Gearbox out-of-gear prevention inverted cone spline design method based on multi-body dynamics

Abstract

The invention provides a gearbox out-of-gear prevention inverted cone spline design method based on multi-body dynamics, and the method comprises the steps: calculating out-of-gear force in a simulation calculation mode based on multi-body dynamics software LMS Virtual.Lab; inversely calculating parameters of the inverted cone spline by using a theoretical calculation form; in order to judge whether the parameters, obtained through back calculation, of the back taper spline are appropriate or not, checking calculation is conducted through multi-body dynamics software LMS Virtual.Lab, if the out-of-gear force is smaller than the anti-off-gear force, the parameters of the back taper spline are appropriate, and if not, the parameters of the back taper spline are selected again. According to the method, the technical problem of how to accurately design the out-of-gear preventing reverse taper spline parameters of the multi-gear power flow gearbox is solved, and the out-of-gear force of the gearbox can be accurately calculated.

Description

Technical Field

[0001] The invention belongs to the technical field of physical computer-aided design, and in particular relates to a design method for a gearbox anti-shifting inverted cone spline based on multi-body dynamics. Background Art

[0002] A multi-speed power flow gearbox is a gearbox that achieves power transmission through multiple sets of gear transmission paths (i.e., multiple gears). Each gear corresponds to a different transmission ratio and is suitable for working conditions that require frequent adjustment of speed and torque (such as automotive transmissions and construction machinery gearboxes).

[0003] Multi-speed power flow gearboxes often use spline clutches as a shifting method. However, when a multi-speed power flow gearbox uses a spline clutch as an important component for transmitting torque in different gears and under different working conditions, there is a risk of gear shifting.

[0004] To prevent gear shifting, current methods rely on empirically designed inverted tapered splines. However, these methods are unable to accurately and effectively design the inverted tapered spline parameters, such as the inverted taper angle a, taper length l, number of spline teeth Z, and spline module m. To address this issue, the following technical solution is proposed. Summary of the Invention

[0005] The technical problem solved by the present invention is to provide a gearbox anti-shifting inverted cone spline design method based on multi-body dynamics, and solve the technical problem of how to accurately design the anti-shifting inverted cone spline parameters of a multi-speed power flow gearbox.

[0006] The technical solution adopted by the present invention is: a design method for an anti-shifting inverted tapered spline of a gearbox based on multi-body dynamics. First, based on the multi-body dynamics software LMS Virtual.Lab, the shifting force is calculated by simulation calculation; secondly, the parameters of the inverted tapered spline are inversely calculated by theoretical calculation; thirdly, in order to determine whether the parameters of the inverted tapered spline obtained by inverse calculation are appropriate, the multi-body dynamics software LMS Virtual.Lab is used for verification. If the shifting force is less than the anti-shifting force, the parameters of the inverted tapered spline are appropriate; otherwise, the parameters of the inverted tapered spline are reselected.

[0007] In the above technical solution, further: the parameters of the inverted cone spline include the inverted cone angle a, the inverted cone length l, the number of spline teeth Z, and the spline module m.

[0008] The above technical solution further comprises the following steps:

[0009] S1. Determine the spline parameters without reverse taper according to the gearbox working conditions and calculate the spline strength.

[0010] S2. Import the multi-body dynamics software LMS Virtual.Lab, establish a multi-body dynamics model based on the specific structure of the gearbox, and solve it.

[0011] S3, extract the disengagement force F1, F2, F3...F of the gearbox spline clutch under various working conditions n .

[0012] S4, according to the maximum disengagement force F max Calculate the inverted taper angle a and inverted taper length l of the inverted taper spline.

[0013] S5. Draw a three-dimensional model of the inverted tapered spline and measure its minimum tooth top thickness S amin , and judge:

[0014] For the quenched and tempered inverted tapered splines, the minimum tooth top thickness should meet the S amin >0.25m; For quenched inverted tapered splines, the minimum tooth top thickness should meet S amin >0.4m; if the requirements are met, proceed to the next step of calculation; if not, return to step S1 to reselect the spline parameters and calculate.

