A method, device, equipment and storage medium for optimizing the overshift force of a car door limiter

Abstract

The present invention relates to the technical field of automobiles, and specifically to a method, device, equipment and storage medium for optimizing the overshift force of a door limiter. The method includes: Step 1, deduce the generation mechanism of the overshift force of the door limiter to determine the core factors causing the change of the overshift force of the limiter; Step 2, establish a simulation model for the limiter to generate a simulated overshift force curve; Step 3, measure the overshift force of the limiter sample to generate a test overshift force curve; Step 4, calibrate the simulation model; Step 5, optimize the structure of the limiter according to the calibrated simulation model. Through the technical solution of the present invention, the deformation trend of the overshift force of the limiter and its influencing factors can be more clearly grasped, and the optimization of the key parameters of the limiter slot is used to complete the optimization work of the overshift force of the limiter, and the overshift force is analyzed and optimized during the limiter design stage, replacing the sample trial production and test verification work.

Description

Technical Field

[0001] The present invention relates to the technical field of automobiles, and specifically to a method, device, equipment and storage medium for optimizing the overshift force of a door limiter. Background Art

[0002] With the increasing maturity of automobile consumption, users' requirements for automobile quality are also constantly improving. The door is a component with a high usage frequency for users, and the experience of opening and closing the door directly affects customers' evaluation of automobile quality. The limiter plays an important role in the process of opening and closing the door, mainly affecting the overshift force during opening and closing, controlling the opening degree of the door, and the sound quality during opening and closing.

[0003] Currently, the measurement of the door opening and closing limit feeling is carried out in the whole vehicle environment, and the test targets are the torque and acceleration values at the door handle. Due to the many influencing factors in the whole vehicle environment, the test results cannot accurately reflect the performance of the limiter. Secondly, the test needs to carry the physical sample of the limiter. For subsequent experimental verification, it is necessary to go through the structural change of the limiter, the sample trial production and the whole vehicle test, and the verification cycle is long and the cost is high.

[0004] In response to the above problems, Patent Document 1 (CN 110735569 A) provides a method for determining the contour line of the main arm of a door limiter, including the following steps: obtaining the movement trajectory line CC' of the centroid of the limiter box during the opening process of the door; the position of the projection point of the rotation axis of the limiter on the plane where the movement trajectory line CC' is located is denoted as A. On the plane where A and the movement trajectory line CC' are located, make a number of concentric cutting circles with A as the center; determine the intersection points of the number of cutting circles and the movement trajectory line; obtain the straight line where A and the intersection points are located, and intercept the line segment between the cutting circle where the intersection point is located and the adjacent outer cutting circle; connect the line segments to obtain the contour line of the main arm of the limiter. The contour line of the main arm of the limiter manufactured by using this method coincides with the movement trajectory line of the limiter box along the main arm of the limiter, so that when the door is opened or closed, the limiter box will not interfere with the main arm of the limiter, thereby making the resistance during the opening or closing of the door smaller and the opening and closing of the door smoother. However, this patent does not include the calculation analysis and optimization process of the overshift force of the limiter.

[0005] Patent Document 2 (CN 102619419 B) discloses a manufacturing method for the main arm of a car door limiter. The car includes a body and a door. The door is hinged to the body through a door rotating shaft and rotates relative to the body. The door limiter includes a main arm (1) and a sliding box (2). The sliding box is fixed to the door and can slide along the main arm. One end of the main arm is hinged to the body through a limiter rotating shaft and rotates, and the other end has a limiting block to prevent the sliding box from sliding out of the main arm. This manufacturing method first determines the center line of the main arm, and then manufactures the main arm according to the center line. The present invention also provides a main arm and a door limiter manufactured by the above manufacturing method. Through the motion characteristics of the door limiter when the door rotates, the coordinates of multiple points on the center line of the main arm of the door limiter are obtained. This method is simple and reliable, easy to implement with a computer, and the design accuracy of the main arm can be controlled by adjusting parameters. Therefore, it can meet various different accuracy requirements with only minor modifications. However, it does not include the calculation analysis and optimization process of the overtravel force of the limiter.

[0006] Patent Document 3 (CN 106351523 B) discloses a non-metallic control box limiter assembly, including a limiter pull plate, a control box, and a limiter bracket. The control box includes a spring, a slider, a screw, and a shock pad. One end of the limiter pull plate is inlaid with a limiter pull plate insert, and the other end of the limiter pull plate passes through the control box and is riveted to the limiter bracket through a bracket rotating shaft; the control box is plastic-coated with two screws; after the control box and the limiter pull plate are assembled, they are riveted through a pin. The structure of the present invention is simple, the design of the control box and the tail structure is reasonable, reducing the space requirement of the limiter for layout; preventing external dust, mud and other substances from entering the limiter and causing corrosion of the control box, extending the service life of the car door limiter, reducing the abnormal noise during the operation of the limiter, increasing the comfort of users, and having good economic and social benefits in popularization and application. However, it does not include the calculation analysis and optimization process of the overtravel force of the limiter. Summary of the Invention

[0007] To solve the above problems, the present invention provides a method, device, equipment and storage medium for optimizing the overtravel force of a door limiter. Only the performance of the limiter itself is tested, and the finite element method is used to model the working process of the limiter, which can more clearly master the deformation trend of the overtravel force of the limiter and its influencing factors, and use the optimization of the key parameters of the limiter slot to complete the optimization work of the overtravel force of the limiter, and the overtravel force can be analyzed and optimized during the design stage of the limiter, replacing the sample trial production and test verification work.

