Impact load test method and device

Abstract

The present invention relates to the technical field of vehicle component reliability testing, and in particular, to an impact load testing method and device. An impact load testing method includes step S10, based on the installation of the drive shaft assembly on the test bench, obtaining the first test swing angle and the second test swing angle of the drive shaft assembly; step S20, based on the first test swing angle and the second test swing angle, controlling the drive assembly to move along a preset direction until the swing angle of the drive shaft body at the inner star wheel position is the first test swing angle, and controlling the load assembly to swing until the swing angle of the drive shaft body at the outer star wheel position is the second test swing angle; step S30, controlling the drive assembly to apply a preset speed and a first preset torque to the drive shaft assembly, and controlling the load assembly to apply a second preset torque to the drive shaft assembly; step S40, obtaining the first test result of the drive shaft assembly. In this way, the problem of low reliability of the impact load test result of the drive shaft is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle component reliability testing, and in particular to an impact load testing method and device. Background Art

[0002] After vehicle production is complete, it must be tested before entering the market to ensure compliance with standards. Vehicle testing may include appearance and assembly inspections, exhaust emissions testing, chassis testing, and driveshaft testing. Appearance and assembly inspections verify the uniformity of the paint, assembly workmanship, and interior craftsmanship, ensuring the vehicle's appearance is flawless and its assembly is tight. Exhaust emissions testing is performed to verify compliance with environmental standards. Chassis inspections typically use specialized equipment to examine the engine, transmission, and other components to ensure the absence of abnormal noise and the tightness of all connections. The driveshaft is a crucial component of the automotive drivetrain and plays a crucial role in vehicle performance and safety. Its primary function is to efficiently transmit transmission power to the wheels, enabling the vehicle to move forward. Therefore, driveshaft testing is crucial. Currently, impact load testing is commonly used to verify the driveshaft's durability, reliability, and impact resistance under impact loads, ensuring that the driveshaft maintains proper functionality under various operating conditions and thereby verifying that its quality meets stringent standards.

[0003] However, current impact load tests use a lift that is detachably connected to the drive shaft, raising and lowering one end of the drive shaft to adjust the swing angle of the drive shaft at the inner and outer planetary gears. This method adjusts the swing angle of the drive shaft to be equal at the inner and outer planetary gears, thereby testing whether the drive shaft meets strict standards at a specific swing angle. This results in a relatively simple test of the drive shaft, and the detection method does not fit actual operating conditions. Under actual operating conditions, the swing angle of the drive shaft at the outer planetary gear will be different from the swing angle of the inner planetary gear as the wheels turn. Current testing equipment cannot simulate real operating conditions, which may reduce the reliability of the drive shaft test results. Summary of the Invention

[0004] In order to solve the problem of low reliability of impact load test results of a drive shaft, the present invention provides an impact load test method and device.

[0005] In a first aspect, the present invention provides an impact load test method, comprising:

[0006] Step S10: obtaining a first test swing angle and a second test swing angle based on the drive shaft assembly being installed on the test bench;

[0007] The drive shaft assembly includes a drive shaft body, an inner star wheel, and an outer star wheel; one end of the drive shaft body is detachably connected to the inner star wheel, and the other end is detachably connected to the outer star wheel; a drive assembly is slidably connected to the test bench; a load assembly is rotatably connected to the test bench; when the drive shaft assembly is installed on the test bench, the inner star wheel is detachably connected to the drive assembly, and the outer star wheel is detachably connected to the load assembly;

[0008] Step S20: Based on the first test swing angle and the second test swing angle, the drive assembly is controlled to move in a preset direction until the swing angle of the drive shaft body at the inner planet position reaches the first test swing angle, and the load assembly is controlled to swing until the swing angle of the drive shaft body at the outer planet position reaches the second test swing angle; during the movement of the drive assembly in the preset direction, the swing angle of the drive shaft body at the outer planet position tends to increase; during the swing of the load assembly in the first rotational direction, the swing angle of the drive shaft body at the outer planet position tends to increase; during the movement of the drive assembly in the preset direction, the load assembly is controlled to swing or remain stationary in the second rotational direction; the second rotational direction is opposite to the first rotational direction;

[0009] Step S30: Based on the swing angle of the drive shaft body at the inner planet gear position reaching the first test swing angle and the swing angle of the drive shaft body at the outer planet gear position reaching the second test swing angle, controlling the drive assembly to apply a preset speed and a first preset torque to the drive shaft assembly, and controlling the load assembly to apply a second preset torque to the drive shaft assembly; the first preset torque and the second preset torque are in opposite directions;

[0010] Step S40 : Acquire a first test result of the drive shaft assembly based on the drive assembly applying the preset speed and the first preset torque to the drive shaft assembly, and the load assembly applying the second preset torque to the drive shaft assembly.

