A bow fatigue detection device and detection method

Abstract

This invention provides a bow fatigue testing device and method, comprising: a frame; a bow mounting mechanism for mounting the bow to be tested; a drawing mechanism for drawing the bow and releasing the bowstring; and a load mechanism for applying a load force simulating that of an arrow to the bowstring, including: a main slide rail; a counterweight slider matching the weight of the arrow and horizontally mounted on the main slide rail; a buffer assembly disposed at the front end of the main slide rail and located on the movement path of the counterweight slider, for absorbing the kinetic energy generated by the high-speed sliding counterweight slider; and a load shifting assembly including a lever for shifting the counterweight slider backward so that the counterweight slider abuts against or approaches the bowstring in a fully drawn state. This bow fatigue testing device is compact in structure, simulates an arrow through load, eliminates the need for repeated drawing and manual intervention, achieves fully automatic testing, and has high testing efficiency.

Description

Technical Field

[0001] This invention relates to a testing device, and more particularly to a bow fatigue testing device and testing method. Background Technology

[0002] Currently, the traditional method for fatigue life testing of bows in the industry is usually through continuous test firing. This method simulates the actual archery process, with manual or simple mechanical devices repeatedly nocking, drawing, and releasing the arrow to complete a full firing cycle. After each cycle, the tester needs to observe the bow for signs of fatigue damage such as cracks or permanent deformation, and record the maximum number of draws it can withstand.

[0003] However, existing fatigue testing methods based on continuous test firing have significant drawbacks in practical operation. First, the placement and installation of the arrows is time-consuming and labor-intensive. Before the test begins, the arrows to be tested need to be precisely fixed on the test stand; after each simulated firing, because the arrows may be fired or detached, operators have to repeatedly perform a series of tedious manual operations such as picking up the arrows, re-nocking them, and adjusting their positions. This high frequency of manual intervention not only greatly increases the workload of the operators but also makes the entire testing process lengthy and inefficient.

[0004] In conclusion, how to simplify the installation and operation process, improve testing efficiency, and reduce labor costs while conducting accurate fatigue simulation tests on bows is a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to provide a bow fatigue detection device and method with a compact structure, which simulates a bow and arrow under load, eliminates the need for repeated bow-loading and manual intervention, and has high detection efficiency.

[0006] This invention provides a bow fatigue detection device, comprising: Rack 1; The bow mounting mechanism 4 is mounted on the frame 1 and is used to mount the bow 9 to be tested; The bow-drawing mechanism 2 is used to hook the bowstring in the first position and pull it back to the second position before releasing it; Loading mechanism 3, used to apply a simulated bow and arrow load force to the bowstring, includes: The main slide rail 31 is installed on the frame 1. The main slide rail 31 is horizontally arranged and its length direction is parallel to the front and rear orientation of the bow body 9. The counterweight slider 33 is matched with the weight of the bow and arrow and is horizontally mounted on the main slide rail 31; A buffer component is disposed at the front end of the main slide rail 31 and located on the movement path of the counterweight slider 33, for absorbing the kinetic energy generated by the high-speed sliding counterweight slider 33. The load shifting assembly includes a lever 351 that can slide along the length direction parallel to the main slide rail 31. The lever 351 is used to move the counterweight slider 33 backward so that the counterweight slider 33 abuts against or approaches the bowstring in a fully drawn state.

[0007] Furthermore, the counterweight slider 33 is provided with a lever 331 corresponding to the lever 351. When the counterweight slider 33 contacts the buffer assembly, the front end of the lever 331 has space and can accommodate the lever 351; and when the lever 351 completes the movement of the counterweight slider 33, it returns to the space.

[0008] Furthermore, the main slide rail 31 includes two parallel rods with a gap between them, forming a working area 310 that can accommodate the bowstring, and the counterweight slider 33 is slidably fitted within the working area 310.

[0009] Furthermore, the main slide rail 31 is provided with a front cylinder 321 and a rear cylinder 322 at both ends, the buffer assembly is disposed in the front cylinder 321, and the rear cylinder 322 is provided with a detection assembly for detecting whether the counterweight slider 33 has moved into place; the buffer assembly includes a buffer body 53 disposed in the front cylinder and capable of contacting the counterweight slider, the buffer body 53 being made of ultra-high molecular weight polyethylene fiber.

[0010] Furthermore, the bow-drawing mechanism 2 includes: The string assembly includes a string slider 22 that is horizontally slidably mounted on the frame 1 and a string cylinder 221 for driving the string slider 22 to slide horizontally. The trigger assembly, mounted on the drawbar slider 22, includes a trigger mounting base 24, on which a trigger latch 26 and a locking block 27 are rotatably mounted. The trigger latch 26 is provided with a drawbar groove 260. An elastic linkage is provided between the trigger latch 26 and the locking block 27, enabling linkage between the trigger latch 26 and the locking block 27. The line connecting the pivot of the trigger latch 26 and the locking block 27 forms a balance line. The force generated by the bowstring in the string groove 260 can cause the trigger latch 26 to rotate and the elastic linkage to cross the balance line, thereby causing the elastic linkage to generate driving forces in different directions on the trigger latch 26, realizing the hooking and releasing of the string. A safety interlock assembly, mounted on the trigger mounting base, is used to radially limit the trigger latch and / or the locking block to achieve locking and fixation.

[0011] Furthermore, the trigger latch 26 is provided with a drawstring groove 260, and the trigger latch 26 can rotate between a first angle and a second angle; When at the first angle, the drawstring groove 260 is tilted forward, and the elastic linkage is located on the first side of the balance line, causing the drawstring groove 260 to have a tendency to rotate forward. When at the second angle, the drawstring groove 260 is tilted backward, and the elastic linkage is located on the second side of the balance line, causing the drawstring groove 260 to have a tendency to rotate backward.

[0012] Furthermore, the elastic linkage includes a strip-shaped guide groove 271 formed on the locking block 27 and a pin 263 fixed on the trigger latch 26. The pivot of the locking block 27 is located on the extension line of the strip-shaped guide groove 271. The axis of the pin 263 is parallel to the rotation axis of the trigger latch 26 and the locking block 27 and is slidably fitted in the strip-shaped guide groove 271. A spring 273 is provided in the strip-shaped guide groove 271. The spring 273 causes the pin 263 to have a tendency to move away from the pivot of the locking block 27.

[0013] Furthermore, the safety interlocking assembly includes a trigger 28 rotatably mounted on the trigger mounting base 24 and a trigger cylinder 251 for driving the trigger 28 to rotate. The side wall of the trigger 28 is provided with a locking groove 280, which can radially limit the end of the locking block 27 and lock and fix the trigger buckle 26 in the hooked state.

[0014] Furthermore, the bow mounting mechanism 4 includes: The base plate 41 is fixed and installed on the frame 1; The bow body fixing plate 42 is slidably installed on the fixing base plate 41 along the length direction parallel to the main slide rail; The mounting components are mounted on the bow body fixing plate 42 for fixing the bow body 9; A limiting component is installed on the fixed base plate 41 and located at the rear end of the bow body fixing plate 42, and is used to limit the sliding stroke of the rear end of the bow body fixing plate 42. The elastic element 46 is disposed between the fixed base plate 41 and the bow body fixing plate 42, so that the bow body fixing plate 42 has a backward movement tendency, and is used to absorb the vibration generated by the bow body 9 after the bowstring is released.

[0015] Furthermore, the elastic element is a gas spring.

