Metal filter joint end finishing device

Abstract

The application discloses a metal filter joint end processing device and relates to the technical field of automatic processing production lines, in particular to a metal filter joint end processing device, which comprises the following: a bottom disc supporting a fixed reference processing equipment main frame, a double-track cam transmission mechanism with a protrusion and a lower concave track entity embedded in a side wall, a planetary self-centering clamping mechanism for sliding centering against the protruding curve, a multi-station planetary cutting mechanism for swing transmission embedded in the lower concave curve, and a bottom end chip removal and lubricating mechanism. In the application, a single driving power source directly drives a double-track cam disc to synchronously rotate, an inner cam ring is used for pushing a wedge-shaped block to drive a jaw locking shockproof, an outer feeding groove is used for synchronously pulling a large gear ring to drive a whole-circle tool holder to radially cooperate with multi-blade cutting processing, a center circle center is used for counteracting a component force to eliminate a tool retracting stroke, and under continuous one-way rotation, final consequences caused by mechanical error accumulation due to partial swing are completely eliminated.

Description

Technical Field

[0001] This invention relates to the field of automated processing production line technology, and in particular to a metal filter connector end processing device. Background Technology

[0002] The field of automated machining production line technology involves various manufacturing equipment that achieves metal blank forming through precision mechanical transmission and tool cutting motion. Among them, traditional metal filter connector end processing devices refer to purely mechanical equipment that uses a fixture to hold the connector base and drives a rotating tool post or a fixed tool post for linear feed to cut and remove metal from the inner and outer diameters and end face contours of the filter connector.

[0003] Existing technology uses a fixed jaw clamping mechanism combined with a single-axis linear feed screw to perform end face cutting on metal joints. This operation relies on the spindle to reciprocate and switch tools during multi-process machining. The frequent advance and retreat of the tool holder generates intermittent mechanical impacts on the main drive shaft system. These impacts cause the internal gear meshing clearance to accumulate continuously, resulting in a relative positional shift between the tool holder and the joint clamping reference surface. The rigid positioning in one direction cannot mechanically buffer and compensate for the cutting vibration, directly leading to inconsistent end face cutting depth and the appearance of local mechanical vibration marks. Summary of the Invention

