Product reliability test equipment and reliability test method

Abstract

This application discloses a product reliability testing device and method, including a frame, a loading mechanism, a first transmission assembly, and a second transmission assembly. The loading mechanism has intersecting first and second motion dimensions. The first output end of the first swing arm assembly of the first transmission assembly slides with the first transmission coupling part in the second motion dimension, driving the loading mechanism to reciprocate in the first motion dimension. The second output end of the second swing arm assembly of the second transmission assembly slides with the second transmission coupling part in the first motion dimension, driving the loading mechanism to reciprocate in the second motion dimension; the first and second swing arm assemblies have a preset phase angle difference. This device utilizes the sliding fit characteristic to improve the dynamic coupling problem of multi-axis motion, ensuring the independence of motion in each dimension. Through phase difference coordinated action, it accurately simulates complex acceleration and deceleration and acceleration changes, improving test realism, mechanical stability, and result consistency.

Description

Technical Field

[0001] This application relates to the field of product reliability testing technology, and in particular to a product reliability testing device and reliability testing method that simulates a complex motion environment. Background Technology

[0002] Some products, especially electronic products such as Bluetooth headsets, smartphones, and wearable smart devices, require reliability assessments to simulate the mechanical environment of the product in real-world usage scenarios. For example, when Bluetooth headsets are placed in a backpack and move with the body while walking, running, jumping, or going up and down stairs, they will experience complex acceleration and deceleration movements and random impacts from multiple dimensions.

[0003] In the process of developing this invention, the inventors discovered that existing testing equipment typically has the following limitations:

[0004] Most commonly used reliability testing equipment can only perform mechanical motion in a single direction (such as only vertical or only horizontal), making it difficult to reproduce the multi-dimensional complex force state in real-world carrying scenarios. Even when attempting to achieve multi-axis coordinated motion, there are often severe mechanical couplings and interferences between the drive mechanisms. When a drive mechanism in one dimension moves, the resulting force can easily interfere with the positioning and trajectory accuracy in another dimension, leading to distortion of the simulated motion waveform.

[0005] Therefore, how to better simulate the mechanical environment of products in actual use scenarios is an urgent problem that needs to be solved in current product reliability testing. Summary of the Invention

[0006] The purpose of this application is to provide a product reliability testing device and a reliability testing method, which realizes highly realistic composite motion simulation and decoupling of multiple motion dimensions.

[0007] To achieve the above-mentioned objectives, one embodiment of this application provides a product reliability testing device, comprising: frame; A loading mechanism is movably mounted on the frame. The loading mechanism includes a fixing part for placing the product to be tested. The loading mechanism has a first motion dimension and a second motion dimension that are intersected with each other. The loading mechanism includes a first transmission coupling part and a second transmission coupling part. The first transmission component includes a first swing arm assembly rotatably connected to the frame. The first swing arm assembly has a first output end. The first output end and the first transmission coupling part form a sliding engagement in the second motion dimension to drive the loading mechanism to generate reciprocating displacement in the first motion dimension. The second transmission component includes a second swing arm assembly rotatably connected to the frame. The first swing arm assembly and the second swing arm assembly have a preset phase angle difference. The second swing arm assembly has a second output end. The second output end and the second transmission coupling part form a sliding engagement in the first motion dimension to drive the loading mechanism to generate reciprocating displacement in the second motion dimension.

[0008] As a further improvement of this application, both the first swing arm group and the second swing arm group include a pivot, a front swing arm and a rear swing arm, wherein the front swing arm and the rear swing arm are connected by the pivot. The first output terminal is the end of the front swing arm of the first swing arm assembly, and the second output terminal is the end of the front swing arm of the second swing arm assembly. The front and rear swing arms of the first swing arm group are flush, and the included angle between the front and rear swing arms of the second swing arm group is the preset phase angle difference.

[0009] As a further improvement of this application, the first transmission assembly further includes a first driving power source and a first cam group, wherein the first driving power source drives the first cam group to rotate, and the rear swing arm end of the first swing arm group abuts against the first cam group. The second transmission assembly further includes a second drive power source and a second cam group. The second drive power source drives the second cam group to rotate, and the rear swing arm end of the second swing arm group abuts against the second cam group.

[0010] As a further improvement of this application, the loading mechanism includes a first layer plate and a second layer plate, the frame includes a third layer plate, the fixing part is fixed to the first layer plate, the first layer plate is connected to the second layer plate through a first guide rail group extending along the first motion dimension, and the second layer plate is connected to the third layer plate through a second guide rail group extending along the second motion dimension. The first motion dimension is the vertical direction, the second motion dimension is the horizontal direction, and the preset phase angle difference is 90°.

[0011] As a further improvement of this application, the first transmission coupling part is a first slide groove formed on the first layer plate and extending along the second motion dimension, and the first output end includes a first roller inserted in the first slide groove. The second transmission coupling part is a second slide groove formed on the second layer plate and extending along the first motion dimension, and the second output end includes a second roller inserted in the second slide groove.

[0012] As a further improvement of this application, the first cam group includes a plurality of cam plates with different profile sizes, and the first transmission assembly further includes a first shifting mechanism. The first shifting mechanism is connected to the first transmission assembly and drives the first cam group to shift to switch different cam plates to abut against the rear swing arm of the first swing arm group. The second cam group includes multiple cam plates with different profile sizes. The second transmission assembly also includes a second shifting mechanism. The second shifting mechanism is connected to the second transmission assembly and drives the second cam group to shift to switch different cam plates abutting against the rear swing arm of the second swing arm group.

[0013] As a further improvement of this application, the plurality of cam plates of the first cam group are arranged coaxially along its axial direction, and the first shifting mechanism is configured to drive the first cam group to move along its axial direction. The second cam group has multiple cam plates arranged coaxially along its axial direction, and the second shifting mechanism is configured to drive the second cam group to move along its axial direction.

[0014] As a further improvement to this application, it also includes a first moving mechanism and a second moving mechanism; The first moving mechanism is configured to cooperate with the first layer plate to drive the first layer plate to displacement and disengage the rear swing arm of the first swing arm assembly from the first cam assembly; The second moving mechanism is configured to cooperate with the second layer plate to drive the second layer plate to displacement and disengage the rear swing arm of the second swing arm assembly from the second cam assembly; Both the first and second swing arm groups have elastic reset members connected to their rotating shafts. The elastic reset members are configured to drive the corresponding swing arm group to rotate so that its rear swing arm re-engages with the corresponding cam group after the driving force of the first or second moving mechanism is removed.