[0011] In some embodiments, in step S10, the second test swing angle changes back and forth within the preset angle range;

[0012] Step S20 includes: based on the first test swing angle and the second test swing angle, controlling the drive assembly to move along a preset direction until the swing angle of the drive shaft body at the inner star wheel position is the first test swing angle, and controlling the load assembly to swing back and forth until the swing angle of the drive shaft body at the outer star wheel position changes back and forth within the preset angle range.

[0013] In some embodiments, in step S21, based on the first test swing angle being smaller than the second test swing angle, the drive assembly is controlled to move along the preset direction until the swing angle of the drive shaft body at the inner star gear position reaches the first test swing angle;

[0014] Step S22: Based on the swing angle of the drive shaft body at the inner planet gear position being the first test swing angle, controlling the load assembly to swing along the first rotation direction until the swing angle of the drive shaft body at the outer planet gear position is the second test swing angle;

[0015] The second test swing angle is a constant value; and the swing angle of the load assembly along the first rotation direction is the difference between the second test swing angle and the first test swing angle.

[0016] In some embodiments, in step S23, based on the first test swing angle being greater than the second test swing angle, the drive assembly is controlled to move in the preset direction, and the load assembly is simultaneously controlled to swing in the second rotational direction until the swing angle of the load assembly reaches a difference between the first test swing angle and the second test swing angle.

[0017] Step S24: Based on the fact that the swing angle of the load assembly along the second rotation direction reaches the difference between the first test swing angle and the second test swing angle, the load assembly is controlled to be stationary, and the drive assembly is controlled to continue to move along the preset direction until the swing angle of the drive shaft body at the inner planet gear position reaches the first test swing angle and the swing angle of the drive shaft body at the outer planet gear position reaches the second test swing angle; wherein the second test swing angle is a constant value.

[0018] In some embodiments, step S20 includes:

[0019] Step S25: Based on the first and second test swing angles obtained, controlling the drive assembly to move in the preset direction, and simultaneously controlling the load assembly to swing about a second rotational direction, until the swing angle of the drive shaft body at the inner planet gear position reaches the first test swing angle; during the swinging of the load assembly in the second rotational direction, the swing angle of the drive shaft body at the outer planet gear position tends to decrease;

[0020] Step S26: Based on the swing angle of the drive shaft body at the inner planet gear position reaching the first test swing angle, the drive assembly is controlled to be stationary, and the load assembly is controlled to swing along the first rotation direction until the swing angle of the drive shaft body at the outer planet gear position reaches the second test swing angle; during the process of the load assembly swinging along the first rotation direction, the swing angle of the drive shaft body at the outer planet gear position gradually increases.

[0021] In some embodiments, during the process of controlling the load assembly to swing along the second rotation direction, the swing angle of the drive shaft body at the outer planetary gear position is 0°.

[0022] In some embodiments, in step S50, the values ​​of the preset speed, the first preset torque, and the second preset torque are adjusted, and steps S30 to S40 are repeated until the number of repetitions reaches a first preset number.

[0023] In some embodiments, in step S60, the value of the second test swing angle is adjusted, and steps S20 to S50 are repeated until the number of repetitions reaches a second preset number; during each cycle, the second test swing angle is a constant value.

[0024] In a second aspect, the present invention provides an impact load testing device, comprising:

[0025] test bench;

[0026] A moving assembly, the moving assembly comprising a first moving seat and a first sliding drive unit; the first moving seat is slidably connected to the test bench along a preset direction; the first sliding drive unit drives the first moving seat to slide;

[0027] A swing assembly, the swing assembly comprising a swing unit and a swing drive unit; the swing unit is rotatably connected to the test bench; the swing drive unit drives the swing unit to swing;

[0028] A drive assembly, the drive assembly comprising a drive motor and a speed sensor; the drive motor is detachably connected to the moving assembly; the drive motor applies a preset speed and a first preset torque to the drive shaft assembly to be tested; the speed sensor detects an actual speed of the drive shaft assembly;

[0029] A load assembly, comprising a load motor and a torque sensor; the load motor is detachably connected to the swing unit; the load motor applies a second preset torque to the drive shaft assembly to be tested; the first preset torque and the second preset torque are in opposite directions; the torque sensor detects the actual torque of the drive shaft assembly.

[0030] In some embodiments, the swing drive unit includes a swing motor, a screw rod, a nut seat and a connecting seat; the swing motor is rotationally connected to the test bench; the screw rod is transmission-connected to the swing motor; the nut seat is threadedly connected to the screw rod; the connecting seat is rotationally connected to the nut seat; the nut seat is slidingly arranged along the screw rod relative to the test bench, and the connecting seat is detachably connected to the swing unit.

