Multi-stage gear meshing driving structure for chain tool magazine

Abstract

The present application relates to chain tool magazine technical field, especially to a kind of multistage gear meshing drive structure for chain tool magazine, including servo drive group, driving wheel group and transmission wheel group;Servo drive group has pinion on output shaft;Driving wheel group includes driving shaft, gear wheel and two wheel plates;Transmission wheel group includes transmission shaft and transmission gear;Transmission gear is engaged between pinion and gear wheel, three coplanar settings and circle center line is collinear;The outer edge of wheel plate is uniformly distributed with multiple shift forks, and the diameter of the inscribed circle in the root of shift fork is greater than the diameter of gear wheel, the outer cylindrical surface of shift fork is provided with driving groove, and the guide wheel of tool sleeve chain is embedded in driving groove.The present application adopts multistage gear meshing transmission path, simultaneously adopts wheel plate shift fork non-meshing structure, divides layer layout gear meshing and chain drive, makes wheel body circumferential force completely symmetrical, eliminates unilateral bending complex stress, shortens power link, improves transmission efficiency and response speed, further improves transmission stability.

Description

Technical Field

[0001] This invention relates to the field of chain tool magazine technology, and more particularly to a multi-stage gear meshing drive structure for chain tool magazines. Background Technology

[0002] The existing chain drive mechanism of the chain tool magazine consists of a driving sprocket, a driven sprocket and a closed-loop chain. The driving sprocket is coaxially connected to the motor drive end through the drive shaft. The motor and the driving sprocket are located at opposite ends of the drive shaft. The motor drives the driving sprocket to rotate, which in turn drives the closed-loop tool holder chain to achieve tool changing.

[0003] However, the aforementioned drive structure uses a power transmission method with center input and outer edge output, and the closed-loop chain only applies force to the drive sprocket on the meshing side, resulting in a completely asymmetrical circumferential force on the drive sprocket. Since the chain tool magazine needs to be frequently started, stopped, and switched between forward and reverse directions according to tool changing requirements, this asymmetrical force will cause the drive sprocket to bear uneven torsional shear stress and bending combined stress. After long-term operation, it is very easy to cause abnormal fluctuations in the meshing clearance, which will lead to abnormal phenomena such as tooth skipping and tooth wear, seriously affecting the transmission stability. Summary of the Invention

[0004] This invention provides a multi-stage gear meshing drive structure for chain tool magazines, which can effectively solve the problems in the background art.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A multi-stage gear meshing drive structure for a chain tool magazine includes: The servo drive assembly has a small gear on its output shaft; The drive gear assembly includes a drive shaft, a large gear rotatably mounted on the drive shaft, and two wheel plates fixedly mounted on both ends of the large gear. A transmission gear set, including a transmission shaft and a transmission gear rotatably mounted on the transmission shaft; The transmission gear meshes between the pinion and the large gear, and the pinion, the transmission gear, and the large gear are arranged in the same plane; and the line connecting the center of the pinion and the transmission gear and the line connecting the center of the transmission gear and the large gear are collinear, with the collinear direction parallel to the line connecting the center of the driving gear set and the driven gear set. Multiple shift forks are evenly distributed on the outer edges of the two wheel plates. The diameter of the inscribed circle at the root of each shift fork is larger than the diameter of the large gear. A drive groove is formed on the outer circular surface of each shift fork. The guide wheel of the tool sleeve chain is embedded in the drive groove. The tool sleeve chain is driven to rotate synchronously by the circumferential movement of the wheel plates following the large gear.

[0006] Furthermore, the drive engagement area between the blade sleeve chain and the shift fork on the drive wheel assembly is located directly below the large gear; The meshing area between the transmission gear and the large gear is located directly above the large gear; The meshing area between the pinion and the transmission gear is located on the side of the transmission gear away from the large gear.

[0007] Furthermore, the servo drive assembly also includes a servo motor, a reducer, and a mounting base; The output shaft of the servo motor is connected to the input shaft of the reducer, and the reducer is mounted on the tool magazine frame via the mounting base; The output shaft of the reducer extends into the internal cavity of the mounting base, and the extended end is connected to the pinion gear; The mounting base has an clearance window on its side wall corresponding to the pinion.

[0008] Furthermore, the axial width of the large gear is greater than the axial width of the transmission gear; A clearance is provided between the two wheel plates and the axial end face of the transmission gear.

