A rod-type spring buffer mechanism with radial forged chuck

Abstract

This invention discloses a rod-type spring buffer mechanism for a radial forging chuck, comprising an inner sleeve, a worm gear, a worm, and several circumferentially distributed spring rods. One end of each spring rod is fixed to the tailstock, and the other end is connected to the worm gear. This mechanism places the buffer point between the worm gear and the inner sleeve, utilizing the bending deformation of the spring rods to absorb forging impact energy. This invention offers advantages such as strong high-frequency adaptability, good transmission system protection, and adjustable buffering force. Furthermore, this invention discloses two optimized embodiments: a spring rod structure with fixed supports at both ends and a layered buffer structure with added compression spring groups; a switching mechanism that allows switching between the two buffering methods; and a continuously variable speed control system for adapting to high-frequency impacts, further improving the performance and reliability of the mechanism.

Description

Technical Field

[0001] This invention relates to the field of radial forging collet buffers, and more specifically to a rod-type spring group buffer mechanism for a radial forging collet. Background Technology

[0002] In radial forging equipment, the billet is subjected to high-frequency impacts from four forging hammers during its rotational motion, causing the billet's rotational motion to be impeded for a short period and resulting in a sharp drop in rotational speed. To ensure the normal operation of the chuck and transmission system, the chuck needs an effective rotary buffer mechanism to absorb and buffer the huge torque peaks generated by these high-frequency impacts. However, existing technical solutions mainly have the following technical problems: For example, some existing technologies use disc springs or leaf springs for buffering, and their buffering mechanisms are usually located at one end of the worm gear and between the worm gear and the motor, which is far from the impact source. Because the transmission chain of such mechanisms is long and relies on the elastic deformation and friction of the components, their response speed has inherent limitations. The chuck cannot restore normal rotational speed in a very short time, the billet rotational speed lags during forging, and the buffer cannot be reset in time. This leads to a mismatch between the billet rotational speed and the forging frequency during the forging process, reduced forging accuracy, and even the inability of the buffer to reset in time and accumulate, causing the impact force to be directly transmitted to the worm gear, worm, motor and other transmission components, causing overload of the transmission system. Over time, the stress concentration and fatigue effect caused by high-frequency impacts will lead to premature wear or even damage to the transmission components, seriously affecting the stability and service life of the equipment. Summary of the Invention

[0003] The purpose of this invention is to provide a rod-type spring group buffer mechanism for a radial forging chuck, which aims to solve the problems of limited response speed and inability to effectively cope with high-frequency impacts in the prior art, resulting in reduced forging accuracy, overload of the transmission system, and fatigue damage of parts.

[0004] To solve the above-mentioned technical problems, the present invention specifically provides the following technical solution:

[0005] A radial forged collet rod-type spring buffer mechanism includes:

[0006] The inner sliding sleeve has a rod-shaped structure;

[0007] Two bearing mounting rings are fixedly installed on the outer sides of both ends of the inner sleeve;

[0008] Two bearings are respectively fixedly sleeved on the outside of two bearing mounting rings;

[0009] The worm gear is sleeved on the outside of the inner sleeve, and the worm gear is axially limited to the middle of the inner sleeve.

[0010] The worm is located outside the worm wheel and the two mesh with each other;

[0011] A plurality of spring rods are evenly distributed circumferentially on the outer side of the inner sliding sleeve. Each spring rod is parallel to the inner sliding sleeve. One end of each spring rod is inserted through one of the bearing mounting rings, and the other end is mechanically connected to the worm gear. The spring rod transmits the torque of the worm gear through the axial elastic deformation of its rod body to achieve the mechanical connection between the worm gear and the inner sliding sleeve.

[0012] The tailstock is fitted onto the outer side of one end of the inner sliding sleeve and is located on the side of one of the bearing mounting rings away from the worm gear. All the spring rods are fixedly connected to the tailstock at one end through the bearing mounting ring.

