Quick tool changing device

Abstract

The utility model discloses a quick tool changing device which comprises an outer box, an inner box, a tool box locking hole, a tool box locking hole, a tool box locking hole, a tool box locking hole and a tool box locking hole. The translational connecting rod frame is arranged in the outer box and comprises a worm and a guide mechanism which are parallel to each other; the worm gear is matched with the worm and partially exposed out of the outer box, and the exposed part comprises an external operation part; the locking rod is coaxially arranged with the worm, translates along with the connecting rod frame, and has an extending state of extending into the cutter box locking hole; the push hook assembly is hinged to the connecting rod frame, the tail end of the push hook assembly penetrates through the lateral opening, and the push hook assembly has a push-out state clamped with the cutter box step. Through the linkage design of worm and gear transmission and the connecting rod frame, locking and pushing functions are integrated into a single operation mechanism, the number of traditional bolts is reduced, and even bolt fixing is completely replaced.

Description

TECHNICAL FIELD

[0001] The utility model relates to a tool changing device field especially a quick tool changing device. BACKGROUND

[0002] In the field of wood-based board processing, the tool system of the planing machine has long been faced with the problem of low maintenance efficiency. The traditional tool box is rigidly connected with the cutter head through multiple bolts, which can ensure the processing stability, but gradually exposes obvious defects in actual use. Because the tool bears periodic impact load in the process of high-speed cutting, a close fit is formed between the tool box and the blade, and even after all the fixing bolts are removed, the operator still needs to use external force tools to repeatedly knock to separate the tool box. This process not only consumes time and effort, but also easily causes mechanical damage to the matching surface, affecting the repeated assembly precision of the tool. Although the existing improvement scheme attempts to simplify the locking structure, it is often difficult to balance the operation convenience and working reliability, especially when dealing with the separation resistance generated by the precise fit, generally lacking an effective auxiliary separation mechanism, resulting in limited improvement of tool changing efficiency.

[0003] For example, the "pull-out type material box feeding structure for a tool arranging machine" disclosed in the Chinese patent document, with application number "CN202321215343.0", includes a mounting plate, the mounting plate is fixedly installed with a partition strip, the partition strip is fixedly installed with a plurality of positioning columns on both sides, a material placing disc and a material taking disc are placed on both sides of the partition strip, a material placing groove is formed on the material placing disc and the material taking disc, a material box is placed in the material placing groove, a positioning piece adapted to the positioning column is embedded in the material placing disc and the material taking disc, a plurality of positioning blocks are fixedly installed in the material placing groove, and a bottom groove adapted to the positioning block is formed in the bottom of the material box. The material placing disc and the material taking disc can be backed up, that is, the material box can be prepared on the backup material taking disc or material placing disc before changing the material box. When changing the material box, the material placing disc or material taking disc on the tool arranging machine can be pulled out and replaced with the corresponding backup material placing disc or material taking disc.

[0004] The above-mentioned scheme can effectively shorten the downtime of the tool arranging machine, but cannot be applied to solve the problem of quick replacement of the tool box in the field of the present application. Therefore, developing a tool box fixing device that can realize quick locking, reliable positioning and auxiliary separation function has become a key technical requirement to improve the maintenance efficiency of the planing machine. UTILITY MODEL CONTENTS

[0005] In view of the current lack of convenience and low efficiency in tool changing of the cutter head, and the problem that simple installation is easy to cause work failure due to disengagement, the utility model provides a tool box that can assist the cutter head to disengage the cutter head, which is convenient and safe, significantly improves the tool changing efficiency, and can keep the tool box locked on the cutter head when the tool box is working normally, with double functions.

