Method for predicting wear life of spline under high-speed working condition

Abstract

The invention discloses a spline wear life prediction method under a high-speed working condition, which comprises the following steps: mounting a spline shaft and a torque transmission shaft as a meshing pair in an established test system, enabling the meshing pair to run for specified times under different simulation working conditions, then respectively carrying out spline tooth surface wear measurement, and finally fitting each wear amount to obtain a wear rule. Therefore, the spline pair can be replaced in time when the allowable maximum abrasion loss is achieved in the working process, safety accidents caused by spline abrasion failure under the high-speed working condition are avoided, the problem that the economic cost is increased due to the fact that the spline pair is replaced too early is solved, the operation safety of the spline pair is improved, and the operation cost is reduced.

Description

Technical Field

[0001] This invention belongs to the field of mechanical wear life, specifically a method for predicting spline wear life under high-speed operating conditions. Background Technology

[0002] In marine propulsion systems, helical splines are commonly used to connect the engine and propeller shafts. They not only need to transmit enormous torque but also withstand the axial thrust generated by the propeller, ensuring efficient and stable power output. In aero engines, helical splines are used for the power connection between the turbine and compressor, requiring reliable performance even under extreme speed and temperature conditions. However, in actual operation, the contact surfaces of helical spline pairs will wear due to relative sliding friction. Long-term wear can lead to material spalling on the tooth surfaces, increased clearance, and consequently reduced drive accuracy and efficiency, or even failure.

[0003] Splines, as a critical detachable transmission component, are widely used in high-speed, high-load applications such as automotive transmissions, wind power generation main drive systems, and aircraft engines. However, during frequent high-speed engagement-disengagement cycles, engaging splines face severe contact impacts and complex lubrication conditions, causing their microscopic surface morphology and material properties to degrade rapidly, directly leading to transmission system failure and safety accidents. For example, the cost of routine repairs for wind turbine main drive systems caused by spline failure can reach hundreds of thousands of yuan, and unforeseen downtime can result in additional economic losses of thousands of yuan per hour. Spline wear and failure during high-speed gear shifts in automotive transmissions have also caused numerous incidents of power interruption or misoperation while driving, resulting in significantly increased recall and repair costs.

[0004] In order to study the wear life of splines during engagement and disengagement, many researchers have designed spline pair wear test devices to study the life of splines during operation.

[0005] CN202411314823.1 discloses a spline wear test device, including a testing mechanism and an adjustment mechanism, which solves the problem of inaccurate experimental results when the spline wear test device is adjusted to different tilt angles of misalignment.

[0006] CN202510104226.4 discloses a fretting wear testing device for spline pairs, including an axial adjustment component, a radial adjustment component, and an angle adjustment component. This avoids the need to disassemble and reassemble the base multiple times during friction and wear tests, and solves various misalignment issues such as parallel misalignment, axial floating, and angular misalignment, thereby increasing the applicability of the device.

[0007] CN201410143622.X discloses a comprehensive test bench for the wear life of involute gears. This test bench can verify the wear life of involute gears with a large tip circle diameter, and provide experimental data for establishing a coordination equation between gear tooth profile error and wear life.

[0008] However, none of the above documents involve research on spline wear life under high-speed operating conditions.

[0009] CN108871769B discloses a fixed involute spline pair fretting wear test device. Through a base, a variable frequency motor drive unit, a laser displacement sensor and a counterweight adjustment system, it can accurately measure the misalignment and wear of the spline pair under low-frequency reciprocating fretting state. However, the device cannot simulate the dynamic engagement-disengagement process under high-speed working conditions and lacks systematic tracking and analysis of the life change law.

[0010] CN108871770B proposes a floating involute spline pair fretting wear test device. By eliminating the support structure and introducing an adjustable counterweight, it expands the testing capability for misalignment. However, it is still limited by low-speed, small-displacement fretting and cannot meet the requirements of high-speed, heavy-load, periodic testing.

[0011] CN106932197A discloses an involute spline pair engagement-disengagement fretting wear test bench, which uses differential loading and small-amplitude reciprocating displacement to simulate adhesive wear behavior, providing a platform for coating performance evaluation. However, the maximum speed and load capacity are limited and insufficient to cover the high-speed start-stop cycle wear characteristics required in actual engineering.

[0012] WO2006028941A2 improves the resistance to fretting wear through DLC coating. Although it improves the surface properties, it is limited to low-frequency vibration tests at room temperature and cannot reveal the evolution law of joint wear under complex actual working conditions.