[0013] Furthermore, all the spring rods pass through the worm gear, and their two ends are respectively inserted into the two bearing mounting rings.

[0014] Furthermore, an annular groove is provided on the side of the worm gear away from the tailstock, and a plurality of first limiting portions extending radially are formed on the inner wall of the annular groove. A first through hole for the inner sliding sleeve to pass through is formed at the center of the annular groove, and the annular groove and the first through hole are coaxial.

[0015] An inner support disk coaxial with the worm gear is provided in the annular groove. The inner support disk is fixedly sleeved on the outside of the inner sliding sleeve. A plurality of second limiting parts extending radially outward are formed at the outer edge of the inner support disk. The number of the second limiting parts is matched with the number of the first limiting parts. Each first limiting part and the corresponding second limiting part are spaced apart from each other in the circumferential direction to form an installation chamber between them.

[0016] Each of the mounting chambers is provided with a first spring, the axis of the first spring being perpendicular to the radial direction of the worm gear, and its two ends respectively abutting against the circumferential force-bearing surfaces of the first limiting part and the second limiting part, so as to transmit and buffer torque;

[0017] An annular end cap for covering all the mounting chambers is fixed to the outside of the annular groove.

[0018] Furthermore, each of the first limiting part and the second limiting part has an arc-shaped groove formed on both sides in the radial direction, and each of the first springs has a positioning block at both ends. The positioning block forms a positioning protrusion extending into the inside of the first spring on one side close to the first spring, and a semi-cylindrical wall structure that slides with the arc-shaped groove is formed on the side of the positioning block away from the positioning protrusion.

[0019] Furthermore, the inner sliding sleeve is formed by coaxially connecting the left half shaft and the right half shaft. Both the left half shaft and the right half shaft are cylindrical. The diameter of the right half shaft is smaller than that of the left half shaft. A stepped portion is formed at the connection between the left half shaft and the right half shaft for the worm gear to abut against. A limiting bushing is provided on the outer side of the right half shaft. The limiting bushing is located between the worm gear and the bearing mounting ring installed at the outer end of the right half shaft. The two ends of the limiting bushing abut against the worm gear and the bearing mounting ring, respectively.

[0020] Furthermore, all the spring rods are fixedly connected to an annular insert at the end near the worm gear. Several protruding inserts are formed on the outer edge of the annular insert, evenly distributed around its circumference. A sleeve ring is formed on the side of the worm gear corresponding to the annular insert. Several slots are formed on the inner wall of the sleeve ring, which are slidably inserted into each of the protruding inserts. An angled guide portion is formed on the side of each protruding insert facing the slot.

[0021] Furthermore, the rod-type spring buffer mechanism also includes a power unit and a shift fork. The shift fork is vertically connected to the power output end of the power unit, which is used to output linear push-pull force. The power output end of the power unit is parallel to the inner sliding sleeve, and an annular groove for the shift fork to connect is formed on the outer side of the tailstock.

[0022] A composite buffer mechanism with a rod-type spring buffer mechanism includes the aforementioned rod-type spring buffer mechanism, and further includes a driving continuously variable transmission (CVT), a driven CVT, a transmission belt connecting the driving CVT and the driven CVT, a speed regulating mechanism for actively adjusting the pitch circle diameter of the driving CVT, and a second spring for passively adjusting the pitch circle diameter of the driven CVT. The driven CVT is coaxially fixed to one end of the worm gear, and the driving CVT is coaxially fixed to a power shaft for driving the worm gear to rotate.

[0023] Furthermore, one end of each spring rod connected to the worm gear passes through the worm gear and is inserted into another bearing mounting ring. The inner support plate has a plurality of second through holes evenly distributed circumferentially for the corresponding spring rods to pass through. The second through holes are configured to allow the spring rods to deform within them.