[0004] One object of the present invention is to provide a metal filter connector end processing device, comprising: The main frame of the processing equipment is fixed to the bottom of the main frame and a load-bearing base. A vertical support column is connected above the load-bearing base and a main bearing seat is fixed at the top of the vertical support column. The double-track cam drive mechanism is horizontally inserted and embedded in the side wall of the vertical support column. The double-track cam drive mechanism has solid transmission surfaces with raised curves and concave curves. The planetary self-centering clamping mechanism is installed at the center of the main bearing housing and on the outer circumferential surface. The raised curved surface of the double-rail cam transmission mechanism abuts against the planetary self-centering clamping mechanism for radial sliding limit engagement. A multi-station planetary cutting mechanism is installed around the outer circumference of the planetary self-centering clamping mechanism. The double-rail cam transmission mechanism is embedded in the concave curve of the multi-station planetary cutting mechanism to perform deflection and oscillation transmission. The chip removal and lubrication mechanism is sleeved on the upper surface of the load-bearing base and positioned below the bottom of the multi-station planetary cutting mechanism; As a further aspect of the present invention, the specific structure of the dual-rail cam transmission mechanism includes: The active input shaft passes through one side wall of the vertical support column via a rolling bearing, and the power input end of the active input shaft is axially machined with a spline. The main gear is fixed to the input end of the drive input shaft by a spline sleeve and rotates coaxially with the drive input shaft. The double-rail cam disc has an inner gear ring at the bottom that meshes with the main gear. The front of the double-rail cam disc is simultaneously machined to form a convex and concave spatial trajectory surface. As a further aspect of the present invention, the specific structure of the planetary self-centering clamping mechanism includes: The connector positioning mandrel is coaxially pressed and fixed in the inner hole of the main bearing housing by interference fit; The sliding guide rail seat is fixed to the outer circumferential surface of the main bearing seat by a flange sleeve, and the surface is provided with guide grooves around the perimeter; The wedge-shaped locking slider is fitted into the guide groove of the sliding guide rail seat, and the raised curved solid surface of the double-rail cam transmission mechanism is in close contact with the end contact surface of the wedge-shaped locking slider. As a further aspect of the present invention, the specific structure of the multi-station planetary cutting mechanism includes: The feed planetary gear ring is mounted on the outer circumference of the main bearing housing via a sliding bearing, and the outer sidewall of the feed planetary gear ring is hinged to the swing transmission output end of the double-rail cam transmission mechanism. The sun gear housing is circumferentially fastened to the front end face of the main bearing housing by bolts, and the solid body has a bearing mounting hole machined through it axially. The tool post planetary gear passes through the bearing mounting hole of the sun gear seat, and the outer end of the ring gear is physically engaged with the inner straight teeth of the feed planetary gear ring. As a further aspect of the present invention, the specific structure of the chip removal and lubrication mechanism includes: The annular chip collection groove has a hollow circular structure and is fitted onto the upper part of the outer periphery of the load-bearing base to receive cutting metal scrap falling from directly above. The guide plate is welded and fixed to the bottom side wall of the annular chip collection groove, and the surface of the guide plate has an outward and downward inclined discharge geometry. The bottom edge of the guide plate extends to the outside of the main frame of the processing equipment. As a further aspect of the present invention, the spatial trajectory surface of the dual-track cam disk specifically includes: The inner locking cam rail is integrally formed in the inner ring area of ​​the front of the double-rail cam disc, presenting a raised slide rail with a continuous closed protruding curve configuration. The outer feed cam groove is cut and recessed into the outer ring area of ​​the front of the double-rail cam disk, and the overall spatial shape presents an Archimedean spiral evolved groove. The transmission roller and the roller fork are connected at the front end of the roller fork. The transmission roller rolls and fits into the inner groove of the outer feed cam. As a further aspect of the present invention, the structure of the planetary self-centering clamping mechanism further includes: The chuck linkage ring is arranged in a ring structure on the end face of the main bearing seat, and the wedge-shaped contact slope of the wedge-shaped locking slider abuts against the outer side of the chuck linkage ring with the center facing it. The self-centering jaw consists of three independent physical jaws arranged in an equidistant array, which are snapped together on the inner wall of the jaw linkage ring. The return spring is fitted around the outer perimeter of the wedge-shaped locking slider, with one end abutting against the slider body and the other end abutting against the inner wall of the sliding guide seat to generate a reverse expansion thrust. As a further aspect of the present invention, the structure of the multi-station planetary cutting mechanism also includes: The transmission bevel gear is coaxially fixed to the inner end shaft of the tool holder planetary gear via an internal spline, and rotates synchronously with the tool holder planetary gear. The feed screw is arranged horizontally in the radial direction, and the outer cylindrical surface is fixedly connected to the reversing bevel gear by a flat key; The reversing bevel gear has a conical tooth profile that meshes with the conical tooth profile of the drive bevel gear at a 90-degree angle, converting the circumferential rotational motion into the in-situ rotational motion of the feed screw. As a further aspect of the present invention, the connection relationship between the feed screw and the cutting end is specifically as follows: The lead screw guide nut has an internal threaded hole machined in the center, and the trapezoidal external thread of the feed lead screw engages and passes through the center of the internal threaded hole of the lead screw guide nut. The movable tool holder has its bottom metal plane fixedly connected to the upper surface of the lead screw guide nut using a rigid welding process. The rotational motion of the feed lead screw forces the lead screw guide nut to push and pull the movable tool holder to make a linear reciprocating sliding motion along the radial trajectory. As a further aspect of the present invention, the end fixing structure of the movable tool holder includes: The end face flat-edged cutter has a straight cutting edge and is directly fixed to the top mounting groove of one of the movable cutter holders by bolt pressure plates; The internal chamfering cutter has a tapered cutting edge with an inclined angle and is rigidly fastened to the front slide plate of another movable cutter holder; The outer edge deburring knife has an arc-shaped scraping side edge, which is screwed onto the surface of the third movable knife holder. The three knives are arranged in a 120-degree star-shaped circular array facing the central positioning point in the spatial layout.

[0005] The beneficial effects of this invention are: This invention utilizes a main gear to drive a dual-rail cam disc to rotate synchronously. The inner locking cam rail pushes a wedge-shaped locking slider to drive a self-centering chuck for radial locking, eliminating clamping vibration. The outer feed cam groove, in conjunction with the transmission roller, moves the feed planetary gear ring to mesh with the evenly distributed tool holder planetary gears. This forces multiple sets of moving tool holders equipped with different cutting tools to complete synchronous radial feed cutting operations through the coordination of reversing bevel gears and feed screws. The dual-rail planetary linkage mechanism with a single power source eliminates the tool change retraction stroke. The centrally symmetrical distribution of cutting points cancels out the radial cutting force, achieving continuous composite machining of the joint end face under uninterrupted unidirectional rotation, fundamentally eliminating the cumulative runout error caused by reciprocating mechanical impact. Attached Figure Description

[0006] The accompanying drawings are provided to further illustrate the invention and form part of the specification. They are used in conjunction with embodiments of the invention to explain the invention and do not constitute a limitation thereof. In the drawings: Figure 1 This is a three-dimensional schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the explosive disassembly of a double-rail cam drive mechanism. Figure 3 This is a partial structural diagram of a planetary self-centering clamping mechanism. Figure 4 for Figure 3 Enlarged view of point A in the middle; Figure 5 This is a schematic diagram of the explosive decomposition of a multi-station planetary cutting mechanism; Figure 6 This is a schematic diagram of the gear ring and planetary gear transmission components. Figure 7 for Figure 6 Enlarged view of point B in the middle; Figure 8 This is a schematic diagram of the multi-tool radial feed section. Figure 9 for Figure 8 Enlarged view of point C in the middle; Figure 10 This is a partial sectional view of the internal transmission of the double-rail cam disc.