[0031] To solve the problem of low reliability of the drive shaft impact load test results, the present invention has the following advantages:

[0032] The swing angles of the drive shaft body and the inner and outer planet wheels can be adjusted, and the first test swing angle and the second test swing angle can be made different. The swing angle of the inner planet wheel that the drive shaft assembly needs to test is a constant value, that is, the installation angle between the drive shaft assembly and the gearbox is fixed. The swing angle of the outer planet wheel can be adjusted in a large range, so that the swing of the tires during driving of the vehicle can be simulated. The drive component can apply a preset speed and a first preset torque to the drive shaft body, and the load component can apply a second preset torque to the drive shaft body. The impact strength of the drive shaft assembly can be detected after applying a certain impact load. This can truly simulate the actual use conditions of the drive shaft when the vehicle is driving, so that the quality of the drive shaft assembly can be guaranteed before it is put into use.

[0033] When adjusting the swing angles of the inner and outer planetary wheels, the present invention can reduce the torque loss caused by the slip resistance between the universal joint and the housing at the position of the inner planetary wheel when adjusting the swing angle by adjusting corresponding steps, thereby ensuring the reliability and accuracy of the test results. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 A schematic flow chart of an impact load test method according to an embodiment is shown;

[0035] Figure 2 A simplified schematic diagram showing an initial state of a drive shaft assembly according to an embodiment;

[0036] Figure 3 A simplified schematic diagram of a drive shaft assembly according to an embodiment is shown;

[0037] Figure 4 A simplified schematic diagram of a drive shaft assembly according to another embodiment is shown;

[0038] Figure 5 A schematic structural diagram of an impact load testing device according to an embodiment is shown;

[0039] Figure 6 A top view of an impact load testing device according to an embodiment is shown.

[0040] Figure numerals: test bench 10; moving assembly 20; first moving seat 21; second moving seat 22; swing assembly 30; swing unit 31; swing seat 311; third moving seat 312; swing drive unit 32; swing motor 321; screw rod 322; nut seat 323; connecting seat 324; drive assembly 40; drive motor 41; speed sensor 42; load assembly 50; load motor 51; torque sensor 52; drive shaft assembly 60; drive shaft body 61; inner star wheel 62; outer star wheel 63. DETAILED DESCRIPTION

[0041] The present disclosure will now be discussed with reference to several exemplary embodiments. It should be understood that these embodiments are discussed only to enable those skilled in the art to better understand and implement the present disclosure, rather than to imply any limitation on the scope of the present disclosure.

[0042] As used herein, the term "including" and its variations are to be interpreted as open-ended terms meaning "including, but not limited to." The term "based on" is to be interpreted as "based, at least in part, on." The terms "one embodiment" and "an embodiment" are to be interpreted as "at least one embodiment." The term "another embodiment" is to be interpreted as "at least one other embodiment." Terms such as "upper," "lower," "left," "right," "front," "back," "top," "bottom," "inner," "outer," "vertical," "horizontal," "transverse," and "longitudinal" indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. These terms are primarily intended to better describe the present application and its embodiments and are not intended to limit the devices, elements, or components indicated to having a specific orientation, or to being constructed and operated in a specific orientation. Furthermore, some of the above terms may be used to indicate other meanings besides orientation or positional relationships. For example, the term "on" may, in certain circumstances, be used to indicate a dependency or connection relationship. Those skilled in the art will understand the specific meanings of these terms in this application based on the specific circumstances. Furthermore, the terms "installed," "disposed," "provided with," "connected," and "connected" are to be interpreted broadly. For example, it can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediate medium, or an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances. In addition, the terms "first", "second", etc. are mainly used to distinguish different devices, elements, or components (the specific types and structures may be the same or different), and are not used to indicate or imply the relative importance or quantity of the indicated devices, elements, or components. Unless otherwise specified, "plurality" means two or more.

[0043] After vehicle production is complete, it must be tested before market release to ensure compliance with stringent standards. Vehicle testing can include chassis inspection and driveshaft testing. Driveshaft testing is typically performed using impact loads. However, current impact load tests utilize a removable lifter connected to the driveshaft to raise and lower one end of the driveshaft, adjusting the driveshaft's swing angle between the inner and outer planets. This method adjusts the driveshaft's swing angles to be equal between the inner and outer planets, allowing testing to verify compliance with stringent standards at specific swing angles. This results in a relatively simple driveshaft test method that is not compliant with actual operating conditions. In actual operating conditions, the driveshaft rotates with the wheels, resulting in different swing angles between the outer and inner planets. Current testing equipment cannot simulate real-world operating conditions, potentially reducing the reliability of driveshaft test results.

[0044] In this embodiment, in order to solve the above problems, Figure 1 As shown, an impact load test method is disclosed. Step S10: Before testing the drive shaft assembly 60, the drive shaft assembly 60 must be installed on the test bench 10. Once the drive shaft assembly 60 is installed on the test bench 10, a first test swing angle α1 and a second test swing angle α2 of the drive shaft assembly 60 to be tested can be obtained.