[0015] S6. Establish and solve the multi-body dynamic model of the gearbox with inverted tapered splines.

[0016] S7, extract the disengagement force F1, F2, F3...F of the inverted tapered spline n And judge: If the anti-slip force F a Greater than the disengagement force F1, F2, F3...F n , the gearbox will not be out of gear and the calculation is completed; otherwise, the gearbox may be out of gear.

[0017] In the above technical solution, further: in step S1, the parameters of the spline without reverse taper are selected according to various working conditions of the gearbox, and the spline strength is calculated according to "GB / T17855-2017 Spline Load Capacity Calculation Method".

[0018] In the above technical solution, further: in step S2, the gearbox has multiple working conditions, and the spline clutch does not use an inverted cone; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; the Bushing force unit in motion is used to simulate the stiffness and damping of each bearing; and the Gear contact force unit in motion is used to define the involute spline parameters and side clearance.

[0019] In the above technical solution, further: in step S2, the involute spline parameters include the number of spline teeth Z, the spline module m, and the tooth width b.

[0020] In the above technical solution, further: step S3, according to the working condition of the gearbox, the initial speed and load are applied to solve and calculate, and the axial force of the gearbox spline clutch under each working condition, that is, the disengagement force F1, F2, F3...F n , according to the analyzed disengagement forces F1, F2, F3...F n Extract the maximum disengagement force F under all working conditions max .

[0021] In the above technical solution, further: Step S4, based on the maximum disengagement force F max , according to the formula: Anti-slip force F a =2000T×tana / dCalculate the inverted taper angle a, inverted taper length l of the inverted taper spline, and calculate the anti-slip force F a Greater than the maximum disengagement force F max .

[0022] In the above technical solution, further: in step S6, the gearbox has multiple working conditions, and the spline clutch uses a reverse cone spline; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; the Bushing force unit in motion is used to simulate the stiffness and damping of each bearing; and the Gear contact force unit in motion is used to define the involute spline parameters and side clearance.

[0023] In the above technical solution, further: in step S6, the involute spline parameters of the inverted tapered spline include the number of spline teeth Z, the spline module m, and the tooth width b.

[0024] The advantages of the present invention compared with the prior art are:

[0025] 1. The present invention uses the multi-body dynamics software LMS Virtual.Lab to construct a multi-power gearbox dynamics model, which can accurately calculate the gearbox's disengagement force; then, the inverted tapered spline parameters can be calculated based on the calculated disengagement force.

[0026] 2. The present invention combines multi-body dynamics simulation with theoretical calculations to ensure the accuracy of parameter design. Virtual prototypes replace physical prototypes, significantly shortening the R&D cycle, reducing the number of physical prototype tests, and lowering R&D costs. The closed-loop verification mechanism ensures the robustness of design parameters, and multidisciplinary coupling analysis improves the comprehensiveness and reliability of the design.

[0027] 3. By precisely defining the parameters of the involute spline (such as the number of teeth, module, tooth width, and pressure angle) and backlash in LMS Virtual.Lab, and combining them with simulation analysis using the Gear Contact Force unit and the Bushing Force unit, this invention can establish a high-precision multi-body dynamics model, comprehensively evaluate the performance of the spline under different operating conditions, optimize design parameters, reduce the risk of gear shifting and wear, and simultaneously reduce R&D costs and cycles. The technical advantages are reflected in the balance between high-precision simulation, adaptability to multiple operating conditions, dynamic performance optimization, and cost-effectiveness, providing a scientific basis for gearbox design and optimization.