[0024] The beneficial effects of this invention are:

[0025] 1. High-frequency adaptability: This invention uses a rod-type spring assembly between the worm gear and the inner sleeve as a buffer mechanism, making the buffer point closer to the impact source. When the rotational motion of the billet is obstructed, this mechanism can quickly activate the buffer, effectively absorbing high-frequency impact energy and significantly improving the equipment's adaptability to high-frequency forging conditions;

[0026] 2. Transmission System Protection: This invention places the buffering function at the forefront, ensuring that the worm gear, worm, and motor can continue to rotate even when the billet rotation is obstructed. Compared with existing technologies, this invention avoids the impact force directly acting on downstream components of the transmission chain, thereby better protecting the entire transmission system and extending its service life.

[0027] 3. Adjustable buffer force: The number of spring rods used in this invention can be increased or decreased according to actual needs, thereby conveniently adjusting the size of the buffer force, so that the mechanism can flexibly adapt to different forging intensities and workpiece process requirements. Attached Figure Description

[0028] To more clearly illustrate the embodiments of the present invention or the technical solutions in 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 merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0029] Figure 1 This is a three-dimensional structural diagram of the first embodiment of the present invention;

[0030] Figure 2 This is a three-dimensional structural diagram of the second embodiment of the present invention;

[0031] Figure 3 This is an exploded three-dimensional structural diagram of the second embodiment of the present invention;

[0032] Figure 4 This is a planar sectional view of the third embodiment of the present invention;

[0033] Figure 5 for Figure 4 A sectional view along line AA in the middle;

[0034] Figure 6 for Figure 4 Plan sectional view along line BB;

[0035] Figure 7 for Figure 4 A sectional view along the CC line;

[0036] Figure 8 This is a schematic diagram illustrating the principle of the continuously variable transmission (CVT) adjustment of the present invention.

[0037] Figure 9 This is a schematic diagram of the planar structure of the fourth embodiment of the present invention;

[0038] Figure 10 for Figure 9 A planar sectional view along line DD;

[0039] The labels in the diagram represent the following: 1-Inner sliding sleeve; 2-Bearing mounting ring; 3-Bearing; 4-Worm gear; 5-Worm; 6-Spring rod; 7-Tailstock; 8-Mounting chamber; 9-First limiting part; 10-Inner support plate; 11-Second limiting part; 12-First spring; 13-Annular end cap; 14-Positioning block; 15-Positioning protrusion; 16-Limiting bushing; 17-Annular insert; 18-Protruding insert; 19-Sleeve ring; 20-Annular groove; 21-Transmission belt; 22-Second spring; 23-Drive shaft; 24-Driving continuously variable transmission (CVT); 25-Driven CVT; 26-Second through hole. Detailed Implementation

[0040] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0041] Reference Figures 1 to 8 The illustrated radial forging chuck with rod-type spring buffer mechanism aims to provide a fast-responding and reliable solution suitable for high-frequency forging. The core of this mechanism lies in the organic integration of buffering and transmission functions to cope with the harsh working conditions under high-frequency impact, and by placing the buffer point forward, more effective protection is achieved for the entire transmission chain.