[0015] To achieve one of the above objectives, one embodiment of this application provides a product reliability testing method, which uses the aforementioned product reliability testing equipment for testing. The reliability testing method includes the following steps: The product to be tested is fixed to the loading mechanism; The first transmission assembly is activated to drive the first swing arm assembly to rotate. Through the sliding cooperation between the first output end and the first transmission coupling part in the second motion dimension, the loading mechanism is driven to generate reciprocating displacement in the first motion dimension. The second transmission component is activated to drive the second swing arm assembly to rotate. Through the sliding engagement between the second output end and the second transmission coupling part in the first motion dimension, the loading mechanism is driven to generate reciprocating displacement in the second motion dimension. The displacement in the first motion dimension and the displacement in the second motion dimension are combined on the loading mechanism to form the test motion trajectory of the product under test.

[0016] To achieve one of the above objectives, one embodiment of this application provides a product reliability testing method, which uses the aforementioned product reliability testing equipment for testing. The reliability testing method includes the following steps: The first moving mechanism and / or the second moving mechanism are activated to drive the corresponding first layer plate and / or the second layer plate to move, thereby causing the rear swing arm of the corresponding first swing arm group and / or the second swing arm group to disengage from the first cam group and / or the second cam group. The first shift mechanism and / or the second shift mechanism drive the corresponding first cam group and / or the second cam group to move axially to switch the positions of cam plates with different profile sizes corresponding to the rear swing arm; When the first moving mechanism and / or the second moving mechanism are activated, the driving force on the first layer plate and / or the second layer plate is removed. Under the action of the elastic reset member, the rear swing arm of the first swing arm group and / or the second swing arm group abuts against the switched cam plate.

[0017] Compared with commonly used technologies, this application has the following beneficial effects: Firstly, the product reliability testing equipment utilizes the sliding fit characteristics of the swing arm output end and the transmission coupling part in a specific dimension. For example, the first transmission component provides sliding margin in the second motion dimension, precisely applying the driving force only to the first motion dimension, solving the dynamic coupling problem between multi-axis motions and ensuring the independence and accuracy of motion in each dimension. Secondly, through the coordinated action of the first and second swing arm groups with a preset phase angle difference, interleaved multi-dimensional reciprocating motion is formed, accurately simulating the complex acceleration and deceleration and acceleration changes in various directions experienced by the product in flexible carriers such as backpacks, significantly improving the simulation degree of the test environment and providing accurate mechanical basis for product reliability assessment. This product reliability testing equipment has better fatigue resistance and mechanical stability in continuous and cyclic motion tests, ensuring the consistency of multiple test results. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the overall structure of a reliability testing device according to an embodiment of this application.

[0019] Figure 2 This is a frontal view structural schematic diagram of a reliability testing device according to an embodiment of this application.

[0020] Figure 3 This is a structural schematic diagram of a reliability testing device according to an embodiment of this application, viewed from the rear.

[0021] Figure 4 yes Figure 3 A magnified view of a portion of point A in the middle.

[0022] Figure 5 This is a top view of a reliability testing device according to an embodiment of this application.

[0023] Figure 6 This is a perspective view of the front view of a reliability testing device according to an embodiment of this application.

[0024] Figure 7 This is a top view of the first and second swing arm assemblies according to an embodiment of this application.

[0025] Figure 8 This is a front view of the first and second swing arm assemblies according to an embodiment of this application.

[0026] Among them, 100, reliability testing equipment; 10, frame; 11, third layer plate; 20, loading mechanism; 21, fixing part; 211, fixing bracket; 22, first layer plate; 221, first transmission coupling part; 221a, first slide groove; 23, second layer plate; 231, second transmission coupling part; 231a, second slide groove; 24, first guide rail assembly; 25, second guide rail assembly; 30, first transmission component; 31, first drive power source; 32, first cam assembly; 321, cam plate; 33, first swing arm assembly; 331, rotating shaft; 3311, connecting rod; 332, front swing arm; 333, rear swing arm; 3331, roller; 334, first transmission... Output end; 3341, first roller; 335, first elastic reset member; 34, first shifting mechanism; 341, shifting motor; 342, linear transmission assembly; 343, bearing part; 3431, first bracket; 3432, second bracket; 3433, bearing seat; 35, first moving mechanism; 40, second transmission assembly; 41, second drive power source; 42, second cam group; 43, second swing arm group; 434, second output end; 4341, second roller; 435, second elastic reset member; 44, second shifting mechanism; 45, second moving mechanism; 50, product; 60, backpack; T1, first motion dimension; T2, second motion dimension. Detailed Implementation

[0027] The present application will now be described in detail with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments do not limit the present application, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the scope of protection of this application.

[0028] It should be understood that terms such as “above,” “over,” “below,” and “under” used herein to indicate spatial relative position are for illustrative purposes to describe the relationship of one unit or feature relative to another unit or feature as shown in the accompanying drawings. The terms “spatial relative position” may be intended to include different orientations of the equipment in use or operation other than those shown in the figures.

[0029] One embodiment of this application provides a product reliability testing device and a reliability testing method, which realizes highly realistic composite motion simulation and decoupling of multiple motion dimensions.

[0030] Product reliability testing involves simulating real-world usage scenarios, especially for electronic products such as Bluetooth headsets, smartphones, and smartwatches. These products are often placed in flexible containers like backpacks or pockets during daily use. As users walk, run, jump, or go up and down stairs, the products undergo multi-dimensional composite movements.

[0031] Existing testing equipment can often only perform single-dimensional simple harmonic motion simulations on rigid platforms, which ignores the cushioning characteristics of the backpack medium and the complex mechanical trajectory with specific waveforms and acceleration characteristics generated during human movement.

[0032] This embodiment provides a product reliability testing device 100 to solve the problems of mechanical interference and control coupling in multidimensional motion synthesis. The reliability testing device 100 transforms complex power source input into precise orthogonal dimensional displacement through the constraint logic of a purely mechanical structure, providing a highly simulated backpack reliability testing environment for product 50.

[0033] Specifically, such as Figure 1-3 As shown, the product reliability testing equipment 100 of this embodiment includes a frame 10, a loading mechanism 20, a first transmission component 30, and a second transmission component 40.

[0034] The frame 10 not only serves as the static support reference for the entire machine, but also provides coordinate references for multi-dimensional motion through its internal spatial layout. A movable loading mechanism 20 is mounted on the frame 10, which carries the product 50 and outputs simulated displacement.

[0035] The loading mechanism 20 is movably mounted on the frame 10. The loading mechanism 20 includes a fixing part 21 for placing the product to be tested 50. The loading mechanism 20 has a first motion dimension T1 and a second motion dimension T2 that are intersected. The loading mechanism 20 includes a first transmission coupling part 221 and a second transmission coupling part 231.