[0008] The technical solution of the present invention is described in conjunction with the accompanying drawings as follows:

[0009] In the first aspect, a method for optimizing the overtravel force of a door limiter includes:

[0010] Step 1: Derive the generation mechanism of the overshift force of the door limiter to determine the core factors that cause changes in the overshift force of the limiter;

[0011] Step 2: Establish a simulation model for the limiter to generate a simulated overshift force curve;

[0012] Step 3: Measure the overshift force of the limiter sample to generate a test overshift force curve;

[0013] Step 4: Calibrate the simulation model;

[0014] Step 5: Optimize the structure of the limiter according to the calibrated simulation model.

[0015] Furthermore, the specific method for Step 1 is as follows:

[0016] 11) The pressure of the limiter pressure block on the pull rod is F 压 , then there is

[0017] F 压 = 2 * K * ΔL

[0018] where K is the spring stiffness;

[0019] ΔL is the compression of the spring on one side of the spring;

[0020] 12) When the pressure block is at a certain point on the convex slope of the pull rod, the arc surface at the edge of the pressure block is tangent to the slope of the pull rod at point O. The pulling force F 拉 required to pull the pressure block is the overshift force of the limiter at this time; the vertical force is balanced, and we get:

[0021] F N * cosα = F 压 + F 摩擦 * sinα

[0022] where F N is the normal reaction force of the inclined plane;

[0023] F 摩擦 is the frictional force generated by the normal reaction force F N ;

[0024] α is the angle between the normal direction of the inclined plane and the spring axis at this time, which is also equal to the angle between the slope and the pull rod plane, that is, the slope angle;

[0025] 13) The horizontal force is balanced, and we get:

[0026] F 拉 = F N * sinα + F 摩擦 * cosα

[0027] 14) Additionally:

[0028] F 摩擦 = F N * μ

[0029] Where: μ is the coefficient of friction.

[0030] According to the above formula, we get:

[0031]

[0032] 15) There is grease inside the stopper, making the coefficient of friction μ between the pressure block and the pull rod small, and the slope angle α not exceeding 45°, resulting in μtanα being much less than 1. Therefore, the formula is simplified to:

[0033] F 拉 = (μ + tanα) * F 压

[0034] Therefore, it is known that the overtravel force is mainly dominated by tanα; when the slope angle α is positive, tanα is positive, and the overtravel force is positive; when the slope angle α is negative and the absolute value of tanα is greater than μ, the overtravel force is negative at this time;

[0035] Since the slope angle α is a geometric parameter reflecting the steepness of the surface morphology of the pull rod, it is known that the core factor causing the change in the overtravel force of the stopper is the surface morphology of the pull rod.

[0036] Furthermore, the method of step two is as follows:

[0037] 21) Divide each part of the stopper in the closed state into tetrahedral meshes according to the three-dimensional data;

[0038] 22) Simulate the rotating shaft of the stopper bracket and the pressure block spring, and set the original length and stiffness of the spring;

[0039] 23) Establish the contact relationship between the pressure block, the box body and the pull rod, and set the coefficient of friction;

[0040] 24) Constrain all degrees of freedom of the installation point of the stopper box, set the center of the hole of the stopper bracket as the loading point and apply a forced displacement perpendicular to the installation surface of the box body

[0041] 25) Calculate and extract the force and displacement of the loading point along the displacement direction and generate a curve.

[0042] Furthermore, the specific method of step two is:

[0043] 21) Divide each part of the stopper in the closed state into tetrahedral meshes according to the three-dimensional data, with the element type being C3D4 and the surface mesh size at the contact position not exceeding 1 mm;

[0044] 22) Use the CONNECTOR element to simulate the rotating shaft of the limiter bracket and the pressure block spring. The property of the rotating shaft element is HINGE, and the property of the pressure block spring element is TRANSLATOR. Assign a material with the card type of CONNECTOR_BEHAVIOR to the spring element, and set the length of the spring in the uncompressed state in Ren_len1 in the CONNECTOR CONSTITUTIVE REFERENCE option of the material card. Set the stiffness of the spring in Stiffness1 in the CONNECTOR ELASTICITY COMPONET = 1 option of the material card.

[0045] 23) Establish the contact relationship between the pressure block, the box body, and the pull rod. The contact type is general contact, set the friction coefficient, and use the penetration function to check the model to ensure that there is no penetration between the meshes of each component.

[0046] 24) Adopt ABAQUS implicit analysis, calculate and extract the force and displacement of the loading point along the displacement direction and generate a curve, which is the simulation overtravel force curve.

[0047] Further, the specific method of step three is as follows:

[0048] 31) Fix the limiter box vertically on the rigid bench, and connect the limiter pull rod bracket and the force sensor with a rigid rod.

[0049] 32) Control the test actuator to push and pull the limiter bracket at a linear speed of 2 mm / s, and the direction is perpendicular to the installation surface of the limiter box.

[0050] 33) Extract the axial force of the sensor and generate a force-displacement curve, which is the test overtravel force curve.