[0042] The main body of the mechanism includes a hollow rod-shaped inner sleeve 1, which serves as a central shaft for mounting grippers to hold workpieces. Two bearing mounting rings 2 are fixedly mounted on the outer sides of both ends of the inner sleeve 1, and bearings 3 are fitted onto them. A worm gear 4 is fitted into the middle of the inner sleeve 1 and is axially limited by a stepped portion on the inner sleeve 1 to ensure its positional stability. A worm 5 is located outside the worm gear 4 and meshes with it, forming the main power input and transmission path. To achieve buffering, several resilient solid spring rods 6 are evenly distributed circumferentially along the outer side of the inner sleeve 1, each spring rod 6 being parallel to the inner sleeve 1. One end of each spring rod 6 is inserted through one of the bearing mounting rings 2, and the other end is connected to the worm gear 4. On the outer side of one end of the inner sleeve 1, on the side of the bearing mounting ring 2 away from the worm gear 4, a tailstock 7 is provided, to which all the spring rods 6 penetrating the bearing mounting ring 2 are fixedly connected. When forging occurs and the inner sleeve 1 (central shaft) is obstructed, the worm gear 4 continues to rotate due to the continuous drive of the worm 5, causing relative rotation between the worm gear 4 and the inner sleeve 1. This causes the spring rod 6 to bend and deform, thereby absorbing the impact energy and achieving buffering. This structure, which places the spring rod 6 between the worm gear 4 and the inner sleeve 1, allows the worm gear 4 to drive the inner sleeve 1 to rotate through an elastic element. Its function is to ensure that the motor, worm gear 4, and worm 5 can continue to rotate during the short-term obstruction and stop of the workpiece's rotation. Compared to the existing technology that places the buffering point between the worm 5 and the motor, this invention places the buffering mechanism closer to the impact source (i.e., the clamped workpiece), activating the buffering mechanism at the first moment the workpiece is obstructed. This effectively protects the entire worm gear 4 and worm 5 transmission system, preventing the impact force from directly acting on downstream components of the transmission chain, and significantly improving the system's stability and service life. To improve the reliability of the axial limiting of the worm gear 4, the inner sleeve 1 can be formed by coaxially connecting the left and right half-shafts, wherein the diameter of the right half-shaft is smaller than that of the left half-shaft, and a stepped portion is formed at the connection for the worm gear 4 to abut against. In addition, a limiting sleeve 16 can be fitted on the outside of the right half-shaft, with its two ends abutting against the worm gear 4 and another bearing mounting ring 2, respectively, thereby further limiting the axial displacement of the worm gear 4.

[0043] To provide more stable cushioning performance, the connection method of the spring rod 6 can be optimized. Specifically, one end of the spring rod 6 connected to the worm gear 4 can be designed to pass through the worm gear 4 and be inserted into another bearing mounting ring 2, thus providing stable rigid support at both ends of the spring rod 6. When the worm gear 4 rotates relative to the inner sleeve 1, it applies a force to the middle of the spring rod 6, causing it to bend and deform to achieve cushioning. This structure with fixed support at both ends allows the bending deformation of the spring rod 6 to be controlled and uniform.

[0044] To further improve the system's impact resistance, an independent buffer mechanism can be added to the worm gear 4 as a supplement, forming a layered buffer. Specifically, an annular groove is provided on the side of the worm gear 4 away from the tailstock 7, and the inner wall of the annular groove forms a first limiting part 9 extending radially. An inner support plate 10 is fixedly sleeved on the inner sliding sleeve 1 and located in the annular groove, and its outer edge forms a second limiting part 11 extending radially, corresponding one-to-one with the first limiting part 9. A mounting chamber 8 is formed between the first limiting part 9 and the second limiting part 11, and a first spring 12 is installed therein. The axis of the first spring 12 is perpendicular to the radial direction of the worm gear 4, and its two ends abut against the side walls of the first limiting part 9 and the second limiting part 11, respectively. When the impact torque is too large, the relative rotation between the worm gear 4 and the inner sliding sleeve 1 will compress these springs, causing them to absorb most of the impact energy through elastic deformation. At this time, the spring rod 6 mechanism acts as a secondary buffer, absorbing the remaining energy. It is worth analyzing in depth that this first-stage buffer structure not only effectively reduces the peak torque, but more importantly, it greatly reduces the shear force of the worm gear 4 on the spring rod 6. In the original design, the spring rod 6 directly bears the driving force of the worm gear 4, and especially at the moment of impact, a large shear stress is generated at its connection. However, this design adds a first spring 12 as a first-stage buffer, and most of the impact force is absorbed by the elastic deformation of the compression spring. The torque transmitted to the spring rod 6 is effectively reduced, thereby significantly reducing the shear stress of the spring rod 6 and its connection, fundamentally solving the problem of high-frequency shear fatigue, and greatly improving the service life of the spring rod 6. To further define this buffer mechanism, arc-shaped grooves can be formed on both sides of the first limiting part 9 and the second limiting part 11, and positioning blocks 14 with positioning protrusions 15 and semi-cylindrical wall structures can be provided at both ends of each first spring 12 to achieve sliding fit with the grooves, ensuring stable spring force and accurate positioning.