[0045] The drive shaft assembly 60 includes a drive shaft body 61, an inner star wheel 62, and an outer star wheel 63. One end of the drive shaft body 61 is detachably connected to the inner star wheel 62, and the other end of the drive shaft body 61 is detachably connected to the outer star wheel 63. A drive assembly 40 can be slidably connected to the test bench 10. A load assembly 50 can be rotatably connected to the test bench 10. When the drive shaft assembly 60 is installed on the test bench 10, the inner star wheel 62 is detachably connected to the drive assembly 40, and the outer star wheel 63 is detachably connected to the load assembly 50. At the connection between the drive shaft body 61 and the inner star wheel 62, the universal joint of the inner star wheel 62 allows the drive shaft body 61 to extend and retract axially relative to the inner star wheel 62 over a short distance. When the drive shaft assembly 60 is installed on the vehicle, the inner star wheel 62 transmits power from the transmission to the drive shaft body 61, and the outer star wheel 63 transmits power from the drive shaft body 61 to the wheels, enabling normal wheel rotation. The drive shaft assembly 60 has a direct impact on the safety and reliability of automobile transmission, and thus the detection of the drive shaft assembly 60 is extremely important.

[0046] In step S20, based on the first test swing angle α1 and the second test swing angle α2, the drive assembly 40 is controlled to move along the preset direction Y1 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches the first test swing angle α1. The load assembly 50 is then controlled to swing until the swing angle of the drive shaft body 61 at the outer planetary gear 63 reaches the second test swing angle α2. When the drive assembly 40 moves along the preset direction Y1, it also moves the end of the drive shaft body 61 connected to the inner planetary gear 62, and the swing angle of the drive shaft body 61 at the outer planetary gear 63 also changes accordingly. In other words, the second test swing angle α2 changes with changes in the first test swing angle α1.

[0047] like Figure 2 As shown, the initial swing angles at both ends of the drive shaft body 61 are 0°. As the drive assembly 40 moves along the preset direction Y1, the swing angles of the drive shaft body 61 at both the inner and outer planetary gears 62 and 63 gradually increase. The first test swing angle α1 and the second test swing angle α2 are located on opposite sides of the extension line of the drive shaft body 61. The first test swing angle α1 is the swing angle of the inner planetary gear 62 that the drive shaft assembly 60 needs to test. It is generally a constant value, meaning that the installation angle between the drive shaft assembly 60 and the gearbox is fixed. The swinging of the second test swing angle α2 does not affect the first test swing angle α1. The second test swing angle α2 can simulate the swinging process of the wheel, so the second test swing angle α2 has a wider adjustable range. When adjusting the second test swing angle α2, the angle of the first test swing angle α1 needs to be taken into account. Specifically, the difference between the first and second test swing angles α1 and α2 can be adjusted. During the movement of the drive assembly 40 along the preset direction Y1, the swing angle of the drive shaft body 61 at the outer planetary wheel 63 tends to increase. During the swinging of the load assembly 50 along the first rotation direction Q1, the swing angle of the drive shaft body 61 at the outer planetary wheel 63 tends to increase. During the movement of the drive assembly 40 along the preset direction Y1, the load assembly 50 is controlled to swing or remain stationary along the second rotation direction Q2. The second rotation direction Q2 is opposite to the first rotation direction Q1. The order of adjusting the angles of the first test swing angle α1 and the second test swing angle α2 can be in no particular order. In this way, the swing angles at both ends of the drive shaft assembly 60 can be differentiated, so that the test results are more in line with the actual driving conditions, thereby testing whether the drive shaft assembly 60 meets strict usage standards.

[0048] In step S30, based on the swing angle of the drive shaft body 61 at the inner planet 62 being a first test swing angle α1 and the swing angle of the drive shaft body 61 at the outer planet 63 being a second test swing angle α2, the drive assembly 40 can be controlled to apply a preset speed and a first preset torque to the drive shaft assembly 60, and the load assembly 50 can be controlled to apply a second preset torque to the drive shaft assembly 60. The first preset torque and the second preset torque are in opposite directions. This simulates the torque applied to the drive shaft assembly 60 by the transmission and tires during vehicle operation, thereby testing whether the drive shaft assembly 60 meets strict standards and preventing the risk of fracture due to insufficient torque tolerance after commissioning.

[0049] In step S40, a first test result of the drive shaft assembly 60 is obtained based on the drive assembly 40 applying a preset speed and a first preset torque to the drive shaft assembly 60, and the load assembly 50 applying a second preset torque to the drive shaft assembly 60. The first test result indicates whether the drive shaft assembly 60 can withstand the preset speed, the first preset torque, and the second preset torque. This indicates whether the drive shaft assembly 60 meets strict operating standards.

[0050] In this embodiment, step S50 adjusts the preset speed, first preset torque, and second preset torque values ​​to simulate different driving conditions. For example, when the wheel turns or hits an obstacle, the torque provided by the load assembly 50 will be greater. Therefore, it is necessary to increase the preset speed, first preset torque, and second preset torque values ​​to simulate actual driving conditions. Steps S30 to S40 are then repeated until the first preset number of repetitions is reached. This results in test results that better reflect the actual driving conditions encountered by the vehicle.