[0007] In the diagram: 1. Main frame of the processing equipment; 11. Load-bearing base; 12. Vertical support column; 13. Main bearing seat; 2. Double-rail cam transmission mechanism; 21. Active input shaft; 22. Main gear; 23. Double-rail cam disc; 24. Inner locking cam rail; 25. Outer feed cam groove; 26. Transmission roller; 27. Roller shift fork; 3. Planetary self-centering clamping mechanism; 31. Sliding guide rail seat; 32. Wedge-shaped locking slider; 33. Return spring; 34. Claw linkage ring; 5. Self-centering chuck; 36. Joint positioning mandrel; 4. Multi-station planetary cutting mechanism; 41. Feed planetary gear ring; 42. Sun gear seat; 43. Tool holder planetary gear; 44. Drive bevel gear; 45. Reversing bevel gear; 46. Feed screw; 47. Screw guide nut; 48. Moving tool holder; 49. End face flat-edge cutter; 410. Internal hole chamfering cutter; 411. External edge deburring cutter; 5. Chip removal and lubrication mechanism; 51. Annular chip collection groove; 52. Guide sloping plate. Detailed Implementation

[0008] The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, illustrating only the basic structure of the invention, and therefore only show the components relevant to the invention.

[0009] Please see Figure 1 and Figure 5This invention provides a technical solution: a metal filter connector end processing device, whose basic frame is mainly composed of a processing equipment main frame 1, a load-bearing base 11, a vertical support column 12, and a main bearing seat 13. The above components are combined into a rigid whole through a high-strength mechanical connection to bear the dynamic heavy load during the cutting process. The processing equipment main frame 1, as the geometric reference and dynamic skeleton of the overall equipment, is integrally cast from gray cast iron material with high damping and vibration reduction characteristics. The flake graphite structure inside the gray cast iron material can effectively absorb the multi-frequency resonance stress generated during metal cutting. The internal wall thickness of the processing equipment main frame 1 is designed to be between 20 mm and 30 mm, and in this embodiment, it is preferably 25 mm. This structural thickness optimizes the distribution of casting cooling stress while ensuring bending and torsional stiffness. The load-bearing base 11, serving as the bottom support component, is fixed to the lowest end of the main frame 1 of the processing equipment. Its fixing process employs full-penetration carbon dioxide gas shielded arc welding, with a weld bevel angle of 60 degrees. After welding, it undergoes overall stress-relief annealing at 550 degrees Celsius to completely eliminate residual micro-stress in the heat-affected zone and prevent structural deformation during long-term service. A vertical support column 12 is vertically fixed above the load-bearing base 11. The cross-section of the vertical support column 12 presents a multi-cavity honeycomb frame structure. This geometric configuration effectively resists overturning moments transmitted from the upper cutting layer. The top of the vertical support column 12 is fixed to the main bearing seat 13 by multiple 12.9 grade high-strength bolts. The preload torque of the bolts is set between 120 Nm and 150 Nm, preferably 135 Nm in this embodiment, to ensure that the main bearing seat 13 does not experience micron-level displacement when subjected to high-frequency axial impact loads. A positioning boss is machined on the circumferential surface of the main bearing housing 13 to establish the coaxiality reference for subsequent assembly components. The chip removal and lubrication mechanism 5, as an auxiliary structure, is tightly fitted below the base frame. The annular chip collection groove 51 is sleeved above the outer periphery of the load-bearing base 11, and is an overall circular hollow stainless steel sheet metal part. Its material is 304 austenitic stainless steel with extremely high pitting resistance, effectively resisting the chemical corrosion of sulfur and chlorine additives in extreme pressure cutting fluid. A guide plate 52 is fixedly connected to the bottom sidewall of the annular chip collection groove 51 by fully sealed argon arc welding. The surface of the guide plate 52 exhibits an outward and downward tilting discharge geometry, with the tilt angle set between 15 and 25 degrees. In this embodiment, 20 degrees is preferred. This angle allows the high-heat metal chips falling from the cut surface to smoothly slide out to the outside of the main frame 1 of the processing equipment under the combined action of their own gravity and the flushing action of the cutting fluid, preventing chips from accumulating inside the frame and interfering with moving parts.