[0045] To facilitate switching between different buffer modes, a switching mechanism can be further designed. The ends of all spring rods 6 closest to the worm gear 4 are fixedly connected to an annular insert 17, with a protruding insert 18 formed on the outer edge of the insert. On the side of the worm gear 4 corresponding to the annular insert 17, a sleeve ring 19 is formed, with several grooves on the inner wall of the sleeve ring 19 corresponding one-to-one with the protruding inserts 18. When the shift fork pushes the tailstock 7 to move axially along the inner sliding sleeve 1, the protruding inserts 18 of the annular insert 17 slide into the grooves of the sleeve ring 19, thereby achieving coaxial connection between the spring rods 6 and the worm gear 4. Each protruding insert 18 has an angled guide on the side facing the groove to facilitate insertion and positioning. The switching mechanism also includes a power unit and a shift fork, which is vertically connected to the power output end of the power unit for outputting linear push-pull force. The shift fork is connected to the annular groove 20 on the outside of the tailstock 7. When the power unit is started, the shift fork pushes the tailstock 7 to move axially along the inner sliding sleeve 1, thereby causing the annular insert 17 to disengage or engage with the groove of the worm gear 4. This switching should be performed during the non-forging interval period to avoid switching under high impact loads, thus ensuring the safety and stability of the system.

[0046] Finally, to ensure smoother regulation of speed fluctuations during forging, this mechanism can be further integrated with a continuously variable transmission (CVT) system. (See reference...) Figure 8As shown, this system includes a driving continuously variable pulley 24, a driven continuously variable pulley 25, and a transmission belt 21 connecting the two. The driven continuously variable pulley 25 is coaxially fixed to one end of the worm gear 5, and the driving continuously variable pulley 24 is coaxially fixed to a power shaft 23 that drives the worm gear 5 to rotate. This power shaft 23 is actually the output shaft of the motor used to drive the worm gear 5 in a radial forging chuck. The continuously variable adjustment system described in this invention is installed between these two. The core principle of this system is to change the transmission ratio by utilizing the change in the meshing position of the tapered pulley and the specially designed wide V-shaped transmission belt 21 in the tapered disc. As shown, both the driving continuously variable pulley 24 and the driven continuously variable pulley 25 consist of two tapered discs. When the speed regulating mechanism applies a speed regulating force F, causing the sliding disc of the driving continuously variable pulley 24 to move away from the belt, the belt pitch line will move radially outward towards the driven continuously variable pulley 25 due to the inertial motion of the driven continuously variable pulley 25. When the conveyor belt is tightened in the driving continuously variable transmission (CVT) pulley 24, the pitch circle diameter of the driving CVT 24 decreases, while the pitch circle diameter of the driven CVT 25 increases, thereby changing the transmission ratio. Conversely, when the speed regulating force F moves the sliding disc of the driving CVT 24 in the direction of belt tightening, the engagement arc of the conveyor belt on the driving CVT 24 widens, causing the belt pitch line to move radially outward from the driving CVT 24. Simultaneously, the second spring 22 of the sliding disc of the driven CVT 25 is compressed until the transmission ratio changes and balance is re-established. The timing of applying this speed regulating force F should match the forging frequency of the forging system, applied just before each forging impact. This pre-reduced transmission ratio through the continuously variable transmission system allows the driven CVT 25 to have a larger torque output when resisted, better buffering the impact. To achieve this timing matching, sensors, such as proximity switches or force sensors, can be installed on the forging mechanism to acquire the forging frequency signal, and the control system can use this signal to precisely control the timing of applying the speed regulating force F.