[0051] In this embodiment, step S60 adjusts the value of the second test swing angle α2, and steps S20 to S50 are repeated, adjusting the second test swing angle α2 to different values ​​to obtain different results. This is repeated until the second predetermined number of times is reached. During each cycle, the second test swing angle α2 remains constant. This simulates the different wheel angles of a vehicle turning while driving, allowing the drive shaft assembly 60 to be tested for strength under different operating conditions using the second test swing angle α2. This allows for more accurate testing of whether the drive shaft assembly 60 meets strict operating standards.

[0052] In this embodiment, step S20 may include step S21 and step S22.

[0053] Step S21, as Figure 3As shown, when the first test swing angle α1 to be tested is less than the second test swing angle α2, the drive assembly 40 can be controlled to move along the preset direction Y1 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches the first test swing angle α1. At this time, the swing angle of the drive shaft assembly 60 at the outer planetary gear 63 is equal to the first test swing angle α1.

[0054] In step S22 , based on the swing angle of the drive shaft body 61 at the inner planet wheel 62 being the first test swing angle α1 , the load assembly 50 is controlled to swing along the first rotation direction Q1 until the swing angle of the drive shaft body 61 at the outer planet wheel 63 is the second test swing angle α2 .

[0055] The second test swing angle α2 is a constant value. The first test swing angle α1 and the second test swing angle α2 are located on opposite sides of the extension line of the drive shaft body 61. As the load assembly 50 swings in the first rotational direction Q1, the swing angle of the drive shaft body 61 at the outer planetary gear 63 gradually increases. The swing angle of the load assembly 50 in the first rotational direction Q1 is the difference between the second test swing angle α2 and the first test swing angle α1. For example, assume that the first test swing angle α1 is 7° and the second test swing angle α2 is 30°. When the drive assembly 40 moves in the preset direction Y1 in step S21 until the first test swing angle α1 of the drive shaft body 61 at the inner planetary gear 62 reaches 7°, the second test swing angle α2 of the drive shaft body 61 at the outer planetary gear 63 is also 7°. Next, step S22 is performed, in which the load assembly 50 is controlled to swing 23° in the first rotational direction Q1, so that the swing angle of the drive shaft assembly 60 at the outer planetary gear 63 reaches 30°.

[0056] When the drive assembly 40 moves, the drive shaft body 61 tends to stretch, causing the drive shaft body 61 to move axially relative to the inner planetary gear 62. This in turn generates slip resistance at the inner planetary gear 62, which is parallel to the axial direction of the drive shaft body 61. When the output shaft of the outer planetary gear 63 forms an angle with the drive shaft body 61, this slip resistance will cause torque loss on the output shaft of the outer planetary gear 63.

[0057] By first moving the drive assembly 40 and then swinging the load assembly 50, the swinging of the load assembly 50 is prevented from expanding the swing angle of the drive shaft assembly 60 at the outer planetary wheel 63 during the process of generating slip resistance, thereby reducing the torque loss generated by the slip resistance on the outer planetary wheel 63 and improving the reliability and accuracy of the drive shaft impact load test results.

[0058] In this embodiment, step S20 may include step S23 and step S24.

[0059] Step S23, as Figure 4As shown, when the first test swing angle α1 to be tested is greater than the second test swing angle α2, the drive assembly 40 can be controlled to move along the preset direction Y1, and the angle of the first test swing angle α1 can be gradually increased. At the same time, the load assembly 50 can be controlled to swing along the second rotation direction Q2 until the swing angle of the load assembly 50 reaches the difference between the first test swing angle α1 and the second test swing angle α2.

[0060] In step S24, the load assembly 50 is controlled to be stationary at the difference between the first test swing angle α1 and the second test swing angle α2 based on the swing angle of the load assembly 50 in the second rotational direction Q2. The drive assembly 40 is then controlled to continue moving in the preset direction Y1 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches the first test swing angle α1. The swing angle of the drive shaft body 61 at the outer planetary gear 63 reaches the second test swing angle α2. The second test swing angle α2 is a constant value. As the load assembly 50 swings in the second rotational direction Q2, the swing angle of the drive shaft body 61 at the outer planetary gear 63 tends to decrease.

