Vehicle brake boost control optimization method, device, equipment and medium

Abstract

The present application relates to a vehicle brake boost control optimization method, device, equipment and medium, which relates to the field of brake control, and the method includes: obtaining the target output conditions and boundary conditions of the brake boost control model; initializing each particle in the particle population using a preset control parameter optimization algorithm, and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents the control parameter combination constructed by the spiral raceway radius, the spiral lead angle, the distance between the center of the spiral raceway and the center of the disc body, and the input torque; determining the optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determining the optimal axial thrust of the moving disc in the variable diameter boost pressure mechanism to act on the pressure-bearing part according to the optimal control parameter combination. The present application helps to improve the performance and stability of the brake system and can ensure the provision of an ideal braking effect.

Description

Technical Field

[0001] The present application relates to the field of brake control, and in particular to a vehicle brake boost control optimization method, a corresponding device, an electronic device and a computer-readable storage medium. Background Art

[0002] In modern automobile braking systems, boosters are often used to increase braking force to ensure vehicle safety under various operating conditions. Currently, common boosters include hydraulic boosters and pneumatic boosters. However, these boosters rely on complex hydraulic or pneumatic systems, which not only increase vehicle manufacturing and maintenance costs, but may also cause system failures under extreme conditions, thus affecting the vehicle's braking performance.

[0003] In the prior art, there are also some force-enhancing devices based on mechanical structures, such as a structure combining a spiral raceway and a ball. However, in practical applications, such structures often have low force-enhancing efficiency due to large rolling resistance under low speed and heavy load. In addition, due to the limitations of the raceway design, the existing mechanical force-enhancing devices cannot achieve a large thrust increase during the torque conversion process, especially when the distribution radius of the rolling element remains unchanged, the thrust increment is small.

[0004] To sum up, due to the limitations of the raceway design, the mechanical force amplification device in the prior art cannot achieve a large thrust increase during the torque conversion process, especially when the rolling element distribution radius remains unchanged, the thrust increment is small, and the like. This application makes corresponding explorations to solve this problem. Summary of the invention

[0005] The purpose of this application is to solve the above-mentioned problems and to provide a vehicle brake boost control optimization method, corresponding device, electronic device and computer-readable storage medium.

[0006] In order to meet the various objectives of this application, this application adopts the following technical solutions:

[0007] A vehicle brake boost control optimization method proposed to meet one of the purposes of this application includes:

[0008] In response to the vehicle brake boost control optimization instruction, the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center, and input torque of the variable diameter boost and pressure mechanism corresponding to the target vehicle are obtained, wherein the disc center is the center of the rotating disc and the moving disc in the variable diameter boost and pressure mechanism;

[0009] According to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter force boosting and pressurizing mechanism, a brake force boosting control model is constructed, wherein the brake force boosting control model represents the axial thrust of the moving disc in the variable diameter force boosting and pressurizing mechanism;

[0010] Obtaining the target output condition and boundary condition of the brake boost control model, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point is greater than the required pressure of the pressure-bearing part corresponding to the point;

[0011] Initialize each particle in the particle population using a preset control parameter optimization algorithm, and determine the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the helix angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque;

[0012] The optimal control parameter combination corresponding to the brake boost control model is determined based on the global optimal solution, and the optimal axial thrust of the moving disk in the variable diameter boost and pressure mechanism is determined based on the optimal control parameter combination to act on the pressure-bearing part to complete the optimization of the vehicle brake boost control.

[0013] Optionally, the step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism includes:

[0014] Obtaining the spiral raceway radius, the spiral lead angle, and the distance between the spiral raceway center and the disk body center;

[0015] Calculate and determine the square value of the distance between the center of the spiral raceway and the center of the disk body and the square value of the radius of the spiral raceway;

[0016] Calculate and determine twice the product of the distance between the center of the spiral raceway and the center of the disk body and the radius of the spiral raceway to determine a first product;

[0017] calculating and determining twice the product of the spiral raceway radius and the tangent value of the helix angle to determine a second product, calculating and determining a first ratio between the axial displacement distance of the moving plate and the second product, and calculating and determining a cosine value of the first ratio;

[0018] Calculate and determine the third product between the first product and the cosine value of the first ratio, calculate and determine the square value of the distance between the center of the spiral raceway and the center of the disk body, the square value of the spiral raceway radius and the first sum of the third product, and determine the rolling body distribution radius in the variable diameter force increasing and pressurizing mechanism based on the square root value of the first sum.

[0019] Optionally, the step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism includes:

[0020] Calculating and determining a fourth product between the rolling element distribution radius and the helix angle, and calculating and determining a tangent value of the fourth product;

[0021] The axial thrust of the moving disk in the variable diameter force boosting and pressurizing mechanism is determined according to a second ratio between the input torque of the variable diameter force boosting and pressurizing mechanism and the tangent value of the fourth product, so as to construct the brake force boosting control model.