[0010] Please see Figure 1 , Figure 2 and Figure 10The dual-rail cam transmission mechanism 2, serving as the core power transmission assembly, is transversely inserted and embedded within the side wall of the vertical support column 12, forming a closed internal power compartment. The specific structure of the dual-rail cam transmission mechanism 2 precisely includes an active input shaft 21, a main gear 22, and a dual-rail cam disc 23. The active input shaft 21 is made of high-hardenability 40Cr alloy structural steel. After quenching and tempering, its surface undergoes high-frequency induction hardening, achieving a core hardness of 240 to 280 Brinell hardness after quenching and tempering, while the journal surface achieves a Rockwell hardness of 50 to 55, to resist long-term alternating torsional shear stress. The active input shaft 21 traverses one side wall of the vertical support column 12 via two sets of staggered tapered roller bearings. These tapered roller bearings can simultaneously withstand the radial load and axial positioning thrust from the external power source, ensuring the rotational accuracy of the active input shaft 21 during high-speed rotation within the speed range of 300 to 600 rpm. In this embodiment, the preferred input speed is 450 rpm. An involute spline is machined axially at the power input end of the active input shaft 21, and a matching internal spline is also machined inside the center hole of the main gear 22. The main gear 22 is rigidly fixed to the input end of the active input shaft 21 via a spline connection, thus achieving absolutely synchronous coaxial rotation with the active input shaft 21. This eliminates the defects of traditional flat key connections, such as keyway rolling or loosening under reciprocating impact. The tooth profile of the main gear 22 adopts a large-module spur gear design with a module between 3 mm and 5 mm. In this embodiment, the module is preferably 4 mm, and the number of teeth is designed to be 22. The large-module design significantly enhances the bending and shearing strength of a single tooth. The bottom end of the double-rail cam disk 23 is integrally machined with an inner ring gear, which physically meshes with the main gear 22 to form a large-ratio internal meshing reduction gear pair. The front disk of the double-rail cam disk 23 is simultaneously machined to form protruding and recessed spatial trajectory surfaces, specifically, the inner locking cam rail 24 and the outer feed cam groove 25. The inner locking cam rail 24 is integrally cast or precision milled in the inner ring area of ​​the front of the double-rail cam disk 23, presenting a continuously closed protruding curve configuration of a protruding slide rail. The radius of its contour curve increases in a step-like manner with the change of the circumferential angle and has a constant segment distribution. The outer feed cam groove 25 is cut and recessed into the front outer ring area of ​​the double-rail cam disk 23. The overall spatial shape presents an Archimedean spiral groove. The groove width tolerance is controlled within an extremely high precision range of ±0.01 mm, and the perpendicularity between the bottom surface of the groove and the two sides of the groove is kept within 0.015 mm.To achieve precise motion transmission, a transmission roller 26 is rolled and fitted inside the outer feed cam groove 25. The outer circumference of the transmission roller 26 is wrapped with an oil-containing solid lubricating wear-resistant layer. The spindle of the transmission roller 26 is fastened to the front end of the roller fork 27 by interference fit. The rear end of the roller fork 27 is hinged to the subsequent actuator. The actual torque when the double-rail cam disk 23 rotates is calculated by multiplying the rated torque of the motor with the transmission ratio of the gear pair, and then deducting the friction loss coefficient of the bearing and the transmission process. When the rated torque of the motor is 50 Nm, the internal meshing transmission ratio is 3.5, and the friction loss ratio is set to 5%, the actual output torque is stable at 166.25 Nm, which is sufficient to provide an extremely strong and uniform physical driving force for the subsequent clamping and cutting processes.

[0011] Please see Figure 1 , Figure 3 and Figure 4 The planetary self-centering clamping mechanism 3 is mechanically installed at the center and outer circumferential surface of the main bearing housing 13, forming the positioning and clamping assembly of the metal filter connector. The specific structure of the planetary self-centering clamping mechanism 3 includes a connector positioning mandrel 36, a sliding guide seat 31, a wedge-shaped locking slider 32, a chuck linkage ring 34, a self-centering chuck 35, and a return spring 33. The connector positioning mandrel 36 serves as the absolute positioning reference for the workpiece's center hole. It is coaxially pressed and fixed in the inner center of the main bearing housing 13 via an interference fit. The tolerance level at the fit is a standard H7 and r6 tight interference fit to eliminate any radial fretting backlash. The outer cylindrical surface of the connector positioning mandrel 36 is ultra-precision ground, achieving a surface roughness of Ra. 0.2 micrometers. The sliding guide seat 31 is fixed to the outer circumferential surface of the main bearing seat 13 by an integrated large circumferential flange. Two to four radial guide grooves are precisely formed at equal intervals and angles along the circumferential direction on the surface of the sliding guide seat 31. In this embodiment, three evenly distributed star-shaped guide grooves are preferred. Precision wear-resistant copper liners are embedded in the sidewalls of the guide grooves. The wedge-shaped locking slider 32 is fitted into the guide groove of the sliding guide seat 31 with a one-to-one geometric mapping relationship, thus restricting the wedge-shaped locking slider 32 to only perform one-dimensional linear reciprocating sliding along the radial direction of the axis. The protruding slide rail surface of the inner locking cam rail 24 in the double-rail cam transmission mechanism 2 is in close contact with and abuts against the outer end contact surface of the wedge-shaped locking slider 32. The inner front surface of the wedge-shaped locking slider 32 is machined into a specific inclined wedge surface with an angle between 15 and 25 degrees. In this embodiment, 20 degrees is preferred. This angle is chosen to maximize the mechanical multiplication effect of converting the tangential pushing force applied by the cam drive plate into the radial clamping force, while avoiding geometric self-locking after clamping, ensuring smooth reset after the external force is removed. The pawl linkage ring 34 is a ring-shaped hollow thin-walled structure disposed on the outer periphery of the end face of the main bearing seat 13. Its outer circumferential surface abuts against the inclined wedge surfaces of the three wedge-shaped locking sliders 32. The inner wall of the pawl linkage ring 34 is connected to three self-centering pawls 35 with equal circumferential arrays by dovetail-shaped buckles. The self-centering jaw 35 is made of Cr12MoV cold work die steel and undergoes overall vacuum quenching and tempering treatment, achieving a Rockwell hardness of 60 to 62. The inner arc surface of the self-centering jaw 35 is machined with regular stepped teeth with a tooth depth of 1.5 mm to engage the metal substrate of the filter connector during clamping, eliminating forward deflection caused by cutting torque. The return spring 33, serving as an energy storage and forced retraction mechanism, is fitted around the outer periphery of the wedge-shaped locking slider 32. The return spring 33 is made of silicon manganese spring steel wire, with one end abutting against the lug of the slider body and the other end abutting against the inner groove wall of the sliding guide seat 31. When the inner locking cam rail 24 rotates to the low profile section, the return spring 33 releases the reverse expansion thrust generated by compression, forcibly pushing and pulling the wedge-shaped locking slider 32 radially outward to release the lock.