[0061] For example, assume the first test swing angle α1 to be tested is 7°, and the second test swing angle α2 is 3°. In step S23, the drive assembly 40 moves along the preset direction Y1 until the swing angle of the drive shaft assembly 60 at the inner star gear 62 reaches 4°. Simultaneously, the drive assembly 40 controls the load assembly 50 to swing 4° in the second rotational direction Q2, so that the load assembly 50 is coaxial with the drive shaft body 61 and the second test swing angle α2 is 0°. The load assembly 50 is then controlled to remain stationary. Next, step S24 is performed, controlling the drive assembly 40 to continue moving along the preset direction Y1 until the swing angle of the drive shaft body 61 at the inner star gear 62 reaches 7°. When the first test swing angle α1 reaches 7°, the second test swing angle α2 correspondingly reaches 3°. This allows the second test swing angle α2 to be adjusted only once in the second direction, resulting in faster adjustment. Thus, in the process of generating slip resistance, the load component 50 is prevented from swinging and expanding the swing angle of the drive shaft assembly 60 at the position of the outer planetary wheel 63, thereby reducing the torque loss caused by the slip resistance to the outer planetary wheel 63 and improving the reliability and accuracy of the impact load test results of the drive shaft.

[0062] In this embodiment, step S20 may include step S25 and step S26.

[0063] In step S25, based on the acquired first and second test swing angles α1 and α2, the drive assembly 40 is controlled to move in the preset direction Y1, while the load assembly 50 is simultaneously controlled to swing in the second rotational direction Q2 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches the first test swing angle α1. As the load assembly 50 swings in the second rotational direction Q2, the swing angle of the drive shaft body 61 at the outer planetary gear 63 tends to decrease.

[0064] In step S26, upon the drive shaft body 61 reaching a first test swing angle α1 at the inner planetary gear 62, the drive assembly 40 is controlled to remain stationary. The load assembly 50 is then controlled to swing in the first rotational direction Q1 until the drive shaft body 61 reaches a second test swing angle α2 at the outer planetary gear 63. As the load assembly 50 swings in the first rotational direction Q1, the swing angle of the drive shaft body 61 at the outer planetary gear 63 gradually increases.

[0065] For example, assuming the first test swing angle α1 is 7° and the second test swing angle α2 is 40°, in step S25, the drive assembly 40 is controlled to move along the preset direction Y1. Simultaneously, the load assembly 50 is controlled to swing about the second rotational direction Q2 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches 7°. The drive assembly 40 is then controlled to remain stationary, and the load assembly 50 is then swung along the first rotational direction Q1 until the second test swing angle α2 reaches 40°. This allows the load assembly 50 and the drive shaft body 61 to become coaxial during their swing about the second rotational direction. This allows the swing angle of the drive shaft assembly 60 at the outer planetary gear 63 to approach 0° during the generation of slip resistance, thereby reducing the torque loss caused by the slip resistance on the outer planetary gear 63 to zero and improving the reliability and accuracy of the drive shaft impact load test results.

[0066] In this embodiment, the swing angle of the drive shaft body 61 at the outer planet 63 can be controlled to be 0° during the swinging of the load assembly 50 in the second rotational direction Q2. This ensures that the load assembly 50 and the drive shaft body 61 are coaxial. This prevents the swinging of the load assembly 50 from increasing the swing angle of the drive shaft assembly 60 at the outer planet 63 during the generation of slip resistance. This reduces the torque loss caused by the slip resistance on the outer planet 63 and improves the reliability and accuracy of the drive shaft impact load test results.

[0067] In this embodiment, in step S10 , the second test swing angle α2 changes back and forth within a preset angle range.

[0068] Step S20 includes controlling the drive assembly 40 to move along a preset direction Y1 based on the first test swing angle α1 and the second test swing angle α2 until the swing angle of the drive shaft body 61 at the inner planetary gear 62 reaches the first test swing angle α1, and then controlling the drive assembly 40 to remain stationary. The load assembly 50 is then controlled to oscillate back and forth, that is, the swing angle of the drive shaft body 61 at the outer planetary gear 63 fluctuates back and forth within a preset angle range. This simulates the frequent steering required by a vehicle during driving, resulting in frequent back-and-forth fluctuations in the second test swing angle α2. This allows testing to determine whether the pull-out force during the reciprocating swing of the second test swing angle α2 meets strict operating standards.

[0069] This embodiment provides an impact load test device applicable to any of the above embodiments, such as Figure 5 As shown, the impact load testing device may include a test bench 10 , a moving assembly 20 , a swing assembly 30 , a driving assembly 40 , and a load assembly 50 .

[0070] like Figure 5 As shown, the moving assembly 20 may include a first moving seat 21 and a first sliding drive unit. The first moving seat 21 may be slidably connected to the test bench 10 along a preset direction Y1. The first sliding drive unit may drive the first moving seat 21 to slide. This allows the inner star wheel 62 and the drive shaft body 61 to form a first test swing angle α1. The moving assembly 20 may also include a second moving seat 22 and a second sliding drive unit. The second moving seat 22 is located on the side of the first moving seat 21 away from the base. The second sliding drive unit may drive the second moving seat 22 to slide. This allows the moving assembly 20 to adapt to the length of the drive shaft assembly 60.