[0022] Optionally, the step of initializing each particle in the particle population using a preset control parameter optimization algorithm, and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary condition and the target output condition includes:

[0023] Initialize the current speed and current position of each particle in the particle swarm according to the target output condition and boundary condition of the brake boost control model using a preset control parameter optimization algorithm;

[0024] Obtaining the current fitness value and the current individual optimal solution corresponding to each particle, and determining the current global optimal solution of the particle population according to the current fitness value and the current individual optimal solution;

[0025] Determining the iteration position and iteration speed of each particle based on a preset particle speed formula, the target output condition and the boundary condition;

[0026] Determine the latest fitness value corresponding to each particle according to the iteration position and the iteration speed, determine the individual optimal solution of each particle after iteration based on the iteration position, and determine the global optimal solution of the particle population corresponding to the control parameter combination according to the latest fitness value and the individual optimal solution after iteration;

[0027] The above steps are repeated until a preset maximum number of iterations is met to determine the optimal control parameter combination corresponding to the global optimal solution.

[0028] Optionally, the step of determining an optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determining an optimal axial thrust of a moving disk in the variable diameter boost pressure mechanism to act on a pressure-bearing part according to the optimal control parameter combination includes:

[0029] Inputting the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center and input torque of the variable diameter force boosting and pressurizing mechanism in the optimal control parameter combination into the brake boosting and pressurizing control model to determine the optimal axial thrust of the moving disc in the variable diameter force boosting and pressurizing mechanism;

[0030] The optimal axial thrust of the moving disk is applied to the pressure-bearing member in the vehicle brake control system to optimize the vehicle brake force boost control.

[0031] Optionally, the radius of the spiral raceway is smaller than the radius of the disk body of the movable disk; the spiral rise angle represents the angle at which the spiral raceway rises on the end surface of the disk body, which determines the inclination of the spiral path of the spiral raceway.

[0032] Optionally, the control parameter optimization algorithm is a particle swarm optimization algorithm, and the pressure-bearing part includes a brake caliper or a brake disc.

[0033] A vehicle brake boost control optimization device provided for another purpose of the present application includes:

[0034] A control parameter acquisition module is configured to respond to the vehicle brake boost control optimization instruction, obtain the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center, and input torque of the variable diameter boost and pressure mechanism corresponding to the variable diameter boost and pressure mechanism of the target vehicle, wherein the disc center is the center of the rotating disc and the moving disc in the variable diameter boost and pressure mechanism;

[0035] A control model building module is configured to build a brake boost control model based on the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism, wherein the brake boost control model represents the axial thrust of the moving disc in the variable diameter boost and pressure mechanism;

[0036] a target condition acquisition module, configured to acquire a target output condition and a boundary condition of the brake boost control model, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point thereof is greater than the required pressure of the pressure-bearing member corresponding to the point;

[0037] a control parameter optimization module, configured to initialize each particle in the particle population using a preset control parameter optimization algorithm, and determine a global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the helix angle, the distance between the spiral raceway center and the disk center, and the input torque;

[0038] The brake control module is configured to determine the optimal control parameter combination corresponding to the brake force boost control model according to the global optimal solution, and determine the optimal axial thrust of the moving disk in the variable diameter force boosting mechanism to act on the pressure-bearing part according to the optimal control parameter combination, so as to optimize the vehicle brake force boost control.

[0039] An electronic device provided to meet another purpose of the present application includes a central processing unit and a memory, wherein the central processing unit is used to call and run a computer program stored in the memory to execute the steps of the vehicle brake force boost control optimization method described in the present application.

[0040] A computer-readable storage medium is provided to meet another purpose of the present application, which stores a computer program implemented according to the vehicle brake force boost control optimization method in the form of computer-readable instructions. When the computer program is called and executed by a computer, the steps included in the corresponding method are executed.

[0041] Compared with the prior art, the present application aims at the problem that the mechanical force-enhancing device in the prior art cannot achieve a large thrust increase during the torque conversion process due to the limitation of the raceway design, especially when the rolling element distribution radius remains unchanged, the thrust increment is small, etc. The present application includes but is not limited to the following beneficial effects:

[0042] First, in the vehicle brake boost control optimization method of the present application, a brake boost control model is constructed by using the spiral raceway radius, spiral lead angle, distance between the center of the spiral raceway and the center of the disc body corresponding to the variable diameter boost pressurizing mechanism, and the input torque of the variable diameter boost pressurizing mechanism, which can more accurately predict the axial thrust of the moving disc, thereby effectively optimizing the brake boost control. By adjusting the control parameter combination through the particle swarm optimization algorithm, the fine adjustment of the axial thrust can be achieved, so that the thrust of each point can meet the pressure required by the corresponding pressure-bearing part, which can greatly improve the response speed and control accuracy of the vehicle's brake control system;

[0043] Secondly, the present application adopts the particle swarm optimization algorithm to optimize the various control parameters in the brake boost control model, which can effectively optimize the spiral raceway design in the variable diameter boost and pressure mechanism, and can make the input rotational torque more efficiently converted into the axial thrust of the variable diameter boost and pressure mechanism. Due to the changes in the helix angle and the radius of the spiral raceway, the input torque and the required axial thrust can be more accurately matched, thereby improving the working efficiency of the entire variable diameter boost and pressure mechanism, especially during the rolling process of the rolling body on the spiral raceway, which can achieve smoother and continuous force transmission and reduce energy loss.