[0012] Please see Figure 1 , Figure 5 , Figure 6 , Figure 7 , Figure 8 and Figure 9The multi-station planetary cutting mechanism 4 is installed around the outer circumference of the planetary self-centering clamping mechanism 3, realizing multi-point linkage composite metal removal in space. The specific structure of the multi-station planetary cutting mechanism 4 is finely decomposed into a feed planetary gear ring 41, a sun gear seat 42, a tool holder planetary gear 43, a transmission bevel gear 44, a reversing bevel gear 45, a feed screw 46, a screw guide nut 47, a moving tool holder 48, an end face flat-edge cutter 49, an inner hole chamfering cutter 410, and an outer edge deburring cutter 411. The feed planetary gear ring 41 is fixed on the outer circumference of the main bearing seat 13 through a high-precision sliding bearing machined on the inner ring, forming a relatively rotatable pair of motion. The outer sidewall of the feed planetary gear ring 41 is hinged to the output end of the roller fork 27 via a pin. When the double-rail cam disk 23 rotates, the Archimedean spiral spatial trajectory of the outer feed cam groove 25 forces the transmission roller 26 and the roller fork 27 to deflect periodically, thereby pulling the feed planetary gear ring 41 to produce a limited angular differential deflection oscillation between 15 and 30 degrees at the outer edge of the main bearing housing 13. The sun gear housing 42 is circumferentially fastened to the front end face of the main bearing housing 13 by multiple circumferentially arranged anti-loosening high-strength bolts, keeping it absolutely stationary. Three bearing mounting holes are machined equidistantly along the axial direction inside the solid body of the sun gear housing 42. Three tool post planetary gears 43 are respectively installed in bearing mounting holes via deep groove ball bearings. The annular gear ring at the outer end of the tool post planetary gear 43 meshes with the spur gear rack machined on the inner side of the feed planetary gear ring 41. When the feed planetary gear ring 41 deflects, since the sun gear seat 42 is fixed, its internal teeth will inevitably drive the three tool post planetary gears 43 to rotate within the bearing holes. The inner end shaft of the tool post planetary gear 43 is coaxially fixed with a drive bevel gear 44 via an involute spline. The drive bevel gear 44 is paired with three reversing bevel gears 45 arranged radially horizontally. The conical tooth profiles of the reversing bevel gears 45 and the drive bevel gears 44 are perpendicular to each other at a 90-degree right angle, and they mesh with each other in a staggered manner, converting the rotational motion in the circumferential horizontal plane into a radial rotational motion perpendicular to the axis without gap. The tooth flank clearance of the bevel gear pair is strictly controlled between 0.03 mm and 0.05 mm, which greatly reduces the reversing idle stroke. The central shaft hole of the reversing bevel gear 45 is rigidly connected and fixed to the outer cylindrical surface of the feed screw 46 via a flat key. The feed screw 46 is made of 42CrMo finely tempered material, with a precision trapezoidal external thread machined on its surface. The pitch is set between 2 mm and 4 mm, preferably 3 mm in this embodiment. The external thread of the feed screw 46 engages with the matching internal thread machined in the central hole of the screw guide nut 47. The screw guide nut 47 is made of high-strength tin bronze to reduce the friction coefficient with the steel screw. The upper surface of the screw guide nut 47 is rigidly connected to the bottom metal plane of the moving tool holder 48 by high-frequency induction welding.The movable tool holder 48 is engaged in the radial slide of the sun gear seat 42. The in-situ rotation driving force of the feed screw 46 is converted into the screw guide nut 47 pushing and pulling the movable tool holder 48 to make precise linear sliding feed along the radial trajectory through the spiral surface rotation action. Its cutting feed is controlled between 0.05 mm per revolution and 0.15 mm per revolution. In this embodiment, it is preferably 0.1 mm per revolution. The ends of the three movable tool holders 48 are respectively fixed with different tools by heavy-duty pressure plates. The end face flat-edge tool 49 is fixed in the top mounting groove of the first movable tool holder 48 by clamping bolts, and is used to perform axial thickness reduction fine turning on the top surface of the filter connector. The inner hole chamfering tool 410 has three straight-edged conical cutting edges and is rigidly fixed to the front end of the second movable tool holder 48. It is used to remove the sharp corners of the inner hole opening and form a standard 45-degree chamfer. The outer edge deburring tool 411 has an arc-shaped reverse scraping side edge and is screwed to the surface of the third movable tool holder 48. It is specifically designed to smooth and remove the micro-burrs on the outer circumferential edge. The three cutting tools mentioned above are arranged in a symmetrical 120-degree star-shaped circular array towards the center positioning point of the connector positioning mandrel 36 in three-dimensional space. This mechanical arrangement enables the radial cutting reaction force generated when cutting into the metal in three directions to be superimposed and reduced to zero at the geometric center point in space, perfectly offsetting the cantilever bending stress generated by the unidirectional rigid feed on the machine tool spindle system, thus eliminating the occurrence of machining vibration marks from a physical perspective.

