous belt, etc.

[0069] The introduction of the first speed reducer 321 and the second speed reducer 322 can further increase the output torque of the transmission mechanism 30. It can be understood that the first speed reducer 321 and the second speed reducer 322 include not only the commercially available speed reducers / reduction gears on the market, but also any transmission components that can be designed or manufactured by oneself and can achieve speed reduction and torque increase. The power transmission components of the first transmission chain are, in order from upstream to downstream, the driving pulley 313, the first driven pulley 311, the first speed reducer 321, the first driving gear 331, and the driven gear 333. The power transmission components of the second transmission chain are, in order from upstream to downstream, the driving pulley 313, the second driven pulley 312, the second speed reducer 322, the second driving gear 332, and the driven gear 333. That is to say, the driving pulley 313 transmits power to the driven gear 333 through the first transmission chain including the first driven pulley 311 and the first driving gear 331 and the second transmission chain including the second driven pulley 312 and the second driving gear 332 respectively. Please refer to FIG. 1(a). The driven gear 333 is in transmission connection with the input end of the rotating base 36, so that the driven gear 333 drives the rotating base 36 to rotate.

[0070] Furthermore, the distances between the pulley centers of the first driven pulley 311 and the second driven pulley 312 and the pulley center of the driving pulley 313 are equal, that is, the connecting lines of the pulley centers of the driving pulley 313, the first driven pulley 311, and the second driven pulley 312 form an isosceles triangle layout, and the pulley center of the driving pulley 313 is located at the vertex of the isosceles triangle. The symmetrically arranged double transmission chains not only make each transmission component on the transmission chain evenly stressed and thus reduce wear, but also facilitate simplifying the physical model for calculating the backlash adjustment amount, so as to conveniently calculate the backlash adjustment amount of the backlash adjustment component according to the desired reduction amount of the tooth side clearance.

[0071] Optionally, in some embodiments of the present application, please refer to FIGS. 3(a) and 3(b). The backlash elimination mechanism 34 further includes a spiral adjustment member 342 and an adjustment wheel shaft 344. The adjustment wheel 341 is rotatably arranged on the adjustment bracket 343 through the adjustment wheel shaft 344. The adjustment wheel shaft 344 is located between the spiral adjustment member 342 and the transmission belt 314. A screw hole adapted to the spiral adjustment member 342 is provided on the adjustment bracket 343, and the spiral adjustment member 342 passes through the screw hole to drive the adjustment wheel shaft 344 to approach or move away from the transmission belt 314.

[0072] The spiral adjusting member 342 is used to drive the gap adjusting wheel 341 to move toward or away from the transmission belt 314. The circumferential surface of the gap adjusting wheel 341 abuts against the outer surface of the transmission belt 314 between the first driven pulley 311 and the second driven pulley 312. The spiral adjusting member 342 drives the gap adjusting wheel shaft 344 to move so that the gap adjusting wheel 341 approaches or moves away from the transmission belt 314, and the spiral adjusting member 342 can more accurately control the displacement of the gap adjusting wheel 341 approaching or moving away from the transmission belt 314. The gap adjusting wheel 341 and the spiral adjusting member 342 work together to tension the transmission belt 314 between the first driven pulley 311 and the second driven pulley 312, thereby applying rotational torques of different rotational directions to the first driven pulley 311 and the second driven pulley 312, respectively, thereby reducing the tooth side clearance of the transmission mechanism 30.

[0073] The screw adjusting member 342 and the screw hole form a threaded transmission pair. The screw adjusting member 342 is rotated to generate linear motion relative to the screw hole, so that the screw adjusting member 342 generates linear displacement relative to the gap adjustment bracket 343. The screw adjusting member 342 drives the gap adjustment wheel shaft 344 to move closer to or away from the transmission belt 314. When the screw adjusting member 342 and the screw hole form a threaded transmission pair that rotates one circle, the linear motion displacement generated is determined by the thread parameters, so the gap adjustment amount (i.e., the displacement of the gap adjustment wheel shaft 344 in a direction perpendicular to the transmission belt 314) can be controlled more accurately.