[0044] Thirdly, the variable diameter force-increasing and pressurizing mechanism of the present application adopts a variable diameter design, so that the radius and helix angle of the spiral raceway can be adjusted according to actual needs. Compared with the traditional fixed radius raceway, a wider range of thrust increase can be achieved under the condition of unchanged input torque. By adjusting the radius of the spiral raceway and the helix angle through the particle swarm optimization algorithm, the axial thrust of the moving disk in the variable diameter force-increasing and pressurizing mechanism can be more effectively improved, thereby improving the overall force-increasing and pressurizing effect;

[0045] Furthermore, by optimizing the spiral raceway radius, spiral lead angle, input torque and other control parameters in the variable diameter force boosting mechanism, the optimal axial thrust can be achieved, thereby optimizing the vehicle brake boosting control system, which helps to improve the performance and stability of the brake system and ensure ideal braking effects under various driving conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0047] Figure 1 A schematic diagram of a process flow of a vehicle brake boost control optimization method in an embodiment of the present application;

[0048] Figure 2 This is a schematic diagram of the structure of the variable diameter force increasing and pressurizing mechanism in the embodiment of the present application;

[0049] Figure 3 A schematic diagram of a flow chart for determining the distribution radius of rolling elements in the variable diameter force increasing and pressurizing mechanism in an embodiment of the present application;

[0050] Figure 4 A schematic diagram of determining various parameters of the variable diameter force increasing and pressurizing mechanism based on the relationship between the compressive deformation and the corresponding pressure in the embodiment of the present application;

[0051] Figure 5 A schematic diagram of a process for constructing a brake force boost control model in an embodiment of the present application;

[0052] Figure 6A schematic diagram comparing thrust curves of a variable diameter force-increasing and pressurizing mechanism and a constant diameter force-increasing and pressurizing mechanism in an embodiment of the present application;

[0053] Figure 7 A schematic diagram of a process for determining a global optimal solution of a particle population corresponding to a control parameter combination in an embodiment of the present application;

[0054] Figure 8 It is a schematic diagram of a process for determining the optimal axial thrust of a moving disk in a variable diameter force increasing and pressurizing mechanism according to an optimal control parameter combination in an embodiment of the present application;

[0055] Fig. 9 This is a principle block diagram of a vehicle brake force boost control optimization device in an embodiment of the present application;

[0056] Fig.10 It is a schematic diagram of the structure of the computer device in the embodiment of the present application. DETAILED DESCRIPTION

[0057] The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application, and cannot be interpreted as limiting the present application.

[0058] It will be understood by those skilled in the art that, unless expressly stated, the singular forms "one", "said", and "the" used herein may also include plural forms. It should be further understood that the term "comprising" used in the specification of the present application refers to the presence of the features, integers, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof. It should be understood that when we refer to an element as being "connected" or "coupled" to another element, it may be directly connected or coupled to the other element, or there may be an intermediate element. In addition, the "connection" or "coupling" used herein may include wireless connection or wireless coupling. The term "and / or" used herein includes all or any unit and all combinations of one or more associated listed items.

[0059] It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as generally understood by those skilled in the art to which this application belongs. It should also be understood that terms such as those defined in common dictionaries should be understood to have meanings consistent with the meanings in the context of the prior art, and will not be interpreted with idealized or overly formal meanings unless specifically defined as here.

[0060] It will be understood by those skilled in the art that the "client", "terminal" and "terminal device" used herein include both devices with wireless signal receivers, which are devices with only wireless signal receivers without transmission capabilities, and devices with receiving and transmitting hardware, which are devices with receiving and transmitting hardware capable of two-way communication on a two-way communication link. Such devices may include: cellular or other communication devices such as personal computers, tablet computers, which have single-line displays or multi-line displays or cellular or other communication devices without multi-line displays; PCS (Personal Communications Service, personal communication system), which can combine voice, data processing, fax and / or data communication capabilities; PDA (Personal Digital Assistant, personal digital assistant), which may include a radio frequency receiver, pager, Internet / intranet access, web browser, notepad, calendar and / or GPS (Global Positioning System, global positioning system) receiver; conventional laptop and / or palmtop computers or other devices, which have and / or include a conventional laptop and / or palmtop computer or other device with and / or including a radio frequency receiver. The "client", "terminal" and "terminal device" used herein may be portable, transportable, installed in a vehicle (air, sea and / or land), or suitable and / or configured to run locally, and / or in a distributed form, at any other location on the earth and / or in space. The "client", "terminal" and "terminal device" used herein may also be a communication terminal, an Internet terminal, a music / video playback terminal, such as a PDA, a MID (Mobile Internet Device) and / or a mobile phone with a music / video playback function, or a smart TV, a set-top box and other devices.

[0061] The hardware referred to by the names such as "server", "client", and "service node" in this application is essentially an electronic device with capabilities equivalent to those of a personal computer. It is a hardware device that has the necessary components revealed by the von Neumann principle, such as a central processing unit (including an arithmetic unit and a controller), a memory, an input device, and an output device. The computer program is stored in its memory, and the central processing unit calls the program stored in the external memory into the internal memory for execution, executes the instructions in the program, and interacts with the input and output devices to complete specific functions.