[0016] Meanwhile, the present invention also provides a detection method for a bow fatigue detection device, which includes the following steps: S1. Clamping: Fix the bow body 9 onto the bow body mounting mechanism 4; S2, draw the bow; S21, the draw string cylinder 221 drives the draw string slider 22 to move forward, which in turn drives the trigger assembly to move forward synchronously; S22. Hooking the string: The string groove 260 of the trigger 26 contacts the stationary bowstring. The bowstring pushes against the rear wall of the string groove 260. Under the reaction force of the bowstring, the trigger 26 is forced to rotate backward. As the trigger 26 rotates, the elastic linkage is compressed or stretched. When the rotation angle exceeds the critical point, that is, when it crosses the balance line, the elastic force of the elastic linkage reverses, changing from resisting rotation to assisting rotation, driving the trigger 26 to quickly rotate backward into place, locking the bowstring into the string groove 260, thus hooking the string. S23, Locking: The safety interlock component is activated, radially limiting the trigger latch 26 or the linkage lock block 27 to prevent the trigger latch 26 from rotating forward. S24. To draw the bow, the string-drawing cylinder 221 drives the string-drawing slider 22 to move backward, starting to draw the bow until it moves to the second position. S3, Load loading; S31, the load shifting cylinder 34 drives the lever 351 to slide backward, and pushes the counterweight slider 33 backward through the lever 331 to abut or approach the bowstring in the fully drawn state. S31, the toggle block is reset. The load shifting cylinder 34 drives the toggle block 351 to move forward to the limit position to avoid interfering with the subsequent release action. S4, Release; S41. Unlock: The safety interlock assembly releases the radial limit on the trigger latch 26 or the locking block 27. S42. The bowstring in a fully drawn state generates a forward restoring force. This force acts on the front side wall of the drawstring groove 260, forcefully pulling the trigger 26 to rotate forward. The trigger 26 begins to rotate forward, causing the elastic linkage to be compressed again. When the rotation angle crosses the balance line again, the elastic force of the elastic linkage instantly changes from resistance to push, assisting the trigger 26 to rotate forward quickly. The opening of the drawstring groove 260 quickly turns, releasing the bowstring. S43. After the bowstring is released, it pushes the counterweight slider 33 located at its front end to move forward along the main slide rail 31, and finally contacts the buffer component at the front end of the main slide rail. The buffer component absorbs the impact energy and makes the counterweight slider 33 stop smoothly. S5. A single test is completed, and this process is repeated.

[0017] Furthermore, steps S2 and S3 can be performed simultaneously.

[0018] Furthermore, it also includes a detection device for detecting whether the drawbar slider 22 and the lever 351 have moved into place.

[0019] This invention relates to a bow fatigue testing device and method. It uses a counterweight slider instead of a real arrow, eliminating the need for repeated loading and significantly improving testing efficiency. Traditional methods require repeated loading and unloading of real arrows, while this invention simulates the inertial load of the arrow by setting a counterweight slider whose weight matches that of the bow and arrow. During the test, the counterweight slider constantly reciprocates on the guide rail, eliminating the need for reloading after each test as in traditional methods. This fundamentally solves the problem of time-consuming and labor-intensive bow and arrow placement, allowing fatigue testing to be performed continuously and automatically, significantly improving testing efficiency. This bow fatigue testing device is compact in structure, simulates a bow and arrow through load, eliminates the need for repeated bow loading and manual intervention, achieves fully automatic testing, and has high testing efficiency. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the bow fatigue detection device of the present invention; Figure 2 This is a schematic diagram showing the usage state of the bow fatigue detection device of the present invention; Figure 3 This is a schematic diagram of the bow-drawing mechanism of the bow fatigue detection device of the present invention; Figure 4 This is a schematic diagram of the bow-drawing mechanism of the bow fatigue detection device of the present invention from another angle; Figure 5 This is a schematic diagram of the trigger assembly of the bow fatigue detection device of the present invention; Figure 6 This is a schematic diagram of the internal structure of the trigger assembly of the bow fatigue detection device of the present invention; Figure 7 This is a schematic diagram of the structure of the locking block of the bow fatigue detection device of the present invention; Figure 8 This is a schematic diagram of the release state of the bow-drawing mechanism of the bow fatigue detection device of the present invention; Figure 9 This is a schematic diagram of the bow-drawing mechanism of the bow fatigue detection device of the present invention, showing the string-hooking state. Figure 10 This is a schematic diagram of the load mechanism of the bow fatigue detection device of the present invention; Figure 11 This is a schematic diagram of the load mechanism of the bow fatigue detection device of the present invention from another angle; Figure 12 for Figure 11 Enlarged view of section E in the middle; Figure 13 This is a schematic diagram of the main slide rail of the bow fatigue detection device of the present invention; Figure 14 This is a schematic diagram of the main slide rail of the bow fatigue detection device of the present invention from another angle; Figure 15 for Figure 14Enlarged view of section F in the middle; Figure 16 This is a cross-sectional view of the main slide rail of the bow fatigue detection device of the present invention; Figure 17 This is a schematic diagram of the counterweight slider of the bow fatigue detection device of the present invention; Figure 18 This is a schematic diagram of the installation of the buffer assembly of the bow fatigue detection device of the present invention; Figure 19 This is a schematic diagram of the bow body mounting mechanism of the bow fatigue detection device of the present invention; Figure 20 This is a schematic diagram of the bow body mounting mechanism of the bow fatigue detection device of the present invention from another angle; In the diagram: 1. Frame; 2. Bowing mechanism; 22. Bowing slider; 221. Bowing cylinder; 24. Trigger mount; 26. Trigger catch; 27. Locking block; 260. Bowing groove; 271. Strip guide groove; 263. Pin; 273. Spring; 261. Front lever; 262. Rear lever; 28. Trigger; 251. Trigger cylinder; 280. Locking groove; 25. Trigger slider; 250. Lever groove; 272. Spring mounting groove; 3. Loading mechanism; 31. Main slide rail; 33. Counterweight slider; 330. Bowing groove; 34. Load shifting cylinder; 351. Lever block; 312. Secondary slide rail; 35. 1. Toggle block slider, 331. Toggle lever, 310. Working area, 36. Top rod, 37. Limit switch, 13. Fixed limit plate, 361. Moving limit plate, 362. Limit pin, 321. Front cylinder, 322. Rear cylinder, 311. Support plate, 4. Bow body mounting mechanism, 41. Fixed base plate, 42. Bow body fixing plate, 46. Elastic element, 411. Mounting plate, 412. Slide rail, 420. Window, 422. Limit contact plate, 461. Piston rod, 462. Connector, 471. Limit rod, 472. Damper, 51. Bushing, 52. Pad, 53. Buffer body, 9. Bow body. Detailed Implementation

[0021] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0022] See Figures 1-20 The present invention provides a bow fatigue detection device, which includes a frame 1, a bow body mounting mechanism 4, a bow drawing mechanism 2 and a load mechanism 3.

[0023] Among them, the frame 1 serves as the main installation body, and the bow body installation mechanism 4, the bow pulling mechanism 2, and the load mechanism 3 are all installed on the frame 1. The frame 1 is a frame structure made of profiles.

[0024] The bow mounting mechanism 4 is mounted on the frame 1 and is used to mount the bow 9 to be tested.

[0025] The bow-drawing mechanism 2 is used to draw the bow; specifically, it is used to hook the bowstring in the first position and pull it back to the second position before releasing it.

[0026] The load mechanism 3 is used to replace the bow and arrow, applying a load force to the bowstring that simulates that of the bow and arrow. It includes a main slide rail 31, a counterweight slider 33, a buffer assembly, and a load shifting assembly. (See attached document.) Figures 10-18 .

[0027] The counterweight slider 33 is horizontally mounted on the main slide rail 31, and its sliding direction is parallel to the bow-drawing direction of the bow mechanism 2. The weight of the counterweight slider 33 matches the bow and arrow, that is, it is basically the same as the mass of the bow and arrow. It is used to simulate the inertial load when the bow and arrow are launched, and to ensure that the test process truly reflects the stress change of the bow body in actual use. A bowstring groove 330 is provided at the rear end of the counterweight slider 33 to accommodate the bowstring. The edge of the bowstring groove is rounded or beveled to guide the bowstring to engage quickly and accurately.

[0028] The buffer assembly is located at the front end of the main slide rail 31, on the movement path of the counterweight slider 33. It is used to absorb the kinetic energy generated by the high-speed sliding counterweight slider 33 after the bowstring is released, thereby making the counterweight slider 33 decelerate smoothly to a stop.

[0029] The load shifting assembly includes a load shifting cylinder 34 and a lever 351. The load shifting cylinder 34 is parallel to the main slide rail 31, and the lever 351 is mounted on the output shaft of the load shifting cylinder 34. Therefore, the moving direction of the lever 351 is consistent with the sliding direction of the counterweight slider 33. The lever 351 is used to move the counterweight slider 33 from the third position to the fourth position. The third position is the position where it contacts the buffer assembly after release, located at the front end of the bowstring's initial stationary position. The fourth position is the ready-to-launch position of the counterweight slider 33 in the fully drawn state, which is used to move the counterweight slider backward, thereby causing the rear end of the counterweight slider 33 to abut or approach the bowstring in the fully drawn state, so that the bowstring groove 330 precisely engages with the bowstring, completing the load loading. After loading, the bowstring is located in the bowstring groove, close to the second position.