[0074] It is understandable that the gap adjustment wheel 341 can also be configured such that its circumferential surface simultaneously abuts against the outer surface of the transmission belt 314 between the driving pulley 313 and the first driven pulley 311 and between the driving pulley 313 and the second driven pulley 312. The gap adjustment wheel 341 can be configured along its axial direction to have a larger diameter at both ends and a smaller diameter in the middle (its longitudinal section is an I-shaped shape), and the transmission belt 314 is just stuck in the concave portion with a smaller diameter in the middle.

[0075] It should be noted that in the embodiment of the present application, in addition to the close contact, the abutment also requires that there is an action or reaction force between the two. The screw adjustment member 342 can be a screw, a bolt, a stud or a ball screw, etc. The thread on the screw adjustment member 342 can be a trapezoidal thread, a rectangular thread, a serrated thread or a ball screw thread, etc.

[0076] Figure 6 as well as Figures 7(a) to 7(e) A more specific implementation of some embodiments of the present application is given. A screw hole is provided on one side of the gap adjustment bracket 343. It is understandable that the screw hole can be directly opened on the surface of one side of the gap adjustment bracket 343, or can be opened on another component (the component is installed on the surface of one side of the gap adjustment bracket 343). For example, Figure 6In it, the backlash elimination mechanism 34 further includes a stopper 345, on which a threaded hole is opened, and the stopper 345 is installed on the surface of one side of the clearance adjustment bracket 343. After installation, the surface of the stopper 345 is substantially flush with other areas of the surface of this side of the clearance adjustment bracket 343. The screw adjustment member 342 (such as a bolt) passes through the threaded hole of the stopper 345 and faces the outer peripheral surface of the clearance adjustment wheel shaft 344. The clearance adjustment wheel 341 rotates around the clearance adjustment wheel shaft 344 through the clearance adjustment wheel bearing 347.

[0077] By reducing or eliminating the backlash, the backlash elimination of the gear transmission mechanism can reduce the return error during the transmission process, thereby improving the accuracy and smoothness of the gear transmission. It is generally considered that the clearance in the gear transmission mechanism is difficult to completely eliminate, so efforts should be made to reduce it.

[0078] Figure 5 The backlash elimination principle of the technical solutions of some embodiments of the present application is shown. It should be noted that although the tensioning mechanism 35 is also arranged on the processing head, a section of the transmission belt 314 provided with the tensioning mechanism 35 is also concave as a whole, but under the action of the tensioning mechanism 35, the entire transmission belt 314 is tensioned, and the force at any position in the length direction of the entire transmission belt 314 is the same. Therefore, a section of the transmission belt 314 provided with the tensioning mechanism 35 can be simplified to a straight outer contour. The backlash elimination mechanism of the processing head provided in the embodiments of the present application drives the clearance adjustment wheel 341 to abut against the outer surface of the transmission belt 314, so that the transmission belt 314 is tensioned inward. After a certain section of the transmission belt 314 is tightened inward, different acting forces will be applied to the circumferential surfaces of the pulleys at both ends thereof. The applied acting force is located on the circumferential surface of the pulley and away from the rotation center of the pulley, so a rotational torque for driving the pulley to rotate is formed. The acting forces applied to the two pulleys are decomposed, and the component forces in the direction of the line connecting the centers of the two pulleys point to each other. Therefore, the rotational directions of the rotational torques applied to the two pulleys are opposite to each other. If one is clockwise rotation, the other is counterclockwise rotation. In Figure 5 In it, the driving pulley 313, the first driven pulley 311, and the second driven pulley 312 all rotate in the same direction under the action of the rotational torque M output by the motor 21. At the same time, the transmission belt 314 tensioned inward applies a rotational torque M 1 to the first driven pulley 311 and a rotational torque M 2 to the second driven pulley 312. It is not difficult to understand that the rotational torque M 1 and the rotational torque M 2 are both smaller than the rotational torque M, and the magnitude relationship between the rotational torque M 1 and the rotational torque M 2 can be arbitrary.