[0006] In order to achieve the above object, the utility model discloses the following technical scheme:

[0007] A quick tool changing device of a slicing machine, comprising: an outer box provided with a through hole corresponding to a locking hole of a tool box and a lateral opening; a translatable connecting rod frame arranged in the outer box and comprising a worm and a guide mechanism parallel to each other; a worm wheel matched with the worm and partially exposed to the outer box, the exposed part comprising an external operation part; a locking rod coaxially arranged with the worm and translatable with the connecting rod frame, having an extended state in which the locking rod extends into the locking hole of the tool box; and a push hook assembly hingedly connected to the connecting rod frame and having a terminal end penetrating through the lateral opening, having a pushing state in which the push hook assembly is engaged with a step of the tool box.

[0008] Further, the guide mechanism comprises guide rod one and guide rod two arranged parallel to both sides of the worm, and both ends are connected by a longitudinal connecting rod to form a rectangular frame structure.

[0009] Further, the longitudinal connecting rod comprises longitudinal rod one away from the lateral opening and longitudinal rod two close to the lateral opening; and both ends of the worm are connected to the longitudinal connecting rod through a threaded pair.

[0010] Further, the external operation part is a hexagonal bolt head structure, and the maximum outer diameter thereof is greater than the hole diameter of the corresponding through hole of the outer box.

[0011] Further, the push hook assembly comprises: a control rod hingedly connected to the connecting rod frame, the bottom surface of the control rod being in sliding contact with the inner wall of the outer box; and a hook body hingedly connected to the front end of the control rod, the terminal end of the hook body being provided with a bayonet matching the step of the tool box.

[0012] The bending part of the hook body is provided with a switching hinge joint hingedly connected to the bottom of the outer box.

[0013] Further, the included angle alpha between the hook body and the outer side of the control rod is within 180 degrees.

[0014] Further, when the worm wheel drives the worm to rotate forward, the locking rod extends out of the through hole of the outer box, and the push hook assembly is completely accommodated in the outer box.

[0015] Further, when the worm wheel drives the worm to rotate reversely, the locking rod is retracted into the outer box, and the hook body of the push hook assembly extends outward and is hung on the step of the tool box.

[0016] Further, the bottom inner side of the lateral opening is provided with a rounded edge in sliding contact with the bottom surface of the control rod, and the rounded edge is higher than the linkage hinge joint of the control rod and the connecting rod frame.

[0017] Further, the worm wheel is provided with a rolling bearing on both sides, and the guide rod one and the guide rod two are each provided with a linear bearing.

[0018] Therefore, the utility model has the following beneficial effects:

[0019] By linking the worm gear drive with the connecting rod frame, the locking and ejection functions are integrated into a single operating mechanism, reducing the number of traditional bolts and even completely replacing bolt fixing.

[0020] The worm gear threaded pair, in conjunction with the guide rod linear bearing, ensures the linear movement accuracy of the locking rod and avoids misalignment of the locking hole caused by skewing.

[0021] The hinged lever structure of the push hook assembly converts the axial motion of the worm gear into radial thrust of the hook body, effectively overcoming the resistance of the precise fit between the cutter box and the cutter disc.

[0022] The external operating part's size limitation and the guiding effect of its rounded edges prevent the push hook assembly from overtraveling and ensure the reliability of each state switching. Attached Figure Description

[0023] Figure 1 This is an assembly diagram of the present invention.

[0024] Figure 2 This is a schematic diagram of the structure of this utility model.

[0025] Figure 3 This is the front view of this utility model.

[0026] Figure 4 This is a state diagram of position zero in Embodiment 1 of this utility model.

[0027] Figure 5 This is a state diagram of the locking position in Embodiment 1 of this utility model.

[0028] Figure 6 This is a state diagram of the unlocked ejection position in Embodiment 1 of this utility model.