[0013] To fully demonstrate the excellent overall machining yield and multi-station composite linkage transmission stability of the metal filter connector end processing device described in this invention in actual industrial metal cutting applications, technicians conducted long-term continuous machining comparison tests on the same batch of stainless steel filter connector blanks in a constant temperature precision workshop with an ambient temperature controlled at 20 degrees Celsius, using both traditional single-axis linear feed machining equipment and the device described in this invention. The results are shown in Table 1 below, which presents the actual test comparison data of cutting performance and mechanical stability.

[0014] Table 1 Comparison of Processing Performance and Mechanical Stability Tests

[0015] As shown in the experimental data analysis in Table 1, the device described in this invention represents a qualitative leap compared to traditional processing equipment. The average processing cycle time per piece has been significantly reduced from 45 seconds to 18 seconds, increasing processing efficiency by more than 250%. The fundamental reason for this is that this invention abandons the traditional method of repeated tool feeding and retraction, requiring machine stops and robotic arm switching between multiple tools, instead concentrating the three core processing steps—end face turning, internal hole chamfering, and external edge burr scraping—into a dual-rail planetary linkage cutting mechanism powered by a single power source. This achieves simultaneous three-dimensional radial linear feed for multiple tools. Simultaneously, the thickness tolerance of the joint end face has been reduced from 25 micrometers to 6 micrometers, and the surface roughness has been improved from Ra... 3.2 micrometers improved to Ra The surface quality of 0.8 micrometers, which is at the micro-precision turning level, and the cumulative runout error of the spindle of the machining equipment only accumulated to 2 micrometers after continuous machining of 5,000 parts, strongly demonstrates the mechanical superiority of the three moving tool holders 48 arranged in a 120-degree star-shaped circular array. The horizontal cutting radial component generated when they simultaneously cut into the workpiece at the same speed completely cancels each other out at the center position, avoiding stress fatigue degradation and clearance accumulation of the main bearing housing 13 under reciprocating alternating load, and achieving extremely high comprehensive machining quality.