[0062] It should be pointed out that the concept of "server" referred to in this application can also be extended to the case of server clusters. According to the network deployment principle understood by those skilled in the art, the servers should be logically divided. In physical space, these servers can be independent of each other but can be called through interfaces, or integrated into a physical computer or a set of computer clusters. Those skilled in the art should understand this flexibility, and should not use it to restrict the implementation of the network deployment method of this application.

[0063] Unless expressly specified, one or more technical features of the present application can be deployed on a server for implementation and accessed by a client through a remote call to obtain an online service interface provided by the server, or can be directly deployed and run on a client for access.

[0064] The neural network models referenced or may be referenced in this application, unless expressly specified, can be deployed on a remote server and remotely called on the client, or can be deployed and directly called on a client with sufficient device capabilities. In some embodiments, when it runs on the client, its corresponding intelligence can be obtained through transfer learning to reduce the requirements for the client's hardware operating resources and avoid excessive occupation of the client's hardware operating resources.

[0065] Unless explicitly specified, the various data involved in this application can be stored remotely on a server or on a local terminal device, as long as it is suitable for being called by the technical solution of this application.

[0066] Those skilled in the art should be aware that, although the various methods of the present application are described based on the same concept and thus present commonality to each other, unless otherwise specified, these methods can be independently executed. Similarly, for each embodiment disclosed in the present application, they are all proposed based on the same inventive concept, therefore, concepts with the same expression, and concepts that are appropriately changed for convenience despite different expressions, should be understood as equivalent.

[0067] Unless the mutually exclusive relationship between the embodiments to be disclosed in this application is explicitly stated, the relevant technical features involved in each embodiment can be cross-combined to flexibly construct a new embodiment, as long as such combination does not deviate from the creative spirit of this application and can meet the needs of the prior art or solve certain deficiencies in the prior art. Those skilled in the art should be aware of this flexibility.

[0068] See also Figure 1 In one embodiment, the vehicle brake boost control optimization method of the present application includes:

[0069] Step S10, responding to the vehicle brake boost control optimization instruction, obtaining the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center, and input torque of the variable diameter boost and pressure mechanism corresponding to the variable diameter boost and pressure mechanism of the target vehicle, wherein the disc center is the center of the rotating disc and the moving disc in the variable diameter boost and pressure mechanism;

[0070] The brake boost control system of the target vehicle can respond to the vehicle brake boost control optimization instruction to obtain the spiral raceway radius, spiral lead angle, distance between the center of the spiral raceway and the center of the disk body, and input torque of the variable diameter boost and pressure mechanism corresponding to the target vehicle's variable diameter boost and pressure mechanism, wherein the center of the disk body is the center of the rotating disk and the movable disk in the variable diameter boost and pressure mechanism, the rotating disk and the movable disk in the variable diameter boost and pressure mechanism have the same center, the spiral raceway radius is smaller than the disk body radius of the movable disk; the spiral lead angle represents the angle at which the spiral raceway rises on the end face of the disk body, which determines the inclination degree of the spiral path of the spiral raceway, and the input torque represents the input rotational torque, which is used to drive the rotating disk in the variable diameter boost and pressure mechanism.

[0071] See also Figure 2 The variable diameter force-enhancing and pressurizing mechanism of the present application includes a rotating disk, a movable disk, a rolling body and a spiral raceway, wherein the rotating disk is provided with a spiral raceway with a certain spiral pitch angle, and the rotating disk drives the operation of the entire variable diameter force-enhancing and pressurizing mechanism through the input rotational torque; the movable disk is arranged opposite to the rotating disk, and the movable disk is also provided with a corresponding spiral raceway, and the corresponding spiral pitch angle of the spiral raceway matches the rotating disk; the rolling body is usually a ball, which is arranged between the rotating disk and the movable disk, and realizes power transmission by rolling on the spiral raceway.

[0072] Specifically, the power transmission mechanism of the variable diameter force boosting and pressurizing mechanism is as follows: when the rotating disk rotates under the action of the input rotational torque, the relative motion between the spiral raceway and the rolling element converts the rotational torque into the axial displacement and axial thrust of the moving disk. Since the spiral raceway adopts a spiral centripetal design, its distribution radius gradually decreases with the increase of the rotation angle of the rotating disk, resulting in a gradual decrease in the distribution radius of the rolling element. According to the dynamic relationship of converting rotational motion into linear motion, as the rotating disk in the variable diameter force boosting and pressurizing mechanism rotates, the axial thrust of the moving disk gradually increases while the input torque remains unchanged, thereby achieving a significant braking force boosting effect.

[0073] More specifically, according to the above-mentioned power transmission mechanism, the rotating disk drives the rolling body to roll on the spiral raceway through the input rotational torque, so that the moving disk generates axial displacement and axial thrust. As the rotating disk rotates, the distribution radius of the spiral raceway gradually decreases, causing the distribution radius of the rolling body to gradually decrease, thereby causing the thrust of the moving disk to gradually increase. This force-enhancing effect can be used to enhance the braking effect.