[0013] None of the technical solutions disclosed in the above documents provide the ability to analyze the wear life of spline pairs under extreme service conditions such as high speed, heavy load, and frequent impact. Summary of the Invention

[0014] The purpose of this invention is to provide a method for predicting the wear life of splines under high-speed operating conditions, so that spline pairs can be replaced in a timely manner when they reach the maximum allowable wear, thereby improving safety and reducing costs.

[0015] The method for predicting the wear life of splines under high-speed operating conditions provided by this invention involves installing the spline shaft and the torsion transmission shaft as a meshing pair in a test system. After the meshing pair is run a specified number of times under different simulated operating conditions, the wear of the spline tooth surface is measured. Finally, the wear values ​​are fitted to obtain the wear pattern.

[0016] When the above method is implemented, the test system includes a rotary drive device, an axial drive device, and a lubrication device. The spline shaft and the torsion transmission shaft are meshing pairs. The rotary drive device realizes the high-speed rotation of the meshing pairs, while the axial drive device realizes the engagement and disengagement of the meshing pairs. The lubrication device provides lubricating oil to the meshing pairs.

[0017] When the above method is implemented, the rotary drive device is fixed on the worktable and includes a stepper motor and a rotating shaft connected to its output shaft; the spline shaft and the torque transmission shaft are fitted in the middle of the rotating shaft in an engaged state, the inner end of the spline shaft is connected to the fixed shaft, and the outer end of the torque transmission shaft is connected to the transmission flange; the connection between the fixed shaft and the rotating shaft realizes the synchronous rotation of the meshing pair and the rotating shaft, and the transmission flange is used to connect the axial drive device.

[0018] When the above method is implemented, the fixed shaft has a convex structure, including a bushing section and a mating section at its outer end. The bushing section and the rotating shaft are connected by a flat key to achieve radial limiting, and the axial limiting is achieved by a nut connected on the rotating shaft. The mating section is used to connect the splined shaft.

[0019] When the above method is implemented, the transmission flange has a convex structure, including a flange and a bushing on its outer side. The flange is connected to the torsion shaft, and the bushing is clearance-fitted with the rotating shaft.

[0020] When the above method is implemented, the axial drive device includes a cylinder, a double-row angular contact ball bearing and its matching bearing housing and nut; the double-row angular contact ball bearing is sleeved on the bushing of the transmission flange, with the inner end limited by the shoulder of the bushing and the outer end limited by the nut connected to the bushing; the cylinder is a guide rail slide cylinder or a rodless cylinder, fixed on the worktable, and a transition seat is connected between the cylinder slider and the bearing housing; the reciprocating motion of the slider causes the reciprocating motion of the torsion shafts in opposite directions and the reciprocating motion of the spline shafts in opposite directions through the transmission flange.

[0021] When the above method is implemented, a central oil hole is provided from the middle to the outer end of the rotating shaft, an oil injection hole is provided on the hole wall corresponding to the meshing pair mounting section, and an oil guide hole is provided on the wall of the torsion shaft.

[0022] When the above method is implemented, the lubrication device includes a hydraulic pipeline and a rotary joint connected to its outer end. The rotary joint is connected to the outer end of the rotating shaft through a reverse thread, so that the rotary joint is sealed to the rotating shaft while not rotating with the rotating shaft.

[0023] The above method includes the following steps:

[0024] (1) Determine the structural and operating parameters of the spline meshing pair;

[0025] (2) Install the spline pair in the test system in an engaged state, with an engagement length of 3 to 40 mm;

[0026] (3) Test the system to work, stop the machine at the set time to measure the wear of the spline tooth surface, and observe whether there are broken teeth and obvious cracks.

[0027] (4) Repeat step (3) for each change in a working parameter of the spline meshing pair.

[0028] (5) Refer to step (2) to replace the spline pair with different structural parameters;

[0029] (6) Repeat steps (3) and (4);

[0030] (7) Repeat steps (5) and (6);

[0031] (8) Analyze and process all the wear data to obtain the number of wear cycles of the spline pair.

[0032] When the above method is implemented, in step (1), the structural parameters include tooth clearance, helix angle, rounding radius, and tooth chamfer radius, and the working parameters include rotational speed, power, pressure, and engagement speed.