[0028] 4. The precise extraction of dynamic disengagement force in the present invention can accurately reflect the dynamic load in actual operation, avoid the limitations of static calculations, and capture the transient peak and fluctuation range of the disengagement force compared to empirical formulas; the scientific verification of the anti-disengagement force can scientifically judge the anti-disengagement performance of the gearbox and ensure design reliability; through the closed-loop process of "simulation-extraction-verification-iteration", the final design of the inverted cone spline is ensured to meet the anti-disengagement requirements, while optimizing other performance indicators such as vibration and noise; the disengagement force extraction and anti-disengagement force verification are completed in a virtual environment, reducing the number of physical prototype tests and reducing R&D costs and cycles. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 Flowchart of the present invention;

[0030] Figure 2 These are the main parameters to be measured for the inverted tapered spline of the present invention;

[0031] Figure 3 It is a three-dimensional diagram of a multi-speed power flow gearbox without using inverted tapered splines;

[0032] Figure 4 It is a three-dimensional diagram of an inverted tapered spline;

[0033] Figure 5 A perspective diagram of a multi-speed power flow gearbox using the calculated inverted tapered spline parameters;

[0034] In the figure: 1, input shaft, 2, intermediate shaft, 3, 1st gear output gear, 4, output shaft, 5, 1 / 2 gear output gear, 6, 3rd gear clutch sleeve, 7, 3rd gear output gear, 8, 1st gear input gear, 9, 2 / 3rd gear input gear, 10, 2nd gear clutch sleeve, 11, 1st gear clutch sleeve, 12, 1st gear input gear, 13, 2 / 3rd gear input gear, 14, inverted tapered spline. DETAILED DESCRIPTION

[0035] The following is a combination of the embodiments of the present invention Figure 1-5The technical solutions in the embodiments of the present invention are clearly and completely described. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of them. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0036] A design method for anti-shifting inverted tapered splines for gearboxes based on multi-body dynamics is proposed. First, the shifting force is calculated using simulation calculations using the multi-body dynamics software LMS Virtual.Lab. Second, the parameters of the inverted tapered spline are inversely calculated using theoretical calculations. Third, to determine whether the inversely calculated parameters of the inverted tapered spline are appropriate, the multi-body dynamics software LMS Virtual.Lab is used for verification. If the shifting force is less than the anti-shifting force, the inverted tapered spline parameters are appropriate. Otherwise, the inverted tapered spline parameters are reselected.

[0037] It should be noted that the present invention simulates and calculates the disengagement force, avoids the errors of traditional empirical formulas or simplified models, and ensures the authenticity of the disengagement force calculation. Theoretically back-calculate the inverted cone parameters to ensure that the parameters meet the basic mechanical conditions for anti-disengagement. Secondary simulation verification and closed-loop verification methods ensure the reliability and robustness of design parameters, and avoid the risk of disengagement due to unreasonable parameters. LMS Virtual.Lab supports multi-body system dynamics simulation, which can simulate various complex working conditions and accurately capture the tiny displacements, contact force changes and disengagement trends during gear meshing. Through parametric modeling, the geometric parameters of the inverted cone spline (such as cone angle, number of teeth, module, etc.) can be quickly adjusted, and the simulation results can be used to compare the disengagement force under different parameters to achieve parameter optimization. LMSVirtual.Lab supports multidisciplinary coupled simulation (such as dynamics, structural mechanics, thermodynamics, etc.), which can comprehensively consider the anti-disengagement performance of the gearbox under factors such as thermal deformation and material fatigue, and improve the comprehensiveness of the design. Traditional design methods require multiple physical prototypes to be made for testing, which is costly and time-consuming. The simulation method based on LMS Virtual.Lab can complete parameter optimization and verification in a virtual environment, significantly reducing the number of physical prototype tests. By quickly iterating different parameter combinations through simulation, the optimal design can be found in a short time, significantly shortening the R&D cycle. Design defects can be discovered in advance in a virtual environment to avoid rework and cost waste caused by failed physical prototype tests, thereby reducing risks and costs. Through the combination of simulation and theoretical calculations, the relationship between the disengagement force and the anti-disengagement force can be accurately controlled to ensure that the inverted tapered spline can reliably prevent disengagement under various working conditions, while avoiding structural redundancy caused by over-design. Not only the static anti-disengagement requirements are considered, but also the disengagement risk of the gearbox under dynamic working conditions is analyzed through simulation to optimize the dynamic performance of the inverted tapered spline.

