Simulation analysis method for strength of automobile traction device

Abstract

The invention discloses an automobile traction device strength simulation analysis method. The method comprises the following steps: S1, establishing an automobile traction device strength simulation analysis finite element model; s2, obtaining a transient impact load process of the traction device through multi-body dynamics simulation analysis; s3, constraint and load are applied to the finite element model, and two analysis steps of loading and unloading are included; s4, submitting the model for calculation; the invention relates to the technical field of automobile traction. Based on an explicit dynamics simulation analysis method, a dynamic impact load is applied to the traction device, the abuse working conditions such as a high-speed trailer and a sudden acceleration trailer of a user can be simulated, and the method is used for evaluating and predicting the response and behavior of the traction device and a fixing part of the traction device when the traction device is suddenly impacted or the load is rapidly changed; the safety and reliability of the automobile traction device checked through the simulation analysis method are higher.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile traction, and in particular to a strength simulation analysis method for an automobile traction device. Background Art

[0002] A vehicle towing device is a component fixed or mounted on a vehicle and connected to it using devices such as a tow rope, tow cable, or tow bar, enabling the vehicle to tow or be towed. Vehicle towing devices are often used to free vehicles in emergency situations and require sufficient strength. Strength verification, simulation analysis, and testing of towing devices are essential components of the vehicle design and development process. GB 32087-2015, "Light Vehicle Towing Devices," stipulates that towing devices must withstand a minimum static load of half the vehicle's maximum permissible gross weight. Under this static load, the towing device and its mountings must not fail, break, or deform in a manner that would affect normal operation. Other components mounted near the towing device must also be free of damage that would impair normal operation. Based on this requirement, static simulation analysis methods are currently used for strength verification and simulation analysis of towing devices. Tensile and compressive static loads are applied to the towing device in various directions, including horizontal, along a ±5° vertical direction, and horizontal ±25°.

[0003] Although automobile manufacturers have carried out strength simulation, calibration and verification of traction devices in accordance with national standards during the design and development process, the phenomenon of traction devices breaking during actual use by users often occurs. The main reason is that when calibrating the traction device, only static loads are considered, and dynamic impact loads are not considered. However, in the actual rescue process, users often perform irregular towing operations, such as towing at a high speed, suddenly accelerating the towing vehicle, etc. This rough towing method will instantly generate a large impact load on the traction device, which can easily cause damage to the traction device. To solve this problem, the present invention provides a strength simulation and analysis method for automobile traction devices based on explicit dynamics, which applies transient impact loads to the traction device, performs strength analysis and calibration on it, and makes the design of the traction device safer and more reliable.

[0004] Currently, strength simulation analysis and verification of automotive traction devices are based on GB 32087-2015, "Light Vehicle Traction Devices." This method employs a static simulation analysis method, slowly applying concentrated loads to the traction device. This method does not account for dynamic impact loads. While the verification results meet national standards, they may not meet user requirements for abuse conditions. Summary of the Invention

[0005] (1) Technical problems solved In view of the deficiencies in the prior art, the present invention provides a method for simulating and analyzing the strength of an automobile traction device, which solves the problems mentioned in the above background technology.

[0006] (2) Technical solution To achieve the above objectives, the present invention is implemented through the following technical solutions: A vehicle traction device strength simulation analysis method includes the following steps: S1. Establish a finite element model for the simulation analysis of the strength of the automobile traction device; S2. Obtain the transient impact load history of the traction device through multi-body dynamics simulation analysis; S3, applying constraints and loads to the finite element model, including two analysis steps of loading and unloading; S4. Submit the model for calculation.

[0007] Preferably, in S1, the finite element model is established using the Abaqus-Explicit interface in the Hypermesh software.

[0008] Preferably, the finite element model should include a traction device, traction device fixings such as connecting plates, a vehicle body or frame partial model, etc.; connections are established between the various components according to the actual connection relationship, and contact pairs are established in areas where there is contact and where contact may occur during traction; the traction device and fixings are both made of elastic-plastic materials, and stress-plastic strain curves are added.