[0009] Furthermore, the radial outer edge region of the transmission gear overlaps with the two wheel plates in the radial direction, forming an annular region; The transmission gear is provided with a plurality of first lubrication holes along the circumferential direction at the position corresponding to the annular region, and the first lubrication holes are provided through the transmission gear along the axial direction. On the axial split surface of the transmission gear, a second lubrication hole is provided radially, corresponding to and communicating with the first lubrication hole. The transmission shaft is provided with a first oil inlet passage and a second oil inlet passage, respectively, corresponding to the meshing position of the transmission gear and the pinion and the meshing position of the transmission gear and the gear.

[0010] Furthermore, spring plungers are provided at both ends of the first lubrication hole along its axial direction; Under normal conditions, the floating steel balls of the two spring plungers protrude from the end face of the transmission gear. The distance between the outer ends of the two opposing floating steel balls in the same first lubrication hole is greater than the distance between the inner end faces of the two wheel plates. The first lubrication hole is in a closed state. When the transmission gear rotates to the position where the first lubrication hole and the shift fork form a radial overlap, the floating steel balls of the spring plungers on both ends of the transmission gear are synchronously squeezed by the relative inner end faces of the two wheel plates, and the first lubrication hole switches to the open state.

[0011] Furthermore, it also includes adjusting components; The adjustment assembly includes a first sliding seat connected to the drive shaft, a second sliding seat connected to the transmission shaft, and a third sliding seat connected to the mounting base; A double-rod drive cylinder is provided between the first sliding seat and the second sliding seat. The cylinder body of the double-rod drive cylinder is fixed on the tool magazine frame. The first piston rod extending from one end of the cylinder body is fixedly connected to the second sliding seat, and the second piston rod extending from the other end of the cylinder body is fixedly connected to the first sliding seat. A double-ended adjusting screw is provided between the second sliding seat and the third sliding seat, and the two ends of the double-ended adjusting screw are respectively threaded to the second sliding seat and the third sliding seat.

[0012] Furthermore, the adjustment assembly is located on the back of the tool magazine rack; The drive shaft, the transmission shaft, and the mounting base are disposed on the front of the tool magazine frame, and a sliding plate is provided between the first sliding base, the second sliding base, the third sliding base and the contact surface between the sliding base and the tool magazine frame; Multiple needle roller rows are provided on the end face of the slide plate facing the tool magazine frame, and the multiple needle rollers on the needle roller rows are arranged sequentially along the collinear direction of the center of the pinion, the transmission gear and the large gear.

[0013] Furthermore, the first piston rod end of the dual-rod drive cylinder is provided with a first piston head, and the second piston rod end is provided with a second piston head; The first piston head is slidably sealed and assembled into the inner cavity of the cylinder of the dual-rod drive cylinder, dividing the inner cavity of the cylinder into a first oil chamber and a second oil chamber; The first piston head has an axial sliding groove on its end face facing the second piston head, and the inner end of the second piston head is slidably sealed and assembled in the axial sliding groove, forming a closed oil cavity with the axial sliding groove. Both the first piston head and the second piston head are provided with a first sealing ring on their outer peripheral surfaces, and the walls of the through holes at both ends of the cylinder for the first piston rod and the second piston rod to extend out are each provided with a second sealing ring.

[0014] Furthermore, the cylinder body of the dual-rod drive cylinder is provided with a first oil port and a second oil port corresponding to the first oil chamber and the second oil chamber, respectively; An adjusting oil passage is provided axially inside the first piston rod, and one end of the adjusting oil passage is connected to the closed oil chamber; The cylinder body of the dual-rod drive cylinder is also provided with a compensation oil circuit. The two ends of the compensation oil circuit are respectively connected to the first oil chamber and the second oil chamber, and a control valve is provided on the compensation oil circuit to control the opening and closing of the compensation oil circuit.

[0015] The technical solution of this invention can achieve the following technical effects: This invention optimizes the power transmission path through a three-stage gear meshing transmission. Simultaneously, both the power input meshing point and the chain output drive point are located on the outer circumference of the large gear, completely eliminating the long radial torque transmission path from the center to the outer edge. This shortens the power transmission link, improves power transmission efficiency and response speed, and adapts to the working conditions requiring frequent start-stop and forward / reverse switching of the tool magazine. Furthermore, it employs a non-meshing structure with wheel plate shift forks to drive the tool sleeve chain, layering the gear meshing transmission and chain drive load. The input meshing point and output drive point are located at opposite ends of the same diameter of the driving gear, allowing the tangential driving force input by the gear and the reverse resistance of the tool sleeve chain to form a pure couple driving the wheel rotation. This achieves complete symmetrical circumferential force on the wheel, eliminating bending composite stress caused by unilateral force, significantly offsetting alternating composite stress, avoiding wheel deformation and tooth accuracy failure, and improving transmission stability, positional accuracy, and operational reliability. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 A first-view isometric structural diagram of a multi-stage gear meshing drive structure; Figure 2 A first-view cross-sectional schematic diagram of a multi-stage gear meshing drive structure; Figure 3 A second-view cross-sectional schematic diagram of a multi-stage gear meshing drive structure; Figure 4 This is a schematic diagram of the transmission gear structure; Figure 5 for Figure 3 A magnified view of part A; Figure 6 for Figure 5 A magnified view of section B; Figure 7 A second-view isometric structural diagram of a multi-stage gear meshing drive structure; Figure 8 This is a schematic diagram showing the installation of the slide plate and the needle roller array; Figure 9 This is a schematic diagram of a dual-rod driven hydraulic cylinder.