[0030] This application uses a counterweight slider instead of a real arrow, eliminating the need for repeated reloading and significantly improving testing efficiency. Traditional methods require repeated installation and removal of real arrows, while this application simulates the inertial load of the arrow by setting a counterweight slider 33 with a weight matching the bow and arrow. During the test, the counterweight slider always reciprocates on the guide rail, eliminating the need for reloading after each test as in traditional methods. This fundamentally solves the problem of time-consuming and laborious bow and arrow placement, enabling fatigue testing to be carried out continuously and automatically, and significantly improving testing efficiency.

[0031] The load shifting assembly consists of a load shifting cylinder and a lever. The cylinder drives the lever to precisely push the counterweight slider backward, so that the bowstring groove at its rear end can accurately abut or approach the bowstring in a fully drawn state. This active precision engagement design ensures that the bowstring can accurately fall into the predetermined position in each test cycle, avoiding test interruptions or data deviations caused by incomplete engagement.

[0032] The counterweight slider is ejected at high speed after the bowstring is released. A buffer component is set at the front end of the main slide rail, which can effectively absorb the huge kinetic energy generated by the high-speed sliding of the slider, so that it can decelerate and stop smoothly after a certain stroke. This not only protects the counterweight slider and the slide rail itself from damage by violent impact, but also avoids the strong vibration caused by the slider stopping from being transmitted to the entire frame, thereby improving the stability and service life of the entire testing device.

[0033] Since the stroke of the counterweight slider 33 has a certain length, the stroke of the load shifting cylinder 34 is also relatively long. In order to avoid the lever arm generating a lateral bending moment on the output shaft of the load shifting cylinder 34 and to improve the running accuracy of the lever block 351, this application also includes a secondary slide rail 312. The secondary slide rail 312 is parallel to the main slide rail 31 and located on one side of it. The lever block slider 35 is slidably mounted on the secondary slide rail 312. The sliding direction of the lever block slider 35 is parallel to the sliding direction of the counterweight slider 33. The output end of the load shifting cylinder 34 is connected to the lever block slider 35 to drive the lever block slider 35 to slide. The lever block 351 is mounted on the lever block slider 35.

[0034] Because the counterweight slider has a long stroke, the piston rod of the load shifting cylinder needs to extend a long distance. If the cylinder relies solely on its own guiding capacity, the long cantilever structure is prone to lateral bending moment on the piston rod due to uneven force or its own weight when shifting the load. This application adds an auxiliary slide rail 312 as an independent load-bearing and guiding path, directly transmitting the force on the shifting block 351 to the rigid slide rail through the shifting block slider 35. The load shifting cylinder 34 is only responsible for providing axial pushing and pulling force. This structural design effectively avoids damage to the cylinder piston rod by lateral force, prevents bending of the piston rod or uneven wear of the seals, and thus significantly improves the service life of the cylinder.

[0035] The auxiliary slide rail 312 has higher guiding accuracy and resistance to lateral loads. The pawl 351 is installed on the pawl slider 35, which is precisely guided by the slide rail. This ensures that the movement trajectory of the pawl during long-distance movement is always absolutely parallel to the main slide rail 31. This allows the pawl 351 to push the counterweight slider 33 to the predetermined position with extremely precise posture. This ensures that the bowstring groove 330 and the bowstring are accurately aligned every time, avoiding engagement failure or jamming caused by pawl shaking or offset. This improves the stability and success rate of the testing process.

[0036] Furthermore, during long-term continuous fatigue testing, the mechanism needs to withstand high-frequency reciprocating motion. The combination design of cylinder and independent slide rail separates the driving function from the guiding and load-bearing function. The rigid slide rail structure can better withstand the impact and vibration during the towing process, so that the entire load shifting component remains stable during high-speed reciprocating motion, which is conducive to improving the reliability and dynamic response performance of the equipment under long-term operation.

[0037] In this embodiment, the counterweight slider 33 is provided with a lever 331 corresponding to the lever 351. When the counterweight slider 33 contacts the buffer assembly, that is, when it is in the third position, the front end of the lever 331 has space to accommodate the lever 351, thus avoiding direct contact and impact between the counterweight slider 33 and the lever 351 when the counterweight slider 33 is released to the third position. During operation, the lever 351 moves backward and contacts the lever, continues to move backward and drives the counterweight slider 33 to slide along the main slide rail 31 to the fourth position, completing the counterweight loading. Then the lever 351 moves forward to reset, avoiding a rigid collision between the counterweight slider 33 and the lever 351 after release.

[0038] By setting the lever 331, a separable connection is formed between the lever block 351 and the counterweight slider 33. When the counterweight slider 33 is bounced back to the third position at high speed, the space at the front end of the lever can accommodate the lever block, and the two do not come into contact. This avoids direct collision between the high-speed moving counterweight slider and the lever block that has not yet been moved during the slider reset process, preventing damage to the parts and eliminating the interference that the impact may cause to the test accuracy.

[0039] This application adopts a complete timing logic of moving the lever backward, applying load, moving the lever forward, and releasing the slider. When the lever moves forward and resets, it no longer undertakes the tossing task, which is equivalent to actively disengaging from contact before the counterweight slider is released. This ensures that when the counterweight slider rebounds under the action of the bowstring, it is in a completely free flight state and is not affected by the friction or resistance of any external mechanism, thus ensuring the accuracy of the test data.

[0040] This application utilizes the space at the front end of the lever to form a physical buffer zone. Due to the clearance space at the front end of the lever, the counterweight slider will not directly collide with the lever block when it rebounds. Unidirectional drive is achieved through a simple structure, eliminating the need for additional electromagnetic clutches or locking mechanisms. The structure is simple and compact, and relies on rigid contact transmission, resulting in low energy loss. This ensures that the slider can be accurately pulled back to the ready position each time, thereby reducing the complexity and cost of the equipment and improving its fault tolerance.

[0041] To improve centering and operational accuracy, the main slide rail 31 in this application includes two parallel rods with a gap between them, forming a working area 310. This working area 310 can accommodate the bowstring, and the counterweight slider 33 is slidably fitted within the working area 310. Preferably, the center of the counterweight slider 33 and the bowstring are located in the same vertical plane. The main slide rail 31 uses two parallel rods to provide dual guiding constraints for the counterweight slider 33. Compared with a single slider or single guide rail structure, this design can effectively limit the slider's rotational freedom in the horizontal plane. At the moment the bowstring is released, the counterweight slider will be subjected to a huge axial impact force. The dual-rail structure can resist the lateral torsional torque caused by uneven force or slider center of mass deviation, ensuring that the slider always slides at high speed along a straight line, avoiding additional friction or jamming caused by sliding wobble, thereby ensuring the stability of the test conditions and the repeatability of the data.

[0042] By setting the two rods parallel and maintaining a distance, a hollow working area 310 is formed in the middle. This area is the movement channel of the bowstring. During the drawing and releasing of the bow, the bowstring can move freely in this working area without contacting or rubbing against the guide rail itself. This ensures the high-speed sliding of the slider, protects the bowstring from wear, and also avoids energy loss or trajectory deviation caused by the bowstring touching the guide rail at the moment of release.

[0043] By placing the counterweight slider within the working area 310, the force transmission path is optimized. When the bowstring acts on the center of the slider, the driving force can be directly transmitted to the guide rails on both sides through the slider's support structure, reducing additional bending moment. Compared to the structure where the slider cantilever is mounted on one side of the guide rail, this design, incorporating the slider between the two rails, results in a more balanced force distribution.

[0044] In this embodiment, the center of gravity of the counterweight slider 33 is located on its geometric center line and the axis of the main slide rail 31, ensuring that the slider is subjected to symmetrical force during acceleration and deceleration, effectively suppressing vibration and sway; preferably, the center of gravity of the counterweight slider is located on the axis of the working area.

