CN-122021058-A - Method for accurately determining key design parameters of magnetorheological damper based on joint simulation

CN122021058ACN 122021058 ACN122021058 ACN 122021058ACN-122021058-A

Abstract

The invention discloses a method for precisely determining key design parameters of a magnetorheological damper based on joint simulation, and belongs to the field of semi-active vibration damping systems of vehicles. Aiming at the problems of high redesign risk and large damping force calculation error of the traditional design method, the method establishes a damping force real-time calculation model through classical fluid theory, combines a whole vehicle dynamics model, an electromagnetic valve current regulation model and a table-look-up damping force preset model, or establishes a joint simulation model through the damping force real-time calculation model, determines a damping force and relative compression stroke target range through simulation, determines a key design parameter value range according to multiple constraint conditions, screens alternative schemes through iterative calculation, and finally selects a whole vehicle performance optimal scheme through simulation verification. According to the method, the control parameters are accurately related to the damping force, the error between the damping force test value and the design target is less than or equal to 5%, the risk of resetting design is avoided, the development period is shortened, the production cost is reduced, and reliable theoretical guidance is provided for the design of the magnetorheological damper.

Inventors

HAO XIN
XIA YUNNI
ZHAO DAYI
WANG ZHOU
LIU YUHUI
CHEN DONG
LI YIWEN

Assignees

重庆大学
辰致科技有限公司

Dates

Publication Date: 20260512
Application Date: 20260325

Claims (10)