[0074] In some embodiments, the radius of the rotating disk and the radius of the moving disk in the variable diameter force increasing and pressurizing mechanism are set to , the end surface of the disk is provided with n spiral raceways, wherein the radius of the spiral raceway is , the helix angle is ,and , the distance between the center of the spiral raceway and the center of the disk is Each spiral raceway rotates with the axis of the disk as the axis, and n spiral raceways rotate with The angles are evenly arranged on the end surface of the disk.

[0075] Step S20, constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism, wherein the brake boost control model represents the axial thrust of the moving disc in the variable diameter boost and pressure mechanism;

[0076] After obtaining the spiral raceway radius, spiral lead angle, distance between the center of the spiral raceway and the center of the disk body and the input torque of the variable diameter force boosting and pressurizing mechanism corresponding to the target vehicle, a brake force boosting and pressurizing mechanism is constructed based on the spiral raceway radius, the spiral lead angle, distance between the center of the spiral raceway and the center of the disk body and the input torque of the variable diameter force boosting and pressurizing mechanism, wherein the brake force boosting and pressurizing mechanism characterizes the axial thrust of the moving disk in the variable diameter force boosting and pressurizing mechanism.

[0077] In some embodiments, see Figure 3 The step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism comprises:

[0078] Step S201, obtaining the spiral raceway radius, the spiral lead angle, and the distance between the spiral raceway center and the disk center;

[0079] Step S202, calculating and determining the square value of the distance between the center of the spiral raceway and the center of the disk body, and the square value of the radius of the spiral raceway;

[0080] Step S203, calculating and determining twice the product of the distance between the center of the spiral raceway and the center of the disk body and the radius of the spiral raceway to determine a first product;

[0081] Step S204, calculating and determining twice the product of the spiral raceway radius and the tangent value of the helix angle to determine a second product, calculating and determining a first ratio between the axial displacement distance of the moving disk and the second product, and calculating and determining a cosine value of the first ratio;

[0082] Step S205, calculate and determine the third product between the first product and the cosine value of the first ratio, calculate and determine the square value of the distance between the center of the spiral raceway and the center of the disk body, the square value of the spiral raceway radius and the first sum of the third product, and determine the rolling body distribution radius in the variable diameter force increasing and pressurizing mechanism according to the square root value of the first sum.

[0083] Specifically, see Figure 4 According to the physical characteristics of the pressure-bearing parts, that is, the relationship between the compressive deformation and the corresponding pressure, the various parameters of the variable diameter force-increasing pressure mechanism are determined. In engineering, the pressure-bearing parts often do not have regular geometric shapes, and their material properties are often nonlinear. Therefore, the relationship between the compressive deformation and the corresponding pressure of the pressure-bearing parts can be obtained through experimental means, and the function curve of the two can be drawn.

[0084] (1)

[0085] in, Indicates the required pressure of the pressure-bearing part. is the deformation of the pressure piece;

[0086] When the rotating disk in the variable diameter force increasing and pressurizing mechanism rotates at an angle of When the rolling element distribution radius It can be expressed as:

[0087] (2)

[0088] in, represents the rolling element distribution radius, Indicates the distance between the center of the spiral raceway and the center of the disc body. represents the spiral raceway radius, It means that when the rotating disk rotates by an angle of When , the arc length of the rolling element rolling on the spiral raceway corresponds to the central angle of the circle;

[0089] In addition, when the rotating disk rotates at an angle of When the rolling element has an axial displacement distance The expression is:

[0090] (3)

[0091] in, Indicates the axial displacement distance of the rolling element;

[0092] Since the rotating disk and the moving disk in the variable diameter force increasing and pressurizing mechanism have the same spiral raceway on the upper and lower sides, the axial displacement distance of the moving disk is is the axial displacement distance of the rolling element The expression is twice:

[0093] (4)

[0094] Combining the above formula (2) and formula (4), we can get the rolling element distribution radius R and the axial displacement distance of the moving plate: The relationship between them is expressed as:

[0095] (5)

[0096] Wherein, R represents the rolling element distribution radius.

[0097] The rolling element distribution radius in the variable diameter force-increasing pressurizing mechanism can be determined by the above formula (5).

[0098] For further examples, see Figure 5 The step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism comprises:

[0099] Step S2001, calculating and determining a fourth product between the rolling element distribution radius and the helix angle, and calculating and determining a tangent value of the fourth product;

[0100] Step S2002, determining the axial thrust of the moving disk in the variable diameter force boosting and pressurizing mechanism according to the second ratio between the input torque of the variable diameter force boosting and pressurizing mechanism and the tangent value of the fourth product, so as to construct the brake force boosting control model.