[0045] In this embodiment, the inner side (i.e., the opposite surface) of the rod is concave to form a guide groove, and a working area 310 is formed between the two guide grooves. This area creates a closed or semi-closed track with four-sided limiting for the counterweight slider. This groove structure can cooperate with the corresponding flange or slider body on the counterweight slider to achieve dual constraint on the slider in the vertical and lateral directions. Even if a huge impact force or vibration is generated at the moment of bowstring release, the slider is firmly restricted in the guide groove and will not jump off the guide rail, ensuring absolute safety under high-speed operation. At the same time, it effectively resists the head-up or head-down torque that the slider may generate during movement, so that the slider always runs close to the reference surface of the guide rail. This improves the running stability of the counterweight slider and further enhances the straightness and repeatability of the motion trajectory. Preferably, the cross-section of the guide groove is triangular, trapezoidal, or U-shaped.

[0046] In order to achieve automated testing process, a detection component is provided at the rear end of the main slide rail 31 in this application. The detection component is used to detect whether the counterweight slider 33 has moved into place.

[0047] By setting up a detection component, the equipment's control system can acquire the position status of the counterweight slider 33 in real time. When the load shifting cylinder 34 pushes the counterweight slider 33 backward to the fourth position, i.e., the ready-to-go state, the detection component sends a position signal to the controller. This signal is a necessary prerequisite for triggering subsequent actions. This closed-loop control logic ensures that each test cycle is executed accurately and error-free, and enables unattended, automated, and continuous testing.

[0048] In this embodiment, the detection component includes a push rod 36, a reset spring, and a limit switch 37. The push rod 36 is slidably mounted on the rear end of the main slide rail 31 and is located on the movement path of the counterweight slider 33. The reset spring causes the push rod 36 to tend to return to its original position. The limit switch 37 is located at the rear end of the push rod 36 and can be triggered by the push rod 36. When the counterweight slider 33 moves backward to the third position, it contacts the push rod 36 and pushes it to move backward. The push rod touches the limit switch 37, thereby triggering signal feedback. After release, the push rod automatically rebounds under the action of the reset spring, and the limit switch is reset. The system completes one state cycle.

[0049] Preferably, the detection assembly further includes a fixed limit plate 13 and a movable limit plate 361. The fixed limit plate 13 is fixed to the rear end of the main slide rail 31. The rear end of the push rod 36 passes through the fixed limit plate 13 and is fixedly connected to the movable limit plate 361, so that the push rod 36 and the movable limit plate 361 move synchronously. The rear end of the movable limit plate 361 can trigger the limit switch 37. At the same time, a limit pin 362 is provided on the movable limit plate 361. The limit pin 362 passes forward through the fixed limit plate 13 and is connected to the return spring, so that the movable limit plate 361 has a forward movement tendency. The movable limit plate 361 and the limit pin 362 cooperate to form a mechanical double limit structure.

[0050] In this application, a front cylinder 321 is provided at the front end of the main slide rail 31, and a rear cylinder 322 is provided at the rear end of the main slide rail 31. The main slide rail (working area), the front cylinder and the rear cylinder are coaxially arranged. The buffer component is located in the front cylinder 321, and the detection component is located in the rear cylinder 322. Specifically, the push rod is located in the rear cylinder. The overall structure is compact.

[0051] The buffer assembly includes a buffer body 53, which is located inside the front cylinder and can directly contact the end of the counterweight slider to decelerate it. The buffer body 53 is made of ultra-high molecular weight polyethylene fiber. Ultra-high molecular weight polyethylene fiber is one of the most wear-resistant materials available, with a wear resistance 7-8 times that of ordinary carbon steel, far superior to common materials such as polytetrafluoroethylene and polyurethane. Under the high-speed, high-frequency reciprocating impact of the counterweight slider 33, the buffer body 53 needs to withstand tens of thousands or even hundreds of thousands of friction and impact cycles. The buffer body made of ultra-high molecular weight polyethylene fiber (UHMWPE) material has extremely slow surface wear and can maintain its original shape and size for a long time. This ensures that the buffer characteristics of the buffer, such as buffer stroke and damping coefficient, remain highly consistent during long-term continuous testing, eliminating the need for frequent replacements and greatly reducing the maintenance frequency of the equipment.

[0052] Meanwhile, the ultra-high molecular weight polyethylene fiber has extremely long molecular chains, resulting in extremely high impact toughness. It can maintain excellent impact resistance within a wide temperature range of -150℃ to 80℃, and the impact energy is effectively absorbed by the orientation and slippage of the molecular chains. At the moment of bowstring release, the counterweight slider 33 carries enormous kinetic energy. The UHMWPE buffer can efficiently convert this kinetic energy into frictional heat and deformation energy of the molecular chains inside the material, achieving smooth deceleration. Its excellent impact resistance ensures that the buffer will not crack, break, or undergo permanent crushing deformation under long-term high-speed impact, greatly ensuring the safety and reliability of equipment operation.

[0053] Unlike the crisp impact sound produced by metal buffers, the contact between polymer materials and metal sliders is a soft contact. When the ultra-high molecular weight polyethylene fiber (UHMWPE) buffer comes into contact with the counterweight slider 33, it can effectively absorb the vibration noise generated by the impact, making the entire buffering process quieter. For laboratories or production workshops that need to run fatigue tests for a long time, it significantly reduces noise pollution and improves the working environment of operators.

[0054] Finally, the lightweight nature of the buffer body 53 makes installation and replacement easier and more convenient. Even if there are lubricating greases or cleaning agents in the working environment of the equipment, the UHMWPE material will not swell, deform or deteriorate, ensuring its long-term stability under various working conditions.

[0055] In this embodiment, the buffer assembly also includes a bushing 51 and a pad 52. The bushing 51, pad 52, and buffer body are arranged sequentially from front to back in the front cylinder, forming a structure with an open rear end. The buffer body is disposed inside this open end and can contact the end of the counterweight slider. The buffer body 53 is made of high-powered webbing folded together. High-powered webbing, which is made of ultra-high molecular weight polyethylene fiber (UHMWPE), exhibits a significant gradual increase in mechanical properties when compressed in a folded state. As the counterweight slider 33 impacts and compresses the folded webbing, the layers of webbing gradually tighten, and the deformation resistance increases steadily. This gradual buffering characteristic avoids the instantaneous huge impact force peak that may occur with traditional rigid buffers, making the process of the counterweight slider from high-speed movement to stop more gentle and linear, and reducing impact damage to the slide rail and the slider itself.

[0056] The folded webbing forms a multi-layered structure. During compression, energy is distributed to the bending deformation and interlayer friction of each layer of webbing. This structure can absorb huge kinetic energy in a limited space. Compared with solid materials, the folded webbing provides higher energy absorption efficiency through the interaction between multiple layers. Even if the slider speed is extremely high, the folded webbing can convert kinetic energy into heat energy through sufficient deformation, ensuring that the slider is reliably braked.

[0057] Furthermore, the webbing is a flexible material with extremely high internal damping. During compression, it dissipates most of its energy as internal friction heat, rather than storing and rebounding like a metal spring. When the counterweight slider hits the folded webbing and stops, the webbing almost does not bounce the slider back. This is crucial for test cycles that require the slider to stop precisely at a certain position. It avoids the slider returning due to rebound and the inconsistency between the initial position of the next test and the initial position of the next test, thus improving the repeatability of the test. At the same time, its use and replacement costs are extremely low.

[0058] In this embodiment, the main slide rail 31 is made of a hollow tube, with two parallel guide grooves cut on both sides of the middle section of the hollow tube. The two ends of the hollow tube form a first cylindrical body, and a second cylindrical body is threaded onto the cylindrical body, thus forming a complete front and rear cylindrical body. Preferably, the buffer body is set in the first cylindrical body of the front cylindrical body, and the end of the buffer body is basically flush with the open end of the rear end of the first cylindrical body, so that after the counterweight slider decelerates, it is located outside the cylindrical body, which is convenient for its reset. The bushing 51 and the pad 52 are set in the second cylindrical body of the front cylindrical body, which is easy to disassemble and facilitates the installation and replacement of the buffer body.

[0059] A strip-shaped support plate 311 is welded and fixed to one side of the hollow tube, and the auxiliary slide rail is fixedly installed on the support plate 311 to form an integral structure and ensure parallelism.

[0060] The bow-drawing mechanism 2 is mainly used to draw the bow and release the bowstring. (See also...) Figures 3-9 It includes a drawstring assembly, a trigger assembly, and a safety interlock assembly.