[0047] Furthermore, based on the aforementioned layered buffering technology, this invention can provide a further optimized embodiment to achieve superior buffering performance. This embodiment, based on the buffering mechanism of the second embodiment, designs one end of the spring rod 6 connected to the worm gear 4 to pass through the worm gear 4 and be inserted into another bearing mounting ring 2, thereby providing stable rigid support at both ends of the spring rod 6. To enable these two buffering mechanisms to work together, the inner support disk 10 has several second through holes 26 evenly distributed circumferentially. These second through holes 26 are configured to allow the spring rod 6 to bend within them when the worm gear 4 rotates relative to the inner sliding sleeve 1. In this structure, when a forging impact occurs, the compression spring assembly acts as the primary buffer, responsible for rapidly reducing the peak torque; subsequently, the spring rod 6 assembly with fixed supports at both ends acts as the secondary buffer, absorbing the remaining energy through more controllable and uniform bending deformation. This design fully utilizes the advantages of both buffering mechanisms, further reducing the shear stress on the spring rod 6, and also improving the system's impact resistance and service life.

[0048] The above embodiments are merely exemplary embodiments of the present invention and are not intended to limit the present invention. The scope of protection of the present invention is defined by the claims. Those skilled in the art can make various modifications or equivalent substitutions to the present invention within its spirit and scope of protection, and such modifications or equivalent substitutions should also be considered as falling within the scope of protection of the embodiments of the present invention.

Claims

1. A rod-type spring buffer mechanism for a radial forged chuck, characterized in that, include: The inner sliding sleeve (1) has a rod-shaped structure; Two bearing mounting rings (2) are fixedly installed on the outer sides of both ends of the inner sleeve (1); Two bearings (3) are respectively fixedly sleeved on the outside of two bearing mounting rings (2); The worm gear (4) is sleeved on the outside of the inner sleeve (1), and the worm gear (4) is axially limited to the middle part of the inner sleeve (1); The worm (5) is located outside the worm wheel (4) and the two mesh; A plurality of spring rods (6) are evenly distributed circumferentially on the outer side of the inner sleeve (1). Each spring rod (6) is parallel to the inner sleeve (1). One end of each spring rod (6) is inserted through one of the bearing mounting rings (2), and the other end is mechanically connected to the worm gear (4). The spring rod (6) transmits the torque of the worm gear (4) through the axial elastic deformation of its rod body to realize the mechanical connection between the worm gear (4) and the inner sleeve (1). Tail seat (7) is sleeved on the outer side of one end of the inner sliding sleeve (1) and located on the side of one of the bearing mounting rings (2) away from the worm gear (4). All the spring rods (6) are fixedly connected to the tail seat (7) through one end of the bearing mounting ring (2). The worm gear (4) is provided with an annular groove on the side away from the tailstock (7). Several first limiting parts (9) extending radially outward are formed on the inner wall of the annular groove. A first through hole for the inner sliding sleeve (1) to pass through is formed at the center of the annular groove. The annular groove and the first through hole are coaxial. An inner support disk (10) coaxial with the worm gear (4) is provided in the annular groove. The inner support disk (10) is fixedly sleeved on the outside of the inner sliding sleeve (1). A plurality of second limiting parts (11) extending radially outward are formed at the outer edge of the inner support disk (10). The number of the second limiting parts (11) is matched with the number of the first limiting parts (9). Each first limiting part (9) and the corresponding second limiting part (11) are spaced apart from each other in the circumferential direction to form an installation chamber (8) between them. Each of the mounting chambers (8) is provided with a first spring (12), the axis of the first spring (12) is perpendicular to the radial direction of the worm gear (4), and its two ends respectively abut against the circumferential force-bearing surfaces of the first limiting part (9) and the second limiting part (11) to transmit and buffer torque; An annular end cap (13) for covering all the mounting chambers (8) is fixed to the outside of the annular groove.