[0038] (like Figure 2As shown) in the above embodiment, further: the parameters of the inverted cone spline include the inverted cone angle a, the inverted cone length l, the number of spline teeth Z, and the spline module m.

[0039] (like Figure 1 In the above embodiment, further comprising the following steps:

[0040] Combine Figure 3 、 Figure 5 The gearbox embodiment shown: The gearbox of this embodiment includes an input shaft 1, on which a 2 / 3 gear input gear 13, a 1st gear input gear 12, an inverted cone spline 14, and a 1st gear clutch sleeve 11 are provided; includes an intermediate shaft 2, on which a 2nd gear clutch sleeve 10, a 2 / 3 gear input gear 9, a 1st gear input gear 8, and a 1st gear output gear 3 are provided; includes an output shaft 4, on which a 3rd gear output gear 7, a 3rd gear clutch sleeve 6, and a 1 / 2 gear output gear 5 are provided.

[0041] S1. Determine the spline parameters without reverse taper according to the gearbox working conditions and calculate the spline strength.

[0042] In the above embodiment, further: in step S1, the parameters of the spline without reverse taper are selected according to various working conditions of the gearbox, and the spline strength is calculated according to "GB / T17855-2017 Spline Load Capacity Calculation Method".

[0043] Specifically: Determine the initial parameters of the spline without reverse taper (module, number of teeth, pressure angle, pitch circle diameter, etc.) based on the dynamic load (such as torque fluctuation, impact load), speed range, temperature change and life requirements of the gearbox. Combined with the "GB / T17855-2017 Spline Load Capacity Calculation Method", adjust the parameters for different working conditions (such as high speed and light load, low speed and heavy load) to ensure the reliability of the spline under extreme working conditions. When calculating the strength of the spline, tooth surface contact strength: Calculate the tooth surface contact stress through the Hertz contact theory to ensure that the tooth surface does not have pitting or wear. Tooth root bending strength: Use finite element analysis (FEA) or standard formula to calculate the tooth root stress to prevent tooth root fracture. Shear strength: Evaluate the shear stress of the spline teeth under torque to ensure that the tooth body does not suffer shear damage. Fatigue life: Combine the SN curve and Miner cumulative damage theory to predict the fatigue life of the spline under cyclic load.

[0044] It should be noted that step S1 of the present invention utilizes multi-condition parameter selection and strength calculation based on GB / T17855-2017, combined with multi-body dynamics simulation and fatigue life analysis. This method enables the design of a highly reliable, long-life anti-slip spline that adapts to complex operating conditions while optimizing both cost and efficiency. The technical advantage lies in the balance between standardization, accuracy, dynamic performance optimization, and cost-effectiveness.

[0045] S2. Import the multi-body dynamics software LMS Virtual.Lab, establish a multi-body dynamics model based on the specific structure of the gearbox, and solve it.

[0046] In the above embodiment, further: in step S2, the gearbox has multiple working conditions, and the spline clutch does not use an inverted cone; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; wherein, the Gear Contact Force unit is used to define the basic parameters (such as the number of teeth, module, pressure angle) and side clearance of the involute gear, and simulate the contact force, friction force and dynamic response during the gear meshing process.

[0047] Specifically, the Bushing Force element in Motion is used to simulate the stiffness and damping of each bearing. The Bushing Force element is used to simulate the stiffness and damping characteristics of the bearing, defining the elastic support and energy dissipation of the bearing in the radial, axial, and angular directions.

[0048] Use the Gear Contact Force unit in Motion to define involute spline parameters and backlash. In the above embodiment, further: in step S2, the involute spline parameters include the number of spline teeth Z, the spline module m, and the tooth width b. The Gear Contact Force unit (Spline) is used to define the parameters and backlash of the involute spline, simulating the contact force and dynamic behavior of a spline clutch under axial load.