[0101] Specifically, the relationship between the input torque M of the variable diameter force increasing and pressurizing mechanism and the axial thrust F of the moving disk is expressed as:

[0102] (6)

[0103] Combining the above formula (5) and formula (6), we can get the axial thrust F of the moving plate and the axial displacement distance of the moving plate: The relationship expression between:

[0104] (7)

[0105] Based on the axial thrust F of the moving plate and the axial displacement distance of the moving plate The relationship expression between is used to determine the brake force boost control model of the present application, and its expression is:

[0106] (8)

[0107] Among them, the above-mentioned variable diameter force increasing and pressurizing mechanism is regarded as a rigid body, and the axial displacement distance of the moving disk is Deformation of the pressure-bearing parts equal.

[0108] Step S30, obtaining the target output condition and boundary condition of the brake boost control model, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point is greater than the required pressure of the pressure-bearing member corresponding to the point;

[0109] After constructing a brake force boost control model based on the spiral raceway radius, the spiral lead angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque of the variable diameter force boosting and pressurizing mechanism, the target output condition and boundary condition of the brake force boost control model are obtained, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point is greater than the required pressure of the pressure-bearing part corresponding to the point, wherein the axial displacement distance of the moving disk The preset threshold range is defined as ,in, It can be determined by technicians in this field according to the product characteristics of the variable diameter force increasing and pressurizing mechanism. Indicates the maximum axial displacement distance of the moving disk in the variable diameter force-increasing pressurizing mechanism.

[0110] Specifically, when the pressure-bearing part has a pressure requirement, the physical properties of the pressure-bearing part can be obtained through experiments, and the required pressure of the pressure-bearing part can be plotted. The deformation of the pressure piece The experimental settings for obtaining the function curve between the required pressure and deformation of the pressure-bearing part are as follows:

[0111] At room temperature, the pressure-bearing part is placed under the press, and 50 points of the required pressure of the pressure-bearing part from zero to the rated pressure are taken as the input of the press, and the pressing depth of the press is taken as the output and recorded. Each set of pressure and deformation corresponds to five experimental tests and the average value is taken as the final recorded value of the deformation under the pressure. After the experiment, the required pressure and deformation data of the pressure-bearing part are obtained, and the data are imported into the preset simulation software. The simulation software is mainly used for numerical calculation, data analysis, visualization, algorithm development, and modeling and simulation in engineering and science fields.

[0112] The deformation of the pressure piece is , the required pressure of the pressure-bearing part is , and the nonlinear least squares method is used to fit it into a cubic polynomial curve , whose expression is:

[0113] ,

[0114] in, Indicates the required pressure of the pressure-bearing part. Indicates the deformation of the pressure piece. is the cubic coefficient, is the coefficient of the quadratic term, is the coefficient of the first-order term, is a constant term.

[0115] For further information, see Figure 6 By adjusting various control parameters, the thrust curve provided by the variable diameter force-increasing and pressurizing mechanism is changed to ensure that within the deformation range of the working range, the axial thrust F of the moving disk provided by the variable diameter force-increasing and pressurizing mechanism is always greater than the required pressure of the pressure-bearing part. , which can ensure normal work within the pressure requirement. By comparing the thrust curves of the variable diameter force-boosting and pressurizing mechanism and the equal diameter force-boosting and pressurizing mechanism, it can be observed that the variable diameter force-boosting and pressurizing mechanism of the present application provides a better force-boosting and pressurizing effect.

[0116] In some embodiments, the brake boost control model The helix angle , the distance between the center of the spiral raceway and the center of the disc , spiral raceway radius and the input torque of the variable diameter force increasing and pressurizing mechanism Both The adjustable control parameters are within the preset threshold range of the axial displacement distance of the moving disk to meet the requirements of the axial displacement distance of the moving disk, that is, The interval is specified as ,in, It can be determined by technicians in this field according to the product characteristics of the variable diameter force increasing and pressurizing mechanism. Indicates the maximum axial displacement distance of the moving disk in the variable diameter force increasing and pressurizing mechanism. By adjusting the above control parameters, it is ensured that The axial thrust of the moving disk at any point in the interval is always greater than the required pressure of the pressure-bearing part corresponding to the point.

[0117] Furthermore, in view of the fact that traditional optimization methods such as gradient descent and genetic algorithms may encounter local optimal solutions or high computational complexity when dealing with high-dimensional and nonlinear problems, this application uses a particle swarm optimization (PSO) algorithm to optimize the spiral rise angle in the brake boost control model. , the distance between the center of the spiral raceway and the center of the disc , spiral raceway radius and the input torque of the variable diameter force increasing and pressurizing mechanism As a global optimization algorithm, the particle swarm optimization (PSO) algorithm can effectively search for the global optimal solution by simulating the predation behavior of bird flocks. , goodness of fit , complexity penalty , smoothness and stability The optimal control parameter combination in the problem solved by the comprehensive evaluation index derived from the five evaluation indicators is used to achieve the lowest redundancy, cost and space occupancy of the spiral raceway design.

[0118] Step S40, initializing each particle in the particle population using a preset control parameter optimization algorithm, and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the helix angle, the distance between the spiral raceway center and the disk center, and the input torque;

[0119] The target output condition and boundary condition of the brake force boost control model are obtained, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and then each particle in the particle population is initialized using a preset control parameter optimization algorithm, and the global optimal solution of the particle population corresponding to the control parameter combination is determined according to the boundary condition and the target output condition, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the spiral lead angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque, wherein the control parameter optimization algorithm is a particle swarm optimization algorithm, and the pressure-bearing parts include brake calipers, brake discs, or other key components of other brake systems, and the like.