[0051] Further, the specific method of step four is as follows:

[0052] 41) Adjust the spring stiffness in the model and the friction coefficients in different contact areas, calculate and extract the simulation overtravel force curves of models with different parameter combinations.

[0053] 42) When the error between the peaks of the simulation overtravel force curve and the peaks of the test overtravel force curve is within ±5% for each peak, complete the model calibration.

[0054] Further, the specific method of step five is as follows:

[0055] 51) Determine the object for optimizing the passing force; During the process of the stopper entering and exiting the pulling cylinder slot, the passing force will experience a process of changing from a positive value to a negative value and then quickly turning back to a positive value. The pulse of the passing force curve is transmitted to the human hand through the vehicle body, which is manifested as the passing feeling. The intensity of the passing feeling is proportional to the amplitude of the passing force change. Therefore, the amplitude of the passing force at a certain gear is set as the object for optimization;

[0056] 52) Determine the optimization target value; Determine the optimization target value according to the amplitude values of the passing forces at each gear of the limiter of the benchmark model, or determine the optimization target value of the passing force amplitude at a certain gear according to the ratio of the passing force amplitudes at each gear of the same limiter;

[0057] 53) Determine the optimization variables and their ranges; The slope angle α of the slot profile is the core factor affecting the passing force. Select four parameters, namely the radius r1 of the upper transition arc of the slot profile controlling the pull rod, the radius r2 of the lower transition arc, the slope angle α of the inclined plane, and the slot depth h, as the optimization variables, and determine the change ranges of each optimization variable, as shown in Table 1:

[0058] Table 1 Variable change ranges

[0059] Number Variable Name Range 1 <![CDATA[r1]]> (-3mm, 3mm) 2 <![CDATA[r2]]> (-3mm, 3mm) 3 α (-10°，10°) 4 h (10mm, 10mm)

[0060] 54) Optimize the profile variables; Use the optimized Latin hypercube algorithm to generate 100 calculation samples, use the plug-in to modify the variable parameters and generate geometric data, and use the automated meshing tool and preprocessing software to embed the sample scheme into the original model in the form of an include file to generate the corresponding finite element model; Calculate and extract the passing force amplitudes at the selected gears in each sample, and use the response surface method to construct a surrogate model between the passing force amplitude and each optimization variable:

[0061]

[0062] where, β0, β i , β ii , β ij are unknown parameters;

[0063] x i is the i-th profile variable;

[0064] x j is the j-th profile variable;

[0065] ε is the error;

[0066] According to the optimization target value of the passing force amplitude, find the variable combination that meets the target through the adaptive simulated annealing method; The optimized variable combination is shown in Table 2;

[0067] Table 2 Optimized results of variable combination

[0068] Number Variable Name Range 1 <![CDATA[r1]]> <![CDATA[r1 - 1.5mm]]> 2 <![CDATA[r2]]> <![CDATA[r2]]> 3 α α+4° 4 h h + 5mm

[0069] In a second aspect, an embodiment of the present invention further provides an overshift force optimization device for a door limiter, including:

[0070] An analysis module for deriving the generation mechanism of the overshift force of the door limiter and determining the core factors causing the change in the overshift force of the limiter;

[0071] A modeling module for establishing a simulation model for the limiter and generating a simulation overshift force curve;

[0072] A measurement module for measuring the overshift force of the limiter sample and testing the overshift force curve;

[0073] A calibration module for calibrating the simulation model;

[0074] An optimization module for optimizing the structure of the limiter according to the calibrated simulation model.

[0075] In a third aspect, an embodiment of the present invention further provides a computer device, including a memory, a processor, and a computer program stored on the memory and executable on the processor. When the processor executes the program, it implements an overshift force optimization method for a door limiter as described in any one of the embodiments of the present invention.

[0076] In a fourth aspect, an embodiment of the present invention further provides a computer-readable storage medium, on which a computer program is stored. When the program is executed by a processor, it implements an overshift force optimization method for a door limiter as described in any one of the embodiments of the present invention.

[0077] The beneficial effects of the present invention are as follows:

[0078] 1) The present invention conducts a theoretical derivation of the overshift force and clarifies the generation mechanism of the overshift force;

[0079] 2) The present invention only tests the performance of the limiter itself, uses the finite element method to model the working process of the limiter, more clearly grasps the deformation trend of the overshift force of the limiter and its influencing factors, and completes the optimization work of the overshift force of the limiter by optimizing the key parameters of the limiter slot;

[0080] 3) The present invention can analyze and optimize the overshift force at the design stage of the limiter, replacing the sample trial production and test verification work. Description of the Drawings

[0081] To more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the accompanying drawings required in the embodiments. It should be understood that the following drawings only show some embodiments of the present invention, and thus should not be regarded as limiting the scope. For those of ordinary skill in the art, without creative efforts, other related drawings can also be obtained based on these drawings.

[0082] Figure 1 is a flowchart of a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0083] Figure 2 is a schematic structural diagram of a device for optimizing the overtravel force of a door limiter in the second embodiment of the present invention;

[0084] Figure 3 is a schematic structural diagram of the limiter in the second embodiment of the present invention;

[0085] Figure 4 is a schematic diagram of the force analysis of the internal system of the limiter in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0086] Figure 5 is a schematic diagram of the test overtravel force curve in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention.