[0049] It should be noted that by precisely defining involute spline parameters (such as the number of teeth, module, tooth width, and pressure angle) and backlash in LMS Virtual.Lab, combined with simulation analysis using the Gear Contact Force and Bushing Force elements, a high-precision multibody dynamics model can be established to comprehensively evaluate spline performance under various operating conditions. This allows for optimized design parameters, reduces the risk of gear shifting and wear, and reduces R&D costs and cycle times. This technological advantage lies in its balanced approach to high-precision simulation, adaptability to multiple operating conditions, dynamic performance optimization, and cost-effectiveness.

[0050] S3, extract the disengagement force F1, F2, F3...F of the gearbox spline clutch under various working conditions n .

[0051] In the above embodiment, further: step S3, according to the working condition of the gearbox, the initial speed and load solution calculation are applied to extract the axial force of the gearbox spline clutch under each working condition, that is, the disengagement force F1, F2, F3...F n , according to the analyzed disengagement forces F1, F2, F3...Fn Extract the maximum disengagement force F under all working conditions max .

[0052] Specifically: Data extraction method: In LMS Virtual.Lab, the axial force curve of the spline clutch is viewed through the post-processing module (such as Post-Processing), and the peak axial force under each working condition is recorded as the disengagement force. The maximum disengagement force of all working conditions is extracted, F max =max(F1, F2, F3...F n ).

[0053] It should be noted that by applying the initial speed and load in LMS Virtual.Lab and running the multi-body dynamics simulation, the disengagement forces F1, F2, F3, ... F under each working condition are extracted. n , and extract the maximum disengagement force F max , which can provide a high-precision, comprehensive basis for the design of inverted tapered splines. The technical advantages are reflected in high-precision prediction, multi-operating condition analysis, dynamic response capture, and cost-effectiveness, ensuring the reliability and optimization of anti-slip design.

[0054] S4, according to the maximum disengagement force F max Calculate the inverted taper angle a and inverted taper length l of the inverted taper spline.

[0055] In the above embodiment, further: Step S4, based on the maximum disengagement force F max According to the formula: anti-slip force Fa = 2000T × tana / d, calculate the inverted cone angle a and the inverted cone length l of the inverted cone spline, and the calculated anti-slip force Fa is greater than the maximum disengagement force F max .

[0056] Where T is the torque transmitted by the spline (unit: N·m); a is the taper angle (unit: degrees); and d is the spline pitch circle diameter (unit: mm). The taper length l is usually determined by empirical formulas or simulation optimization, for example:

[0057]

[0058] Among them, μ is the friction coefficient, which is usually 0.1 to 0.2; k is the safety factor, which is usually 1.5 to 2.0.

[0059] It should be noted that calculating the taper angle a through a formula and optimizing the taper length l in combination with the friction coefficient μ and safety factor k provides a scientific and reliable basis for the design of taper splines. The technical advantages are reflected in the precise design of anti-slip forces, optimized taper angles, safe taper lengths, consideration of dynamic performance, and standardized processes, ensuring the reliability and optimization of anti-slip designs.

[0060] S5. Draw a three-dimensional model of the inverted tapered spline and measure its minimum tooth top thickness S amin , and judge:

[0061] For the quenched and tempered inverted tapered splines, the minimum tooth top thickness should meet the S amin >0.25m; For quenched inverted tapered splines, the minimum tooth top thickness should meet S amin >0.4m; if the requirements are met, proceed to the next step of calculation; if not, return to step S1 to reselect the spline parameters and calculate.

[0062] Specifically, use CAD software (such as SolidWorks, UG NX, CATIA, etc.) to draw a three-dimensional model based on the geometric parameters of the inverted tapered spline (number of teeth Z, module m, inverted taper angle a, inverted taper length l). Create an involute tooth profile and apply the inverted taper angle and length. Ensure that the transition fillet of the tooth top and tooth root meets the processing requirements. In the CAD software, extract the minimum tooth top thickness S of the inverted tapered spline through cross-section analysis or measurement tools. amin .