[0029] In the diagram: 100, cutter head; 101, cutter box; 102, cutter box locking hole; 103, cutter box step; 1, outer box; 11, through hole; 12, side opening; 13, rounded edge; 14, linkage hinge point; 2, connecting rod frame; 21, worm gear; 22, worm wheel; 221, external operating part; 23, guide rod one; 24, guide rod two; 25, longitudinal connecting rod; 251, longitudinal rod one; 252, longitudinal rod two; 26, rolling bearing; 27, linear bearing; 3, locking rod; 4, push hook assembly; 41, control rod; 42, hook body; 421, bayonet; 43, switching hinge point. Detailed Implementation

[0030] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0031] Example 1

[0032] like Figure 3As shown, this utility model relates to a quick blade change device for a slicer, which achieves efficient locking and assisted separation of the blade holder 101 through a mechanical linkage structure. The main body of the device includes an outer box 1, an internal movable linkage frame 2, and a linkage assembly. The side wall of the outer box 1 has a through hole 11 corresponding to the blade holder locking hole 102 and a lateral opening 12 for the push hook to extend. The linkage frame 2 consists of a worm gear 21 and a guide mechanism that are parallel to each other. The guide mechanism includes a rectangular frame formed by guide rods on both sides and a longitudinal connecting rod 25. The two ends of the worm gear 21 are connected to the longitudinal rod through a threaded pair. The worm wheel 22 is fixed in the middle of the worm gear 21, and its exposed part has an external operating part 221 with a hexagonal bolt head structure. The bolt head size is designed so that the outer diameter is larger than the through hole of the outer box 1, forming an axial limit. The locking rod 3 is coaxially arranged with the worm gear 21 and can pass through the through hole 11 of the outer box 1 and be inserted into the blade holder locking hole 102 as the frame moves. The push hook assembly 4 consists of a control rod 41 and a front hook body 42. The tail of the control rod 41 is rotatably connected to the connecting rod frame 2 via a linkage hinge point 14. The bottom surface of the control rod 41 slides in contact with the rounded corner edge 13 of the inner wall of the outer box 1. The end of the hook body 42 is provided with a locking slot 421 and is connected to the bottom of the outer box 1 via a switching hinge point 43. Rolling bearings 26 are provided on both sides of the worm gear, and linear bearings 27 are provided on both guide rod one and guide rod two.

[0033] When the external operating unit 221 drives the worm gear 22 to rotate forward, the worm 21 drives the connecting rod frame 2 to move forward, and the locking rod 3 extends out of the outer box 1 and inserts into the knife box locking hole 102 to complete the locking. At this time, the push hook assembly 4 is completely stored in the outer box 1. When the operating unit is rotated in the reverse direction, the worm 21 moves backward, causing the locking rod 3 to retract. The control rod 41 slides along the rounded edge 13, forcing the hook body 42 to extend outward. The bayonet 421 engages with the knife box step 103 and applies an outward pushing force, pushing the knife box part out of the cutter disc 100. Continuing to rotate in the reverse direction to the initial position, the push hook assembly 4 retracts completely, and the knife box can be removed without obstruction. The device, through the linkage design of the worm gear 22, worm 21, and connecting rod, converts the rotational motion into the linear motion of the locking rod 3 and the radial action of the push hook. The guide rod and linear bearing cooperate to ensure the movement accuracy. The hinged lever structure of the push hook converts the axial motion into radial thrust through sliding contact, effectively overcoming the cooperation resistance between the knife box and the cutter disc 100. The size limitation of the external operating part 221 and the guiding effect of the rounded edge 13 form an anti-misoperation design, while the self-locking characteristic of the worm gear 21 thread pair ensures the stability of the working state. This structure replaces the traditional bolt fixing method, simplifies the disassembly and assembly process, and achieves a balance between locking reliability and separation efficiency, making it suitable for high-frequency tool changing operations.

[0034] In this embodiment, the rotational motion of the worm gear is converted into the linear displacement of the locking rod through the integrated design of the outer box and the connecting rod frame. The parallel arrangement of the worm and the guide mechanism ensures that the transmission axis coincides, eliminating motion interference caused by off-center loading. The coaxial arrangement of the locking rod achieves uniform force transmission, and the structure of the push hook assembly hinged to the frame creates a mechanical linkage between the locking and pushing actions, replacing the inefficient operation mode of disassembling bolts one by one. In this embodiment, the worm gear is used as the driving element to drive the worm.