1. The method for precisely determining the key design parameters of the magnetorheological damper based on the joint simulation is characterized by comprising the following steps of: 1) Determining key design parameters of the magneto-rheological damper to be designed by utilizing correlation analysis and sensitivity analysis; 2) According to a classical fluid N-S theory, a Darcy-Wei Siba Hz theory, a mechanical balance principle and a bingham model, constructing a real-time damping force calculation model of the magnetorheological damper by utilizing key design parameters of the magnetorheological damper to be designed, wherein the real-time damping force calculation model is used for expressing mathematical relations between various key design parameters of the magnetorheological damper and damping force output by the magnetorheological damper; 3) Constructing a first combined simulation model consisting of a table-lookup type damping force preset model, an electromagnetic valve current regulation model and a whole vehicle dynamics model of the magnetorheological damper, and performing whole vehicle performance simulation by using the first combined simulation model to determine the damping force target range of the magnetorheological damper and the value range of each key design parameter when the whole vehicle performance index reaches the standard; 4) Based on a damping force target range and a value range of key design parameters, iterative computation is carried out by utilizing a damping force real-time calculation model and an electromagnetic coil analysis model of the magnetorheological damper, and specific values of all key design parameters of the magnetorheological damper are determined by combining the current adjustment value range of the electromagnetic coil and the minimum magnetorheological fluid consumption requirement, so that a plurality of design schemes are formed as alternative schemes; 5) And (3) replacing a table-lookup type damping force preset model in the first joint simulation model with a damping force real-time calculation model to form a second joint simulation model, importing the alternative scheme obtained in the step (4) into the second joint simulation model for simulation analysis, and taking the alternative scheme with the best overall vehicle performance as a final design scheme of the magnetorheological damper.
2. The method according to claim 1, wherein in step 1), the obtaining manner of the key design parameter includes: 1-1) carrying out correlation analysis on all design parameters of the magnetorheological damper with respect to damping force of the magnetorheological damper, and screening out strong correlation parameters of the damping force of the magnetorheological damper; 1-2) carrying out sensitivity analysis on the damping force of the magnetorheological damper on the screened strong relevant parameters of the damping force of the magnetorheological damper, quantifying the influence amplitude of each strong relevant parameter on the damping force, and determining a plurality of key design parameters of the magnetorheological damper by combining with the working mechanism verification of the magnetorheological damper.
3. The method of claim 1 or 2, wherein the key design parameters include an initial pressure of the reservoir, an initial length of the rod chamber, an initial length of the rodless chamber, an initial length of the reservoir at a relative compression stroke of 0; the piston length, the bypass hole length, the gap width, the gap median radius, the bypass hole diameter, the piston rod diameter and the cylinder barrel inner diameter; the electromagnetic coil is provided with an axial length, an electromagnetic coil width and an electromagnetic coil layout size, and the electromagnetic coil is provided with current regulation and coil turns.
4. The method according to claim 1, wherein in step 2), the construction of the damping force real-time calculation model includes: 2-1) determining a pressure drop gradient model of a magnetic field area and a non-magnetic field area in a piston gap flow channel according to an N-S theory; 2-2) determining a pressure drop gradient model of the bypass orifice according to the Darcy-Wei Siba Hz theory; 2-3) obtaining flow distribution rules of the clearance flow channel and the bypass holes according to the characteristics of the magnetorheological fluid and the flow rules of the fluid, and establishing a piston pressure drop model by combining the results of the step 2-1) and the step 2-2); 2-4) obtaining the pressure change rule of each chamber of the magnetorheological damper in motion according to a thermodynamic state equation; 2-5) determining the relation between the damping force and the motion speed, the friction force and the pressure of each chamber according to the mechanical balance principle to obtain a real-time damping force calculation model of the magnetorheological damper.
5. The method according to claim 1, wherein in step 3), the damping force target range of the magnetorheological damper and the value range of each key design parameter are determined when the performance index of the whole vehicle meets the standard, and the method specifically comprises the following steps: 3-1) according to design experience, taking the motion speed of the magnetorheological damper and the electromagnetic coil regulating current as input parameters, taking the damping force of the magnetorheological damper as output parameters, constructing a table-look-up type damping force preset model of the magnetorheological damper to be designed, and storing damping force output data corresponding to a plurality of different input parameter combinations; 3-2) constructing a whole vehicle dynamics model and an electromagnetic valve current regulation model, and combining the table-lookup type damping force preset model obtained in the step 3-1) to form a first joint simulation model; 3-3) performing simulation analysis on the whole vehicle performance by using a first joint simulation model to obtain a damping force target range of the magnetorheological damper and a relative compression stroke range of the magnetorheological damper when the whole vehicle performance index related to the magnetorheological damper completely meets the standard; 3-4) determining the value range of each key design parameter of the magnetorheological damper according to the damping force target range, the relative compression stroke range and the energy consumption requirement of the magnetorheological damper.