[0009] Preferably, in said S2, the transient impact load history of the traction device is obtained by multi-body dynamics simulation analysis, which specifically includes the following steps: S21: Establishing multi-body dynamics model: By building a multi-body dynamics model of the rescue vehicle and the towed vehicle in Adams, the towed vehicle is assumed to have a half-load capacity (the load capacity can be increased appropriately depending on the vehicle type and its operating conditions); S22: Establishment and simulation analysis of the traction connection between the rescue vehicle and the towed vehicle, and load output: 1) Establishment and simulation analysis of the horizontal stretching traction position and the traction connection between the rescue vehicle and the towed vehicle, as well as load output; 2) Establishment and simulation analysis of the traction connection between the rescue vehicle and the towed vehicle in the horizontally compressed traction position, as well as load output.

[0010] Preferably, in the above 1), the specific method is: when the towing position is in tension, a flexible connection is established in the horizontal position direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the rope during towing; When the towing position is stretched, the whole vehicle motion simulation is performed by setting the initial speed of the rescue vehicle to 0 and linear acceleration until the speeds of the rescue vehicle and the towed vehicle are equal. The simulation is terminated to obtain the load at the tow hook position of the towed vehicle and output the time domain curve.

[0011] Preferably, in the above 2), the specific method is: when the towing position is compressed, a rigid connection is established in the horizontal position direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the hard connection state during towing; When the towing position is compression, the whole vehicle motion simulation is performed by setting the rescue vehicle's initial speed to 0 and reversing in a straight line. The simulation is terminated when the speeds of the rescue vehicle and the towed vehicle are equal. The load at the tow hook position of the towed vehicle is obtained and the time domain curve is output. Similarly, 10 working conditions were established, including traction and compression at ±5° in the vertical direction and tension and compression at ±25° in the horizontal direction.

[0012] Preferably, said S3 comprises the following steps: S31: Apply global constraints to the model: constrain the translational degrees of freedom in the X, Y, and Z directions of each node of the frame longitudinal beam section, and set the constraints as initial conditions; S32: Load steps 1 loading analysis step settings: select explicit dynamics for analysis type; apply the load and time domain curve determined in S2 to the loading point of the traction device; set the analysis step time to be consistent with the time domain curve time of the load; S33: Load steps 2 unloading analysis step settings: Select explicit dynamics as the analysis type, keep the constraints described in S31, unload the load applied in S32, and set the unloading time to 0.001S.

[0013] Preferably, the constraints and loads for 10 working conditions are set respectively: horizontal tension, horizontal compression, tension and compression along the vertical direction of ±5°, and tension and compression along the horizontal direction of ±25°.

[0014] Preferably, in said S4, the model compiled in S1 and S3 is submitted for calculation, and the solver software used is Abaqus; and the result files of the overall maximum displacement, residual displacement, and equivalent plastic strain of the traction device and its fixing parts are output.

[0015] (3) Beneficial effects This invention provides a method for simulating and analyzing the strength of a vehicle towing device. Compared to existing technologies, this method offers the following advantages: Based on an explicit dynamics simulation analysis method, this method applies dynamic impact loads to the towing device, simulating abusive conditions such as towing at high speeds or sudden acceleration. This method is used to evaluate and predict the response and behavior of the towing device and its mountings when subjected to sudden impacts or rapidly changing loads. Vehicle towing devices verified using this simulation analysis method exhibit enhanced safety and reliability. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1The finite element model of a certain vehicle traction device provided by the present invention and the load steps 1 constraint and loading schematic diagram; Figure 2 This is a schematic diagram of the load loading history curve provided by the present invention. DETAILED DESCRIPTION