[0036] The fixing part 21 can securely attach the product 50 to be tested, or fix the test backpack 60 containing the product 50. Every displacement of the carrying mechanism 20 can be transmitted to the product 50 through the backpack 60, thereby truly evaluating the stability and structural reliability of the product 50 in a dynamic environment.

[0037] To clearly describe the relative positions and motion trajectories of each component, this case establishes the following three-dimensional Cartesian coordinate system: Z-axis (first motion dimension T1): extends along the direction of gravity, with gravity pointing downwards and upwards in the opposite direction, responsible for simulating vertical vibration and jump displacement during the test process.

[0038] X-axis (second motion dimension T2): a horizontal axis that simulates left-right swaying and lateral displacement during the test.

[0039] Y-axis (shifting dimension): The horizontal depth axis. Multiple cam plates 321 described below are arranged coaxially along this axis for stroke switching and gear adjustment.

[0040] Since the dimensions of backpack 60 in both the vertical and horizontal directions are generally much larger than its dimensions in the thickness direction (front-to-back direction), the movement of product 50 within backpack 60 is mainly limited to vertical or horizontal movement within the internal space of backpack 60. However, its front-to-back movement is more restricted by the front and rear inner walls of backpack 60, resulting in less relative displacement between product 50 and backpack 60 in the Y-axis direction compared to the X and Z axes. Therefore, this embodiment primarily focuses on testing product 50 in the left-to-right X-axis and vertical Z-axis directions.

[0041] The X, Y, and Z axes also correspond to left and right, front and back, and up and down, respectively. You can refer to them. Figure 2 , 3 As shown in Figure 5, the fixing part 21 (including the fixing bracket 211 for fixing the backpack 60) is located at the front end of the reliability testing equipment 100 (closer to the operator's side); all drive mechanisms (motors, cams, etc.) are arranged at the rear end of the reliability testing equipment 100. With the front of the reliability testing equipment 100 as a reference, the first transmission component 30 that controls the up and down movement of the Z-axis is arranged on the right side; the second transmission component 40 that controls the left and right movement of the X-axis is arranged on the left side.

[0042] The first transmission coupling unit 221 and the second transmission coupling unit 231 enable the driving of the first motion dimension T1 and the second motion dimension T2 without mechanical jamming or power loss. The first transmission coupling unit 221 and the second transmission coupling unit 231 play the role of displacement filtering. The first transmission component 30 and the second transmission component 40, which cooperate with them, output power through the swing arm assembly that is rotatably connected to the frame 10.

[0043] The first transmission assembly 30 includes a first swing arm assembly 33 rotatably connected to the frame 10. The first swing arm assembly 33 has a first output end 334. The first output end 334 and the first transmission coupling part 221 form a sliding engagement in the second motion dimension T2 to drive the loading mechanism 20 to generate reciprocating displacement in the first motion dimension T1.

[0044] The second transmission assembly 40 includes a second swing arm assembly 43 rotatably connected to the frame 10. The first swing arm assembly 33 and the second swing arm assembly 43 have a preset phase angle difference. The second swing arm assembly 43 has a second output end 434. The second output end 434 and the second transmission coupling part 231 form a sliding fit in the first motion dimension T1 to drive the loading mechanism 20 to generate reciprocating displacement in the second motion dimension T2.

[0045] The first swing arm assembly 33 reciprocates under the drive of the power source. In the second motion dimension T2, the first output end 334 can slide freely within the first transmission coupling part 221. This sliding guidance effectively filters out the power component in the direction of the second motion dimension T2. ​​In the first motion dimension T1, the cooperation between the first output end 334 and the first transmission coupling part 221 manifests as rigid displacement transmission, thereby driving the loading mechanism 20 to produce precise reciprocating displacement along the first motion dimension T1. The logic of the second transmission assembly 40 corresponds to this, but it acts in the opposite dimension.

[0046] The phase angle difference is not only a geometric misalignment, but also a temporal arrangement in mechanical synthesis. The first transmission component 30 and the second transmission component 40 can independently control the acceleration waveforms of the load-bearing mechanism 20 in the first motion dimension T1 and the second motion dimension T2 within a unified mechanical cycle. Since each motion dimension achieves component force filtering through its respective transmission coupling part, the reliability testing equipment 100 can synthesize highly complex composite motion trajectories such as "slight swaying when walking slowly" or "severe impact when running fast" through purely mechanical rigid constraints.

[0047] This embodiment, through the sliding engagement of the swing arm and the coupling part, spontaneously completes the vector decomposition and synthesis of power through the mechanical structure without the need for precise electronic control intervention, reducing energy loss and vibration noise during multi-axis linkage. Furthermore, due to the adoption of physical decoupling logic, waveform distortion caused by axial interference during high-speed operation of the reliability testing equipment 100 is effectively avoided, ensuring the accuracy and reproducibility of the test data. Because of the mechanical decoupling between the first motion dimension T1 and the second motion dimension T2, the motion mode in each direction can be independently and stably adjusted. Even under simulated extreme acceleration conditions, the efficient and stable mechanical transmission remains, providing a scientific and solid mechanical basis for the reliability evaluation of product 50 in a carrying environment.

[0048] To further simulate the stress state of product 50 in real-life scenarios, in one embodiment, such as Figure 1-3 As shown, the fixing part 21 includes a fixing bracket 211 for fixing the backpack 60. The fixing bracket 211 is provided with straps or clamps for fixing the backpack 60. The backpack 60 is used to place the product 50 to be tested.

[0049] The fixed bracket 211 is mounted on the outermost plate assembly of the loading mechanism 20. The fixed bracket 211 serves as a structure capable of bearing and simulating a flexible loading environment. The design of the straps or clamps fully considers the testing requirements of different specifications, materials, and loading weights. Through an adjustable tension mechanism, the backpack 60 containing the product under test 50 can be securely constrained within the effective load-bearing range of the bracket. During high-frequency or high-acceleration reciprocating motion simulations, the straps or clamps ensure that there is no unexpected displacement or shift between the backpack 60 and the bracket, guaranteeing the consistency of the test trajectory and the repeatability of the data.

[0050] The product 50 under test does not directly bear the impact from the swing arm, but is placed inside the backpack 60. The kinetic energy generated during movement needs to pass through the friction of the backpack 60's fabric, the cushioning of the internal filling, and the suspension effect of the shoulder strap system before it is applied to the product 50. This mechanical transmission path is consistent with the user's actual walking and running scenarios, which can more accurately test the product's performance in terms of outer shell abrasion resistance, internal structural component fatigue resistance, and electronic component solder joint reliability.

[0051] Furthermore, when the carrying mechanism 20 performs reciprocating motion in orthogonal dimensions, the product 50 inside the backpack 60 will experience slight secondary oscillations or jumps. This complex vibration characteristic generated by the flexible connection reveals the potential failure risk of the product under extreme dynamic environments more clearly than simple rigid vibration.