6. The method according to claim 5, wherein in step 3-2), the first joint simulation model is constructed in a manner that specifically includes: 3-2-1) respectively constructing a whole vehicle dynamics model, a table-lookup damping force preset model of the magnetorheological damper and a solenoid valve current regulation model: 3-2-1-1) defining input parameters of the whole vehicle dynamics model as damping force, and outputting sensor signals (such as suspension height change signals, whole vehicle directional acceleration signals and the like) of the vibration absorber motion speed and the whole vehicle chassis system as output parameters to construct the whole vehicle dynamics model; 3-2-1-2) defining input parameters of a table-look-up type damping force preset model as the motion speed of the shock absorber and the adjusting current of the electromagnetic coil, and constructing the table-look-up type damping force preset model as the output parameters of the table-look-up type damping force preset model; 3-2-1-3) defining input parameters of a solenoid valve current regulation model as sensor signals of a whole vehicle chassis system, and outputting parameters as solenoid valve current regulation current to construct the solenoid valve current regulation model; 3-2-2) signal interface connection, namely connecting a sensor signal output interface of the whole vehicle dynamics model with an input interface of a solenoid valve current regulation model, connecting a solenoid valve current regulation current output interface of the solenoid valve current regulation model with a current input interface of a table-looking-up type damping force preset model, simultaneously connecting a damper motion speed output interface of the whole vehicle dynamics model with a speed input interface of the table-looking-up type damping force preset model, and connecting a damping force output interface of the table-looking-up type damping force preset model with a damping force input interface of the whole vehicle dynamics model to complete the construction of a joint simulation model.
7. The method according to claim 5, wherein in step 3-3), the first joint simulation model is used to perform simulation analysis on the performance of the whole vehicle, so as to obtain a damping force target range of the magnetorheological damper when the performance index of the whole vehicle related to the magnetorheological damper is all up to standard, and a relative compression stroke range of the magnetorheological damper, and the method specifically comprises: 3-3-1) setting a simulation working condition and a virtual road surface, wherein the simulation working condition comprises an angular step working condition, a sine sweep working condition, an elk working condition and a steering center sensing working condition, and the virtual road surface comprises road surfaces with different roughness and a deceleration strip road surface; 3-3-2) running a first joint simulation model, and performing simulation analysis on the steering stability performance, steering performance and smoothness performance of the whole vehicle to obtain a plurality of simulation index values, wherein the plurality of simulation index values comprise the roll angle speed, the roll angle overshoot, the 1Hz vehicle body roll speed gradient, the ground leaving state of the elk simulation wheel, the primary pitching acceleration root mean square value, the primary rolling acceleration root mean square value, the vehicle body vertical vibration acceleration root mean square value and the simulation value of the flutter index; 3-3-3) comparing all simulation index values with a preset target range, and if all the simulation index values fall within the preset target range, determining a damping force target range and a relative compression stroke range of the magnetorheological damper based on the current joint simulation result.
8. The method according to claim 5, wherein in step 3-4), the range of values of each key design parameter of the magnetorheological damper is determined according to the damping force target range, the relative compression stroke range and the energy consumption requirement of the magnetorheological damper, and specifically comprises: 3-4-1) determining the initial pressure of the air storage chamber, the initial length of the rod cavity, the initial length of the rodless cavity and the value range of the initial length of the air storage chamber according to the relative compression stroke range and the requirement of stable pressure of the chamber; 3-4-2) determining the value range of the diameter of the piston rod and the inner diameter of the cylinder barrel according to the strength and durability requirements; 3-4-3) determining the value ranges of the gap width, the gap median radius and the bypass hole diameter according to the damping force characteristic requirements corresponding to the damping force target range; 3-4-4) determining the value ranges of the electromagnetic coil regulating current, the electromagnetic coil axial length, the electromagnetic coil width and the coil turns according to the energy consumption requirement and the magnetorheological fluid characteristics; 3-4-5) according to the structure matching requirement, determining the value ranges of the gap length, the bypass hole length and the piston length, and defining the numerical matching relation of the gap length, the bypass hole length and the piston length.
9. The method according to claim 1, wherein in step 4), the obtaining manner of the alternative solution specifically includes: 4-1) taking the value range of the key design parameters determined in the step 3) as a constraint boundary, and coupling the damping force real-time calculation model with the electromagnetic coil analysis model; 4-2) setting an iteration step length of the electromagnetic coil adjusting current, performing traversal calculation within the range of 0-5A, and simultaneously meeting the minimum constraint of the consumption of the magnetorheological fluid; 4-3) verifying whether the corresponding damping force calculated value falls within the damping force target range determined in the step 3) after each iterative calculation of a group of parameter combinations is completed; 4-4) screening out a plurality of parameter combinations which reach the damping force standard and meet the minimum dosage requirement of the magnetorheological fluid, and taking the parameter combinations as an alternative scheme.
10. The method according to claim 1, wherein in step 5), the determination of the final design of the magnetorheological damper specifically comprises: 5-1) removing a table-look-up type damping force preset model in the first joint simulation model, and connecting the damping force real-time calculation model established in the step 2) to a signal interface of the table-look-up type damping force preset model, so as to keep the connection relation between other models and signals unchanged and form a second joint simulation model; 5-2) respectively importing the multiple alternatives obtained in the step 4) into a second joint simulation model, and rerun the simulation under the simulation working condition and the virtual pavement; 5-3) comparing the simulation values of the performance indexes of the whole vehicle corresponding to each group of alternative schemes, wherein the simulation values comprise roll angle speed, roll angle overshoot, 1Hz vehicle body roll speed gradient, primary pitching acceleration root mean square value, primary roll acceleration root mean square value, vehicle body vertical vibration acceleration root mean square value and flutter indexes; 5-4) selecting an alternative scheme which is optimal in all performance index simulation values and meets the preset target requirements as a final design scheme of the magnetorheological damper.