[0033] In step (3), the set time is determined based on the set number of spline engagement-disengagement cycles; the worn spline is measured using a measuring bar, and the wear step height is evaluated using the spline span bar distance to determine whether the spline is damaged.

[0034] This invention establishes a new testing system to simulate the motion of spline pairs under different high-speed operating conditions. After the spline pairs run a specified number of times under different simulated operating conditions, the wear of the spline tooth surfaces is measured. Finally, the wear values ​​are fitted to obtain the wear pattern, which allows the spline pairs to be replaced in time when they reach the maximum allowable wear during operation. This avoids safety accidents caused by spline wear failure under high-speed operating conditions and solves the problem of increased economic costs due to premature replacement of spline pairs. In other words, it improves the operational safety of spline pairs and reduces operating costs. Attached Figure Description

[0035] Figure 1 This is a schematic diagram of the overall layout of the test system in one embodiment of the present invention.

[0036] Figure 2 for Figure 1 Enlarged structural diagram of the rotary drive device (rotary joint with lubrication device connected to the end of the shaft).

[0037] Figure 3 for Figure 1 The oil collection cover has been removed and only the structural diagram of the rotary joint is shown (the lubrication device is not fully shown).

[0038] Figure 4 for Figure 3A schematic diagram of the structure after removing the bearing housing of the double-row angular contact ball bearing. Detailed Implementation

[0039] This embodiment takes the helical spline of the aerospace tail thrust clutch system as the research object, simulates the power transmission scenario in the engine system, builds a test system, and studies the wear life of the helical spline tooth surface under high power and high speed conditions through the test system, that is, how many engagement-disengagement cycles can be performed, providing technical support for the spline pair to be replaced at the appropriate time, improving the operational safety of the spline pair and reducing operating costs.

[0040] like Figure 1 , Figure 3 As shown, the testing system includes a rotary drive unit 1, an axial drive unit 2, and a lubrication unit 3. The rotary drive unit 1 and the axial drive unit 2 are mounted on the worktable 4. The structure of the testing system and the installation of the spline pair (spline shaft and torque transmission shaft) in the testing system are described in detail below.

[0041] like Figure 1 , Figure 2 As shown, the rotary drive device 1 includes a stepper motor 11, a coupling 12, and a rotating shaft 13. The stepper motor 11 is fixed to the base on the top surface of the workbench via a base. The motor output shaft is connected to the rotating shaft 13 via the coupling 12 and a key. The stepper motor 11 drives the rotating shaft 13 to rotate.

[0042] like Figure 1 , Figure 3 As shown, the spiral spline shaft 5 of the workpiece to be tested and the torque transmission shaft 6 meshing with its right end are installed in the middle section of the rotating shaft 13. Therefore, the two sides of the middle section of the rotating shaft 13 are fixed to the support base on the top surface of the worktable by bearings and bearing seats respectively. Figure 1 In the middle, the spline shaft and the torque transmission shaft are covered by the oil collection tank JYX.

[0043] As shown in Figure 3, the mounting structure of the helical spline shaft 5 is a fixed shaft 7, which has a convex structure, including a bushing section at the left end and a mating section at the right end. The bushing section is radially positioned by a key connection to the rotating shaft 13, and axially positioned by a nut connected to the rotating shaft, allowing the fixed shaft 7 to rotate with the rotating shaft 13. The mating section is connected to the spline shaft by an axial pin, allowing the spline shaft 5 to rotate with the rotating shaft 13.

[0044] The side wall of the torsion shaft 6 is provided with an oil guide hole.

[0045] The initial state of the torsion shaft 6 is to maintain a meshing length of at least 3 mm with the spline shaft 5.

[0046] like Figure 3 , Figure 4As shown, the right end of the torsion shaft 6 has a mounting structure with a bushing, a transmission flange 8, whose bushing is fitted onto the rotating shaft 13 with a clearance fit, and its flange is connected to the torsion shaft by an axial pin.

[0047] like Figure 1 , Figure 3 and Figure 4 As shown, the axial drive device 2 includes a cylinder 21, a transition seat 22, a double-row angular contact ball bearing 23, a bearing housing 24, and a nut LM.

[0048] Cylinder 21 is a guide rail slide cylinder or a rodless cylinder, horizontally fixed on the worktable 4. The cylinder's slider is connected to the vertical transition seat 22.

[0049] The double-row angular contact ball bearing 23 is connected to the bushing of the transmission flange 8. The left end is limited by the shoulder on the bushing, and the right end is limited by the nut LM connected to the bushing.