[0052] In one embodiment, such as Figure 4-8 As shown, the first swing arm assembly 33 and the second swing arm assembly 43 have a high degree of structural symmetry in their configuration. Both the first swing arm assembly 33 and the second swing arm assembly 43 include a pivot 331, a front swing arm 332, and a rear swing arm 333, which are connected by the pivot 331. The first output end 334 is the end of the front swing arm 332 of the first swing arm assembly 33, and the second output end 434 is the end of the front swing arm 332 of the second swing arm assembly 43.

[0053] The rotating shaft 331 is rotatably connected to the frame 10 via bearings, ensuring that the first swing arm group 33 or the second swing arm group 43 has sufficient rigidity and rotational accuracy when subjected to high-frequency reciprocating loads.

[0054] In this embodiment, the front swing arm 332 and the rear swing arm 333 of the first swing arm assembly 33 are flush, that is, their central axes coincide or are parallel in the radial plane of the rotating shaft 331, such as... Figure 7 and 8 As shown. The angle between the front swing arm 332 and the rear swing arm 333 of the second swing arm assembly 43 is a preset phase angle difference. This difference in geometric angle allows the two sets of transmission components to output displacement responses with a phase difference when receiving the same power input.

[0055] Alternatively, the angle between the front swing arm 332 and the rear swing arm 333 of the first swing arm group 33 can be θ1, and the angle between the front swing arm 332 and the rear swing arm 333 of the second swing arm group 43 can be θ2, with the difference between θ1 and θ2 being a preset phase angle difference.

[0056] Because there is a specific included angle (e.g., 90°) between the front and rear swing arms 333 of the second swing arm assembly 43, when the power source drives the rear swing arm 333 to swing in the vertical plane, the front swing arm 332 can efficiently guide the displacement vector to another dimension due to the angle change. This scheme of achieving motion direction conversion by changing the geometric phase of the same component not only decouples the complex transmission chain at the physical level, but also ensures the stability of the X-axis and Z-axis motion synthesis through a fixed mechanical angle, so that the motion posture of the product 50 remains highly accurate when simulating the real gait curve.

[0057] In one embodiment, such as Figure 4 and 5 As shown, the first transmission assembly 30 further includes a first driving power source 31 and a first cam group 32. The first driving power source 31 drives the first cam group 32 to rotate, and the end of the rear swing arm 333 of the first swing arm group 33 abuts against the first cam group 32. The second transmission assembly 40 further includes a second driving power source 41 and a second cam group 42. The second driving power source 41 drives the second cam group 42 to rotate, and the end of the rear swing arm 333 of the second swing arm group 43 abuts against the second cam group 42.

[0058] When the first drive power source 31 (such as a servo motor) rotates under control, it directly drives the first cam group 32 to rotate synchronously. Similarly, the second transmission component 40 uses the same drive and contact logic. In the reliability test of product 50, simple uniform displacement often cannot reflect the real scene. By finely designing the asymmetric surface curve of each cam plate 321 in the cam group, the acceleration change law generated by human walking or running can be directly reflected on the edge of the cam. When the motor drives the cam group to rotate at a uniform speed, the rear swing arm 333 that contacts it will generate complex variable acceleration swing according to the undulation of the cam surface, and then transmit this specific acceleration waveform to product 50 on the loading mechanism 20 through the swing arm group, thereby improving the realism and reliability of the simulated environment.

[0059] The cam mechanism exhibits greater rigidity when generating high-g instantaneous impact loads and irregular frequency responses, and is less prone to delays or instability in the electronic control system. The abutment transmission between the end of the rear swing arm 333 and the first cam group 32 or the second cam group 42 allows the reliability testing equipment 100 to withstand dynamic inertial impacts from heavy loads such as the backpack 60 without affecting the accuracy of the output waveform. This embodiment utilizes a scheme that reproduces complex motion waveforms using a purely mechanical cam profile, which not only reduces reliance on high-order motion control algorithms but also ensures the consistency of the test trajectory for each product 50 through mechanical hard constraints.

[0060] In motion simulation, if a single cam is used to drive motion in two dimensions simultaneously (such as simultaneously driving the X-axis and Z-axis), it is usually necessary to design a complex spatial cam profile or a multi-dimensional composite trajectory. In this case, motion vectors of different dimensions are physically coupled on the same cam profile, which makes the mathematical modeling and geometric design process of the cam profile curve more complex and makes it difficult to accurately control the acceleration characteristics of specific dimensions.

[0061] This embodiment decouples the first motion dimension T1 and the second motion dimension T2 in the mechanical structure, so that the first cam group 32 only needs to be responsible for the displacement and acceleration changes of the first motion dimension T1, while the second cam group 42 only needs to be responsible for the displacement and acceleration changes of the second motion dimension T2. ​​This decomposes the multidimensional motion requirements that originally needed to be combined on a single surface into two independent one-dimensional motion requirements.

[0062] Furthermore, since each cam group is designed for a single-dimensional motion trajectory, the profile curves of the cam surfaces of the first cam group 32 and the second cam group 42 are simplified. Designers can independently calculate and determine the dimensional changes of the cam plate 321 in the corresponding motion dimensions based on the acceleration waveforms required for the first motion dimension T1 and the second motion dimension T2, thereby simplifying and reducing the modeling difficulty of the cam surface design and effectively avoiding the complex calculations and complex machining contouring required for multi-dimensional motion synthesis.

[0063] Furthermore, this decoupled design enhances the flexibility of test parameter adjustment. When it is necessary to adjust the motion intensity or acceleration characteristics of a specific dimension, only the corresponding cam group for that dimension needs to be designed or replaced specifically, without remodeling the entire composite motion trajectory. In this way, the reliability testing equipment 100 simplifies the design process of the first cam group 32 and the second cam group 42 and helps improve the reproducibility accuracy of the acceleration waveform in each motion dimension.

[0064] In order for the reliability testing equipment 100 to simulate exercise scenarios of varying intensities, such as the transition from leisurely walking to high-intensity sprinting, in one embodiment, such as Figure 4 and 5As shown, the first cam group 32 includes multiple cam plates 321 with different profile sizes, and the first transmission assembly 30 also includes a first shifting mechanism 34. The first shifting mechanism 34 is connected to the first transmission assembly 30 and drives the first cam group 32 to shift to switch different cam plates 321 to abut against the rear swing arm 333 of the first swing arm group 33.

[0065] Similarly, such as Figure 4 and 5 As shown, the second cam group 42 includes multiple cam plates 321 with different profile sizes, and the second transmission assembly 40 also includes a second shifting mechanism 44. The second shifting mechanism 44 is connected to the second transmission assembly 40 and drives the second cam group 42 to shift to switch different cam plates 321 to abut against the rear swing arm 333 of the second swing arm group 43.