[0016] The overall operating principle of the metal filter connector end processing device described in this invention is as follows: When the system starts and executes a complete processing cycle, the external spindle rotation power source injects torque into the spline end of the active input shaft 21. The active input shaft 21 drives the main gear 22 to rotate coaxially at a constant speed of 450 revolutions per minute. The main gear 22 drives the double-rail cam disk 23 to generate a low-speed, high-torque counterclockwise rotation inside the vertical support column 12 through the meshing pair of the inner ring gear with a large transmission ratio. In the first stage of the initial rotation of the double-rail cam disk 23, from zero to thirty degrees phase angle, the radius of the protruding rail surface of the inner locking cam rail 24 gradually expands outward and rises eccentrically, thereby strongly pushing the wedge-shaped locking slider 32 radially toward the center. The wedge-shaped locking slider 32 overcomes the back resistance of the return spring 33 and slides radially along the sliding guide seat 31. Through the mechanical amplification effect of its 20-degree inclined wedge surface, it smoothly and forcefully squeezes the claw linkage ring 34, causing the three self-centering claws 35 installed on the inner wall to retract inward, and firmly clamping the outer circumference of the filter connector blank pre-inserted on the outside of the connector positioning mandrel 36 with self-centering and shockproof locking. As the double-rail cam disk 23 continues to rotate backward continuously in the forward direction, entering the second stage with a phase angle of 30 to 180 degrees, the Archimedean spiral evolution trajectory of the outer feed cam groove 25 on the front of the cam disk begins to play a role, and the groove wall drives the transmission roller 26 together with the roller shift fork 27 to produce a differential deflection towards the axis. The oscillation of the roller fork 27 forces the feed planetary gear ring 41 to generate a fixed circumferential differential deflection oscillation on the outer edge of the main bearing housing 13. The internal spur teeth of the feed planetary gear ring 41 drive the three tool holder planetary gears 43, which are evenly distributed in the hole of the fixed sun gear housing 42, to rotate in the same direction at a high frequency. The tool holder planetary gears 43 transmit torque to the coaxial drive bevel gear 44 through the spline shaft. The drive bevel gear 44, through its right-angle staggered pair with the reversing bevel gear 45, converts the rotational power into the radial in-situ rotation of the feed screw 46. When the feed screw 46 rotates, its precise trapezoidal external thread forces the screw guide nut 47, which is welded and fixed to the bottom of the moving tool holder 48, to slide in a one-dimensional straight line along the slide rail of the sun gear housing 42 towards the geometric center point. At this time, the end face flat-edge cutter 49, the inner hole chamfering cutter 410, and the outer edge deburring cutter 411, which are respectively clamped and mounted at the front end of the three movable tool holders 48, simultaneously approach and cut into the high-heat rotating filter joint end face to be processed from three directions forming an angle of 120 degrees with a precision feed rate of 0.1 mm per revolution. The radial cutting forces generated by the three tools achieve perfect self-balancing and cancellation at the axis of the filter joint. The high-heat metal chips generated during the metal cutting process fall into the annular chip collection groove 51 at the bottom under their own gravity, and under the drive of the extreme pressure cutting fluid, slide out of the main frame 1 of the processing equipment along the guide plate 52 that is inclined outward at 20 degrees.After the double-rail cam disk 23 rotates past the maximum stroke phase angle point, the outer feed cam groove 25 enters the reverse retraction trajectory, and the lead screw and bevel gear transmission mechanism rotate in the opposite direction. The lead screw guide nut 47 drives the three moving tool holders 48 to retract radially back to their original positions. Immediately afterwards, the inner locking cam rail 24 rotates to the low profile section, losing the radial pressure of the cam protrusion. The return spring 33 instantly releases the accumulated compression energy, forcibly pushing the wedge-shaped locking slider 32 outward. The self-centering chuck 35 returns to the open state, and the finished filter connector is unloaded by the operator or external robot. Thus, in the uniform unidirectional circumferential rotation motion of a single input shaft without retraction, a complete life cycle work loop of pure mechanical linkage continuous composite processing of the entire metal filter connector end is achieved.

[0017] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A metal filter connector end processing device, characterized in that, include: The main frame of the processing equipment (1) is fixed to the bottom of the main frame of the processing equipment (1), and a vertical support column (12) is vertically connected above the support column (11). The main bearing seat (13) is fixed at the top of the vertical support column (12). The double-track cam transmission mechanism (2) is transversely inserted and embedded in the side wall of the vertical support column (12). The double-track cam transmission mechanism (2) has a solid transmission surface with a raised curve and a concave curve. The planetary self-centering clamping mechanism (3) is installed at the center and outer circumferential surface of the main bearing seat (13). The raised curved surface of the double-rail cam transmission mechanism (2) abuts against the planetary self-centering clamping mechanism (3) for radial sliding limit engagement. The multi-station planetary cutting mechanism (4) is installed around the outer circumference of the planetary self-centering clamping mechanism (3). The concave curve of the double-rail cam transmission mechanism (2) is embedded in the multi-station planetary cutting mechanism (4) for deflection and swing transmission. The chip removal and lubrication mechanism (5) is sleeved on the upper surface of the load-bearing base (11) and positioned below the bottom end of the multi-station planetary cutting mechanism (4).

2. The metal filter connector end processing device according to claim 1, characterized in that, The specific structure of the dual-rail cam transmission mechanism (2) includes: The active input shaft (21) passes through one side wall of the vertical support column (12) via a rolling bearing, and the power input end of the active input shaft (21) is axially machined with a spline; The main gear (22) is fixed to the input end of the active input shaft (21) by a spline sleeve and rotates coaxially with the active input shaft (21). The inner ring gear at the bottom of the double-track cam disk (23) meshes with the main gear (22). The front plate of the double-track cam disk (23) is simultaneously machined to form a convex and concave spatial trajectory surface.

3. The metal filter connector end processing device according to claim 1, characterized in that, The specific structure of the planetary self-centering clamping mechanism (3) includes: The connector positioning mandrel (36) is coaxially pressed and fixed in the inner hole of the main bearing seat (13) by interference fit; The sliding guide rail seat (31) is fixed to the outer circumferential surface of the main bearing seat (13) by means of a flange sleeve, and the surface is provided with guide grooves around the perimeter; The wedge-shaped locking slider (32) is fitted into the guide groove of the sliding guide rail seat (31), and the raised curved solid surface of the double-rail cam transmission mechanism (2) is in close contact with the end contact surface of the wedge-shaped locking slider (32).