[0050] The double-row angular contact ball bearing 23 is interference-fitted with the bearing housing 24 and the transition housing 22.

[0051] The principle of how an axial drive device enables the torque transmission shaft to move along the rotating shaft:

[0052] When the cylinder 21 works, it causes the slider to reciprocate left and right. The transition seat 22 carries the bearing seat 24 to reciprocate left and right. The bearing seat and the double row angular contact ball bearing 23 are interference fit to form a whole. The double row angular contact ball bearing is limited by the nut and the shaft shoulder. Therefore, the bearing seat 24 can carry the torque shaft 6 to reciprocate left and right through the transmission flange 8.

[0053] The stroke of cylinder 21 is at least 3mm longer than the length of torque transmission shaft 6 to ensure stable meshing between torque transmission shaft and spline shaft 5.

[0054] like Figure 1 As shown, the lubrication device 3 includes an oil pump 31 and its connected hydraulic pipeline, with a rotary joint 32 at the end of the hydraulic pipeline. The rotary joint is an outsourced component, manufactured by Tengzhou Jiangsheng Rotary Joint Co., Ltd.

[0055] The lubrication device 3 supplies oil to the rotating shaft 13 through the rotary joint 32.

[0056] An oil inlet hole is provided from the middle to the right end along the axial center of the rotating shaft 13. The right end also has a threaded hole section with a diameter larger than the oil inlet hole. An oil spray hole (e.g., ...) is provided on the shaft wall at the position corresponding to the splined shaft. Figure 2 (As shown).

[0057] The connecting end of the rotary joint 32 is connected to the right end of the rotating shaft 13 by a reverse thread, so that the rotary joint is sealed to the rotating shaft and does not rotate with the rotating shaft.

[0058] The principle of the lubrication device providing lubricating oil to the spline gear surfaces:

[0059] The oil pump 31 pressurizes the lubricating oil and sends it into the oil inlet of the rotating shaft 13 through the rotary joint 32. While the rotating shaft is rotating at high speed, it throws the hydraulic oil out from the oil injection hole to the spline gear surface.

[0060] After the lubricating oil lubricates the spline tooth surface, it will be thrown out under the action of centrifugal force. Therefore, the middle section of the rotating shaft 13 is connected to the oil collection tank 9, which is equipped with an oil drain pipe, which drains the oil to the oil drum.

[0061] When setting up the test system and installing the splined connector, please pay attention to the following two points:

[0062] The testing system must be axially / radially aligned to prevent eccentricity from increasing the wear of the spline pair. Use a high-precision dial indicator or laser alignment instrument for calibration to ensure that the coaxiality of the spline pair and the shaft is ≤0.02mm and the axial deviation angle is ≤0.05°.

[0063] Before connecting the lubrication device 3 to the rotating shaft 13, run it unloaded for 5 minutes to ensure that the pressurized oil can be normally sent into the oil inlet hole inside the rotating shaft and thrown out.

[0064] When performing wear testing on spline pairs using a testing system, the following steps are included:

[0065] (1) Prepare the number of spline pairs for testing.

[0066] The structural parameters of a spline pair include: tooth flank clearance, helix angle, fillet radius, and tooth flank chamfer radius;

[0067] Operating parameters include: speed, power, pressure, and engagement speed.

[0068] In this embodiment, the standard values ​​of the structural parameters of the spline pair are as follows: tooth clearance 0.07mm, helix angle 50°, rounding radius 0.4mm, and tooth chamfer radius 0.1mm; the standard values ​​of the operating parameters are as follows: rotational speed 4500r / min, power 2.5kW, pressure 100N, and engagement speed 2.75mm / s. The standard values ​​of the structural and operating parameters are selected based on the general conditions of high-speed spline operation.

[0069] Then, the structural and operating parameters were adjusted, one parameter at a time, with each parameter adjusted twice. For example, the rotational speed was adjusted from 4500 r / min to 4000 r / min and then to 5000 r / min. Finally, the number of tests for the spline pair was determined.

[0070] The specific adjustments for each parameter are shown in the table below (Table 1):

[0071] (2) Testing of spline pairs with standard parameters under standard operating conditions:

[0072] The stepper motor of the rotary drive device operates, causing its speed to increase in a stepwise manner, with each increase being 500 revolutions, and stabilizing for 3 minutes after each increase;

[0073] The cylinder operates, causing the axial movement speed of the torque transmission shaft to be 2.75 mm / s (engagement speed). After every 1000 engagement-disengagement cycles, a 20-minute pause is taken for thermal balance compensation.