[0066] The first shifting mechanism 34 and the second shifting mechanism 44 can both be configured as servo drive systems driven by servo motors, driving the first transmission component 30 and the second transmission component 40 located above to move linearly along the Y-axis to switch between different gears. The surface curves of the cam plates 321 of the first cam group 32 and the second cam group 42 are pre-customized according to human kinematic data, and each plate corresponds to a specific acceleration characteristic and displacement stroke. The first shifting mechanism 34 and the second shifting mechanism 44 realize the flexible switching of these motion modes, acting directly on the corresponding cam group through mechanical connection, driving the entire cam group to produce displacement, and changing the cam plate 321 that abuts against the end of the rear swing arm 333 of the first swing arm group 33 or the second swing arm group 43.

[0067] The first shift mechanism 34 and the second shift mechanism 44 have the same structure, such as Figure 3-5 As shown, the following description uses the first shifting mechanism 34 as an example. The first shifting mechanism 34 includes a shifting motor 341, a linear transmission assembly 342, and a support part 343. The shifting motor 341 and the linear transmission assembly 342 are both firmly mounted on the rear reference surface of the frame 10, serving as the starting point of the power. The linear transmission assembly 342 includes a module of guide rails and lead screws, outputting linear motion. The support part 343 supports the first drive power source 31 and the first cam assembly 32.

[0068] The shift motor 341 drives the bearing portion 343 to linear displacement via the linear transmission assembly 342, thereby causing the first cam group 32 and the first drive power source 31 to move back and forth along the axial direction of the first cam group 32 along with the bearing portion 343. Since both the first drive power source 31 and the first cam group 32 are located on the bearing portion 343, they will move axially synchronously with the bearing portion 343 as a whole. By controlling the amount of linear displacement of the bearing portion 343, the engagement of the target cam plate 321 with the rear swing arm 333 can be precisely controlled.

[0069] This embodiment further optimizes its mechanical support structure. For example... Figure 3 As shown, the load-bearing part 343 is specifically embodied as a highly rigid frame system, which includes a first bracket 3431 and a second bracket 3432 arranged at intervals along the displacement direction (i.e., the Y-axis direction). Bearing seats 3433 are precisely mounted on both brackets to bear the rotational load of the first cam assembly 32. The two ends of the long shaft of the first cam assembly 32 are rotatably supported within the two bearing seats 3433, forming a stable simply supported beam structure with resistance to alternating stress. Furthermore, the first drive power source 31 is directly fixed to one of the brackets, such as the first bracket 3431 located at the rear. The output shaft of the first drive power source 31 is coaxially connected to one end of the first cam assembly 32 via a coupling.

[0070] The dual-point support of the first bracket 3431 and the second bracket 3432 ensures that the first cam assembly 32 will not pitch or skew during axial shifting, while also providing a stable anti-torsional base for the first drive power source 31. This compact and rigid support structure ensures that no additional structural resonance occurs inside the first shifting mechanism 34 and the second shifting mechanism 44 when the product 50 is subjected to a large acceleration impact test, guaranteeing stable testing at each gear position.

[0071] This embodiment transforms the complex reliability testing requirements of product 50 into a combination of mechanical structures and preset motion logic. Through the actions of the first shift mechanism 34 and the second shift mechanism 44, the reliability testing equipment 100 can quickly switch from "low frequency, short stroke" to "high frequency, long stroke" without replacing the core transmission components, thereby significantly expanding the testing coverage of a single device.

[0072] Since the displacement trajectories of different gears are physically determined by the rigid cam profile, this physical gear-shifting method eliminates random errors caused by unstable motor speed regulation or fluctuations in the control algorithm. Whether simulating slight vibrations or severe impacts, the equipment provides extremely high motion consistency and repeatability for testing each product 50, ensuring a consistent basis for comparing the failure mechanism analysis of product 50 at different test levels.

[0073] The first cam group 32 and the second cam group 42 can be switched synchronously or asynchronously. Taking the first cam group 32 and the second cam group 42 each having 4 cams as an example, 16 compound motion modes can be combined.

[0074] This embodiment optimizes the spatial design of the cam assembly arrangement and shifting action, such as... Figure 4 and 5As shown, multiple cam plates 321 of the first cam group 32 are arranged coaxially along its axial direction, and the first shifting mechanism 34 is configured to drive the first cam group 32 to move along its axial direction. When it is necessary to switch the test gear, the motor shaft or power support of the first shifting mechanism 34 carries the entire first cam group 32 to slide along the axial direction, so that the target cam plate 321 is accurately aligned with the end of the rear swing arm 333 of the first swing arm group 33.

[0075] Similarly, the multiple cam plates 321 of the second cam group 42 are arranged coaxially along its axial direction, and the second shifting mechanism 44 is configured to drive the second cam group 42 to move along its axial direction.

[0076] A roller can be installed on the rear swing arm 333, and the end face of the roller 3331 contacts the end face of the cam of the first cam group 32 and the second cam group 42.

[0077] This embodiment simplifies the motion chain of the shifting mechanism by limiting the shifting dimension to the axial direction. Axial displacement shifting ensures that the rollers 3331 on the rear swing arms 333 of the first swing arm group 33 and the second swing arm group 43 can always make smooth contact with different cams, ensuring that the mechanical system of the product 50 can stably respond to the load changes of various cams in various simulated complex working conditions.

[0078] In one embodiment, the loading mechanism 20 includes a first layer plate 22 and a second layer plate 23, the frame 10 includes a third layer plate 11, the fixing part 21 is fixed to the first layer plate 22, the first layer plate 22 is connected to the second layer plate 23 through a first guide rail group 24 extending along the first motion dimension T1, and the second layer plate 23 is connected to the third layer plate 11 through a second guide rail group 25 extending along the second motion dimension T2. The first layer plate 22, the second layer plate 23, and the third layer plate 11 are arranged in parallel order from front to back. The fixing part 21 is securely placed on the first layer plate 22 at the front. The first layer plate 22 is responsible for vertical movement, and the second layer plate 23 is responsible for horizontal movement. Since the first layer plate 22 is slidably connected to the second layer plate 23 through the first guide rail group 24, which extends vertically, when the second layer plate 23 moves horizontally, it drives the first guide rail group 24, the first layer plate 22, and the fixing bracket 211 to move horizontally synchronously. The vertical movement of the first layer plate 22 and the horizontal movement of the second layer plate 23 do not interfere with each other, thus achieving mechanical decoupling.