[0087] Figure 6 is a schematic diagram for comparing the test and simulation overtravel force curves in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0088] Figure 7 is a schematic diagram of the limiter pull rod retaining groove in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0089] Figure 8 is a schematic diagram of the retaining groove shape parameters in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0090] Figure 9 is a schematic diagram for comparing the simulation overtravel force curves before and after optimization in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0091] Figure 10 is a schematic diagram for comparing the test overtravel force curves before and after optimization in a method for optimizing the overtravel force of a door limiter in the first embodiment of the present invention;

[0092] Figure 11 is a schematic structural diagram of a computer device in the third embodiment of the present invention.

[0093] In the figure:

[0094] 1. Limiter mounting bracket; 2. Bracket rotating shaft; 3. Limiter box body; 4. Spring; 5. Pressure block; 6. Limiter pull rod; 7. Rubber stopper; 8. First gear over-travel force curve region; 9. Test over-travel force curve; 10. Simulation over-travel force curve; 11. Limiter pull rod retaining groove; 12. Upper transition arc radius; 13. Lower transition arc radius; 14. Inclined plane slope angle; 15. Retaining groove depth; 16. Simulation over-travel force curve before optimization; 17. Simulation over-travel force curve after optimization; 18. Test over-travel force curve before optimization; 19. Test over-travel force curve after optimization. Detailed implementation mode

[0095] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It can be understood that the specific embodiments described herein are only used to explain the present invention, rather than limiting the present invention. Additionally, it should be noted that for the sake of description, only parts related to the present invention are shown in the accompanying drawings, rather than all the structures.

[0096] It should be noted that: Similar reference numerals and letters denote similar items in the following drawings. Therefore, once an item is defined in one drawing, it does not need to be further defined and explained in subsequent drawings. At the same time, in the description of the present invention, terms such as "first", "second", etc. are only used for differential description, and cannot be understood as indicating or implying relative importance.

[0097] Embodiment 1

[0098] Refer to Figure 3 , the limiter includes a limiter mounting bracket 1, a bracket rotating shaft 2, a limiter box body 3, a spring 4, a pressure block 5, a limiter pull rod 6 and a rubber stopper 7.

[0099] Figure 1 A method for optimizing the over-travel force of a car door limiter provided in Embodiment 1 of the present invention is executed by the car door limiter over-travel force device in the embodiment of the present invention. This device can be implemented in software and / or hardware, as Figure 1 shown, the method specifically includes the following steps:

[0100] Refer to Figure 4 , Step 1: Deduce the mechanism of the over-travel force generation of the car door limiter to determine the core factors causing the change in the over-travel force of the limiter;

[0101] The specific method of Step 1 is as follows:

[0102] 11) The pressure of the limiter pressure block on the pull rod is F 压 , then there is

[0103] F 压 = 2 * K * ΔL

[0104] Wherein, K is the spring stiffness;

[0105] ΔL is the compression of the single-side spring;

[0106] 12) When the pressing block is at a certain position on the convex slope of the pull rod, the arc surface at the edge of the pressing block is tangent to the slope of the pull rod at point O, and the pulling force F required to pull the pressing block 拉 is the over-blocking force of the limiter at this time; the vertical force is balanced, and we get:

[0107] F N *cosα = F 压 +F 摩擦 *sinα

[0108] Wherein, F N is the normal reaction force of the inclined plane;

[0109] F 摩擦 is the frictional force generated by the normal reaction force F N ;

[0110] α is the angle between the normal of the inclined plane and the axis of the spring at this time, and is also equal to the angle between the slope and the plane of the pull rod, that is, the slope angle;

[0111] 13) The horizontal force is balanced, and we get:

[0112] F 拉 = F N *sinα + F 摩擦 *cosα

[0113] 14) Additionally:

[0114] F 摩擦 = F N *μ

[0115] Wherein: μ is the friction coefficient.

[0116] According to the above formula, we get:

[0117]

[0118] 15) There is grease inside the limiter, making the friction coefficient μ between the pressing block and the pull rod small, and the slope angle α does not exceed 45°, resulting in μtanα being much less than 1, so the formula is simplified to:

[0119] F 拉 = (μ + tanα)*F 压

[0120] Therefore, it is known that the over-blocking force is mainly dominated by tanα; when the slope angle α is positive, tanα is positive, and the over-blocking force is positive; when the slope angle α is negative and the absolute value of tanα is greater than μ, the over-blocking force is negative at this time;

[0121] Since the slope angle α is a geometric parameter reflecting the steepness of the surface morphology of the pull rod, it is known that the core factor causing the change in the over-travel force of the stopper is the surface morphology of the pull rod.

[0122] Step 2: Establish a simulation model for the stopper and generate a simulation over-travel force curve;

[0123] The specific method of Step 2 is as follows:

[0124] 21) Divide each part of the stopper in the closed state into tetrahedral meshes according to the 3D data. The element type is C3D4, and the surface mesh size at the contact position does not exceed 1 mm;

[0125] 22) Use the CONNECTOR element to simulate the rotating shaft of the stopper bracket and the pressure block spring. The attribute of the rotating shaft element is HINGE, and the attribute of the pressure block spring element is TRANSLATOR. Assign a material with the card type of CONNECTOR_BEHAVIOR to the spring element, and set the length of the spring in the uncompressed state in Ren_len1 in the CONNECTOR CONSTITUTIVE REFERENCE option in the material card, and set the stiffness of the spring in Stiffness1 in the CONNECTOR ELASTICITY COMPONET = 1 option in the material card.