[0079] The rotational torques M 1 and M with opposite rotational directions applied to the two pulleys2 They are respectively transmitted to the first driving gear 331 and the second driving gear 332 through two transmission chains. The first driving gear 331 and the second driving gear 332 are respectively meshed on both sides of the driven gear 333. Under the action of the rotational torques M 1 and M 2 , the teeth of the first driving gear 331 and the second driving gear 332 that are in the meshed state respectively abut against the opposite meshing surfaces of the corresponding two teeth of the driven gear 333. In this case, during the process that the motor 21 changes from forward driving to reverse driving, the gear transmission hardly has or significantly reduces the backlash caused by the tooth side clearance, so as to achieve the purpose of eliminating or reducing the tooth side clearance.

[0080] Currently, the existing backlash elimination mechanisms usually strive to reduce the tooth side clearance, and cannot accurately control the adjustment amount. This will result in that although the tooth side clearance is reduced, the desired result still cannot be achieved. However, in the embodiment of the present application, the component of the backlash elimination mechanism 34 for controlling the magnitude of the displacement of the adjustment wheel 341 moving towards or away from the transmission belt 314 (i.e., the magnitude of the adjustment amount) is the screw adjustment member 342. Compared with driving the adjustment wheel 341 to move towards the transmission belt 314 by using an elastic element or other components, the technical solution of the embodiment of the present application can more accurately control the adjustment amount, and can maintain long-term stability after adjustment, and there will be no positioning drift under alternating loads.

[0081] Furthermore, in some embodiments of the present application, the backlash elimination mechanism 34 further includes a push block 346. The push block 346 is fixedly connected to the adjustment wheel shaft 344, and a through groove 3461 is formed in the push block 346. The through groove 3461 forms a notch on the surface perpendicular to the extending direction of the screw adjustment member 342. The screw adjustment member 342 is provided with an annular groove on its circumferential surface. The screw adjustment member 342 cooperates with the two side walls of the through groove 3461 through the annular groove, so that the screw adjustment member 342 cannot pass through the through groove 3461 along the through direction of the through groove 3461. The outer diameter d of the other part of the screw adjustment member 342 except the annular groove in the axial direction is greater than the opening width l of the through groove 3461. Further, the outer diameter d of at least one end of the screw adjustment member 342 facing the adjustment wheel shaft 344 is greater than the opening width l of the through groove 3461, so that the screw adjustment member 342 cannot pass through the through groove 3461 along the through direction of the through groove 3461.

[0082] The pushing block 346 is fixedly connected to the clearance adjusting wheel shaft 344. Therefore, the linear motion of the pushing block 346 can drive the clearance adjusting wheel shaft 344 to move in the same direction by the same displacement. The outer diameter d of the screw adjusting member 342 is greater than the opening width l of the through groove 3461. Thus, when the screw adjusting member 342 moves in the direction away from the transmission belt 314, it can drive the pushing block 346 to move in the same direction, and further make the clearance adjusting wheel shaft 344 move away from the transmission belt 314 (i.e., the clearance adjusting wheel 341 also moves away from the transmission belt 314). With such a setting, the screw rotation of the screw adjusting member 342 can not only drive the clearance adjusting wheel 341 to approach the transmission belt 314, but also drive the clearance adjusting wheel 341 to move away from the transmission belt 314.

[0083] Optionally, in some alternative embodiments of the present application, there are two sets of clearance eliminating mechanisms 34. Each set of clearance eliminating mechanisms 34 includes a clearance adjusting wheel 341 and a screw adjusting member 342. One set of clearance adjusting wheels 341 is located outside the transmission belt 314 between the driving pulley 313 and the first driven pulley 311, and the other set of clearance adjusting wheels 341 is located outside the transmission belt 314 between the driving pulley 313 and the second driven pulley 312. Similarly, due to the existence of the two sets of clearance eliminating mechanisms 34, the first driven pulley 311 and the second driven pulley 312 are respectively applied with rotational torques M 1 and M 2 .