[0061] The bow assembly includes a bow slider 22 horizontally mounted on the frame 1 and a bow cylinder 221 for driving the bow slider 22 to slide horizontally between a first position and a second position, which is used for drawing the bow.

[0062] The trigger assembly is mounted on the bowstring slider 22 and includes a trigger mounting base 24. The trigger mounting base 24 is mounted on the bowstring slider 22. A trigger latch 26 and a locking block 27 are rotatably mounted on the trigger mounting base 24. The rotation axes of the trigger latch 26 and the locking block 27 are parallel. A bowstring groove 260 is provided on the trigger latch 26 to accommodate the bowstring and realize the drawing and releasing of the bowstring. An elastic linkage is provided between the trigger latch 26 and the locking block 27. This elastic linkage can realize the linkage between the trigger latch 26 and the locking block 27, that is, it can realize the linkage rotation.

[0063] The line connecting the pivot (hinge point) of the trigger latch 26 and the locking block 27 forms a balance line. The force generated by the bowstring in the string groove 260 can make the trigger latch 26 rotate. As the trigger latch 26 rotates, the elastic linkage can cross the balance line, thereby causing the elastic linkage to generate driving forces in different directions on the trigger latch 26, realizing the hooking and release.

[0064] The safety interlocking assembly is mounted on the trigger mount 24 and is used to radially limit the trigger latch 26 and / or the locking block 27, thereby locking and fixing the trigger latch 26 and ensuring that the angle of the trigger latch 26 is locked during the drawing of the bow, thus preventing accidental rotation that could cause the bowstring to fall off.

[0065] During operation, the drawstring cylinder 221 drives the drawstring slider 22 to move in the direction of the bowstring (forward). When the drawstring groove 260 of the trigger 26 contacts the stationary bowstring, the bowstring pushes against the rear wall of the drawstring groove 260. Under the reaction force of the bowstring, the trigger 26 is forced to rotate backward. As the trigger 26 rotates, the elastic linkage is compressed or stretched. When the rotation angle exceeds the critical point, that is, when it crosses the balance line, the elastic force of the elastic linkage reverses, changing from resisting rotation to assisting rotation, thus driving the bowstring to rotate. The trigger pull 26 quickly rotates backward to its final position, locking the bowstring into the draw string groove 260. At this point, the bowstring is securely hooked; this is the first position, which can be adjusted depending on the bow type. The safety interlock component activates, radially limiting the trigger pull 26 (or locking block 27) and preventing any forward rotation. Even with high bowstring tension, the trigger pull 26 cannot be pushed open. The draw string cylinder 221 changes direction, driving the draw string slider 22 to move backward (the second position), initiating the drawing of the bow. Because the trigger pull itself has a certain self-locking force, there can be a time difference between the action of the draw string cylinder and the action of the safety interlock component. Throughout the entire draw stroke, the bowstring tension always acts on the trigger pull 26, but due to the physical limit of the safety interlock component and the self-locking tendency of the over-center structure, the trigger is locked and fixed, ensuring that the bowstring will not fall off midway. When the draw string slider 22 moves to the preset second position (the maximum draw distance, which can be set), after the detection is completed, the safety interlock component unlocks, and the bowstring under huge tension generates a forward restoring force. This force acts on the front side wall of the draw string groove 260, forcefully pulling the trigger pull 26 to rotate forward. Once the trigger pull 26 starts to rotate forward, the elastic linkage is compressed again. When the rotation angle crosses the balance line again, the elastic force of the elastic linkage instantly changes from resistance to push, assisting the trigger pull 26 to rotate forward at an extremely fast speed. The opening of the draw string groove 260 quickly turns, and the bowstring is released in a very short time, knocking out the counterweight slider at the front end of the bowstring, completing one draw cycle.

[0066] In this application, upon release, the tension of the bowstring directly triggers the trigger. Once the elastic linkage crosses the balance line, the trigger will instantly spring open under the combined action of the bowstring tension and elastic force. The bowstring is pushed away or ejected from the hook groove, rather than sliding out due to friction. The bowstring hardly slips at the moment of disengagement from the drawbar, which greatly reduces bowstring wear and heat generation, significantly extends the bowstring's service life, ensures that fatigue testing can be conducted continuously for a long time, and the test results are closer to the actual fatigue state of the bow limbs.

[0067] Traditional technology requires an additional cylinder to control the rotation of the hook, which presents complex electrical timing issues. This application utilizes the mechanical movement of the drawbar slider during its movement and the over-center switching of the elastic linkage to automatically complete the draw and release actions. It completely eliminates the complex air circuits and solenoid valves used to drive the hook rotation. The control system only needs to control the forward and backward movement of the drawbar cylinder, realizing the completion of the entire draw and release cycle by a single power source. The control logic is greatly simplified, the failure rate is significantly reduced, and the action response is faster.

[0068] During fatigue testing of high-load bow limbs, the tension of the bowstring on the trigger pull is extremely high. If the locking structure of a traditional latch is unreliable, there is a risk of accidental disengagement due to vibration. This application provides dual safety protection through a center-locking self-locking and safety interlocking component.

[0069] This application solves the industry pain points of severe bowstring wear, complex control, and significant safety hazards in traditional bow fatigue detection devices by using a purely mechanical linkage mechanism based on the over-center principle, and achieves high-frequency, low-wear, and highly reliable automated fatigue detection.

[0070] In this embodiment, the trigger latch 26 can rotate between a first angle and a second angle; when it is at the first angle, the drawstring groove 260 is tilted forward, and the elastic linkage is located on the first side of the balance line, causing the drawstring groove 260 to have a forward rotation tendency; when it is at the second angle, the drawstring groove 260 is tilted backward, and the elastic linkage is located on the second side of the balance line, causing the drawstring groove 260 to have a backward rotation tendency.

[0071] In the first angle (with the drawstring groove facing forward) and the second angle (with the drawstring groove facing backward), the elastic linkage is located on both sides of the balance line, giving the trigger latch a forward or backward tendency to move. Therefore, at the two extreme angles, no external energy or additional mechanical structure is needed to maintain the state. During the drawing of the bow, the huge tension of the bowstring actually works in conjunction with the backward tendency of the elastic linkage, and the trigger latch is in a stable self-locking state. In the reset or initial state, the trigger latch is also stable. Compared with the traditional solution that requires a cylinder to continuously hold the hook or an electromagnet to keep it locked, this application only requires external force to overcome the critical point of the elastic linkage at the moment of switching states. Once the critical point is crossed, the mechanism automatically stabilizes. This greatly reduces the burden on the safety interlock components. In some working conditions, locking can even be achieved simply by over-center self-locking, and the safety interlock is only used as redundant protection.

[0072] The above scheme forms a clear dead point boundary, ensuring crisp and clean action and avoiding a half-clutch state. The two sides of the balance line have distinctly different movement trends, which fundamentally eliminates the possibility of the trigger pull being in an ambiguous state in the middle. In mechanical design, the most dangerous state is often half-clutch, that is, the state where the string-pulling component is in a state of being neither fully disengaged nor fully locked. This can lead to severe friction or sudden loosening. However, in this application, as soon as the elastic linkage component crosses the balance line, the elastic force will immediately change from resistance to power, accelerating the trigger pull to another extreme position. This ensures that the string-pulling action and the release action are instantaneous, jumping movements. The bowstring is either firmly locked at the bottom of the slot or completely released, with no intermediate wear zone in between.

[0073] Safety interlock components can be miniaturized, and their locking and unlocking timing requirements can be relatively relaxed because they do not require forcibly pulling out the pin under huge loads. They only add a safety measure after the state has stabilized, which greatly improves the durability and reliability of the system.

[0074] In this application, the elastic linkage includes a strip guide groove 271 formed on the locking block 27 and a pin 263 fixed on the trigger latch 26. The axis of the pin 263 is parallel to the rotation axis of the trigger latch 26 and the locking block 27. The pin 263 is slidably fitted in the strip guide groove 271. Simultaneously, a spring 273 is provided within the strip guide groove 271. Specifically, a spring mounting groove 272 is formed within the locking block 27, perpendicular to the rotation axis of the locking block. The spring 273 passes through the strip guide groove and is installed in the spring mounting groove, causing the pin 263 to tend to move away from the rotation axis of the locking block 27. This pin-strip guide groove-spring structure effectively constructs a cam-driven system with a defined motion trajectory. It converts the linear elastic force of the spring into a variable torque on the rotating component. The first and second angles of the trigger latch are precisely defined by the endpoint of the pin's stroke within the guide groove, achieving high reliability, long lifespan, and easy adjustability of the mechanical bistable mechanism.