[0126] 23) Establish the contact relationship between the pressure block, the box body and the pull rod. The contact type is general contact. Set the friction coefficient and use the penetration function to check the model to ensure that there is no penetration between the meshes of each component;

[0127] 24) Adopt the implicit analysis of ABAQUS, calculate and extract the force and displacement of the loading point along the displacement direction and generate a curve, which is the simulation over-travel force curve.

[0128] Step 3: Measure the over-travel force of the stopper sample and generate a test over-travel force curve;

[0129] Refer to Figure 5 , in the figure, 8 is the area of the first-gear over-travel force curve.

[0130] The specific method of Step 3 is as follows:

[0131] 31) Fix the stopper box vertically on the rigid bench, and connect the stopper pull rod bracket and the force sensor with a rigid rod;

[0132] 32) Control the test actuator to push and pull the stopper bracket at a linear speed of 2 mm / s, and the direction is perpendicular to the mounting surface of the stopper box;

[0133] 33) Extract the axial force of the sensor and generate a force-displacement curve, which is the test overtravel force curve.

[0134] Step Four: Calibrate the simulation model;

[0135] Refer to Figure 6 , in the figure, 9 represents the test overtravel force curve; 10 represents the simulation overtravel force curve;

[0136] The specific method of the above Step Four is as follows:

[0137] 41) Adjust the spring stiffness in the model and the friction coefficients in different contact areas, calculate and extract the simulation overtravel force curves of models with different parameter combinations;

[0138] 42) When the errors between the peaks of the simulation overtravel force curve and the peaks of the test overtravel force curve are all within ±5%, the model calibration is completed.

[0139] Step Five: Optimize the limiter structure according to the calibrated simulation model.

[0140] Refer to Figure 6 , the specific method of the above Step Five is as follows:

[0141] 51) Determine the overtravel force optimization object; refer to Figure 7 , during the process of the stop block entering and exiting the drawbar slot 11 of the limiter, the overtravel force will experience a process of changing from a positive value to a negative value and then quickly changing back to a positive value. The pulse of the overtravel force curve is transmitted to the human hand through the vehicle body, which is manifested as the overtravel feeling. The intensity of the overtravel feeling is proportional to the amplitude change of the overtravel force. Therefore, the amplitude of the overtravel force in a certain gear is set as the optimization object;

[0142] 52) Determine the optimization target value; determine the optimization target value according to the overtravel force amplitude values of each gear of the limiter of the reference vehicle model, or determine the optimization target value of the overtravel force amplitude of a certain gear according to the ratio of the overtravel force amplitudes of each gear of the same limiter;

[0143] For example: usually, the ratio of the overtravel force amplitudes of the first two gears of the limiter is set to 0.8:1, and the ratio of the overtravel force amplitudes of the first two gears of a certain limiter is 0.5:1. Then, 80% of the overtravel force amplitude of the second gear can be set as the optimization target value of the overtravel force amplitude of the first gear.

[0144] 53) Determine the optimization variables and their ranges; the slope angle α of the drawbar slot profile is the core factor affecting the overtravel force size; select four parameters, namely, the radius r1 of the upper transition arc 12 on the drawbar slot that controls the drawbar slot profile, the radius r2 of the lower transition arc 13, the slope angle 14 of the inclined plane, and the drawbar slot depth 15 defined as h, as the optimization variables. Refer to Figure 7 shown in, determine the change ranges of each optimization variable, as shown in Table 1:

[0145] Table 1 Variable range

[0146] Number Variable Name Range 1 <![CDATA[r1]]> (-3mm, 3mm) 2 <![CDATA[r2]]> (-3mm, 3mm) 3 α (-10°，10°) 4 h (10mm, 10mm)

[0147] 54) Morphological variable optimization: 100 calculation samples were generated using the optimized Latin hypercube algorithm. A plug-in was used to modify variable parameters and generate geometric data. The sample solution was embedded in the original model as an include file using automated meshing tools and pre-processing software to generate the corresponding finite element model. The over-blocking force amplitude of the selected gear position in each sample was calculated and extracted. A proxy model between the over-blocking force amplitude and each optimization variable was constructed using the response surface methodology:

[0148]

[0149] Among them, β0, β i , β ii , β ij is an unknown parameter;

[0150] x i is the i-th morphological variable;

[0151] x j is the jth morphological variable;

[0152] ε is the error;

[0153] The target value is optimized according to the over-blocking force amplitude, and the variable combination that meets the target is found through the adaptive simulated annealing method (ASA). The optimized variable combination is shown in Table 2.