[0071] like Figure 5 As shown, the swing assembly 30 may include a swing unit 31 and a swing drive unit 32. The swing unit 31 may be rotatably connected to the test bench 10. The swing drive unit 32 may drive the swing unit 31 to swing. The swing unit 31 may include a swing seat 311, a third movable seat 312, a third sliding drive unit and a swing drive unit 32. The swing seat 311 is detachably connected to the base, and the swing assembly 30 may swing on the swing seat 311 so that the outer planetary wheel 63 and the drive shaft body 61 form a second test swing angle α2. The third movable seat 312 is detachably connected to the swing seat 311, and the third sliding drive unit may drive the third movable seat 312 to slide. In this way, the length of the swing unit 31 and the drive shaft assembly 60 can be adapted. The first sliding drive unit, the second sliding drive unit and the third sliding drive unit may be driven in any manner.

[0072] like Figure 5 As shown, the drive assembly 40 may include a drive motor 41 and a speed sensor 42. The drive motor 41 may be detachably connected to the moving assembly 20. The drive motor 41 may apply a preset speed and a first preset torque to the drive shaft assembly 60 under test. The speed sensor 42 detects the actual speed of the drive shaft assembly 60. This allows the drive assembly 40 to simulate the transmission applying and detecting the preset speed and first preset torque to the drive shaft assembly 60 during vehicle operation. This allows the simulation of the actual operating conditions of the drive shaft assembly 60 during use.

[0073] like Figure 5As shown, the load assembly 50 includes a load motor 51 and a torque sensor 52. The load motor 51 is detachably connected to the swing unit 31. The load motor 51 applies a second preset torque to the drive shaft assembly 60 under test. The first preset torque and the second preset torque are in opposite directions. The torque sensor 52 detects the actual torque of the drive shaft assembly 60. This allows the drive assembly 40 to simulate the transmission applying and detecting the second preset torque to the drive shaft assembly 60 during vehicle operation. This allows the drive shaft assembly 60 to simulate the actual operating conditions of the drive shaft assembly 60 during use.

[0074] In this embodiment, if Figure 6 As shown, the swing drive unit 32 may include a swing motor 321, a screw rod 322, a nut seat 323 and a connecting seat 324. The swing motor 321 may be rotatably connected to the test bench 10. The screw rod 322 may be transmission-connected to the swing motor 321. The nut seat 323 may be threadedly connected to the screw rod 322. The connecting seat 324 may be rotatably connected to the nut seat 323. The nut seat 323 may be slidably arranged along the screw rod 322 relative to the test bench 10, and the connecting seat 324 may be detachably connected to the swing unit 31. The swing drive unit 32 may drive the swing unit 31 to swing, thereby simulating the angle of the wheel swing when the vehicle turns. This may increase the effectiveness of the impact load test method.

[0075] Those skilled in the art will appreciate that the above-mentioned embodiments are specific examples for implementing the present disclosure, and that in actual applications, various changes may be made thereto in form and detail without departing from the scope of the present disclosure.

Claims

1. An impact load test method, characterized in that: The impact load test method includes: Step S10, based on the drive shaft assembly being installed on the test bench, obtaining a first test swing angle and a second test swing angle; Wherein, the drive shaft assembly comprises a drive shaft body, an inner star wheel and an outer star wheel; one end of the drive shaft body is detachably connected to the inner star wheel, and the other end is detachably connected to the outer star wheel; a drive assembly is slidably connected to the test bench; a load assembly is rotatably connected to the test bench; when the drive shaft assembly is installed on the test bench, the inner star wheel is detachably connected to the drive assembly, and the outer star wheel is detachably connected to the load assembly; Step S20, based on the first test swing angle and the second test swing angle, control the drive assembly to move in a preset direction until the swing angle of the drive shaft body at the inner star wheel position is the first test swing angle, and control the load assembly to swing until the swing angle of the drive shaft body at the outer star wheel position is the second test swing angle; during the movement of the drive assembly in the preset direction, the swing angle of the drive shaft body at the outer star wheel position tends to increase; during the swing of the load assembly in the first rotation direction, the swing angle of the drive shaft body at the outer star wheel position tends to increase; during the movement of the drive assembly in the preset direction, control the load assembly to swing or remain stationary in the second rotation direction; the second rotation direction is opposite to the first rotation direction; Step S30, based on the swing angle of the drive shaft body at the inner star wheel position reaching the first test swing angle, and the swing angle of the drive shaft body at the outer star wheel position reaching the second test swing angle, controlling the drive component to apply a preset speed and a first preset torque to the drive shaft assembly, and controlling the load component to apply a second preset torque to the drive shaft assembly; the first preset torque and the second preset torque are in opposite directions; Step S40: Acquire a first test result of the drive shaft assembly based on the drive assembly applying the preset rotational speed and the first preset torque to the drive shaft assembly, and the load assembly applying the second preset torque to the drive shaft assembly.