[0120] In some embodiments, see Figure 7 The step of initializing each particle in the particle population using a preset control parameter optimization algorithm and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions comprises:

[0121] Step S401, using a preset control parameter optimization algorithm to initialize the current speed and current position of each particle in the particle swarm according to the target output condition and boundary condition of the brake boost control model;

[0122] Step S402, obtaining the current fitness value and the current individual optimal solution corresponding to each particle, and determining the current global optimal solution of the particle population according to the current fitness value and the current individual optimal solution;

[0123] Step S403, determining the iteration position and iteration speed of each particle based on a preset particle speed formula, the target output condition and the boundary condition;

[0124] Step S404, determining the latest fitness value corresponding to each particle according to the iteration position and the iteration speed, determining the individual optimal solution of each particle after iteration based on the iteration position, and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the latest fitness value and the individual optimal solution after iteration;

[0125] Step S405: Repeat the above steps until a preset maximum number of iterations is met to determine an optimal control parameter combination corresponding to the global optimal solution.

[0126] Specifically, each particle in the particle population is initialized using a preset control parameter optimization algorithm, and the global optimal solution of the particle population corresponding to the control parameter combination is determined according to the boundary conditions and the target output conditions. The specific steps include:

[0127] Step S4001: First define the axial displacement distance of the moving disk The value range is , and is discretized into 100 points. Its objective function includes:

[0128] ,

[0129] in, , the boundary conditions are , the target output condition is for any Within the interval, < .

[0130] Step S4002: Determine various parameters in the particle swarm optimization algorithm (PSO), which includes ,in, represents the number of particles, represents the number of iterations, represents the self-perception coefficient, represents the social cognition coefficient, represents the inertia weight;

[0131] Step S4003: Initialize the current speed and current position of each particle in the particle swarm, where: , , and In the interval [ α 1 , α 2 ] , [ δ 1 , δ 2 ] , [ R 2 1 , R 2 2 ] and [ M 1 , M 2 ] Randomly generated.

[0132]

[0133]

[0134]

[0135]

[0136] Initialize the particle speed and is 0, and the velocity expression corresponding to each particle includes:

[0137]

[0138]

[0139]

[0140]

[0141] in, Indicates that the particle The speed of change of direction, Indicates that the particle The speed of change of direction, Indicates that the particle The speed of change of direction, Indicates that the particle Speed ​​of change of direction.

[0142] Step S4004: Calculate and determine the fitness value corresponding to each particle and initialize the fitness array and valid combination arrays .

[0143] ,

[0144] ;

[0145] For each particle ,calculate

[0146]

[0147] Check in interval Whether If the conditions are met, set the fitness to 1 and record the effective , , and The constructed control parameter combination.

[0148] Step S4005: Initializing the optimal position, which includes:

[0149]

[0150]

[0151]

[0152]

[0153]

[0154] in, represents the individual optimal solution of each particle value, represents the individual optimal solution of each particle value, represents the individual optimal solution of each particle value, represents the individual optimal solution of each particle value, Represents the individual optimal fitness value of each particle;

[0155] Initialize the global optimal position, which includes:

[0156] [~, idx]=max(fitness);

[0157]

[0158]

[0159]

[0160]

[0161]

[0162] in, Represents the global optimal solution value, Represents the global optimal solution value, Represents the global optimal solution value, The global optimal solution value; Represents the global optimal fitness value;

[0163] Step S4006, iteratively updating the particle position. For each iteration, the following steps are performed, which include:

[0164] Step S40061: updating the speed of each particle, which includes:

[0165]

[0166]

[0167]

[0168]

[0169] Step S40062: updating the position of each particle, which includes:

[0170]

[0171]

[0172]

[0173]

[0174] Step S40063: Ensure that the particle position is within the interval ], which includes:

[0175]

[0176]

[0177]

[0178]

[0179] Step S40064: Evaluate whether the current state of the particle meets the target condition, and recalculate the fitness value corresponding to each particle using the following fitness function, which includes:

[0180] ,

[0181] in, particle The corresponding fitness value.

[0182] Right now:

[0183]

[0184] ,

[0185] ;

[0186] Step S40065, updating the individual optimum, which includes:

[0187]

[0188]

[0189]

[0190]

[0191]

[0192]

[0193] Step S40066, updating the global optimum, includes:

[0194]

[0195]

[0196]

[0197]

[0198]

[0199]

[0200] .

[0201] The above steps are repeated until a preset maximum number of iterations is met to determine the optimal control parameter combination corresponding to the global optimal solution.

[0202] In some embodiments, evaluation indicators can be introduced and the optimal solution can be calculated. After iteratively updating the particle position and fitness evaluation, comprehensive evaluation indicators need to be introduced to calculate the optimal solution. These indicators include the sum of squared errors , goodness of fit , complexity penalty , smoothness and stability , the following are the specific steps for optimizing by combining these indicators, which include:

[0203] (1) Define evaluation indicators:

[0204] Error sum of squares : Measures the difference between the predicted value and the actual value.