[0154] Table 2 Variable combination optimization results

[0155] Number Variable Name Range 1 <![CDATA[r1]]> <![CDATA[r1 - 1.5mm]]> 2 <![CDATA[r2]]> <![CDATA[r2]]> 3 α α+4° 4 h h + 5mm

[0156] Example 2

[0157] See Figure 2 This is a schematic diagram of the structure of a door stopper over-stop force optimization device provided in the second embodiment of the present invention. The device can be implemented in software and / or hardware. The device can be integrated into any device that provides the function of optimizing the over-stop force display of the door stopper, such as Figure 2 As shown, the door stopper over-blocking force optimization device specifically includes:

[0158] An analysis module is used to deduce the mechanism of door stopper overload force generation and identify the core factors that cause the overload force of the door stopper to change;

[0159] Modeling module, used to establish a simulation model for the limiter and generate a simulated over-blocking force curve;

[0160] A measurement module for measuring the over-travel force of the limiter sample and testing the over-travel force curve;

[0161] A calibration module for calibrating the simulation model;

[0162] An optimization module for optimizing the limiter structure according to the calibrated simulation model.

[0163] The above product can execute the method provided by any embodiment of the present invention and has the corresponding functional modules and beneficial effects for executing the method.

[0164] The technical solution of this embodiment can analyze and optimize the over-travel force during the limiter design stage through the analysis module, modeling module, measurement module, calibration module, and optimization and verification module, replacing the sample trial production and test verification work.

[0165] Embodiment III

[0166] Figure 11 It is a schematic structural diagram of a computer device in Embodiment IV of the present invention. Figure 11 The block diagram of an exemplary computer device 20 suitable for implementing the embodiments of the present invention is shown. Figure 11 The displayed computer device 20 is only an example and should not impose any limitations on the functions and usage scope of the embodiments of the present invention.

[0167] As Figure 11 shown, the computer device 20 is presented in the form of a general-purpose computing device. The components of the computer device 20 may include, but are not limited to: one or more processors or processing units 21, a system memory 22, and a bus 23 connecting different system components (including the system memory 22 and the processing unit 21).

[0168] The bus 23 represents one or more of several types of bus structures, including a memory bus or a memory controller, a peripheral bus, a graphics acceleration port, a processor, or a local bus using any of the multiple bus structures. For example, these architectures include, but are not limited to, the Industry Standard Architecture (ISA) bus, the Micro Channel Architecture (MAC) bus, the Enhanced ISA bus, the Video Electronics Standards Association (VESA) local bus, and the Peripheral Component Interconnect (PCI) bus.

[0169] The computer device 20 typically includes a variety of computer system-readable media. These media can be any available media accessible by the computer device 20, including volatile and non-volatile media, removable and non-removable media.

[0170] System memory 22 may include computer system readable media in the form of volatile memory, such as random access memory (RAM) 24 and / or cache memory 25. The computer device 20 may further include other removable / non-removable, volatile / non-volatile computer system storage media. By way of example only, storage system 26 can be used for reading and writing on non-removable, non-volatile magnetic media ( Figure 4 not shown, commonly referred to as a "hard disk drive"). Although Figure 11 not shown in the figure, a disk drive for reading and writing on removable non-volatile disks (such as "floppy disks"), and an optical disk drive for reading and writing on removable non-volatile optical disks (such as CD-ROM, DVD-ROM or other optical media) can be provided. In these cases, each drive can be connected to the bus 23 through one or more data media interfaces. Memory 28 may include at least one program product having a set (e.g., at least one) of program modules that are configured to perform the functions of the embodiments of the present invention.

[0171] A program / utility with a set (at least one) of program modules 27 can be stored, for example, in memory 28. Such program modules 27 include—but are not limited to—an operating system, one or more application programs, other program modules, and program data. Each or some combination of these examples may include the implementation of a network environment. Program modules 27 generally execute the functions and / or methods in the embodiments described in the present invention.

[0172] The computer device 20 can also communicate with one or more external devices 29 (such as a keyboard, a pointing device, a display 30, etc.), and can also communicate with one or more devices that enable a user to interact with the computer device 20, and / or communicate with any device that enables the computer device 20 to communicate with one or more other computing devices (such as a network card, a modem, etc.). Such communication can be carried out through an input / output (I / O) interface 31. Additionally, in this embodiment, the display 30 of the computer device 20 does not exist as an independent entity but is embedded in the mirror. When the display surface of the display 30 is not displaying, the display surface of the display 30 visually merges with the mirror surface. Moreover, the computer device 20 can also communicate with one or more networks (such as a local area network (LAN), a wide area network (WAN), and / or a public network, such as the Internet) through a network adapter 32. As shown in the figure, the network adapter 32 communicates with other modules of the computer device 20 through the bus 23. It should be understood that although not shown in the figure, other hardware and / or software modules can be used in conjunction with the computer device 20, including but not limited to: microcode, device drivers, redundant processing units, external disk drive arrays, RAID systems, tape drives, and data backup storage systems, etc.

[0173] The processing unit 21 executes various functional applications and data processing by running the programs stored in the system memory 22, for example, implementing a method for optimizing the overshift force of a door limiter provided by the embodiments of the present invention.

[0174] Embodiment 4

[0175] Embodiment 4 of the present invention provides a computer-readable storage medium, on which a computer program is stored. When the program is executed by a processor, it implements the method for optimizing the overshift force of a door limiter provided by all the embodiments of the present application.