2. An impact load test method according to claim 1, characterized in that: In the step S10, the second test swing angle changes back and forth within a preset angle range; Step S20 includes: based on the first test swing angle and the second test swing angle, controlling the drive assembly to move along a preset direction until the swing angle of the drive shaft body at the inner star wheel position is the first test swing angle, and controlling the load assembly to swing back and forth until the swing angle of the drive shaft body at the outer star wheel position changes back and forth within the preset angle range.

3. The impact load test method according to claim 1, characterized in that: The step S20 comprises: Step S21, based on the fact that the first test swing angle is smaller than the second test swing angle, controlling the drive assembly to move along the preset direction until the swing angle of the drive shaft body at the inner star wheel position is the first test swing angle; Step S22, based on the swing angle of the drive shaft body at the inner star wheel position being the first test swing angle, controlling the load assembly to swing along the first rotation direction until the swing angle of the drive shaft body at the outer star wheel position is the second test swing angle; The second test swing angle is a constant value; and the swing angle of the load component along the first rotation direction is the difference between the second test swing angle and the first test swing angle.

4. The impact load test method according to claim 1, characterized in that: The step S20 comprises: Step S23, based on the first test swing angle being greater than the second test swing angle, controlling the drive assembly to move along the preset direction, and controlling the load assembly to swing along the second rotation direction, until the swing angle of the load assembly reaches the difference between the first test swing angle and the second test swing angle; Step S24, based on the fact that the swing angle of the load assembly along the second rotation direction reaches the difference between the first test swing angle and the second test swing angle, the load assembly is controlled to be stationary, and the drive assembly is controlled to continue to move along the preset direction until the swing angle of the drive shaft body at the inner star wheel position reaches the first test swing angle, and the swing angle of the drive shaft body at the outer star wheel position reaches the second test swing angle; wherein the second test swing angle is a constant value.

5. The impact load test method according to claim 1, characterized in that: The step S20 comprises: Step S25, based on the first test swing angle and the second test swing angle obtained, controlling the drive assembly to move along the preset direction, and controlling the load assembly to swing around the second rotation direction, until the swing angle of the drive shaft body at the inner star wheel position reaches the first test swing angle; during the swinging of the load assembly along the second rotation direction, the swing angle of the drive shaft body at the outer star wheel position has a decreasing trend; Step S26, based on the swing angle of the drive shaft body at the inner star wheel position reaching the first test swing angle, the drive assembly is controlled to be stationary, and the load assembly is controlled to swing along the first rotation direction until the swing angle of the drive shaft body at the outer star wheel position reaches the second test swing angle; during the swinging of the load assembly along the first rotation direction, the swing angle of the drive shaft body at the outer star wheel position gradually increases.

6. An impact load test method according to claim 4 or 5, characterized in that: In the process of controlling the load assembly to swing along the second rotation direction, the swing angle of the drive shaft body at the outer planetary wheel position is 0°.

7. The impact load test method according to claim 1, characterized in that: The impact load test method also includes: Step S50, adjusting the values ​​of the preset speed, the first preset torque and the second preset torque, and repeating steps S30 to S40 until the number of repetitions reaches a first preset number of times.

8. An impact load test method according to claim 7, characterized in that: The impact load test method also includes: Step S60, adjusting the value of the second test swing angle, repeating steps S20 to S50 until the number of repetitions reaches a second preset number; during each cycle, the second test swing angle is a constant value.

9. An impact load test device, applied to an impact load test method according to any one of claims 1 to 8, characterized in that: The impact load testing device comprises: Test bench; A moving assembly, the moving assembly comprising a first moving seat and a first sliding drive unit; the first moving seat is slidably connected to the test bench along a preset direction; the first sliding drive unit drives the first moving seat to slide; A swing assembly, the swing assembly comprising a swing unit and a swing drive unit; the swing unit is rotatably connected to the test bench; the swing drive unit drives the swing unit to swing; A driving assembly, the driving assembly comprising a driving motor and a speed sensor; the driving motor is detachably connected to the moving assembly; the driving motor applies a preset speed and a first preset torque to the driving shaft assembly to be tested; the speed sensor detects the actual speed of the driving shaft assembly; A load component, the load component includes a load motor and a torque sensor; the load motor is detachably connected to the swing unit; the load motor applies a second preset torque to the drive shaft assembly to be tested; the first preset torque and the second preset torque are in opposite directions; the torque sensor detects the actual torque of the drive shaft assembly.

10. An impact load testing device according to claim 9, characterized in that: The swing drive unit includes a swing motor, a screw rod, a nut seat and a connecting seat; the swing motor is rotationally connected to the test bench; the screw rod is transmission-connected to the swing motor; the nut seat is threadedly connected to the screw rod; the connecting seat is rotationally connected to the nut seat; the nut seat is slidingly arranged along the screw rod relative to the test bench, and the connecting seat is detachably connected to the swing unit.

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