[0079] In this embodiment, the first motion dimension T1 is set as the vertical direction, the second motion dimension T2 is set as the horizontal direction, and the preset phase angle difference is 90°. The first layer plate 22 is constrained to only move vertically up and down relative to the second layer plate 23, while the second layer plate 23 can only move horizontally back and forth relative to the bottom third layer plate 11.

[0080] Because the directions of the first guide rail group 24 and the second guide rail group 25 are perpendicular and orthogonal to each other, they respectively lock all degrees of freedom outside their respective dimensions, reducing the cross interference of X-axis and Z-axis forces during transmission. When the first driving power source 31 causes the first plate 22 to jump up and down relative to the second plate 23, the force transmission is restricted within the vertical guide rails, preventing unnecessary horizontal jitter. Similarly, the horizontal movement of the second plate 23 drives the first plate 22 to move horizontally synchronously through the vertical guide rail group, without affecting the stability of the vertical dimension. With the preset 90° phase angle difference of the swing arm group, the loading mechanism 20 can transform the originally independent rotational input into a two-dimensional planar composite motion trajectory through the composite displacement of these two plates.

[0081] In one embodiment, the first transmission coupling part 221 is a first groove 221a formed on the first layer plate 22 and extending along the second motion dimension T2, and the first output end 334 includes a first roller 3341 inserted in the first groove 221a; the second transmission coupling part 231 is a second groove 231a formed on the second layer plate 23 and extending along the first motion dimension T1, and the second output end 434 includes a second roller 4341 inserted in the second groove 231a.

[0082] Both the first groove 221a and the second groove 231a can be oblong holes. The first roller 3341 and the second roller 4341 roll within the grooves, utilizing geometric constraints to extract a single-dimensional vector. Taking the first layer plate 22 as an example, the first roller 3341 has a degree of freedom in the horizontal direction within the first groove 221a. When the arc motion at the output end of the first swing arm assembly 33 generates a horizontal component, this component is filtered out due to the idle sliding of the roller within the groove, and will not drive the plate to undergo horizontal displacement. However, in the vertical direction, due to the rigid constraint of the groove sidewall, the first roller 3341 can form a displacement resistance with the first layer plate 22, thereby converting the vertical force of the swing arm into the vertical displacement of the first layer plate 22.

[0083] This embodiment utilizes the low-friction sliding fit between the rollers and the grooves to dynamically filter out force components from other dimensions while maintaining the responsiveness of the main motion dimension. Since this decoupling process is purely mechanically geometric, it ensures that the first plate 22 and the second plate 23 always travel precisely along their predetermined axes without relying on complex sensor feedback. This solves the problems of motion overload and inter-axis interference in multi-dimensional motion simulation, ensuring that the acceleration waveform experienced by product 50 remains within the design tolerance range during long-term, high-frequency reliability testing.

[0084] In one embodiment, such as Figure 2 , 5As shown in Figure 6, the reliability testing equipment 100 also includes a first moving mechanism 35 and a second moving mechanism 45; the first moving mechanism 35 is configured to cooperate with the first layer plate 22 to drive the first layer plate 22 to move and disengage the rear swing arm 333 of the first swing arm group 33 from the first cam group 32; the second moving mechanism 45 is configured to cooperate with the second layer plate 23 to drive the second layer plate 23 to move and disengage the rear swing arm 333 of the second swing arm group 43 from the second cam group 42.

[0085] The first moving mechanism 35 and the second moving mechanism 45 are used to interrupt power. Both the first moving mechanism 35 and the second moving mechanism 45 can be cylinders. During normal reliability test motion, the first moving mechanism 35 and the second moving mechanism 45 maintain a certain spatial distance from the corresponding first layer plate 22 or second layer plate 23, and the two do not interfere with each other, thereby ensuring that the load-bearing mechanism 20 can be driven by the swing arm assembly to perform high-precision simulated motion.

[0086] When a shift command is received requiring a change in simulated motion intensity, the first moving mechanism 35 and the second moving mechanism 45 will activate. The first moving mechanism 35 activates and extends its drive end, acting on the first layer plate 22 to drive it to produce a specific offset displacement, such as lifting the first layer plate 22 upwards. Similarly, the second moving mechanism 45 acts on the second layer plate 23, such as pushing the second layer plate 23 to the left. Utilizing the overall displacement of the first layer plate 22 and the second layer plate 23, the front swing arm 332 is rotated, which in turn pulls the rear swing arm 333 of the first transmission assembly 30 and the second transmission assembly 40 upwards, causing the roller at its end to disengage from the current cam assembly surface.

[0087] In this way, the first shifting mechanism 34 and the second shifting mechanism 44 can smoothly move the cam group without the mechanical pressure of the rear swing arm 333, reducing the risk of mechanical wear or jamming caused by the rollers on the rear swing arm 333 forcibly sliding along the edges of cam plates 321 of different diameters, significantly improving the service life of the cam profile, and also ensuring the safety and reliability of motion state switching when the product 50 is undergoing long-term, multi-stage automated continuous testing.

[0088] After the axial displacement shift of the cam group is completed, the transmission chain needs to be re-closed to restore the simulated drive to product 50. In one embodiment, elastic reset members are connected to the rotating shafts 331 of the first swing arm group 33 and the second swing arm group 43. The elastic reset members are configured to drive the corresponding swing arm group to rotate so that the rear swing arm 333 re-engages with the corresponding cam group after the driving force is removed by the first moving mechanism 35 or the second moving mechanism 45.

[0089] The elastic reset element can be as follows Figure 4 and 6As shown, there are long-stroke tension springs or torsion springs. These elastic reset elements always apply a preset bias torque to the corresponding swing arm assembly. The direction of this torque is opposite to the direction of the pushing force generated by the aforementioned moving mechanism.

[0090] Specifically, on the one hand, the free end of the rear swing arm 333 is configured to abut against the upper position of the cam plate 321, so as to achieve contact stability by utilizing the gravity of the rear swing arm 333.

[0091] On the other hand, a connecting rod 3311 extending radially outward is fixedly connected to the pivot 331 of the swing arm assembly. The connecting rod 3311 rotates synchronously with the pivot 331. One end of an elastic reset member (such as a tension spring) is attached to the end of the connecting rod 3311, and the other end is anchored to the frame 10. The elastic reset member continuously applies a bias torque in a preset direction to the pivot 331 through the lever arm of the connecting rod 3311. This bias torque is converted into a downward pressing force on the profile of the cam plate 321 by the roller 3331 on the rear swing arm 333. This ensures that when the first cam group 32 and the second cam group 42 rotate at high frequency and irregularly, the roller 3331 of the rear swing arm 333 can always run in close contact with the profile of the cam plate 321, and it is not easy to disengage. This ensures that the acceleration fluctuations on the profile of the cam plate 321 can be completely and undamagedly captured and transmitted to the front swing arm 332, thus achieving stable mechanical input.