[0084] Optionally, in some embodiments of the present application, please refer to Figures 7(a) to 7(e) , a first guiding structure 3431 is provided on the clearance adjusting bracket 343, and a second guiding structure 3441 adapted to the first guiding structure 3431 is provided on the clearance adjusting wheel shaft 344. One of the first guiding structure 3431 and the second guiding structure 3441 is a chute structure and the other is a convex block structure. Among them, the opening width of the chute structure is greater than the bottom width of the chute structure, and / or the protruding end width of the convex block structure is less than the root width of the convex block structure. That is to say, on the side where the opening of the chute structure is located, the cross-sectional shape of the opening narrows along the direction in which the chute structure is inserted; and / or, on the protruding end of the convex block structure, the longitudinal section shape of the convex block structure narrows along the direction of inserting into the chute structure.

[0085] In Fig. 7(e), on both sides of the outer peripheral surface of the gap adjusting wheel shaft 344, there are second guiding structures 3441, and the second guiding structures 3441 are chute structures; on the gap adjusting bracket 343, there are first guiding structures 3431 adapted to the second guiding structures 3441, and the first guiding structures 3431 are bump structures. It can be understood that the first guiding structures 3431 can also be chute structures, while the second guiding structures 3441 are bump structures. In the middle of the gap adjusting wheel shaft 344 in its left-right direction, there can also be a cavity, and on the side wall of the cavity, there is a chute structure or a bump structure, while the gap adjusting bracket 343 is provided with a slideway capable of passing through the cavity of the gap adjusting wheel shaft 344, and the cavity of the gap adjusting wheel shaft 344 slides along the slideway of the gap adjusting bracket 343. On one of the side wall of the cavity and the slideway, there can be a bump structure or a chute structure, while on the other, there is a chute structure or a bump structure.

[0086] Under the mutual cooperation of the first guiding structure 3431 and the second guiding structure 3441, the gap adjusting wheel shaft 344 is restricted to have only one degree of freedom, that is, the movement along the extending direction of the first guiding structure 3431. Therefore, the gap adjusting wheel shaft 344 will not fall off nor deviate its moving direction to other angles (as shown in Fig. 7(a) and Fig. 7(b)).

[0087] As shown in Fig. 7(d) and Fig. 7(e), the bump structure as the first guiding structure 3431 has a guiding portion in at least a partial area of the extending end, and the shape of the longitudinal section of the guiding portion gradually narrows along the direction of inserting into the chute structure. That is to say, the thickness of the bump structure at the end of the extending end is the smallest. During the process of inserting the bump structure into the chute structure, the guiding portion is the first to be inserted into the cavity defined by the chute structure. The guiding portion with a smaller thickness is more likely to be inserted into the cavity defined by the chute structure with the same thickness or a larger thickness. It can be understood that the chute structure as the second guiding structure 3441 can also be provided with a guiding portion in at least a partial area on the side where its opening is located, and the shape of the cross section of the opening of the guiding portion gradually narrows along the direction of inserting the chute structure, that is, the opening of the chute structure on the surface where the opening is located is the largest. As it goes deeper into the cavity, the opening gradually closes until it no longer becomes smaller. The guiding portion with a larger opening is more likely to guide the bump structure with the same thickness or a smaller thickness to be inserted.

[0088] Optionally, in some embodiments of the present application, in Fig. 7(d), scale lines are provided on the gap adjusting bracket 343 along the extending direction of the first guiding structure 3431. The extending direction of the first guiding structure 3431 is also the linear movement direction of the screw adjusting member 342. The provision of the scale lines helps the operator to more accurately control the magnitude of the linear displacement of the screw adjusting member 342 (i.e., the magnitude of the gap adjustment).

[0089] Further, in some embodiments of the present application, as shown in FIGS. 3(a) and 3(b), the distance from the circumferential surface of the clearance adjusting wheel 341 to the center of each pulley of the first driven pulley 311 and the second driven pulley 312 at the abutting position on the outer surface of the transmission belt 314 is equal, that is, the clearance adjusting wheel 341 abuts at a certain position on the midline of the line connecting the centers of the first driven pulley 311 and the second driven pulley 312. Even if the abutting position of the clearance adjusting wheel 341 is not on this midline, the side clearance can also be reduced. However, designing the abutting position on this midline is conducive to simplifying the calculation of the clearance adjustment amount.