[0017] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention. Example

[0018] A method for simulating and analyzing the strength of an automobile traction device comprises the following steps: S1. Use the Abaqus-Explicit interface in Hypermesh software to establish a finite element model for the strength simulation analysis of the vehicle traction device. The finite element model should include the traction device, traction device fixings such as connecting plates, and a partial model of the vehicle body or frame. Connect the components according to their actual connection relationships, and establish contact pairs in areas where contact exists and where contact may occur during traction. The traction device and fixings should all be made of elastic-plastic materials, and stress-plastic strain curves should be added. S2. Obtain the transient impact load history of the traction device through multi-body dynamics simulation analysis; The transient impact load history of the traction device is obtained through multi-body dynamics simulation analysis, which specifically includes the following steps: S21: Establishing multi-body dynamics model: By building a multi-body dynamics model of the rescue vehicle and the towed vehicle in Adams, the towed vehicle is assumed to have a half-load capacity (the load capacity can be increased appropriately depending on the vehicle type and its operating conditions); S22: Establishment and simulation analysis of the traction connection between the rescue vehicle and the towed vehicle, and load output: 1) Establishment and simulation analysis of the horizontal stretching traction position and the traction connection between the rescue vehicle and the towed vehicle, as well as load output; When the towing position is in tension, a flexible connection is established in the horizontal direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the rope during towing; When the towing position is stretched, the whole vehicle motion simulation is performed by setting the initial speed of the rescue vehicle to 0 and linear acceleration until the speeds of the rescue vehicle and the towed vehicle are equal. The simulation is terminated to obtain the load at the tow hook position of the towed vehicle and output the time domain curve.

[0019] 2) Establishment and simulation analysis of the towing connection between the rescue vehicle and the towed vehicle in the horizontally compressed towing position, as well as load output; When the towing position is compressed, a rigid connection is established in the horizontal direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the hard connection state during towing; When the towing position is compression, the whole vehicle motion simulation is performed by setting the rescue vehicle's initial speed to 0 and reversing in a straight line. The simulation is terminated when the speeds of the rescue vehicle and the towed vehicle are equal. The load at the tow hook position of the towed vehicle is obtained and the time domain curve is output. Similarly, 10 working conditions were established, including tension and compression along the vertical direction ±5° and tension and compression along the horizontal direction ±25°. S3, applying constraints and loads to the finite element model, including two analysis steps of loading and unloading; Specifically: S31: Apply global constraints to the model: constrain the translational degrees of freedom in the X, Y, and Z directions of each node of the frame longitudinal beam section, and set the constraint as the initial condition.

[0020] S32: Load steps 1 loading analysis step settings: select explicit dynamics for analysis type; apply the load and time domain curve determined by S2 at the loading point of the traction device; set the analysis step time to be consistent with the time domain curve time of the load.

[0021] S33: Load steps 2 unloading analysis step settings: select explicit dynamics for analysis type, keep the constraints described in S31, unload the load applied in S32, and set the unloading time to 0.001S; Set constraints and loads for 10 working conditions: horizontal tension, horizontal compression, tension and compression along the vertical direction ±5°, and tension and compression along the horizontal direction ±25°. S4. Submit the model for calculation. Submit the model organized in S1 and S3 for calculation using Abaqus solver software. Output the overall maximum displacement, residual displacement, and equivalent plastic strain result files of the traction device and its fixings.

[0022] Meanwhile, the contents not described in detail in this specification belong to the prior art known to those skilled in the art.

[0023] It should be noted that, in this document, relational terms such as first and second, etc., are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "comprises," "comprising," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that includes a list of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus.

[0024] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to these embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the appended claims and their equivalents.

Claims

1. A method for simulating and analyzing the strength of a vehicle traction device, characterized in that: The following steps are involved: S1. Establish a finite element model for strength simulation analysis of automobile traction device; S2. Obtain the transient impact load history of the traction device through multi-body dynamics simulation analysis; S3, applying constraints and loads to the finite element model, including two analysis steps of loading and unloading; S4. Submit the model for calculation.