[0063] It should be noted that the minimum tooth top thickness S of the inverted tapered spline is accurately measured through 3D modeling. amin , and verify whether it meets S according to the heat treatment process amin >0.25m(quenched and tempered) or S amin >0.4µm (quenching), ensuring design reliability and manufacturing feasibility. The technical advantages are reflected in 3D modeling accuracy, dynamic verification of tooth top thickness, heat treatment process compatibility, design closed-loop optimization, and reduced processing risks, providing a scientific basis for the optimized design of inverted tapered splines.

[0064] S6. Establish and solve the multi-body dynamic model of the gearbox with inverted tapered splines.

[0065] In the above embodiment, further: in step S6, the gearbox has multiple working conditions, and the spline clutch uses a reverse cone spline; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; the Bushing force unit in motion is used to simulate the stiffness and damping of each bearing; and the Gear contact force unit in motion is used to define the involute spline parameters and side clearance.

[0066] In the above embodiment, further: in step S6, the involute spline parameters of the inverted tapered spline include the number of spline teeth Z, the spline module m, and the tooth width b.

[0067] It should be noted that using the Gear Contact Force element to define the geometric parameters and backlash of involute gears and splines accurately simulates the dynamic behavior of gear mesh and spline contact, avoiding the errors of traditional empirical formulas. Compared to simplified models, this model can capture subtle gear mesh displacements, contact force variations, and spline de-gearing tendencies. Including the effects of the back-taper angle a and length l on axial force in the model optimizes the anti-de-gear performance of the back-taper spline and reduces the risk of de-gearing. Using the Bushing Force element to simulate bearing stiffness and damping accurately reflects the bearing's support role under dynamic loads, reducing vibration and noise. Compared to the rigid support assumption, this model provides a more realistic simulation of the gearbox's dynamic response. By covering all gearbox operating conditions, the simulation ensures that the design meets performance requirements under various operating conditions, avoiding design flaws caused by omitted operating conditions. For example, under impact load conditions, the simulation can capture the transient axial force peak of the spline, ensuring the reliability of the anti-de-gear design. Performing multibody dynamics simulation in a virtual environment reduces the number of physical prototype tests, reducing R&D costs and time.

[0068] S7, extract the disengagement force F1, F2, F3...F of the inverted tapered spline n And judge: If the anti-slip force F a Greater than the disengagement force F1, F2, F3...F n , the gearbox will not be out of gear and the calculation is completed; otherwise, the gearbox may be out of gear.

[0069] It should be noted that the precise extraction of dynamic disengagement force can accurately reflect the dynamic load in actual operation, avoid the limitations of static calculations, and capture the transient peak and fluctuation range of the disengagement force compared to empirical formulas. The scientific verification of the anti-disengagement force can scientifically judge the anti-disengagement performance of the gearbox and ensure the reliability of the design. Through the closed-loop process of "simulation-extraction-verification-iteration", the final design of the inverted cone spline is ensured to meet the anti-disengagement requirements, while optimizing other performance indicators (such as vibration and noise). The disengagement force extraction and anti-disengagement force verification are completed in a virtual environment, reducing the number of physical prototype tests and reducing R&D costs and cycles.

[0070] From the above description, it can be found that the present invention uses the multi-body dynamics software LMS Virtual.Lab to construct a multi-power gearbox dynamic model, which can accurately calculate the gearbox's disengagement force; then, the inverted cone spline parameters can be calculated based on the calculated disengagement force.

[0071] The present invention combines multi-body dynamics simulation with theoretical calculations to ensure the accuracy of parameter design. Virtual prototypes replace physical prototypes, significantly shortening the R&D cycle, reducing the number of physical prototype tests, and lowering R&D costs. The closed-loop verification mechanism ensures the robustness of design parameters, and multidisciplinary coupling analysis improves the comprehensiveness and reliability of the design.

[0072] Each embodiment in this specification is described in a related manner. The same or similar parts between the embodiments can be referred to each other. Each embodiment focuses on the differences from other embodiments.

[0073] The above description is only a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications and equivalent replacements made within the spirit and principles of the present invention are included in the scope of protection of the present invention.