[0074] Stop the machine after 8000 cycles of spline engagement and disengagement, remove the spline pair from the test system, and measure the wear of the spline tooth surfaces.

[0075] The wear step height is evaluated by measuring with a gauge bar and by the spline span. If the wear step height of the inner and outer spline tooth surfaces does not exceed 0.15mm (the maximum wear amount for spline failure), the helical spline is considered to be undamaged.

[0076] (3) Reinstall the spline pair in the test system, and only change the speed to 4000 r / min and 5000 r / min respectively to perform the test according to step (2) to obtain the wear data of the spline tooth surface;

[0077] (4) Refer to step (3) to change the power, pressure and engagement speed of the spline pair and conduct tests to obtain the wear data of the spline tooth surface;

[0078] (5) Install the new spline pairs into the test system according to the structural parameters in Table 1. Following the steps above, obtain a wear data for each parameter changed until all structural parameters in Table 1 have been tested and the corresponding spline tooth surface wear data are obtained.

[0079] (6) Data summary

[0080] The data obtained from the above test are as follows:

[0081] Under standard structural parameters and standard operating conditions, the total wear of the spline pair after 8000 engagement-disengagement cycles is approximately 0.0398 mm. Calculations show that the wear per engagement-disengagement cycle is approximately 4.98 × 10⁻⁶ mm. -6 mm.

[0082] The total wear of the spline pair after 8000 engagement-disengagement cycles and the wear after one engagement-disengagement cycle under other structural and operating parameters are shown in Table 2 below.

[0083] (7) Data processing

[0084] The wear amount of a single engagement / disengagement was calculated using the different working conditions and structural parameters in Table 2. The influence of different parameter variations on the wear amount y was then fitted into a formula, and the fitting was performed according to the following steps:

[0085] 1. Data Acquisition: Collect relevant data on different structural parameters and operating conditions, and perform preprocessing, including data cleaning, handling missing values, and handling outliers.

[0086] 2. Data visualization: Displaying data in the form of charts and graphs to intuitively observe data trends.

[0087] 3. Model Construction: The obtained wear data is fitted using multivariate nonlinear regression, and regularization techniques are combined to improve model stability in order to capture the complex coupling relationship between parameters.

[0088] 4. Function Optimization: Feature selection and coefficient optimization. Through cross-validation and residual analysis, the contribution of each input indicator to life prediction is evaluated; redundant parameters with little impact on the results are eliminated, and the regression coefficients of key parameters are iteratively corrected to balance prediction accuracy and engineering interpretability.

[0089] 5. Model Validation: Validate the fitted model to see if it is suitable and whether it is overfitted or underfitted.

[0090] The fitting results obtained by following the above steps are shown below:

[0091] In the above formula, W is the wear amount of one engagement and disengagement under standard working conditions, n: rotational speed (r / min), P: power (kW), F: pressure (N), V: engagement speed (mm / s), G: tooth backlash (mm), β: helix angle (°), R: rounding radius (mm), C: tooth chamfer radius (mm).

[0092] The structural parameters and operating parameters (n) of the standard operating condition are used. 标 =4500r / min, P 标 =2.5kW, F 标 =100N, V 标 =2.75mm / s, G 标 =0.07mm, β 标 =50°R 标 =0.4mm, C 标 Substituting (=0.10mm) into the above formula, we obtain the wear amount W = 4.98 × 10⁻⁶ mm for one disengagement of the helical spline pair. -6 mm. This verifies that the above fitting formula is correct.

[0093] When all other parameters remain unchanged, and only the rotational speed n=5000 r / min is changed... y = 5.74 × 10 -6 mm

[0094] The result calculated using the above formula is compared with the data obtained from the test (5.68 × 10). -6 The error between mm and the above fitting formula is 1.05%, which is within the acceptable range. Therefore, the above fitting formula is verified to be correct.

[0095] The wear amount is required to be no more than 0.15mm. Under standard operating conditions, according to the formula:

[0096] In the above formula, W max The maximum wear amount is specified in the index, and N is the number of engagement and disengagement cycles. According to the above formula, under standard working conditions, when the maximum wear amount is required to be 0.15mm, the spiral spline pair can engage and disengage more than 30,000 times, which meets the requirement of 8,000 cycles in the test.