[0018] Reference numerals: 1. Servo drive assembly; 11. Pinion; 12. Servo motor; 13. Reducer; 14. Mounting base; 14a. Clearance window; 2. Drive wheel assembly; 21. Drive shaft; 22. Large gear; 23. Wheel plate; 231. Shift fork; 231a. Drive groove; 3. Transmission wheel assembly; 31. Transmission shaft; 32. Transmission gear; 3a. First lubrication hole; 3b. Second lubrication hole; 3c. First oil inlet passage; 3d. Second oil inlet. 4. Passage; 51. Spring plunger; 52. First sliding seat; 53. Second sliding seat; 54. Third sliding seat; 55. Double-rod drive cylinder; 56. First piston rod; 57. Second piston rod; 58. First oil chamber; 59. Closed oil chamber; 50. First oil port; 51. Second oil port; 52. Second oil port; 53. Compensation oil passage; 54. Adjustment oil passage; 55. Double-headed adjusting screw; 56. Slide plate; 57. Needle roller set. Detailed Implementation

[0019] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0020] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0021] like Figures 1-9 As shown, this application provides a multi-stage gear meshing drive structure for a chain tool magazine, including: a servo transmission group 1, a drive wheel group 2, and a transmission wheel group 3; The output shaft of the servo drive unit 1 has a pinion 11; The drive wheel assembly 2 includes a drive shaft 21, a large gear 22 rotatably mounted on the drive shaft 21, and two wheel plates 23 fixedly mounted on both ends of the large gear 22. The transmission wheel assembly 3 includes a transmission shaft 31 and a transmission gear 32 rotatably mounted on the transmission shaft 31; The transmission gear 32 meshes between the pinion 11 and the large gear 22. The pinion 11, the transmission gear 32, and the large gear 22 are arranged in the same plane. The line connecting the center of the pinion 11 and the transmission gear 32, and the line connecting the center of the transmission gear 32 and the large gear 22 are collinear, and the collinear direction is parallel to the line connecting the center of the driving gear set 2 and the driven gear set. Multiple shift forks 231 are evenly distributed on the outer edges of the two wheel plates 23. The diameter of the inscribed circle at the root of the shift fork 231 is larger than the diameter of the large gear 22. A drive groove 231a is provided on the outer circular surface of the shift fork 231. The guide wheel of the tool sleeve chain is embedded in the drive groove 231a. The tool sleeve chain is driven to rotate synchronously by the wheel plate 23 following the circumferential movement of the large gear 22.

[0022] In this embodiment, the mating structure of the wheel plate 23 and the shift fork 231 can be implemented in various ways. For example, the shift fork 231 and the wheel plate 23 can be integrally stamped, or the shift fork 231 and the wheel plate 23 can be detachably fixedly connected by high-strength bolts. As long as the function of driving the blade sleeve chain to rotate with the circumferential movement of the wheel plate 23 can be achieved, it is acceptable. In practical applications, the integrally stamped structure is preferred. Its structure has stronger rigidity, the force is uniform during circumferential movement, and it is not easy to deform. It can effectively avoid the problems of jamming and skipping teeth when the shift fork 231 and the guide wheel are mated. The number of shift forks 231 can be matched according to the pitch of the blade sleeve chain. The distance between two adjacent shift forks 231 is adapted to the installation distance of the guide wheel of the blade sleeve chain to ensure that the drive groove 231a can continuously mate with the guide wheel to achieve the smooth operation of the blade sleeve chain. It should be noted that in this invention, the transmission gear 32 is rotatably mounted on the transmission shaft 31 via bearings, while the large gear 22 is sandwiched in the middle by two wheel plates 23. The inner hole edge of one of the wheel plates 23 extends axially, and the large gear 22 and the other wheel plate 23 are sequentially sleeved on the extended shaft section. The extended shaft section is rotatably mounted on the drive shaft 21 via two bearings, and a spacer is provided between the two bearings. The two sides of the spacer abut against the inner ring of the bearing.