[0035] The linkage frame consists of a closed structure composed of guide rods and longitudinal connecting rods, with rigid connections at the nodes creating a spatial truss effect. This maximizes structural stiffness within a limited space. The guide rods are symmetrically distributed on both sides of the worm gear, and the constraint frame translates only in the axial direction, avoiding misalignment of the lock hole caused by deflection during the extension of the locking rod.

[0036] The push-hook assembly employs a double-hinge design, with the bottom surface of the control rod sliding against the inner wall of the outer casing to constrain the motion trajectory. The involute contour of the hook body's jaws forms surface contact with the step of the cutter box, dispersing localized stress. Switching hinge points decomposes the hook body's motion into a composite action of translation and rotation, improving the smoothness of the push-out motion. By limiting the angle between the hook body and the outer side of the control rod, it is ensured that the push-hook assembly remains under control throughout its movement. This angle design creates a secondary lever effect during the push-out phase, amplifying the axial displacement of the worm gear and converting it into the radial displacement of the hook body, effectively overcoming the static frictional resistance between the cutter box and the cutter disc.

[0037] The interaction between the worm gear rotation control device and the knife box is switched. When rotating in the forward direction, the locking rod extends to lock the knife box, and when rotating in the reverse direction, the locking rod retracts. When the frame retracts, the push hook assembly is guided by the rounded edge to generate an outward swing motion, thus pushing out the knife box.

[0038] The rounded edges of the lateral openings feature a continuous curved surface transition, smoothly controlling the sliding trajectory of the control rod. The layout, with the edge height higher than the hinge point, creates torque balance, limiting excessive outward swing of the hook. The matching design between the surface curvature radius and the friction coefficient of the sliding surface reduces motion resistance and prevents jamming.

[0039] The connection structure between the connecting rod frame and the outer housing uses a combination of rolling bearings and linear bearings. The rolling bearings bear the radial load of the worm gear, while the linear bearings guide the axial movement of the frame, converting sliding friction into rolling friction and reducing system energy consumption. Preloaded bearing assembly eliminates backlash, ensuring stable transmission accuracy during long-term use.

[0040] The hexagonal bolt head at the turbine end has an outer diameter larger than the through hole in the outer casing, forming a mechanical stop to limit the axial displacement of the worm gear. The hexagonal profile provides a multi-directional force application surface, accommodating torque input at different operating angles. The clearance fit between the through hole and the bolt head ensures rotational freedom while preventing external dust from entering the transmission pair.

[0041] It is worth noting that in the field of mechanical transmission, the conventional application of worm gear pairs is that the worm is the driving component and the worm wheel is the driven component, such as in reducers and lifting mechanisms. This technical principle stems from the natural compatibility between the worm's lead angle and its frictional self-locking characteristics. This application, through structural reconstruction, sets the worm wheel as the active input component of an external operating unit, making the worm a passive actuator, thus subverting the classic driving logic of worm gear pairs.

[0042] According to traditional technology, the diameter of the worm gear is typically 3-5 times that of the worm. This significantly increases the lever arm length of the external operating part (hexagonal bolt head), allowing for a greater axial thrust on the worm when the operator applies the same torque. Actual measurement data shows that, under the same thrust requirement, the operating torque in the worm gear active mode is only 1 / 4-1 / 3 of that in the worm gear active mode, greatly reducing manual operation intensity. Furthermore, the radial arrangement of the worm gear allows the operating part to be exposed on the side of the equipment, avoiding the front and rear space required for traditional worm gear axial operation, and better adapting to the structural limitations of the densely arranged circumferential cutter heads in planing machines. When the worm gear rotates actively, the self-locking effect of the worm thread pair remains effective, resisting unexpected backlash caused by cutting vibration of the cutter box. When the worm gear rotates in the opposite direction, the operating torque acts directly on the worm gear tooth surface, generating an axial unlocking force through the decomposition of the tooth profile pressure angle, breaking through the self-locking critical condition and achieving controllable release.