Description

Method for accurately determining key design parameters of magnetorheological damper based on joint simulation Technical Field The invention relates to the field of semi-active vibration reduction systems of vehicles, in particular to a method for precisely determining key design parameters of a magnetorheological vibration damper based on joint simulation. Background The magneto-rheological damper is characterized by simple structure, low energy consumption, wide damping force adjustable range, quick damping adjustment response and the like, and is widely applied to industries such as automobiles, civil construction, aerospace, robots, medical treatment and the like. Currently, along with the gradual maturation and cost declining of the domestic technology of magnetorheological fluid, the magnetorheological damper has wider market prospect in the automobile industry. The design of the magneto-rheological damper covers a plurality of crossed fields such as structures, fluids, electromagnetism, materials and the like, and the design parameters are numerous, so that the design difficulty is extremely high. The design flow of a typical magnetorheological damper is as follows: ⑴ The host factory gives out a damping force target range and a relative compression stroke target according to a whole vehicle performance target related to the magnetorheological shock absorber by means of a theoretical calculation formula and experience, and gives out a space envelope boundary according to a whole vehicle arrangement requirement; ⑵ The magneto-rheological shock absorber manufacturer determines a design scheme by means of theoretical calculation and CAE analysis according to the damping force target range, the relative compression stroke target and the energy consumption requirement; ⑶ Manufacturing a magneto-rheological shock absorber sample, performing damping force test, comparing a damping test value with a target range, completing design if the damping test value meets the target range, optimizing a scheme if the damping test value does not meet the target range, and repeating the step ⑵～⑶; ⑷ And (3) mounting the sample on a vehicle to perform performance adjustment tests such as vehicle steering stability, riding comfort and the like, optimizing a damping force target and a relative compression stroke target range if the performance target of the vehicle is not reached, repeating the step ⑵～⑷ until reaching the standard, and finally determining the design parameters of the magneto-rheological shock absorber. However, in long-term practical operation, a number of persons skilled in the art have found that using the conventional manner described above to determine the design parameters of a magnetorheological damper has a number of problems: ① The damping force target and the relative compression stroke target range given by a host factory based on a theoretical formula and experience cannot be directly equivalent to the standard of the whole vehicle performance, and the method has great scheme redesign risk, is time-consuming and labor-consuming and has high cost; ② The damping design method has the defect that the traditional damping force theory algorithm only considers the influence of part of design parameters on the damping force, so that calculation errors exist. How to reduce the design target of the damping force of the magnetorheological damper and the error between the damping force test value obtained after the preparation and production of the magnetorheological damper as much as possible while reducing the design risk of the scheme reset is always a problem to be solved by the technicians in the field. Disclosure of Invention Aiming at the corresponding defects of the prior art, the invention provides a method for precisely determining key design parameters of a magnetorheological damper based on joint simulation, which aims at precisely associating a control damping force with each parameter, avoiding scheme re-design risk, shortening design period, reducing design production cost and improving product competitiveness. The invention is realized by adopting the following scheme: a method for precisely determining key design parameters of a magnetorheological damper based on joint simulation comprises the following steps: 1) Determining key design parameters of the magneto-rheological damper to be designed by utilizing correlation analysis and sensitivity analysis; 2) According to a classical fluid N-S theory, a Darcy-Wei Siba Hz theory, a mechanical balance principle and a bingham model, constructing a real-time damping force calculation model of the magnetorheological damper by utilizing key design parameters of the magnetorheological damper to be designed, wherein the real-time damping force calculation model is used for expressing mathematical relations between various key design parameters of the magnetorheological damper and damping force output by the magnetorheological damper; 3) Constructing a