[0023] In the non-working static state, the servo transmission group 1 is in a power-off locked state, with the pinion 11, transmission gear 32, and large gear 22 all in a stationary locked position. The guide wheel of the tool holder chain is embedded in the drive groove 231a of the corresponding shift fork 231, and the whole machine is in a standby state. In the working state, the servo transmission group 1 outputs rotational power, driving the pinion 11 to rotate synchronously. Through meshing transmission, it drives the transmission gear 32 to rotate around the transmission shaft 31. Then, through the meshing transmission of the transmission gear 32 and the large gear 22, it drives the large gear 22 to rotate around the drive shaft 21. The wheel plates 23 fixed at both ends of the large gear 22 move in a circular motion synchronously with the large gear 22. The shift fork 231 on the outer edge of the wheel plate 23 engages with the guide wheel of the tool holder chain in sequence with the circular motion. The guide wheel is embedded in the drive groove 231a. Through the circular motion of the shift fork 231, it drives the guide wheel to move along a preset path, thereby driving the tool holder chain to complete the cycle and realize the switching of the tool position.

[0024] This invention optimizes the power transmission path through a three-stage gear meshing transmission. Simultaneously, both the power input meshing point and the chain output drive point are located on the outer circumference of the large gear 22, eliminating the long radial torque transmission path from the center to the outer edge, shortening the power transmission link, and improving power transmission efficiency and response speed. This adapts to the working conditions requiring frequent start-stop and forward / reverse switching of the tool magazine. Furthermore, a non-meshing structure of the shift fork 231 drives the tool holder chain, layering the gear meshing transmission and chain drive load. The input meshing point and output drive point are located at opposite ends of the same diameter of the large gear 22, allowing the tangential driving force input from the large gear 22 and the reverse resistance of the tool holder chain to form a pure couple driving the wheel rotation. This achieves complete symmetrical circumferential force on the wheel, eliminating bending composite stress caused by unilateral force, significantly offsetting alternating composite stress, avoiding wheel deformation and tooth accuracy failure, and significantly improving transmission stability, positional accuracy, and operational reliability.

[0025] As a further optimization of the above embodiment, the drive engagement area of ​​the blade sleeve chain and the shift fork 231 on the drive wheel assembly 2 is located directly below the large gear 22; the meshing area of ​​the transmission gear 32 and the large gear 22 is located directly above the large gear 22; and the meshing area of ​​the pinion 11 and the transmission gear 32 is located on the side of the transmission gear 32 away from the large gear 22.

[0026] By separating the chain-driven load area and the gear meshing transmission area on the upper and lower sides of the large gear 22, the radial force of the large gear 22 is symmetrically distributed along the axis, effectively offsetting the radial bending moment and bending combined stress, significantly reducing the deformation of the drive shaft 21 and the large gear 22, avoiding the decrease in tooth indexing accuracy and meshing clearance fluctuation, and reducing tooth skipping and tooth biting failures from the root.

[0027] As a further optimization of the above embodiment, the servo drive assembly 1 also includes a servo motor 12, a reducer 13 and a mounting base 14; the output shaft of the servo motor 12 is connected to the input shaft of the reducer 13, and the reducer 13 is mounted on the tool magazine frame via the mounting base 14; The output shaft of the reducer 13 extends into the internal cavity of the mounting base 14, and the extended end is connected to the pinion 11; the mounting base 14 has a clearance window 14a on the side wall corresponding to the pinion 11.

[0028] The mounting base 14 enables precise positioning and installation of the reducer 13 and the pinion 11, ensuring the gear meshing transmission accuracy. At the same time, the internal cavity forms a protective barrier, isolating the gear meshing pair from the contamination of cutting fluid and dust, and preventing the decrease in accuracy caused by accelerated tooth surface wear. The clearance window 14a provides sufficient movement space for gear meshing transmission, avoiding structural interference.

[0029] In this preferred embodiment, the structure of the mounting base 14 can be either a cast integral structure or a welded steel plate split structure, as long as it can achieve the fixed installation of the reducer 13 and the protection function of the internal cavity. In practical applications, the cast integral structure is preferred because it has strong structural rigidity and high dimensional and positional tolerance accuracy, which can better ensure the coaxiality of the reducer 13 and the pinion 11. The opening size of the clearance window 14a is larger than the meshing area size of the pinion 11 and the transmission gear 32, ensuring no structural interference during meshing transmission.

[0030] As a further optimization of the above embodiment, the axial width of the large gear 22 is greater than the axial width of the transmission gear 32; a clearance is reserved between the two wheel plates 23 and the axial end faces of the transmission gear 32.