[0043] Specifically, such as Figure 1 , 2 As shown, the cutter head 100 is provided with uniformly arranged cutter boxes. The cutter boxes can be locked and pushed out by the quick tool changer disclosed in this application. The quick tool changer includes an outer box 1, and a connecting rod frame 2 is provided inside the outer box 1. The connecting rod assembly includes a first guide rod 23, a worm gear 21 and a second guide rod 24 arranged in parallel. The first guide rod 23 and the second guide rod 24 are respectively located on both sides of the worm gear 21. The first guide rod 23 and the second guide rod 24 are respectively fixed to the left and right sides of the first guide rod 23 and the second guide rod 24. Linear bearings are provided on both the first guide rod 23 and the second guide rod 24. The two ends of the worm gear 21 are also fixedly connected to the first guide rod 251 and the second guide rod 252.

[0044] like Figure 5 As shown, the locking process of the tool box is as follows: When the worm gear 22 drives the worm 21 to rotate, and the worm 21 rotates and moves to the right relative to the worm gear 22, the connecting rod frame 2 moves synchronously with the worm 21 on the linear bearing. At this time, the locking rod 3, which passes through the longitudinal rod 252 at the right end of the worm 21, moves to the right until it passes through the corresponding through hole 11 in the outer box 1 and is inserted into the tool box locking hole that fits the outer box 1, so that the tool box is locked in the tool disc 100 and will not move up or down. The tool box is completely locked. At this time, the push hook is located in the opening of the outer box 1 and the locking rod 3 is located outside the outer box 1, which is the locking position of this device.

[0045] like Figure 6As shown, the process of ejecting the tool box is as follows: when the worm gear 22 drives the worm 21 to rotate, and the worm 21 rotates and moves to the left relative to the worm gear 22, the connecting rod frame 2 moves synchronously with the worm 21 on the linear bearing. A push-hook mechanism is hinged to the second longitudinal rod 252. The push-hook mechanism includes a control rod 41 hinged to the second longitudinal rod 252 and a hook 42 hinged to the end of the control rod 41 away from the first longitudinal rod 251. The outer box 1 has an opening corresponding to the push-hook mechanism. When the worm gear 22 drives the connecting rod frame 2 away from the opening, the bottom surface of the control rod 41 abuts against the lower side of the opening and slides. When the control rod 41 moves away from the opening, the hook 42 gradually tilts outward and hooks the side step of the knife box. At this time, the worm gear 21 continues to rotate, and the connecting frame continues to move away from the opening. At this time, the angle between the tail of the hook 42 and the upper side of the control rod 41 is about 180°. The angle will not continue to expand, so that the front end of the hook 42, the latch 421, retracts while applying a downward pushing force to the side step of the knife box. This ensures that the push-hook can push the outer box 1 out of the knife disc 100 a certain distance, making it convenient for the user to take it out. At this time, the push-hook is located outside the opening of the outer box 1, and the locking rod 3 is located inside the outer box 1, which is the unlocked and pushed-out position of this device.

[0046] like Figure 4 As shown, after the blade box is pushed out, the turbine reverses. At this time, the control lever 41 moves to the right. Since the bottom of the control lever 41 is always in contact with the lower end of the opening, as the connecting rod frame 2 moves closer to the blade box, the control lever 41 gradually tilts upward, causing the hook 42 to disengage from the side step of the blade box. The hook 42 then retracts into the opening of the outer box 1, and the worm gear 21 returns to the initial position. At this time, the push hook assembly 4 and the locking lever 3 are both located inside the outer box 1, which is the zero position of this device.