[0075] Preferably, the pivot of the locking block 27 is located on the extension line of the strip guide groove 271. When the pivot of the locking block 27 is exactly located on the extension line of the strip guide groove 271, no matter what angle the trigger latch 26 rotates to, the direction of the pressure of the pin 263 on the side wall of the guide groove, that is, the direction of the thrust of the spring 273, is always perpendicular or parallel to the rotation radius of the locking block 27, or more precisely, the line of force passes through or is parallel to the rotation center line of the locking block. This design ensures that the torque generated by the spring 273 on the locking block 27 is zero or minimal. The locking block 27 mainly serves as a support and guide in the mechanism. It should not be driven to rotate by the spring force. If the pivot is not on the extended line, the spring will generate an additional torque when pushing the pin, attempting to make the locking block 27 rotate as well. This will cause unnecessary frictional resistance between the locking block 27 and its mounting base, and may even cause mechanical self-locking at certain angles due to excessive lateral force. This design ensures that the locking block 27 is in a neutral position, so that the rotational resistance of the trigger latch 26 comes entirely from the linear compression of the spring, rather than additional friction, ensuring a crisp and clean action.

[0076] In this application, the balance line is parallel to the sliding direction of the drawbar slider 22. The parallelism of the balance line to the sliding direction achieves mechanical decoupling, which ensures the stability of the mechanism under high loads and guarantees the sensitivity during triggering. This provides a guarantee for the mechanical over-center trigger design to adapt to high-poundage bow fatigue testing.

[0077] In this embodiment, the trigger latch 26 is provided with a front lever 261 and a rear lever 262. There is a gap between the front lever 261 and the rear lever 262, forming a drawstring groove 260. The front lever is located at the front end, and the rear lever is located at the rear end. The length of the front lever 261 is less than the length of the rear lever 262, forming an inlet and outlet inclined to the drawstring groove 260, which facilitates the entry and exit of the bowstring and reduces the rotation angle of the trigger latch 26. The design of the front-short and rear-long levers essentially uses asymmetrical geometry to create a smooth entry and exit channel for the bowstring within a limited space and rotation angle. This ensures stable locking of the bowstring under heavy load, while the long rear lever enables rapid and sensitive release. The short front lever and minimal rotation angle are details that ensure the trigger mechanism can achieve high-frequency, low-wear fatigue detection.

[0078] The safety interlock assembly includes a trigger 28 rotatably mounted on a trigger mount 24 and a trigger cylinder 251 for driving the trigger 28 to rotate. A locking groove 280 is provided on the side wall of the trigger 28, which radially limits the end of the locking block 27 and locks the trigger catch 26 in the hooked state. The safety interlock assembly, through a rotating trigger 28 and locking groove 280, constructs a rigid locking point independent of the main triggering mechanism. Unlike traditional solutions, it does not require withstanding huge impact loads, and it can achieve precise timing control through an independent air path, providing reliable safety redundancy for mechanical triggers and improving response speed and operational safety.

[0079] In this embodiment, the safety interlock assembly also includes a trigger slider 25 that is slidably mounted on the trigger mounting base 24 and connected to the trigger cylinder 251. A groove 250 is provided on the side wall of the trigger slider 25, and the end of the trigger 28 is located in the groove 250. Specifically, a guide wheel is provided at the end of the trigger 28, and the guide wheel is embedded in the groove 250. This allows the linear motion of the trigger cylinder 251 to be accurately converted into the rotational motion of the trigger 28, resulting in a compact structure and good driving effect.

[0080] In this embodiment, the rotation axis of the trigger 28 is coaxial with the rotation axis of the trigger latch 26, and they share a rotation axis, which further improves the structural compactness, greatly reduces the installation space, and reduces the difficulty of production and assembly.

[0081] In this application, the hinge point of the locking block 27 is defined as A, the hinge point of the trigger latch 26 and the trigger 28 is defined as B, and the axis of the pin is defined as C. When in the release phase, see [reference needed]. Figure 8 This forms ∠CAB, with a size of 25°~30°. At this point, the pin contacts the end of the strip guide groove, achieving angle limiting. That is, at this point, the trigger pull cannot continue to rotate forward. At this point, the bow string groove is tilted forward and can allow the bow string to enter from front to back.

[0082] When in the string-picking phase, the pivot pin is located on the other side of the balance line. (See reference...) Figure 9 At this time, ∠CAB is on the other side of the balance line, with a size of 10°~15°. At this time, the end of the locking block contacts one of the side walls of the locking groove, achieving the first direction of limitation. When the tension of the bowstring exceeds the force of the elastic linkage, the other side wall of the locking groove 280 contacts the end of the locking block 27, forming a limitation in the other direction. By contacting the side wall of the locking groove to achieve radial limitation, the angle of the trigger pull to rotate backward can be reduced, the rotation angle stroke can be reduced, and the response speed can be improved.

[0083] In this application, the trigger latch 26 is plate-shaped, there are two of them, and they are symmetrically arranged at both ends of the locking block and the trigger 28. On the one hand, it can improve the structural compactness and reduce the volume, and on the other hand, it can increase the contact area with the bowstring and improve the stability and reliability of the bowstring.

[0084] The bow mounting mechanism is used for mounting and securing the bow body 9. (See attached document.) Figures 19-20 It includes a fixed base plate 41, a bow body fixing plate 42, an installation component, a limiting component, and an elastic element 46.

[0085] The fixed base plate 41 serves as an installation carrier and can be installed on the frame 1. In this embodiment, the fixed base plate 41 is vertically arranged, that is, perpendicular to the horizontal plane.

[0086] The bow body fixing plate 42 is slidably mounted on the fixed base plate 41, and the bow body fixing plate 42 is parallel to the fixed base plate 41.

[0087] The mounting components are set on the bow body fixing plate 42 to fix the bow body 9. After fixing, the front-back direction of the bow body 9 is parallel to the sliding direction of the bow body fixing plate 42. The front-back direction of the bow body is the pulling direction of the bowstring.

[0088] The limiting component is installed on the fixed base plate 41. It is located at the rear end of the bow body fixing plate 42 and is used to limit the sliding stroke of the rear end of the bow body fixing plate 42, that is, to limit the rear limit position of the bow body fixing plate 42.

[0089] The elastic element 46 is disposed between the fixed base plate 41 and the bow body fixing plate 42, so that the bow body fixing plate 42 has a backward movement tendency, which is used to absorb the vibration generated by the bow body 9 after the bowstring is released.

[0090] This application slides the bow body fixing plate 42 onto the fixed base plate 41 and sets an elastic element 46 between the two, so that the bow body is in a flexible support state. The vibration generated by the bow body is absorbed and attenuated by the elastic element 46, which greatly reduces the vibration energy transmitted to the frame and external detection components, thereby effectively protecting the expensive precision detection components and extending the service life of the equipment.

[0091] When the bowstring is released, the bow body experiences not only vibration but also a reverse impact force. The elastic element 46 acts as a buffer, absorbing the impact energy generated at the moment of bowstring release. Simultaneously, the elastic element 46 ensures that the bow body fixing plate 42 maintains a backward movement tendency. After the impact, it smoothly pulls the bow body fixing plate 42 back to the limiting component, ensuring the bow body quickly and accurately returns to a consistent initial test position, preparing for the next test cycle. Before each test, the bow body precisely returns to the same spatial position, guaranteeing a high degree of consistency in the initial conditions for each bow draw, thereby significantly improving the repeatability and reliability of fatigue test data.

[0092] In this embodiment, the bow fixing plate 42 is horizontally slidably mounted on the fixed base plate 41 via two slide rails 412, and the elastic element 46 is disposed between the two slide rails 412. The elastic element 46 is positioned in the exact center of the two slide rails, so that the elastic force it applies acts on the symmetrical center line of the bow fixing plate 42. When the elastic element 46 pushes the bow fixing plate 42 backward to press against the limiting component, the elastic force is evenly distributed on the two slide rails 412, forming symmetrical force. This avoids lateral torque or jamming tendency caused by unilateral force application, making the force on the bow fixing plate 42 more balanced during sliding, the movement smoother, and also reducing the uneven wear of the slide rail pair, thus extending the service life of the guide rail.