[0097] In this application, "engagement-disengagement" of the spline pair refers to the movement of the spline shaft and the torque transmission shaft towards each other until their end faces are aligned, and then the movement of the spline shaft towards the opposite side of the torque transmission shaft until the initial engagement state is reached.

[0098] This invention is also applicable to predicting the wear life of spline pairs under high-speed operating conditions.

Claims

1. A method for predicting spline wear life under high-speed operating conditions, characterized in that: The method involves installing the splined shaft and the torsion transmission shaft as a meshing pair in a constructed test system. After the meshing pair is run a specified number of times under different simulated working conditions, the wear of the spline tooth surface is measured. Finally, the wear values ​​are fitted to obtain the wear pattern.

2. The method as described in claim 1, characterized in that: The testing system includes a rotary drive device, an axial drive device, and a lubrication device. The spline shaft and the torsion transmission shaft are meshing pairs. The rotary drive device enables high-speed rotation of the meshing pairs, while the axial drive device enables engagement and disengagement of the meshing pairs. The lubrication device provides lubricating oil to the meshing pairs.

3. The method as described in claim 2, characterized in that: The rotary drive device is fixed on the worktable and includes a stepper motor and a rotating shaft connected to its output shaft; the spline shaft and the torque transmission shaft are meshed in the middle of the rotating shaft, the inner end of the spline shaft is connected to the fixed shaft, and the outer end of the torque transmission shaft is connected to the transmission flange; the connection between the fixed shaft and the rotating shaft enables the meshing pair to rotate synchronously with the rotating shaft, and the transmission flange is used to connect the axial drive device.

4. The method as described in claim 3, characterized in that: The fixed shaft has a convex structure, including a bushing section and a mating section at its outer end. The bushing section is connected to the rotating shaft by a flat key to achieve radial limiting, and a nut connected to the rotating shaft to achieve axial limiting. The mating section is used to connect the splined shaft.

5. The method as described in claim 3, characterized in that: The transmission flange has a convex structure, including a flange and a bushing on its outer side. The flange is connected to the torsion shaft, and the bushing is clearance-fitted with the shaft.

6. The method as described in claim 2, characterized in that: The axial drive device includes a cylinder, a double-row angular contact ball bearing and its matching bearing housing and nut; the double-row angular contact ball bearing is sleeved on the outside of the bushing of the transmission flange, with the inner end limited by the shoulder of the bushing and the outer end limited by the nut connected to the bushing; the cylinder is a guide rail slide cylinder or a rodless cylinder, fixed on the worktable, and a transition seat is connected between the cylinder slider and the bearing housing; the reciprocating motion of the slider causes the reciprocating motion of the torsion shafts in opposite directions and the spline shafts in opposite directions through the transmission flange.

7. The method as described in claim 2, characterized in that: A central oil hole is provided from the middle to the outer end of the rotating shaft, and an oil injection hole is provided on the hole wall corresponding to the meshing pair mounting section. An oil guide hole is provided on the wall of the torsion shaft.

8. The method as described in claim 7, characterized in that: The lubrication device includes a hydraulic pipeline and a rotary joint connected to its outer end. The rotary joint is connected to the outer end of the rotating shaft by a reverse thread, so that the rotary joint is sealed to the rotating shaft and does not rotate with the rotating shaft.

9. The method according to any one of claims 1-8, characterized in that, Includes the following steps: (1) Determine the structural and operating parameters of the spline meshing pair; (2) Install the spline pair in the test system in an engaged state, with an engagement length of 3 to 40 mm; (3) Test the system to work, stop the machine at the set time to measure the wear of the spline tooth surface, and observe whether there are broken teeth and obvious cracks. (4) Repeat step (3) for each change in a working parameter of the spline meshing pair. (5) Refer to step (2) to replace the spline pair with different structural parameters; (6) Repeat steps (3) and (4); (7) Repeat steps (5) and (6); (8) Analyze and process all the wear data obtained, and calculate the theoretical wear count of the spline pair.

10. The method as described in claim 9, characterized in that: In step (1), the structural parameters include tooth clearance, helix angle, rounding radius, and tooth chamfer radius, and the working parameters include rotational speed, power, pressure, and engagement speed. In step (3), the set time is determined based on the set number of spline engagement-disengagement cycles; the worn spline is measured using a measuring bar, and the wear step height is evaluated using the spline span bar distance to determine whether the spline is damaged.

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