[0047] Example 2

[0048] This embodiment optimizes and improves the transmission mechanism based on Embodiment 1, replacing the original worm gear structure with a composite transmission system of gear rack and pinion and ratchet linkage. This reconfiguration of the mechanical transmission achieves a more efficient operating experience and more stable self-locking performance. While retaining the core functions of quick locking of the tool box and assisted ejection, the improved device overcomes the limitations of low efficiency and long operating stroke of worm gear transmission, making it particularly suitable for high-dust and high-vibration working environments.

[0049] In this embodiment, the core of the transmission mechanism consists of a main drive gear, a driven ratchet, and a rack. The main drive gear and the driven ratchet are coaxially connected via a one-way bearing. The rack is arranged parallel to the original worm gear position and meshes with the main drive gear on both sides. A T-shaped guide rail is machined on the back of the rack, which slides in conjunction with the guide groove on the inner wall of the outer box, replacing the guiding function of the original linear bearing. The external operating part is changed to a straight handle rocker arm structure. The end of the rocker arm is designed as a hexagonal prism insertion part, which is inserted into the keyway of the main drive gear and fixed in axial position by a limiting snap ring. An elastic pawl is provided on the outside of the driven ratchet. The pawl is fixed to the side wall of the outer box by a pin. The ratchet teeth are designed with a 70° inclination angle to form a one-way self-locking mechanism with the pawl. The push hook assembly is equipped with a transition connecting rod, one end of which is hinged to the end of the rack, and the other end is connected to the middle of the control rod, forming a two-stage lever amplification mechanism.

[0050] When the operator inserts the rocker arm and rotates it clockwise, the main drive gear drives the rack to move linearly to the right, pushing the connecting rod frame to extend the locking lever and lock the tool box. At this time, the one-way bearing allows the main drive gear and the driven ratchet to rotate relative to each other, and the pawl slides along the back of the ratchet teeth under the action of the spring, without generating resistance to the rotational movement. After the locking lever is fully extended, continuing to rotate the rocker arm allows for fine adjustment of the locking force. The tight fit between the T-shaped guide rail of the rack and the guide groove of the outer box ensures the accuracy of the movement trajectory. After locking is completed, the elastic pawl engages with the ratchet tooth groove to achieve mechanical hard limit. Even if external vibration or impact loads are applied to the tool box, the engagement between the pawl and the ratchet can effectively prevent the rack from retracting, completely eliminating the risk of locking failure.

[0051] When the blade holder needs to be replaced, rotating the rocker counterclockwise triggers the unlocking mechanism. The one-way bearing in this direction disconnects the main drive gear from the ratchet, causing the rack to move to the left and push down the control lever via the transition link. The transition link is designed to be half the length of the control lever, creating a 2:1 ratio between the rack's travel distance and the hook's extension stroke, significantly amplifying the extension force. The bottom surface of the control lever slides along the rounded edge of the outer box opening, forcing the hook to extend and engage with the blade holder step. Due to the two-stage lever mechanism, the operator only needs to apply a small rotational torque to generate sufficient extension force, easily overcoming the resistance between the blade holder and the blade disc. During the extension process, the pawl slides freely along the back of the ratchet teeth, without interfering with the unlocking action.

[0052] After the knife box is ejected, simply pull out the rocker arm to disengage the connector from the gear set, and manually pull the rack back to its initial position for quick reset. The push hook assembly automatically retracts into the outer box under the action of the reset spring, avoiding the cumbersome operation of traditional worm gear mechanisms that require multiple reverse rotations. The module design of the rack and gear is larger than that of the original worm gear, and with the double-sided involute tooth profile, the transmission efficiency is increased by about 40%, and the rotation angle per operation is reduced from 270° to 120°, significantly reducing the intensity of operation. The sliding pair of the T-shaped guide rail and guide groove uses oil-lubricated copper material, which is more suitable for sawdust environments than linear bearings, and the maintenance cycle is extended by more than 3 times.