2. The method for simulating and analyzing the strength of a vehicle traction device according to claim 1, characterized in that: In S1, a finite element model is established using the Abaqus-Explicit interface in the Hypermesh software.

3. The method for simulating and analyzing the strength of a vehicle traction device according to claim 1, characterized in that: The finite element model should include the traction device, traction device fixings such as connecting plates, vehicle body or frame partial models, etc.; connections are established between various components according to actual connection relationships, and contact pairs are established in areas where there is contact and where contact may occur during traction; the traction device and fixings are made of elastic-plastic materials, and stress-plastic strain curves are added.

4. The method for simulating and analyzing the strength of a vehicle traction device according to claim 1, characterized in that: In S2, the transient impact load history of the traction device is obtained through multi-body dynamics simulation analysis, which specifically includes the following steps: S21: Establishing multi-body dynamics model: By building a multi-body dynamics model of the rescue vehicle and the multi-body dynamics model of the towed vehicle in Adams, the load of the towed vehicle is half-loaded (the load can be appropriately increased according to the type of vehicle and its operating conditions); S22: Establishment and simulation analysis of the traction connection between the rescue vehicle and the towed vehicle, and load output: 1) Establishment and simulation analysis of the horizontal stretching traction position and the traction connection between the rescue vehicle and the towed vehicle, as well as load output; 2) Establishment and simulation analysis of the traction connection between the rescue vehicle and the towed vehicle in the horizontally compressed traction position, and load output.

5. The method for simulating and analyzing the strength of a vehicle traction device according to claim 4, characterized in that: In the above 1), the specific method is: when the towing position is stretched, a flexible connection is established in the horizontal position direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the rope during towing; When the towing position is stretched, the whole vehicle motion simulation is performed by setting the initial speed of the rescue vehicle to 0 and linear acceleration until the speeds of the rescue vehicle and the towed vehicle are equal, and the simulation is terminated to obtain the load at the trailer hook position of the towed vehicle and output the time domain curve.

6. The method for simulating and analyzing the strength of a vehicle traction device according to claim 4, characterized in that: In the above 2), the specific method is: when the towing position is compressed, a rigid connection is established in the horizontal position direction of the trailer hook position of the towing vehicle and the towed vehicle to simulate the hard connection state during towing; When the towing position is compression, the whole vehicle motion simulation is performed by setting the initial speed of the rescue vehicle to 0 and reversing in a straight line until the speeds of the rescue vehicle and the towed vehicle are equal, and the simulation is terminated to obtain the load at the tow hook position of the towed vehicle and output the time domain curve; Similarly, 10 working conditions were established, including ±5° traction and compression in the vertical direction and ±25° stretching and compression in the horizontal direction.

7. The method for simulating and analyzing the strength of a vehicle traction device according to claim 1, characterized in that: The S3 comprises the following steps: S31: Apply global constraints to the model: constrain the translational freedom of each node in the X, Y, and Z directions of the frame longitudinal beam section, and set the constraint as the initial condition; S32: Load steps 1 setting: select explicit dynamics for analysis type; apply the load and time domain curve determined by S2 to the loading point of the traction device; set the analysis step time to be consistent with the time domain curve time of the load; S33: Load steps 2 unloading analysis step settings: Select explicit dynamics as the analysis type, keep the constraints described in S31, unload the load applied by S32, and set the unloading time to 0.001S.

8. The method for simulating and analyzing the strength of a vehicle traction device according to claim 7, characterized in that: Ten working conditions of constraints and loads are set respectively: horizontal tension, horizontal compression, tension and compression along the vertical direction ±5°, and tension and compression along the horizontal direction ±25°.

9. The method for simulating and analyzing the strength of a vehicle traction device according to claim 1, characterized in that: In S4, the models sorted out in S1 and S3 are submitted for calculation, and the solver software used is Abaqus; the overall maximum displacement, residual displacement, and equivalent plastic strain result files of the traction device and its fixings are output.

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