[0031] By widening the axial width of the large gear 22, while fixing the wheel plates 23 at both ends, an axial clearance is formed between the wheel plates 23 and the transmission gear 32, avoiding axial contact friction, reducing operating resistance, reducing wear of parts, ensuring long-term stability of gear meshing clearance, and avoiding tooth skipping failure.

[0032] Based on the above embodiments, more preferably, the radial outer edge region of the transmission gear 32 and the two wheel plates 23 have a projection overlap in the radial direction, forming an annular region; The transmission gear 32 is provided with a plurality of first lubrication holes 3a along the circumferential direction at the position corresponding to the annular region. The first lubrication holes 3a are provided through the transmission gear 32 along the axial direction. On the axial split surface of the transmission gear 32, a second lubrication hole 3b is provided in the radial direction, which is connected to the first lubrication hole 3a. On the transmission shaft 31, a first oil inlet passage 3c and a second oil inlet passage 3d are provided respectively, corresponding to the meshing position of the transmission gear 32 and the pinion 11 and the meshing position of the transmission gear 32 and the gear 22.

[0033] Specifically, the first oil inlet passage 3c corresponds to the meshing position of the transmission gear 32 and the large gear 22, and the second oil inlet passage 3d corresponds to the meshing position of the transmission gear 32 and the small gear 11. During the transmission of the tool sleeve chain, as the transmission gear 32 rotates, there will always be two second lubrication holes 3b connected to the first oil inlet passage 3c and the second oil inlet passage 3d. At this time, lubricating oil enters the two second lubrication holes 3b. A portion of the lubricating oil in the second lubrication holes 3b will flow radially to the tooth surface to lubricate the gear meshing surface; another portion will flow axially into the first lubrication hole 3a to lubricate the contact surface between the wheel plate 23 and the transmission gear 32.

[0034] By cooperating with the first lubrication hole 3a, the second lubrication hole 3b and the two oil inlet passages, the lubricating oil is accurately delivered to the meshing tooth surface of the transmission gear 32 and the overlapping area of ​​the wheel plate 23, ensuring sufficient lubrication in the meshing area, while reducing tooth surface wear and meshing noise, and extending the service life of the gear.

[0035] In this preferred embodiment, the number of first lubrication holes 3a can be 6, 8, or 12, evenly distributed along the circumference of the transmission gear 32, as long as uniform delivery of lubricating grease is achieved. In practical applications, a scheme with 8 first lubrication holes 3a evenly distributed is preferred, which can ensure uniform oil supply while avoiding the impact of too many holes on the structural strength of the transmission gear 32. Preferably, the diameter of the second lubrication hole 3b is smaller than that of the first lubrication hole 3a, which can create a throttling effect on the lubricating grease, ensuring stable delivery of lubricating grease to the meshing tooth surface. The oil outlets of the first oil inlet passage 3c and the second oil inlet passage 3d are respectively aligned with the meshing tooth surfaces of the transmission gear 32 and the pinion 11, and the transmission gear 32 and the gear 22, to achieve precise oil supply.

[0036] As a further optimization of the above embodiment, spring plungers 4 are provided at both ends of the first lubrication hole 3a along its axial direction; Under normal conditions, the floating steel balls of the two spring plungers 4 protrude from the end face of the transmission gear 32. The distance between the outer ends of the two opposing floating steel balls in the same first lubrication hole 3a is greater than the distance between the opposing inner end faces of the two wheel plates 23, and the first lubrication hole 3a is in the closed state. When the transmission gear 32 rotates to the position where the first lubrication hole 3a and the shift fork 231 form a radial overlap, the floating steel balls of the spring plungers 4 on both ends of the transmission gear 32 are synchronously squeezed by the relative inner end faces of the two wheel plates 23, and the first lubrication hole 3a switches to the open state.

[0037] By cooperating with the spring plunger 4 and the wheel plate 23, the opening and closing control of the first lubrication hole 3a is realized. The oil supply is only opened when the first lubrication hole 3a rotates to the corresponding position in the meshing area, which reduces grease waste and avoids grease adhering to impurities in the non-meshing area, further reducing the risk of tooth surface wear.

[0038] In this preferred embodiment, for the selection of the spring plunger 4, a stainless steel spring plunger 4 or a carbon steel galvanized spring plunger 4 can be selected, as long as it can realize the telescopic opening and closing function of the floating steel ball. In practical applications, a stainless steel spring plunger 4 is preferred because of its excellent rust resistance and suitability for harsh working conditions such as machine tool cutting fluid and dust. The protrusion height of the floating steel ball of the spring plunger 4 can be matched and set according to the gap between the wheel plate 23 and the transmission gear 32 to ensure that the steel ball protrudes to form a reliable seal under normal conditions and can be completely retracted when squeezed by the wheel plate 23, so as to realize the full opening of the lubrication hole.