2. The rod-type spring group buffer mechanism for a radial forged chuck according to claim 1, characterized in that, All the spring rods (6) pass through the worm gear (4), and their two ends are respectively inserted into the two bearing mounting rings (2).

3. The rod-type spring buffer mechanism for a radial forged chuck according to claim 1, characterized in that, Each of the first limiting part (9) and the second limiting part (11) has an arc-shaped groove on both sides in the radial direction. Each of the first springs (12) has a positioning block (14) at both ends. The positioning block (14) forms a positioning protrusion (15) that extends into the inside of the first spring (12) on one side of the first spring (12). The positioning block (14) has a semi-cylindrical wall structure that slides with the arc-shaped groove on the side away from the positioning protrusion (15).

4. The rod-type spring group buffer mechanism for a radial forged chuck according to claim 1, characterized in that, The inner sliding sleeve (1) is formed by the coaxial connection of the left half shaft and the right half shaft. Both the left half shaft and the right half shaft are cylindrical. The diameter of the right half shaft is smaller than that of the left half shaft. A stepped part is formed at the connection between the left half shaft and the right half shaft for the worm gear (4) to abut against. A limiting bushing (16) is provided on the outer side of the right half shaft. The limiting bushing (16) is located between the worm gear (4) and the bearing mounting ring (2) installed at the outer end of the right half shaft. The two ends of the limiting bushing (16) abut against the worm gear (4) and the bearing mounting ring (2) respectively.

5. The rod-type spring buffer mechanism for a radial forged chuck according to claim 1, characterized in that, All the spring rods (6) are fixedly connected to an annular insert (17) at one end near the worm gear (4). Several protruding inserts (18) are formed on the outer edge of the annular insert (17) and are evenly distributed around its circumference. A sleeve ring (19) is formed on the side of the worm gear (4) corresponding to the annular insert (17). Several slots are formed on the inner wall of the sleeve ring (19) and are slidably inserted into each of the protruding inserts (18). An angled guide portion is formed on the side of each protruding insert (18) facing the slot.

6. The rod-type spring group buffer mechanism for a radial forged chuck according to claim 5, characterized in that, The rod-type spring buffer mechanism also includes a power unit and a shift fork. The shift fork is vertically connected to the power output end of the power unit. The power output end of the power unit is used to output linear push and pull force. The power output end of the power unit is parallel to the inner sliding sleeve (1). An annular groove (20) for connecting the shift fork is formed on the outer side of the tailstock (7).

7. The rod-type spring buffer mechanism for a radial forged chuck according to claim 1, characterized in that, All the spring rods (6) have one end connected to the worm gear (4) passing through the worm gear (4) and inserted into another bearing mounting ring (2); The inner support plate (10) has a plurality of second through holes (26) evenly distributed in the circumferential direction for the corresponding spring rods (6) to pass through, and the second through holes (26) are configured to allow the spring rods (6) to deform therein.

8. A composite buffer mechanism comprising a rod-type spring buffer mechanism as described in any one of claims 1 to 7, characterized in that, The composite buffer mechanism also includes an active continuously variable wheel (24), a driven continuously variable wheel (25), a transmission belt (21) connecting the active continuously variable wheel (24) and the driven continuously variable wheel (25), a speed regulating mechanism for actively adjusting the pitch circle diameter of the active continuously variable wheel (24), and a second spring (22) for passively adjusting the pitch circle diameter of the driven continuously variable wheel (25). The driven continuously variable wheel (25) is coaxially fixed to one end of the worm (5), and the active continuously variable wheel (24) is coaxially fixed to a power shaft (23) for driving the worm (5) to rotate.

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