[0090] Optionally, in some embodiments of the present application, as shown in FIGS. 1(a) and 1(b), the axis of rotation of the rotating base 36 forms a 45° angle with the axis of the main shaft. The headstock 12 is fixedly connected to the rotating base 36, and the outer circumferences of the rotating base 36 and the machining head base 40 are hermetically connected through a fixed sealing ring and a rotating sealing ring.

[0091] When the headstock 12 rotates around the axis of rotation of the rotating base 36, the axis of the main shaft in the headstock 12 can be switched between the horizontal state and the vertical state, so that the machining head can be applied to a vertical and horizontal machining machine tool. It can be understood that, according to needs, the angle between the two can also be other angles. The outer circumferences of the machining head base 40 and the rotating base 36 are hermetically connected through the cooperation of a stationary ring (i.e., the fixed sealing ring) and a moving ring (i.e., the rotating sealing ring), effectively preventing external liquid or impurities from entering the interior of the machining head.

[0092] The second aspect of the embodiments of the present application provides a machining machine tool. In some embodiments of the present application, the machining machine tool includes the machining head described in one of the foregoing embodiments. The machining machine tool can be a vertical and horizontal machining machine tool. In the vertical working mode, the axis of the main shaft of the machining head is in the vertical state; in the horizontal working mode, the axis of the main shaft of the machining head is in the horizontal state.

[0093] Configuring the machining head described in one of the foregoing embodiments of the present application can achieve the expected values of both the tension of the transmission belt and the side clearance of the gear with fewer adjustment times.

[0094] The foregoing are only preferred embodiments of the present application, and of course, the scope of rights of the present application cannot be limited thereby. Therefore, equivalent changes made according to the claims of the present application still fall within the scope covered by the present application.

Claims

1. A processing head, characterized in that: include: A spindle assembly, comprising a spindle box and a spindle installed in the spindle box; A drive mechanism, including a motor; The transmission mechanism includes a belt transmission mechanism, a gear transmission mechanism, a backlash elimination mechanism, a tensioning mechanism and a rotating base, wherein the belt transmission mechanism is drivingly connected to the output end of the motor, the gear transmission mechanism is drivingly connected to the belt transmission mechanism, the input end of the rotating base is drivingly connected to the gear transmission mechanism, and the rotating base is used to drive the spindle box to rotate; Wherein, the belt transmission mechanism includes a driving pulley, a first driven pulley and a second driven pulley connected by a transmission belt, and the driving pulley, the first driven pulley and the second driven pulley are arranged in a triangle; the gap eliminating mechanism includes a gap adjusting wheel and a gap adjusting bracket for installing the gap adjusting wheel, and the gap adjusting wheel abuts against the outer side of the transmission belt between the first driven pulley and the second driven pulley; the tensioning mechanism includes a tensioning wheel and a tensioning bracket for installing the tensioning wheel, and the tensioning wheel abuts against the outer side of the transmission belt between the driving pulley and the first driven pulley or between the driving pulley and the second driven pulley.

2. The processing head according to claim 1, characterized in that The processing head also includes: A processing head base, the driving mechanism is arranged on the processing head base, and the gap adjustment bracket is connected to the processing head base; The tensioning mechanism further includes a tensioning wheel shaft, a spring and a sliding member, the tensioning wheel is rotatably connected to the sliding member via the tensioning wheel shaft, the sliding member is used to drive the tensioning wheel shaft to approach or move away from the transmission belt, one end of the tensioning bracket is fixedly connected to the processing head base, the other end of the tensioning bracket is connected to the sliding member via the spring, the tensioning bracket partially overlaps with the sliding member, the overlapping area of ​​the tensioning bracket and the sliding member is matched with a locking element via a plurality of through holes, the sliding member is slidably connected relative to the tensioning bracket, and the locking element is used to lock the sliding member and the tensioning bracket at a specific position.