[0039] As a preferred embodiment of the above, the drive structure further includes an adjustment component; the adjustment component includes a first sliding seat 51 connected to the drive shaft 21, a second sliding seat 52 connected to the transmission shaft 31, and a third sliding seat 53 connected to the mounting base 14; A double-rod drive cylinder 54 is provided between the first sliding seat 51 and the second sliding seat 52. The cylinder body of the double-rod drive cylinder 54 is fixed on the tool magazine frame. The first piston rod 55 extending from one end of the cylinder body is fixedly connected to the second sliding seat 52, and the second piston rod 56 extending from the other end of the cylinder body is fixedly connected to the first sliding seat 51. A double-ended adjusting screw 57 is provided between the second sliding seat 52 and the third sliding seat 53. The two ends of the double-ended adjusting screw 57 are threadedly connected to the second sliding seat 52 and the third sliding seat 53, respectively.

[0040] The active wheel set 2 and the transmission wheel set 3 are synchronously adjusted by the double-rod drive cylinder 54, which synchronously adapts the chain tension and gear meshing backlash. At the same time, the distance between the transmission wheel set 3 and the servo transmission set 1 is finely adjusted by the double-headed adjusting screw 57, which precisely controls the gear meshing backlash, avoids transmission failure caused by backlash fluctuations, and greatly improves adjustment efficiency and long-term stability of transmission accuracy.

[0041] In this preferred embodiment, the installation of the dual-rod drive cylinder 54 can be either horizontal or vertical, as long as it enables synchronous driving of the first sliding seat 51 and the second sliding seat 52. In practical applications, a horizontal installation along the collinear direction of the gear centers is preferred, which ensures that the adjustment force is applied along the centerline of gear meshing, avoiding radial force that could cause gear meshing misalignment. The two ends of the double-headed adjusting screw 57 are provided with external threads in opposite directions. Rotating the double-headed adjusting screw 57 allows the second sliding seat 52 and the third sliding seat 53 to move towards or away from each other, thus completing the precise fine adjustment of the meshing gap.

[0042] As a preferred embodiment of the above, the adjustment assembly is located on the back of the tool magazine frame; the drive shaft 21, the transmission shaft 31 and the mounting base 14 are located on the front of the tool magazine frame, and a sliding plate 58 is provided between the first sliding base 51, the second sliding base 52 and the third sliding base 53 and the contact surface with the tool magazine frame; multiple needle roller rows 59 are provided on the end face of the sliding plate 58 facing the tool magazine frame, and multiple needle rollers on the needle roller rows 59 are arranged sequentially along the collinear direction of the center of the pinion 11, the transmission gear 32 and the gear 22.

[0043] By using a split layout on both the front and back sides, the space utilization of the tool magazine frame is optimized, and motion interference with the tool holder chain and tool changing mechanism is avoided. At the same time, the sliding friction is converted into rolling friction by the needle roller row 59, which greatly reduces the adjustment resistance, improves the smoothness of adjustment and the fine-tuning accuracy, avoids jamming during the adjustment process, and ensures that the meshing clearance adjustment is precise and controllable.

[0044] In this preferred embodiment, the material of the slide plate 58 can be either bearing steel or cemented carbide, as long as wear resistance and supporting rigidity are guaranteed. In practical applications, bearing steel is preferred for the slide plate 58 due to its good machinability and excellent wear resistance. The number of needle roller rows 59 can be set to 2, 3, or 4 groups depending on the size of the sliding seat, ensuring uniform force distribution and no wobbling during sliding seat adjustment. Additionally, the tool magazine frame is equipped with slotted holes to ensure both connection and sliding adjustment requirements.

[0045] As a preferred embodiment of the above, the first piston rod 55 of the dual-rod drive cylinder 54 is provided with a first piston head at its end, and the second piston rod 56 is provided with a second piston head at its end; the first piston head is slidably sealed and assembled in the cylinder cavity of the dual-rod drive cylinder 54, dividing the cylinder cavity into a first oil cavity 54a and a second oil cavity 54b. An axial sliding groove is provided on the end face of the first piston head facing the second piston head. The inner end of the second piston head is slidably sealed and assembled in the axial sliding groove, forming a closed oil cavity 54c with the axial sliding groove. Both the outer circumferential surfaces of the first piston head and the second piston head are provided with a first sealing ring, and the walls of the through holes at both ends of the cylinder body for the first piston rod 55 and the second piston rod 56 to extend are each fitted with a second sealing ring.