[0053] This embodiment has several advantages over Embodiment 1: First, the mechanical hard self-locking of the ratchet mechanism completely solves the problem of reduced locking force due to wear after long-term use of the worm gear friction self-locking mechanism; second, the plug-in design of the straight shank rocker arm enables separation of man and machine, and removing the rocker arm during tool changes completely eliminates the risk of misoperation, meeting mechanical safety standards; third, the two-stage lever push-hook mechanism can produce a larger push displacement under the same operating force, making it particularly suitable for heavy-duty tool boxes with large locking hole depths. Actual testing shows that the improved device did not experience locking failure or push-out jamming during 1000 consecutive tool change cycles, significantly reducing the failure rate compared to Embodiment 1.

[0054] Furthermore, the modular design of the transmission system enhances maintenance convenience. The gear set and rack are mounted as independent modules within the outer housing via locating pins, allowing for quick and complete replacement when wear occurs, eliminating the need to adjust the worm gear meshing clearance as required in Example 1. The hardening treatment process on the rack surface makes its wear resistance significantly superior to the original worm material, and its service life under the same operating conditions is expected to be extended to more than 5 years.

Claims

1. A quick tool changer, characterized in that, include: The outer box (1) is provided with a through hole (11) corresponding to the knife box locking hole and a side opening (12). The movable linkage frame (2) is located inside the outer box and includes parallel worm gears (21) and a guide mechanism; The worm gear (22) is fitted to the worm and partially exposed outside the outer box, the exposed part including an external operating part (221). The locking rod (3) is coaxially arranged with the worm gear (21) and moves with the connecting rod frame, and has an extended state that extends into the locking hole of the knife box; The push hook assembly (4) is hinged to the connecting rod frame (2) and its end passes through the lateral opening (12), and has an extended state that engages with the knife box step.

2. The quick tool changer according to claim 1, characterized in that: The guiding mechanism includes guide rod one (23) and guide rod two (24) arranged parallel to each other on both sides of the worm gear, and the two ends are connected by longitudinal connecting rods (25) to form a rectangular frame structure.

3. The quick tool changer according to claim 2, characterized in that: The longitudinal connecting rod (25) includes a longitudinal rod one (251) away from the lateral opening (12) and a longitudinal rod two (252) close to the lateral opening (12); the two ends of the worm (21) are connected to the longitudinal connecting rod by threaded pairs.

4. The quick tool changer according to claim 1, characterized in that: The external operating part (221) has a hexagonal bolt head structure, and its maximum outer diameter is larger than the diameter of the corresponding through hole of the outer box.

5. The quick tool changer according to any one of claims 1-4, characterized in that: The push-hook component (4) includes: The control rod (41) is hinged to the linkage frame, and its bottom surface slides in contact with the inner wall of the outer box. The hook (42) is hinged to the front end of the control lever, and the end is provided with a bayonet (421) that matches the step of the knife box. The bent part of the hook (42) is provided with a switching hinge point (43) that is hinged to the bottom of the outer box on the side near the control rod.

6. The quick tool changer according to claim 5, characterized in that: The angle α between the hook (42) and the outer side of the control rod is within 180°.

7. The quick tool changer according to claim 1, characterized in that: When the worm gear drives the worm to rotate in the forward direction, the locking rod (3) extends out from the outer box through hole, and the push hook assembly (4) is completely stored in the outer box.

8. The quick tool changer according to claim 1, characterized in that: When the worm gear drives the worm to rotate in the opposite direction, the locking rod (3) retracts into the outer box, and the hook body (42) of the push hook assembly (4) extends outward and hooks the step of the card box.

9. The quick tool changer according to claim 5, characterized in that: The inner bottom of the side opening (12) is provided with a rounded edge (13) that slides in contact with the bottom surface of the control rod (41). The rounded edge (13) is higher than the linkage hinge point (14) between the control rod (41) and the linkage frame (2).

10. The quick tool changer according to claim 2, characterized in that: Rolling bearings (26) are provided on both sides of the worm gear (22), and linear bearings (27) are provided on both the guide rod one and the guide rod two.

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