Claims

1. A design method for anti-shifting inverted tapered splines for gearboxes based on multi-body dynamics, characterized by: Firstly, the disengagement force is calculated by simulation based on the multi-body dynamics software LMS Virtual.Lab. Secondly, the parameters of the inverted tapered spline are inversely calculated using theoretical calculations. Thirdly, to determine whether the parameters of the inverted tapered spline obtained by inverse calculation are appropriate, the multi-body dynamics software LMS Virtual.Lab is used for verification. If the disengagement force is less than the anti-disengagement force, the parameters of the inverted tapered spline are appropriate. Otherwise, the parameters of the inverted tapered spline are reselected.

2. The design method according to claim 1, characterized in that: The parameters of the inverted cone spline include the inverted cone angle a, the inverted cone length l, the number of spline teeth Z, and the spline module m.

3. The design method according to claim 1, characterized in that: The steps include: S1. Determine the spline parameters without reverse taper according to the gearbox working conditions and calculate the spline strength; S2. Import the multi-body dynamics software LMS Virtual.Lab, establish a multi-body dynamics model based on the specific structure of the gearbox, and solve it; S3, extract the disengagement force F1, F2, F3...F of the gearbox spline clutch under various working conditions n ; S4, according to the maximum disengagement force F max Calculate the inverted taper angle a and inverted taper length l of the inverted taper spline; S5. Draw a three-dimensional model of the inverted tapered spline and measure its minimum tooth top thickness S amin , and judge: For the quenched and tempered inverted tapered splines, the minimum tooth top thickness should meet the S amin >0.25m; For quenched inverted tapered splines, the minimum tooth top thickness should meet S amin >0.4m; if it meets the requirements, proceed to the next step of calculation; if it does not meet the requirements, return to step S1 to reselect the spline parameters and calculate; S6. Establish and solve the multi-body dynamics model of the gearbox with inverted tapered splines; S7, extract the disengagement force F1, F2, F3...F of the inverted tapered spline n And judge: If the anti-slip force F a Greater than the disengagement force F1, F2, F3...F n , the gearbox will not be out of gear and the calculation is completed; otherwise, the gearbox may be out of gear.

4. The design method according to claim 3, characterized in that: In step S1, the parameters of the spline without reverse taper are selected according to various working conditions of the gearbox, and the spline strength is calculated according to the "GB / T17855-2017 Spline Load Capacity Calculation Method".

5. The design method according to claim 3, characterized in that: In step S2, the gearbox has multiple working conditions, and the spline clutch does not use an inverted cone; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; the Bushing force unit in motion is used to simulate the stiffness and damping of each bearing; and the Gear contact force unit in motion is used to define the involute spline parameters and side clearance.

6. The design method according to claim 5, characterized in that: In step S2, the involute spline parameters include the number of spline teeth Z, the spline module m, and the tooth width b.

7. The design method according to claim 3, characterized in that: Step S3: Apply the initial speed and load calculation according to the working condition of the gearbox to extract the axial force of the gearbox spline clutch under each working condition, that is, the disengagement force F1, F2, F3...F n , according to the analyzed disengagement forces F1, F2, F3...F n Extract the maximum disengagement force F under all working conditions max .

8. The design method according to claim 3, characterized in that: Step S4: Based on the maximum disengagement force F max , according to the formula: Anti-slip force F a =2000T×tana / dCalculate the inverted taper angle a, inverted taper length l of the inverted taper spline, and calculate the anti-slip force F a Greater than the maximum disengagement force F max .

9. The design method according to claim 3, characterized in that: In step S6, the gearbox has multiple working conditions, and the spline clutch uses an inverted tapered spline; in the dynamic model, the Gear contact force unit in motion is used to define the basic parameters and side clearance of the involute gear; the Bushing force unit in motion is used to simulate the stiffness and damping of each bearing; and the Gear contact force unit in motion is used to define the involute spline parameters and side clearance.

10. The design method according to claim 9, characterized in that: The involute spline parameters of the inverted tapered spline in step S6 include the number of spline teeth Z, the spline module m, and the tooth width b.

Images