[0176] One or more arbitrary combinations of computer-readable media can be adopted. A computer-readable medium can be a computer-readable signal medium or a computer-readable storage medium. A computer-readable storage medium can be, for example, but not limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination of the above. More specific examples (a non-exhaustive list) of the computer-readable storage medium include: an electrical connection having one or more wires, a portable computer disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above. In this document, a computer-readable storage medium can be any tangible medium that contains or stores a program, and this program can be used by or in combination with an instruction execution system, apparatus, or device.

[0177] A computer-readable signal medium can include a data signal propagated in a baseband or as part of a carrier wave, in which the computer-readable program code is carried. Such a propagated data signal can take various forms, including - but not limited to - an electromagnetic signal, an optical signal, or any suitable combination of the above. A computer-readable signal medium can also be any computer-readable medium other than a computer-readable storage medium, and this computer-readable medium can send, propagate, or transmit a program for use by or in combination with an instruction execution system, apparatus, or device.

[0178] The program code contained on a computer-readable medium can be transmitted by any appropriate medium, including - but not limited to - wireless, wire, optical cable, RF, etc., or any suitable combination of the above.

[0179] Computer program code for performing the operations of the present invention can be written in one or more programming languages or combinations thereof. The programming languages include object-oriented programming languages such as Java, Smalltalk, C++, and also include conventional procedural programming languages such as the "C" language or similar programming languages. The program code can be executed entirely on the user's computer, partially on the user's computer, executed as an independent software package, partially on the user's computer and partially on a remote computer, or entirely on a remote computer or server. In the case of a remote computer, the remote computer can be connected to the user's computer through any type of network, including a local area network (LAN) or a wide area network (WAN), or can be connected to an external computer (e.g., connected through the Internet using an Internet service provider).

[0180] Embodiment Five

[0181] This embodiment verifies the effectiveness of the optimized combination.

[0182] The simulation overshift force curves before and after optimizing the rod shape variables are as Figure 9 shown. After optimization, the overshift force amplitude of the first gear in the simulation model is increased to 83% of the overshift force amplitude of the second gear. According to the optimized variable parameters, a prototype of the limiter is manufactured. The test overshift force curves of the limiter before and after optimization are as Figure 10 shown. After optimization, the overshift force amplitude of the first gear in the test is increased to 82% of the overshift force amplitude of the second gear, achieving the overshift force optimization goal.

[0183] Note that the above is only the preferred embodiment of the present invention and the applied technical principles. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein. Various obvious changes, re-adjustments, and substitutions can be made by those skilled in the art without departing from the protection scope of the present invention. Therefore, although the present invention has been described in more detail through the above embodiments, the present invention is not limited to the above embodiments. Without departing from the concept of the present invention, more other equivalent embodiments can be included, and the scope of the present invention is determined by the scope of the appended claims.

Claims

1. An optimization method for the overshift force of a car door limiter, characterized in that, Including: Step 1: Deduce the generation mechanism of the overtravel force of the door limiter to determine the core factors causing the change of the overtravel force of the limiter; Step 2: Establish a simulation model for the limiter to generate a simulated overtravel force curve; Step 3: Measure the overtravel force of the limiter sample to generate a test overtravel force curve; Step 4: Calibrate the simulation model; Step 5: Optimize the structure of the limiter according to the calibrated simulation model, specifically as follows: 51) Determine the overtravel force optimization object; during the process of the stopper entering and exiting the pull cylinder slot, the overtravel force will experience a process of changing from a positive value to a negative value and then quickly turning into a positive value. The pulse of the overtravel force curve is transmitted to the human hand through the door, which is manifested as the overtravel feeling. The intensity of the overtravel feeling is proportional to the change amplitude of the overtravel force. Therefore, set the overtravel force amplitude of a certain gear as the optimization object; 52) Determine the optimization target value; Determine the optimization target value according to the overtravel force amplitude values of each gear of the limiter of the benchmark vehicle model, or determine the optimization target value of the overtravel force amplitude of a certain gear according to the ratio of the overtravel force amplitudes of each gear of the same limiter; 53) Determine the optimization variables and their ranges; the slope angle α of the slot profile is the core factor affecting the overtravel force; Select the radius of the upper transition arc of the slot that controls the slot profile of the control pull rod as r1, the radius of the lower transition arc as r2, the slope angle of the inclined plane as α, and the slot depth as h. These four parameters are used as optimization variables, and the change ranges of each optimization variable are determined as shown in Table 1: Table 1 Variable change ranges 54) Optimize the profile variables; use the optimized Latin hypercube algorithm to generate 100 calculation samples, use the plug-in to modify the variable parameters and generate geometric data, use the automated meshing tool and pre-processing software to embed the sample scheme into the original model in the form of an include file to generate the corresponding finite element model; calculate and extract the overtravel force amplitudes of the selected gears in each sample, and use the response surface method to construct a surrogate model between the overtravel force amplitude and each optimization variable: Among them, β0, β i , β ii , β ij are unknown parameters; x i is the i-th topography variable; x j is the j-th topography variable; ε is the error; According to the overtravel force amplitude optimization target value, find the variable combination that meets the target through the adaptive simulated annealing method; the optimized variable combination is shown in Table 2: Table 2 Optimized results of variable combination 。 2. The method for optimizing the overshift force of a car door limiter according to claim 1, characterized in that The specific method of the above Step 1 is as follows: 11) The pressure of the limiter pressing block on the pull rod is F 压 , then there is F 压 = 2 * K * ΔL Where K is the spring stiffness; ΔL is the compression amount of the single-sided spring of the spring; 12) When the briquette is at a certain position on the slope surface of the pull rod protrusion, the arc surface at the edge of the briquette is tangent to the slope surface of the pull rod at point O, and the required pulling force F for pulling the briquette 拉 is the over-blocking force of the limiter at this time; the force is balanced in the vertical direction, and we get: F N *cosα = F 压 +F 摩擦 *sinα Among them, F N is the normal reaction force of the inclined plane; F 摩擦 is the normal reaction force F N that generates the frictional force; α is the angle between the normal direction of the inclined plane and the spring axis at this time, which is also equal to the angle between the slope and the pull rod plane, that is, the slope angle; 13) The force balance in the horizontal direction gives: F 拉 = F N * sinα + F 摩擦 * cosα 14) In addition: F 摩擦 = F N * μ Where: μ is the friction coefficient; We get: 15) There is grease inside the limiter, making the friction coefficient μ between the pressing block and the pull rod small, and the slope angle α does not exceed 45°. As a result, μtanα is much smaller than 1. Therefore, the formula is simplified to: F 拉 = (μ + tanα) * F 压 Therefore, it is known that the overtravel force is mainly dominated by tanα; when the slope angle α is positive, tanα is positive and the overtravel force is positive; when the slope angle α is negative and the absolute value of tanα is greater than μ, the overtravel force is negative at this time; Since the slope angle α is a geometric parameter reflecting the steepness of the pull rod surface profile, it is known that the core factor causing the change of the overtravel force of the limiter is the pull rod surface profile.