[0046] The hydraulic oil in the sealed oil chamber 54c enables the synchronous linkage of the two piston heads, adjusting the distance between the drive shaft 21 and the transmission shaft 31. This changes the center distance between the large gear 22 and the transmission gear 32, ensuring gear meshing stability and uniform circumferential force distribution on the gears. Furthermore, the depth of the axial sliding groove is greater than the maximum extension / retraction stroke of the second piston head, preventing rigid collisions during piston head movement. Simultaneously, the use of multiple sealing rings enhances the sealing performance of the cylinder, preventing hydraulic oil leakage and ensuring stable output of the tension adjustment force.

[0047] As a further optimization of the above embodiment, the cylinder body of the dual-rod drive cylinder 54 is provided with a first oil port 54d and a second oil port 54e corresponding to the first oil chamber 54a and the second oil chamber 54b, respectively; the first piston rod 55 has an adjusting oil passage 54g opened in the axial interior, and one end of the adjusting oil passage 54g is connected to the closed oil chamber 54c. The cylinder body of the dual-rod drive cylinder 54 is also provided with a compensation oil passage 54f. The two ends of the compensation oil passage 54f are respectively connected to the first oil chamber 54a and the second oil chamber 54b. A control valve is provided on the compensation oil passage 54f to control the opening and closing of the compensation oil passage 54f.

[0048] In this preferred solution, for the selection of control valve, either an electromagnetic directional valve or a manual shut-off valve can be used, as long as it can reliably control the on / off state of the compensation oil circuit 54f. In practical applications, the electromagnetic directional valve is preferred, as it can realize electronic automatic on / off control, adapt to the automated operation requirements of the tool magazine, and can change the on / off state of the compensation oil circuit 54f in real time according to the tool magazine process to ensure the positional accuracy of the tool change point of the tool holder chain.

[0049] Oil can be supplied to the closed oil chamber 54c by adjusting the oil circuit 54g, enabling independent fine-tuning of the second piston rod 56 and individual compensation for gear meshing clearance. The servo motor 12, transmission wheel set 3, and drive wheel set 2 are centrally arranged at the lower end of the tool magazine, significantly lowering the overall center of gravity. When the chain experiences slight stretching after long-term operation, the pressure of the first oil chamber 54a and the second oil chamber 54b can be quickly balanced through the cooperation of the compensation oil circuit 54f and the control valve. The slight chain stretching can be compensated in real time by the weight of the drive structure, ensuring the driving stability of the shift fork 231 and the guide wheel, further ensuring the continuous and stable output of tension, thereby maintaining stable gear meshing clearance and improving the transmission smoothness and reliability under frequent start-stop conditions of the tool magazine. When the tool sleeve chain stops driving, the control valve is closed, and the position of the drive structure is fixed, thus ensuring the stability of the chain during tool changing.

[0050] Although this application has been described in conjunction with specific features and embodiments, it is obvious that various modifications and combinations can be made thereto without departing from the spirit and scope of this application. Accordingly, this specification and drawings are merely exemplary illustrations of the application as defined herein, and are to be considered as covering any and all modifications, variations, combinations, or equivalents within the scope of this application. Clearly, those skilled in the art can make various alterations and modifications to this application without departing from its scope. Thus, if such modifications and modifications fall within the scope of this application and its equivalents, this application intends to include such modifications and modifications.

Claims

1. A multi-stage gear meshing drive structure for a chain tool magazine, characterized in that, include: The servo drive assembly has a small gear on its output shaft; The drive gear assembly includes a drive shaft, a large gear rotatably mounted on the drive shaft, and two wheel plates fixedly mounted on both ends of the large gear. A transmission gear set, including a transmission shaft and a transmission gear rotatably mounted on the transmission shaft; The transmission gear meshes between the pinion and the large gear, and the pinion, the transmission gear, and the large gear are arranged in the same plane; the line connecting the center of the pinion and the transmission gear, and the line connecting the center of the transmission gear and the large gear are collinear, and the collinear direction is parallel to the line connecting the center of the driving gear set and the driven gear set; Multiple shift forks are evenly distributed on the outer edges of the two wheel plates. The diameter of the inscribed circle at the root of each shift fork is larger than the diameter of the large gear. A drive groove is formed on the outer circular surface of each shift fork. The guide wheel of the tool sleeve chain is embedded in the drive groove. The tool sleeve chain is driven to rotate synchronously by the circumferential movement of the wheel plates following the large gear.

2. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 1, characterized in that, The drive engagement area between the blade sleeve chain and the shift fork on the drive wheel assembly is located directly below the large gear; The meshing area between the transmission gear and the large gear is located directly above the large gear; The meshing area between the pinion and the transmission gear is located on the side of the transmission gear away from the large gear.

3. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 1, characterized in that, The servo drive assembly also includes a servo motor, a reducer, and a mounting base; The output shaft of the servo motor is connected to the input shaft of the reducer, and the reducer is mounted on the tool magazine frame via the mounting base; The output shaft of the reducer extends into the internal cavity of the mounting base, and the extended end is connected to the pinion gear; The mounting base has an clearance window on its side wall corresponding to the pinion.

4. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 1, characterized in that, The axial width of the large gear is greater than the axial width of the transmission gear; A clearance is provided between the two wheel plates and the axial end face of the transmission gear.

5. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 4, characterized in that, The radial outer edge region of the transmission gear overlaps with the two wheel plates in the radial direction, forming a ring-shaped region; The transmission gear is provided with a plurality of first lubrication holes along the circumferential direction at the position corresponding to the annular region, and the first lubrication holes are provided through the transmission gear along the axial direction. On the axial split surface of the transmission gear, a second lubrication hole is provided radially, corresponding to and communicating with the first lubrication hole. The transmission shaft is provided with a first oil inlet passage and a second oil inlet passage, respectively, corresponding to the meshing position of the transmission gear and the pinion and the meshing position of the transmission gear and the gear.

6. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 5, characterized in that, Spring plungers are provided at both ends of the first lubrication hole along its axial direction; Under normal conditions, the floating steel balls of the two spring plungers protrude from the end face of the transmission gear. The distance between the outer ends of the two opposing floating steel balls in the same first lubrication hole is greater than the distance between the inner end faces of the two wheel plates. The first lubrication hole is in a closed state. When the transmission gear rotates to the position where the first lubrication hole and the shift fork form a radial overlap, the floating steel balls of the spring plungers on both ends of the transmission gear are synchronously squeezed by the relative inner end faces of the two wheel plates, and the first lubrication hole switches to the open state.

7. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 3, characterized in that, It also includes adjustment components; The adjustment assembly includes a first sliding seat connected to the drive shaft, a second sliding seat connected to the transmission shaft, and a third sliding seat connected to the mounting base; A double-rod drive cylinder is provided between the first sliding seat and the second sliding seat. The cylinder body of the double-rod drive cylinder is fixed on the tool magazine frame. The first piston rod extending from one end of the cylinder body is fixedly connected to the second sliding seat, and the second piston rod extending from the other end of the cylinder body is fixedly connected to the first sliding seat. A double-ended adjusting screw is provided between the second sliding seat and the third sliding seat, and the two ends of the double-ended adjusting screw are respectively threaded to the second sliding seat and the third sliding seat.

8. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 7, characterized in that, The adjustment assembly is located on the back of the tool magazine rack; The drive shaft, the transmission shaft, and the mounting base are disposed on the front of the tool magazine frame, and a sliding plate is provided between the first sliding base, the second sliding base, the third sliding base and the contact surface between the sliding base and the tool magazine frame; Multiple needle roller rows are provided on the end face of the slide plate facing the tool magazine frame, and the multiple needle rollers on the needle roller rows are arranged sequentially along the collinear direction of the center of the pinion, the transmission gear and the large gear.

9. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 7, characterized in that, The first piston rod end of the dual-rod drive cylinder is provided with a first piston head, and the second piston rod end is provided with a second piston head; The first piston head is slidably sealed and assembled into the inner cavity of the cylinder of the dual-rod drive cylinder, dividing the inner cavity of the cylinder into a first oil chamber and a second oil chamber; The first piston head has an axial sliding groove on its end face facing the second piston head, and the inner end of the second piston head is slidably sealed and assembled in the axial sliding groove, forming a closed oil cavity with the axial sliding groove. Both the first piston head and the second piston head are provided with a first sealing ring on their outer peripheral surfaces, and the walls of the through holes at both ends of the cylinder for the first piston rod and the second piston rod to extend out are each provided with a second sealing ring.

10. The multi-stage gear meshing drive structure for a chain tool magazine according to claim 9, characterized in that, On the cylinder body of the dual-rod drive cylinder, a first oil port and a second oil port are respectively provided corresponding to the first oil chamber and the second oil chamber; An adjusting oil passage is provided axially inside the first piston rod, and one end of the adjusting oil passage is connected to the closed oil chamber; The cylinder body of the dual-rod drive cylinder is also provided with a compensation oil circuit. The two ends of the compensation oil circuit are respectively connected to the first oil chamber and the second oil chamber, and a control valve is provided on the compensation oil circuit to control the opening and closing of the compensation oil circuit.

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