[0093] Preferably, the elastic element 46 in this application is located on the same horizontal plane as the centerline of the bow body, so that the point of application of the elastic force and the center point of force on the bow body are in the same plane. If the point of application of the elastic element deviates from the centerline of the bow body, a torque will be formed when the bow body is impacted or reset, causing the bow body to tend to flip forward or backward or twist left or right. This deflection torque will cause the bow body fixing plate 42 to generate lateral pressure on the slide rail 412, increasing the sliding resistance and even causing jamming. However, this application completely eliminates this potential torque by coplanar arrangement, ensuring that the bow body is only subjected to pure axial force and the movement posture always remains upright.

[0094] The elastic element 46 is a gas spring, which is parallel to the sliding direction of the bow fixing plate 42. The cylinder of the gas spring is mounted on the fixed base plate 41, and the piston rod 461 of the gas spring is set to the rear and connected to the bow fixing plate 42, thereby generating a rearward thrust on the bow fixing plate 42. In the unloaded state, the rear end of the bow fixing plate 42 contacts the limiting component. When the bowstring is released, the generated counter-impact force pushes the bow fixing plate 42 to slide forward, compressing the gas spring and realizing shock absorption.

[0095] The working characteristic of the gas spring is that the spring force output is relatively smooth and approximately constant within the effective stroke. During the entire sliding stroke of the bow body fixing plate 42, the backward thrust applied by the gas spring to the bow body fixing plate remains basically stable, avoiding the problem of large fluctuations in force value caused by changes in compression of traditional metal springs. This constant preload makes the movement of the bow body more stable during the reset process.

[0096] At the moment the bowstring is released, the enormous reverse impact force pushes the bow body fixing plate 42 forward, compressing the gas spring. The damping effect inside the gas spring absorbs some of the impact energy and converts it into heat energy. This damping characteristic makes the gas spring not only an elastic element but also a highly efficient shock absorber, which can more effectively attenuate the high-frequency residual vibration transmitted from the bow body, further protecting the precision detection components on the frame.

[0097] Specifically, the piston rod 461 is connected to the connecting block 421 on the bow body fixing plate 42 via a connector 462. The connector is a threaded connector, and its overall length can be adjusted. At the same time, an opening is provided on the bow body fixing plate 42 to form a window 420, which allows the connector 462 to be exposed and is used to adjust the length of the connector 462, thereby adjusting the preload of the gas spring on the bow body fixing plate 42.

[0098] This adjustment function allows operators to fine-tune the initial compression of the gas spring on the bow fixing plate 42, thereby precisely setting the magnitude of the rearward preload. For bows of different tension levels or weights, the most suitable preload can be obtained through simple adjustments, ensuring that the bow fixing plate 42 can firmly adhere to the limiting component without increasing unnecessary sliding resistance or affecting the normal vibration mode of the bow due to excessive preload. This achieves true online adjustability. During equipment debugging or maintenance, operators do not need to disassemble the bow fixing plate 42, gas spring, or other peripheral components; they can directly use wrenches or other tools to rotate the connector through window 420, greatly simplifying the adjustment process and saving debugging time, especially when the equipment is already installed on a rack and space is limited.

[0099] The limiting component in this embodiment includes a limiting rod 471 or a damper 472, or both a limiting rod 471 and a damper 472. Specifically, a mounting plate 411 is fixed at the rear end of the fixed base plate 41, and the limiting component is mounted on the mounting plate 411 and faces the bow body fixing plate 42. The structure is compact and the installation and removal are convenient and quick.

[0100] The limiting rod 471 provides a precise and rigid mechanical stop; the damper (i.e., a flexible buffer) not only serves as a limiter but, more importantly, absorbs kinetic energy at the moment of contact, achieving flexible buffering. When the limiting rod 471 and the damper 472 are set up simultaneously, they form a precise, coordinated working system of buffering followed by limiting. During the rearward repositioning of the bow body fixing plate 42, it first contacts the damper 472, which absorbs most of the repositioning kinetic energy, allowing the bow body fixing plate 42 to decelerate smoothly. Subsequently, the bow body fixing plate 42 gently adheres to and presses against the limiting rod 471. This combination avoids the rebound and noise caused by rigid impact, while ensuring the accuracy of the final stopping position through the limiting rod, balancing stability and precision, and reducing operating noise.

[0101] The limiting rod 471 in this application is a bolt (or screw) with an adjustable exposed length toward the bow fixing plate 42, i.e., an adjustable effective length, thereby achieving precise fine-tuning of the final reset position of the bow fixing plate 42 to adapt to different bow installation heights and preload stroke requirements.

[0102] To improve the wear resistance and replaceability of the limiting contact surface, in this application, a limiting contact plate 422 is detachably installed on the side wall of the bow body fixing plate 42 for contacting the limiting component. The contact area between the limiting component and the bow body fixing plate 42 is the area that is subjected to high-frequency impact and friction, and is prone to wear after long-term use. By setting an independent limiting contact plate 422, wear-resistant materials (such as wear-resistant steel, inlaid hard alloy or polymer wear-resistant plate) can be concentrated on this vulnerable part. Even after a large number of test cycles, wear only occurs on the replaceable limiting contact plate 422, while the main body of the bow body fixing plate 42, which is more expensive and more complex to manufacture, is effectively protected, thereby greatly extending the service life of the entire bow body fixing plate.

[0103] The installation components in this application include positioning components and fixing components. The positioning components are used to position and support the bow body 9, while the fixing components are used to fix the bow body 9. In this embodiment, the positioning components include multiple positioning posts and positioning blocks. The positioning posts are used to limit the front-to-back tilt of the bow body 9, thereby making the bowstring perpendicular to the sliding direction of the bow body fixing plate 42; while the positioning blocks are used to limit the left-to-right tilt of the bow body 9, thereby making the bow body 9 parallel to the bow body fixing plate 42.

[0104] Meanwhile, the present invention also provides a detection method for a bow fatigue detection device, which includes the following steps: S1. Clamping: Fix the bow body 9 onto the bow body mounting mechanism 4 and make the bow body vertical. S2, draw the bow; S21, the draw string cylinder 221 drives the draw string slider 22 to move forward, which in turn drives the trigger assembly to move forward synchronously; S22. String hooking: The string groove 260 of the trigger 26 contacts the stationary bowstring. The bowstring pushes against the rear wall of the string groove 260. Under the reaction force of the bowstring, the trigger 26 is forced to rotate backward. As the trigger 26 rotates, the elastic linkage is compressed or stretched. When the rotation angle exceeds the critical point, i.e., crosses the balance line, the elastic force of the elastic linkage reverses, changing from resisting rotation to assisting rotation, driving the trigger 26 to quickly rotate backward into position, locking the bowstring into the string groove 260, thus hooking the string. This position is the first position, which can be set according to different types of bows. S23, Locking: The safety interlock component is activated, radially limiting the trigger latch 26 or the linkage lock block 27 to prevent the trigger latch 26 from rotating forward. S24. Draw the bow. The string-drawing cylinder 221 drives the string-drawing slider 22 to move backward to begin drawing the bow until it moves to the second position. At this time, the bow is fully drawn. S3, Load loading; S31, the load shifting cylinder 34 drives the lever 351 to slide backward, contact the lever 331, and move the counterweight slider backward, pushing the counterweight slider 33 backward to abut or approach the bowstring in the fully drawn state, that is, moving the counterweight slider backward to the fourth position. S31, the lever is reset, and the load shifting cylinder 34 drives the lever 351 to move forward to the limit position to avoid the counterweight slider after the bowstring is released from collide with the lever during high-speed movement; at this time, the lever is located in the clearance space, which is the distance reserved at the front end of the lever on the counterweight slider when the counterweight slider contacts the buffer component, that is, when it is in the third position. S4, Release; S41. Unlock: The safety interlock assembly releases the radial limit on the trigger latch 26 or the locking block 27. S42. The bowstring in a fully drawn state generates a forward restoring force. This force acts on the front side wall of the drawstring groove 260, forcefully pulling the trigger 26 to rotate forward. The trigger 26 begins to rotate forward, causing the elastic linkage to be compressed again. When the rotation angle crosses the balance line again, the elastic force of the elastic linkage instantly changes from resistance to push, assisting the trigger 26 to rotate forward quickly. The opening of the drawstring groove 260 quickly turns, releasing the bowstring. S43. After the bowstring is released, it pushes the counterweight slider 33 located at its front end to move forward at high speed along the main slide rail 31, and finally contacts the buffer component at the front end of the main slide rail. The buffer component absorbs the impact energy and makes the counterweight slider 33 stop smoothly. S5. A single test is completed, and this process is repeated.