[0092] After the first shifting mechanism 34 and / or the second shifting mechanism 44 pushes the target cam plate 321 to the predetermined position, the first moving mechanism 35 or the second moving mechanism 45 begins to remove the driving force, such as the cylinder retracting. The shelf, having lost its external thrust, begins to reset due to gravity or constraint, while the elastic reset member connected to the rotating shaft 331 quickly drives the first swing arm group 33 and the second swing arm group 43 to rotate in opposite directions, pulling the roller at the end of the rear swing arm 333 towards the cam group until the roller 3331 engages with the profile of the switched cam plate 321.

[0093] This embodiment achieves adaptive alignment after gear shifting. Driven by the elastic reset component, the rear swing arm 333 roller 3331 can automatically adapt to the contact height of cam plates 321 with different diameters. The elastic reset component provides a continuous mechanical preload for the entire transmission chain, ensuring that the rear swing arm 333 can always be in close contact with the cam profile when executing high-frequency, high-acceleration waveforms, effectively eliminating mechanical collisions and waveform distortion caused by gaps.

[0094] This solution, through the synergistic cooperation of the above structures, fully realizes the dimensional decoupling, precise driving, and automated shift protection required in the reliability testing of product 50.

[0095] This embodiment provides a product reliability testing method, using the aforementioned product 50 reliability testing equipment 100 for testing. The reliability testing method includes steps S10-S30. Although this application provides method operation steps as shown in the following embodiments, based on conventional or non-creative labor, the execution order of steps in which there is no necessary causal relationship in logic is not limited to the execution order provided in the embodiments of this application. For example, the order of steps S20 and S30 below can be arbitrarily adjusted, or performed simultaneously, without distinguishing the chronological order.

[0096] Step S10: Fix the product to be tested 50 to the carrier mechanism 20.

[0097] Step S20: Start the first transmission assembly 30 to drive the first swing arm assembly 33 to rotate. Through the sliding engagement of the first output end 334 and the first transmission coupling part 221 in the second motion dimension T2, drive the loading mechanism 20 to generate reciprocating displacement in the first motion dimension T1.

[0098] Step S30: Start the second transmission assembly 40 to drive the second swing arm assembly 43 to rotate. Through the sliding engagement between the second output end 434 and the second transmission coupling part 231 in the first motion dimension T1, drive the loading mechanism 20 to generate reciprocating displacement in the second motion dimension T2.

[0099] Steps S20 and S30 form a composite trajectory, where the displacement of the first motion dimension T1 and the displacement of the second motion dimension T2 are combined on the loading mechanism 20 to form the test motion trajectory of the product under test 50.

[0100] In step S10, the product 50 to be tested is placed inside the backpack 60, and the opening of the backpack 60 is closed. Then, the backpack 60 is placed on the fixed bracket 211 at the front end of the carrying mechanism 20, and the backpack 60 is securely locked using the attached straps or clamps to ensure that it does not undergo relative displacement during subsequent high-frequency movements.

[0101] Step S20 involves motion in the first motion dimension T1 (Z-axis): the first driving power source 31 drives the first cam assembly 32 to rotate. The first swing arm assembly 33 is driven to swing, and the first roller 3341 at the end of the front swing arm 332 of the first swing arm assembly 33 slides in the first groove 221a on the first layer plate 22 and extending along the X-axis direction. In this process, the horizontal displacement of the first roller 3341 in the first groove 221a is filtered out, and only the vertical thrust is applied to the first layer plate 22, thereby driving it to move up and down reciprocally along the Z-axis.

[0102] Step S30 involves the second motion dimension T2 (X-axis) motion: Similarly, the action of the second transmission component 40 drives the second roller 4341 at the end of its front swing arm 332 to slide in the second groove 231a extending vertically on the second layer plate 23, filtering out vertical displacement and only driving the second layer plate 23 to move left and right reciprocally in the X direction.

[0103] A composite trajectory is formed through steps S20 and S30: with the help of the nested guiding relationship between the first plate 22 and the second plate 23 on the Z-axis and X-axis, the backpack 60 fixed bracket 211 at the top generates a complex composite displacement, thereby causing the product 50 inside the bag to experience a highly simulated motion environment impact.

[0104] This embodiment also provides a product reliability testing method, mainly in its gear shifting method, which includes steps S40-S60.

[0105] Step S40: The first moving mechanism and / or the second moving mechanism are activated to drive the corresponding first layer plate and / or the second layer plate to move, thereby causing the rear swing arm of the corresponding first swing arm group and / or the second swing arm group to disengage from the first cam group and / or the second cam group.

[0106] Step S50: The first shifting mechanism and / or the second shifting mechanism drive the corresponding first cam group and / or second cam group to move axially to switch the positions of the cam plates 321 with different profile sizes and the rear swing arm.

[0107] Step S60: The first moving mechanism and / or the second moving mechanism are activated to remove the driving force on the first layer plate and / or the second layer plate. Under the action of the elastic reset member, the rear swing arm of the first swing arm group and / or the second swing arm group abuts against the switched cam plate 321.

[0108] In step S40, the first moving mechanism 35 and / or the second moving mechanism 45 are activated (both can be activated, or only the required moving mechanisms can be activated, the same below). Taking a cylinder as an example, the cylinder pushes out, and by driving the corresponding first layer plate 22 and / or second layer plate 23 to move, it drives the rear swing arm 333 of the first swing arm group 33 and the second swing arm group 43 to lift upward, so that the roller 3331 at its end is disengaged from the profile of the current cam plate 321.

[0109] After the disengagement action is completed, step S50 is executed, in which the first shift mechanism 34 and / or the second shift mechanism 44 move the first cam group 32 and / or the second cam group 42 along the Y-axis direction to switch the cam plate 321 of the target size to the position corresponding to the rear swing arm 333.

[0110] After the gear shift is completed, step S60 is executed, and the first moving mechanism 35 and / or the second moving mechanism 45 actuate (cylinder retracts), removing the driving force. At this time, under the force of the elastic reset member, the rear swing arm 333 returns to its original position and re-engages on the surface of the switched cam 321, completing the closure of the transmission chain.