3. The method for optimizing the overshift force of a door limiter according to claim 2, characterized in that The method of the above Step 2 is as follows: 21) Divide each part of the closed - state limiter into tetrahedral meshes according to the 3D data; 22) Simulate the limiter bracket rotating shaft and the pressure block spring, and set the original length and stiffness of the spring; 23) Establish the contact relationship between the pressure block, the box body and the pull rod, and set the friction coefficient; 24) Constrain all degrees of freedom of the limiter box installation point, set the center of the limiter bracket hole as the loading point and apply a forced displacement perpendicular to the box body installation surface 25) Calculate and extract the force and displacement of the loading point along the displacement direction and generate a curve.

4. A method for optimizing the overshift force of a door limiter according to claim 3, characterized in that The specific method of the second step is as follows: 21) Divide each part of the closed - state limiter into tetrahedral meshes according to the 3D data. The element type is C3D4, and the surface mesh size at the contact position does not exceed 1 mm; 22) Use the CONNECTOR element to simulate the limiter bracket rotating shaft and the pressure block spring. The attribute of the rotating shaft element is HINGE, and the attribute of the pressure block spring element is TRANSLATOR. Assign a material with the card type of CONNECTOR_BEHAVIOR to the spring element, and set the length of the spring in the uncompressed state in Ren_len1 in the CONNECTOR CONSTITUTIVE REFERENCE option in the material card, and set the stiffness of the spring in Stiffness1 in the CONNECTOR ELASTICITY COMPONET = 1 option in the material card; 23) Establish the contact relationship between the pressure block, the box body and the pull rod. The contact type is general contact, set the friction coefficient, and use the penetration function to check the model to ensure that there is no penetration between the meshes of each component; 24) Adopt ABAQUS implicit analysis, calculate and extract the force and displacement of the loading point along the displacement direction and generate a curve, which is the simulation over - travel force curve.

5. A method for optimizing the overshift force of a door limiter according to claim 3, characterized in that, The specific method of the third step is as follows: 31) Vertically fix the limiter box body on the rigid bench, and connect the limiter pull rod bracket and the force sensor with a rigid rod; 32) Control the test actuator to push and pull the limiter bracket at a linear speed of 2 mm / s, and the direction is perpendicular to the limiter box body installation surface; 33) Extract the axial force of the sensor and generate a force - displacement curve, which is the test over - travel force curve.

6. A method for optimizing the overshift force of a door limiter according to claim 3, characterized in that, The specific method of the fourth step is as follows: 41) Adjust the spring stiffness in the model and the friction coefficients in different contact areas, calculate and extract the simulation over - travel force curves of models with different parameter combinations; 42) When the error between each peak value of the simulation over - travel force curve and each peak value of the test over - travel force curve is within ±5%, complete the model calibration.

7. A method for optimizing the overshift force of a car door limiter according to claim 1, characterized in that It is realized through a device for optimizing the over - travel force of a car door limiter, including: An analysis module for deducing the generation mechanism of the over - travel force of the car door limiter and determining the core factors causing the change of the limiter over - travel force; A modeling module for establishing a simulation model of the limiter and generating a simulation over - travel force curve; A measurement module for measuring the over - travel force of the limiter sample and obtaining the test over - travel force curve; A calibration module for calibrating the simulation model; An optimization module for optimizing the limiter structure according to the calibrated simulation model.

8. A computer device, comprising a memory, a processor, and a computer program stored on the memory and executable on the processor, characterized in that, When the processor executes the program, it implements a method for optimizing the overshift force of a door limiter as described in any one of claims 1-6.

9. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the program is executed by the processor, it implements a method for optimizing the overshift force of a door limiter as described in any one of claims 1-6.

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