[0105] To improve work efficiency, steps S2 and S3 can be performed simultaneously, that is, opening the bow and loading the load can be performed simultaneously. The timing controller coordinates the action phase of the bow-pulling cylinder 221 and the load-shifting cylinder 34. When the bow-pulling slider 22 moves backward, the load-shifting cylinder 34 synchronously drives the toggle block 351 to move backward, thereby reducing waiting time and improving the overall work rhythm and efficiency.

[0106] To achieve automated detection, this application also includes a detection device for detecting whether the drawbar slider 22 and the lever 351 have moved into position. On the one hand, it serves as a position feedback sensor to monitor in real time whether the drawbar slider 22 has reached the full bow position and whether the lever 351 has accurately reached the clearance space; on the other hand, it serves as a trigger signal source for the safety interlock component to ensure that each actuator completes the state switching at the precise position.

[0107] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A bow fatigue detection device, characterized in that, include: frame; A bow mounting mechanism, mounted on the frame, is used to mount the bow to be tested; A bow-drawing mechanism is used to hook the bowstring in a first position and pull it back to a second position before releasing it; A load-bearing mechanism, used to apply a load force simulating that of a bow and arrow to the bowstring, includes: The main slide rail is mounted on the frame and is horizontally arranged with its length direction parallel to the front and rear orientation of the bow body. The counterweight slider is matched to the weight of the bow and arrow and is horizontally mounted on the main slide rail; A buffer assembly is disposed at the front end of the main slide rail and located on the movement path of the counterweight slider, for absorbing the kinetic energy generated by the high-speed sliding counterweight slider; The load shifting assembly includes a lever that can slide along a length direction parallel to the main slide rail. The lever is used to move the counterweight slider backward so that the counterweight slider abuts against or approaches the bowstring in a fully drawn state.

2. The bow fatigue testing device as described in claim 1, characterized in that: The counterweight slider is provided with a lever corresponding to the lever. When the counterweight slider contacts the buffer assembly, the front end of the lever has space and can accommodate the lever. After the lever completes the movement of the counterweight slider, it returns to the space.

3. The bow fatigue testing device as described in claim 1, characterized in that: The main slide rail includes two parallel rods with a gap between them, forming a working area that can accommodate the bowstring, and the counterweight slider is slidably fitted within the working area.

4. The bow fatigue testing device as described in claim 1, characterized in that: The main slide rail is provided with a front cylinder and a rear cylinder at both ends. The buffer assembly is disposed in the front cylinder, and the rear cylinder is provided with a detection assembly for detecting whether the counterweight slider has moved into place. The buffer assembly includes a buffer body disposed in the front cylinder and capable of contacting the counterweight slider. The buffer body is made of ultra-high molecular weight polyethylene fiber.

5. The bow fatigue testing device as described in claim 1, characterized in that: The bow-drawing mechanism includes: The drawstring assembly includes a drawstring slider that is horizontally slidable on the frame and a drawstring cylinder for driving the drawstring slider to slide horizontally. A trigger assembly, mounted on the drawbar slider, includes a trigger mounting base, on which a trigger latch and a locking block are rotatably mounted. The trigger latch has a drawbar groove. An elastic linkage is provided between the trigger latch and the locking block, enabling linkage between the trigger latch and the locking block. The line connecting the trigger latch and the pivot of the locking block forms a balance line. The force generated by the bowstring in the string groove can cause the trigger latch to rotate and the elastic linkage to cross the balance line, thereby causing the elastic linkage to generate driving forces in different directions on the trigger latch, realizing the hooking and releasing of the string. A safety interlock assembly, mounted on the trigger mounting base, is used to radially limit the trigger latch and / or the locking block to achieve locking and fixation.

6. The bow fatigue testing device as described in claim 5, characterized in that: The trigger latch is provided with a drawbar groove, and the trigger latch can rotate between a first angle and a second angle; When at the first angle, the drawstring groove is tilted forward, and the elastic linkage is located on the first side of the balance line, causing the drawstring groove to have a tendency to rotate forward. When at the second angle, the drawstring groove is tilted backward, and the elastic linkage is located on the second side of the balance line, causing the drawstring groove to have a tendency to rotate backward.

7. The bow fatigue testing device as described in claim 5, characterized in that: The elastic linkage includes a strip-shaped guide groove formed on the locking block and a pin fixed on the trigger latch. The pivot of the locking block is located on the extension line of the strip-shaped guide groove. The axis of the pin is parallel to the rotation axis of the trigger latch and the locking block and is slidably fitted in the strip-shaped guide groove. A spring is provided in the strip-shaped guide groove, and the spring causes the pin to have a tendency to move away from the pivot of the locking block.

8. The bow fatigue testing device as described in claim 5, characterized in that: The safety interlocking assembly includes a trigger rotatably mounted on the trigger mounting base and a trigger cylinder for driving the trigger to rotate. The side wall of the trigger is provided with a locking groove, which can radially limit the end of the locking block and lock and fix the trigger buckle in the hooked state.

9. The bow fatigue testing device as described in claim 1, characterized in that: The bow mounting mechanism includes: The base plate is fixed and installed on the frame; The bow body fixing plate is slidably mounted on the fixing base plate along the length direction parallel to the main slide rail; The mounting components are installed on the bow body fixing plate for fixing the bow body; A limiting component is installed on the fixed base plate and located at the rear end of the bow body fixing plate, and is used to limit the sliding stroke of the rear end of the bow body fixing plate; An elastic element is disposed between the fixed base plate and the bow body fixing plate, so that the bow body fixing plate has a backward movement tendency and is used to absorb the vibration generated by the bow body after the bowstring is released.

10. A detection method for a bow fatigue detection device, characterized in that, Includes the following steps: S1. Clamping: Securely install the bow body onto the bow body mounting mechanism; S2, draw the bow; S21. The draw string cylinder drives the draw string slider to move forward, causing the trigger assembly to move forward synchronously. S22. String hooking: The string groove of the trigger pull contacts the stationary bowstring. The bowstring pushes against the rear wall of the string groove. Under the reaction force of the bowstring, the trigger pull is forced to rotate backward. As the trigger pull rotates, the elastic linkage is compressed or stretched. When the rotation angle exceeds the critical point, that is, when it crosses the balance line, the elastic force of the elastic linkage reverses, changing from resisting rotation to assisting rotation, driving the trigger pull to quickly rotate backward into place, locking the bowstring into the string groove, thus hooking the string. S23. Locking: The safety interlock component is activated to radially limit the trigger latch or locking block, preventing the trigger latch from rotating forward. S24. Draw the bow. The bowstring cylinder drives the bowstring slider to move backward to begin drawing the bow until it reaches the second position. S3, Load loading; S31, The load shifting cylinder drives the lever to slide backward, and pushes the counterweight slider backward through the lever to abut or approach the bowstring in the fully drawn state. S32, Toggle block reset: The load shifting cylinder drives the toggle block to move forward to the limit position to avoid interfering with subsequent release actions; S4, Release; S41. Unlock: The safety interlock assembly releases the radial limit on the trigger latch or locking block. S42. The bowstring in a fully drawn state generates a forward restoring force. This force acts on the front wall of the drawstring groove, forcefully pulling the trigger to rotate forward. The trigger starts to rotate forward, causing the elastic linkage to be compressed again. When the rotation angle crosses the balance line again, the elastic force of the elastic linkage instantly changes from resistance to push, assisting the trigger to rotate forward quickly. The opening of the drawstring groove quickly turns, releasing the bowstring. S43. After being released, the bowstring pushes the counterweight slider located at its front end to move forward along the main slide rail, and finally contacts the buffer assembly at the front end of the main slide rail. The buffer assembly absorbs the impact energy and makes the counterweight slider stop smoothly. S5. A single test is completed, and this process is repeated.

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