[0111] Compared with commonly used technologies, this embodiment has the following advantages: The product reliability testing equipment 100 utilizes the sliding fit characteristics of the swing arm output end and the transmission coupling part in a specific dimension. For example, the first transmission component 30 provides sliding margin in the second motion dimension T2, precisely applying the driving force only to the first motion dimension T1, thus solving the dynamic coupling problem between multi-axis motions and ensuring the independence and accuracy of motion in each dimension. Furthermore, through the coordinated action of the first swing arm group 33 and the second swing arm group 43 with a preset phase angle difference, interleaved multi-dimensional reciprocating motions are formed, accurately simulating the complex acceleration and deceleration and acceleration changes in various directions experienced by product 50 in flexible carriers such as backpacks 60. This significantly improves the simulation degree of the test environment and provides accurate mechanical basis for the reliability assessment of product 50. The product reliability testing equipment 100 exhibits better fatigue resistance and mechanical stability in continuous and cyclic motion tests, ensuring the consistency of multiple test results.

[0112] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0113] The detailed descriptions listed above are merely specific descriptions of feasible implementation methods of this application, and are not intended to limit the scope of protection of this application. All equivalent implementation methods or modifications made without departing from the specific spirit of this application should be included within the scope of protection of this application.

Claims

1. A product reliability testing device, characterized in that, include: frame; A loading mechanism is movably mounted on the frame. The loading mechanism includes a fixing part for placing the product to be tested. The loading mechanism has a first motion dimension and a second motion dimension that are intersected with each other. The loading mechanism includes a first transmission coupling part and a second transmission coupling part. The first transmission component includes a first swing arm assembly rotatably connected to the frame. The first swing arm assembly has a first output end. The first output end and the first transmission coupling part form a sliding engagement in the second motion dimension to drive the loading mechanism to generate reciprocating displacement in the first motion dimension. The second transmission component includes a second swing arm assembly rotatably connected to the frame. The first swing arm assembly and the second swing arm assembly have a preset phase angle difference. The second swing arm assembly has a second output end. The second output end and the second transmission coupling part form a sliding engagement in the first motion dimension to drive the loading mechanism to generate reciprocating displacement in the second motion dimension.

2. The product reliability testing equipment according to claim 1, characterized in that, Both the first swing arm assembly and the second swing arm assembly include a pivot, a front swing arm, and a rear swing arm, wherein the front swing arm and the rear swing arm are connected by the pivot. The first output terminal is the end of the front swing arm of the first swing arm assembly, and the second output terminal is the end of the front swing arm of the second swing arm assembly. The front and rear swing arms of the first swing arm group are flush, and the included angle between the front and rear swing arms of the second swing arm group is the preset phase angle difference.

3. The product reliability testing equipment according to claim 2, characterized in that, The first transmission assembly further includes a first drive power source and a first cam group. The first drive power source drives the first cam group to rotate, and the rear swing arm end of the first swing arm group abuts against the first cam group. The second transmission assembly further includes a second drive power source and a second cam group. The second drive power source drives the second cam group to rotate, and the rear swing arm end of the second swing arm group abuts against the second cam group.

4. The product reliability testing equipment according to claim 3, characterized in that, The loading mechanism includes a first layer plate and a second layer plate, the frame includes a third layer plate, the fixing part is fixed to the first layer plate, the first layer plate is connected to the second layer plate through a first guide rail group extending along the first motion dimension, and the second layer plate is connected to the third layer plate through a second guide rail group extending along the second motion dimension. The first motion dimension is the vertical direction, the second motion dimension is the horizontal direction, and the preset phase angle difference is 90°.

5. The product reliability testing equipment according to claim 4, characterized in that, The first transmission coupling part is a first slide groove formed on the first layer plate and extending along the second motion dimension, and the first output end includes a first roller inserted in the first slide groove; The second transmission coupling part is a second slide groove formed on the second layer plate and extending along the first motion dimension, and the second output end includes a second roller inserted in the second slide groove.

6. The product reliability testing equipment according to claim 4, characterized in that, The first cam group includes multiple cam plates with different profile sizes, and the first transmission assembly also includes a first shifting mechanism. The first shifting mechanism is connected to the first transmission assembly and drives the first cam group to shift to switch different cam plates to abut against the rear swing arm of the first swing arm group. The second cam group includes multiple cam plates with different profile sizes. The second transmission assembly also includes a second shifting mechanism. The second shifting mechanism is connected to the second transmission assembly and drives the second cam group to shift to switch different cam plates abutting against the rear swing arm of the second swing arm group.

7. The product reliability testing equipment according to claim 6, characterized in that, The plurality of cam plates of the first cam group are arranged coaxially along its axial direction, and the first shifting mechanism is configured to drive the first cam group to move along its axial direction. The second cam group has multiple cam plates arranged coaxially along its axial direction, and the second shifting mechanism is configured to drive the second cam group to move along its axial direction.

8. The product reliability testing equipment according to claim 7, characterized in that, It also includes a first moving mechanism and a second moving mechanism; The first moving mechanism is configured to cooperate with the first layer plate to drive the first layer plate to displacement and disengage the rear swing arm of the first swing arm assembly from the first cam assembly; The second moving mechanism is configured to cooperate with the second layer plate to drive the second layer plate to displacement and disengage the rear swing arm of the second swing arm assembly from the second cam assembly; Both the first and second swing arm groups have elastic reset members connected to their rotating shafts. The elastic reset members are configured to drive the corresponding swing arm group to rotate so that its rear swing arm re-engages with the corresponding cam group after the driving force of the first or second moving mechanism is removed.

9. A product reliability testing method, characterized in that, The reliability testing method, performed using the product reliability testing equipment as described in any one of claims 1-8, includes the following steps: The product to be tested is fixed to the loading mechanism; The first transmission assembly is activated to drive the first swing arm assembly to rotate. Through the sliding cooperation between the first output end and the first transmission coupling part in the second motion dimension, the loading mechanism is driven to generate reciprocating displacement in the first motion dimension. The second transmission assembly is activated to drive the second swing arm assembly to rotate. Through the sliding engagement between the second output end and the second transmission coupling part in the first motion dimension, the loading mechanism is driven to generate reciprocating displacement in the second motion dimension. The displacement in the first motion dimension and the displacement in the second motion dimension are combined on the loading mechanism to form the test motion trajectory of the product under test.

10. A product reliability testing method, characterized in that, The reliability testing method, performed using the product reliability testing equipment as described in claim 8, includes the following steps: The first moving mechanism and / or the second moving mechanism are activated to drive the corresponding first layer plate and / or the second layer plate to move, thereby causing the rear swing arm of the corresponding first swing arm group and / or the second swing arm group to disengage from the first cam group and / or the second cam group. The first shift mechanism and / or the second shift mechanism drive the corresponding first cam group and / or the second cam group to move axially to switch the positions of cam plates with different profile sizes corresponding to the rear swing arm; When the first moving mechanism and / or the second moving mechanism are activated, the driving force on the first layer plate and / or the second layer plate is removed. Under the action of the elastic reset member, the rear swing arm of the first swing arm group and / or the second swing arm group abuts against the switched cam plate.

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