4. The metal filter connector end processing device according to claim 1, characterized in that, The specific structure of the multi-station planetary cutting mechanism (4) includes: The feed planetary gear ring (41) is mounted on the outer circumference of the main bearing housing (13) via a sliding bearing, and the outer sidewall of the feed planetary gear ring (41) is hinged to the swing transmission output end of the double-rail cam transmission mechanism (2). The sun gear seat (42) is circumferentially fastened to the front end face of the main bearing seat (13) by bolts, and a bearing mounting hole is machined through the solid body along the axial direction; The tool holder planetary gear (43) is installed through the bearing mounting hole of the sun gear seat (42), and the annular gear ring at the outer end meshes with the inner straight teeth of the feed planetary gear ring (41).

5. The metal filter connector end processing device according to claim 1, characterized in that, The specific structure of the chip removal and lubrication mechanism (5) includes: The annular chip collection groove (51) has a hollow annular structure and is fitted above the outer periphery of the load-bearing base (11) to receive the cutting metal scrap falling from directly above. The guide plate (52) is welded and fixed to the bottom side wall of the annular chip collection groove (51), and the surface of the guide plate (52) presents an outward and downward inclined discharge geometry. The bottom edge of the guide plate (52) extends to the outside of the main frame (1) of the processing equipment.

6. The metal filter connector end processing device according to claim 2, characterized in that, The spatial trajectory surface of the dual-track cam disk (23) specifically includes: The inner locking cam rail (24) is integrally formed in the inner ring area of ​​the front side of the double-rail cam disk (23), and presents a raised slide rail with a continuous closed protruding curve configuration. The outer feed cam groove (25) is cut and recessed into the front outer ring area of ​​the double-rail cam disk (23), and the overall spatial shape presents an Archimedean spiral evolution groove. The transmission roller (26) and the roller fork (27) are connected at the front end of the transmission roller (26), and the transmission roller (26) is rolled and fitted inside the outer feed cam groove (25).

7. The metal filter connector end processing device according to claim 3, characterized in that, The structure of the planetary self-centering clamping mechanism (3) also includes: The pawl linkage ring (34) is arranged in a ring structure on the end face of the main bearing seat (13), and the wedge-shaped contact slope of the wedge-shaped locking slider (32) abuts against the outside of the pawl linkage ring (34) towards the center; The self-centering jaw (35) comprises three independent solid jaws distributed in an equidistant array, which are snapped together on the inner wall of the jaw linkage ring (34). The reset spring (33) is fitted around the outer periphery of the side of the wedge-shaped locking slider (32), with one end abutting against the slider body and the other end abutting against the inner wall of the sliding guide seat (31) to generate a reverse expansion thrust.

8. The metal filter connector end processing device according to claim 4, characterized in that, The structure of the multi-station planetary cutting mechanism (4) also includes: The transmission bevel gear (44) is coaxially fixed to the inner end shaft position of the tool holder planetary gear (43) through an inner spline, and rotates synchronously with the tool holder planetary gear (43); The feed screw (46) is arranged horizontally in the radial direction, and the outer cylindrical surface is fixedly connected to the reversing bevel gear (45) by a flat key. The reversing bevel gear (45) has a conical tooth profile that meshes with the conical tooth profile of the transmission bevel gear (44) at a 90-degree angle, converting the circumferential rotational motion into the in-situ rotational motion of the feed screw (46).

9. The metal filter connector end processing device according to claim 8, characterized in that, The connection relationship between the feed screw (46) and the cutting end is as follows: The lead screw guide nut (47) has an internal threaded hole machined in the center, and the trapezoidal external thread of the feed lead screw (46) is screwed through the center of the internal threaded hole of the lead screw guide nut (47). The bottom metal plane of the movable tool holder (48) is fixedly connected to the upper surface of the lead screw guide nut (47) by a rigid welding process. The rotational motion of the feed lead screw (46) forces the lead screw guide nut (47) to push and pull the movable tool holder (48) to make a linear reciprocating sliding motion along the radial trajectory.

10. The metal filter connector end processing device according to claim 9, characterized in that, The end fixing structure of the movable tool holder (48) includes: The end face flat-edged cutter (49) has a straight cutting edge and is directly fixed to the top mounting groove of one of the movable cutter holders (48) by means of a bolt plate; An internal chamfering cutter (410) with a tapered cutting edge at an inclined angle is rigidly fastened to the front slide plate of another movable cutter holder (48); The outer edge deburring knife (411) has an arc-shaped scraping side edge, is screwed onto the surface of the third movable knife holder (48), and the three knives are arranged in a 120-degree star-shaped circular array facing the central positioning point in the spatial layout.

Images