3. The processing head according to claim 2, characterized in that: One end of the tensioning bracket is fixedly connected to the processing head base through the gap adjustment bracket, the other end of the tensioning bracket is provided with a first spring mounting seat, the sliding member is provided with a second spring mounting seat, a plurality of the springs are arranged side by side and the two ends of the plurality of the springs are respectively against the first spring mounting seat and the second spring mounting seat; One of the tensioning bracket and the sliding member is provided with a plurality of through holes at equal intervals along the sliding direction of the sliding member in the overlapping area, and the other is provided with a waist-shaped hole in the overlapping area, and the waist-shaped hole can be aligned with at least one of the plurality of through holes to allow the locking element to pass through for locking.

4. The processing head according to claim 3, characterized in that The cam is provided with a mounting hole at one end of the sliding member near the tension wheel, and the sliding member is also fixedly connected to the tension wheel shaft mounting seat, and the tension wheel shaft mounting seat is provided with a clamping hole at a position opposite to the mounting hole, and the tension wheel shaft passes through the mounting hole and the clamping hole in sequence, and the tension wheel is installed between the mounting hole and the clamping hole, and the clamping hole has an opening in the circumferential direction, and one side of the tension wheel shaft mounting seat is separated by the opening into a first locking portion and a second locking portion that are spaced apart and relatively arranged, and the first locking portion and the second locking portion are respectively connected with the inner wall of the opening of the clamping hole, and the first locking portion and the second locking portion are respectively provided with locking holes aligned with each other, and a locking bolt is passed through the locking hole, and the locking bolt is used to lock the tension wheel shaft.

5. The processing head according to claim 4, characterized in that The tensioning mechanism also includes a tensioning wheel bearing and a guide rod, and the tensioning wheel is sleeved on the tensioning wheel shaft through the tensioning wheel bearing; a guide hole is provided on the first spring mounting seat, one end of the guide rod is fixedly connected to the second spring mounting seat, and the other end of the guide is slidably inserted into the guide hole, and the spring is sleeved on the guide rod.

6. The processing head according to any one of claims 1 to 5, characterized in that The gear transmission mechanism includes a driven gear and a first driving gear and a second driving gear respectively meshing with the driven gear; the first driven pulley is connected to the first driving gear through a first reducer, and the second driven pulley is connected to the second driving gear through a second reducer; the transmission belt is a synchronous belt.

7. The processing head according to claim 6, characterized in that The gap elimination mechanism further comprises a spiral adjustment member, a gap adjustment wheel shaft and a push block, wherein the gap adjustment wheel is rotatably arranged on the gap adjustment bracket through the gap adjustment wheel shaft, the gap adjustment wheel shaft is located between the spiral adjustment member and the transmission belt, and the gap adjustment bracket is provided with a screw hole adapted to the spiral adjustment member, and the spiral adjustment member passes through the screw hole to drive the gap adjustment wheel shaft to approach or move away from the transmission belt; The pushing block is fixedly connected to the gap adjustment wheel shaft, and a through groove is provided on the pushing block. The through groove forms a notch on the surface perpendicular to the extension direction of the spiral adjustment member, and the spiral adjustment member is provided with an annular groove on its own circumferential surface, and the spiral adjustment member cooperates with the two side walls of the through groove through the annular groove.

8. The processing head according to claim 7, characterized in that A first guide structure is provided on the gap adjustment bracket, and a second guide structure matched with the first guide structure is provided on the gap adjustment wheel shaft, one of the first guide structure and the second guide structure is a slide groove structure and the other is a protrusion structure; the opening width of the slide groove structure is greater than the groove bottom width of the slide groove structure, and / or the protruding end width of the protrusion structure is less than the root width of the protrusion structure.

9. The machining head according to any one of claims 2 to 5, characterized in that The rotation axis of the rotating base forms an angle of 45° with the axis of the main shaft, the main shaft box is fixedly connected to the rotating base, and the outer peripheries of the rotating base and the processing head base are sealed by a fixed sealing ring and a rotating sealing ring.

10. A processing machine tool, characterized in that: Comprising a processing head according to any one of claims 1 to 9.

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