[0205] ,

[0206] Goodness of fit : reflects the proportion of data variability explained by the model.

[0207] ,

[0208] Complexity penalty : Penalize models with too many parameters to prevent overfitting. is the regularization coefficient.

[0209] ,

[0210] Smoothness : It measures the smoothness of the function curve and can be expressed by the absolute value integral of the second-order derivative.

[0211] ,

[0212] stability : Measures the sensitivity of a function to input changes and can be expressed by the maximum value of the first-order derivative of the function.

[0213] ,

[0214] (2) Constructing a comprehensive evaluation function:

[0215] Combining the above indicators, a comprehensive evaluation function is constructed, which weighs all indicators by giving a weight coefficient and gives a single value to facilitate comparison of the effects of different parameter combinations.

[0216] ;

[0217] in, , , , , is the weight coefficient, which is used to balance the importance of each indicator.

[0218] (3) Adjust parameters and recalculate fitness:

[0219] In each iteration, the comprehensive evaluation index of each particle is calculated according to the new particle position, and the fitness value is updated. If the new fitness is better than the previous individual optimum or global optimum, the corresponding optimal position is updated.

[0220] (4) Output optimal parameters:

[0221] When the stop condition is met, the current global optimal parameters are output , , and as the optimal control parameter combination.

[0222] Step S50, determining the optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determining the optimal axial thrust of the moving disk in the variable diameter boost pressure mechanism to act on the pressure-bearing part according to the optimal control parameter combination to optimize the vehicle brake boost control.

[0223] A preset control parameter optimization algorithm is used to initialize each particle in the particle population. After the global optimal solution of the particle population corresponding to the control parameter combination is determined according to the boundary conditions and the target output conditions, the optimal control parameter combination corresponding to the brake force boost control model is determined according to the global optimal solution. According to the optimal control parameter combination, the optimal axial thrust of the moving disk in the variable diameter force boosting and pressurizing mechanism is determined to act on the pressure part, so as to complete the optimization of the vehicle brake force boost control.

[0224] See also Figure 8The steps of determining the optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determining the optimal axial thrust of the moving disk in the variable diameter boost pressure mechanism to act on the pressure-bearing part according to the optimal control parameter combination include:

[0225] Step S501, inputting the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center and input torque of the variable diameter force boosting and pressurizing mechanism in the optimal control parameter combination into the brake force boosting control model to determine the optimal axial thrust of the moving disc in the variable diameter force boosting and pressurizing mechanism;

[0226] Step S502: Apply the optimal axial thrust of the movable disk to the pressure-bearing part in the vehicle brake control system to optimize the vehicle brake force boost control.

[0227] Specifically, the pressure-bearing parts include brake calipers, brake discs or other key components of the brake system. When they are subjected to the axial thrust of the moving disc in the variable diameter force-increasing and pressure-increasing mechanism, they will enhance the braking effect through force-increasing. By optimizing the control parameters such as the spiral raceway radius, spiral lead angle, and input torque in the variable diameter force-increasing and pressure-increasing mechanism, the optimal axial thrust is achieved, thereby optimizing the vehicle brake force-increasing control system. This optimization helps to improve the performance and stability of the brake system and ensure that ideal braking effects can be provided under various driving conditions.

[0228] It can be seen from the above embodiments that, compared with the prior art, the present application aims at the problem that the mechanical force-enhancing device in the prior art cannot achieve a large thrust increase during the torque conversion process due to the limitation of the raceway design, especially when the rolling element distribution radius remains unchanged, the thrust increment is small, and the like. The present application includes but is not limited to the following beneficial effects:

[0229] First, in the vehicle brake boost control optimization method of the present application, a brake boost control model is constructed by using the spiral raceway radius, spiral lead angle, distance between the center of the spiral raceway and the center of the disc body corresponding to the variable diameter boost pressurizing mechanism, and the input torque of the variable diameter boost pressurizing mechanism, which can more accurately predict the axial thrust of the moving disc, thereby effectively optimizing the brake boost control. By adjusting the control parameter combination through the particle swarm optimization algorithm, the fine adjustment of the axial thrust can be achieved, so that the thrust of each point can meet the pressure required by the corresponding pressure-bearing part, which can greatly improve the response speed and control accuracy of the vehicle's brake control system;

[0230] Secondly, the present application adopts the particle swarm optimization algorithm to optimize the various control parameters in the brake boost control model, which can effectively optimize the spiral raceway design in the variable diameter boost and pressure mechanism, and can make the input rotational torque more efficiently converted into the axial thrust of the variable diameter boost and pressure mechanism. Due to the changes in the helix angle and the radius of the spiral raceway, the input torque and the required axial thrust can be more accurately matched, thereby improving the working efficiency of the entire variable diameter boost and pressure mechanism, especially during the rolling process of the rolling body on the spiral raceway, which can achieve smoother and continuous force transmission and reduce energy loss.

[0231] Thirdly, the variable diameter force-increasing and pressurizing mechanism of the present application adopts a variable diameter design, so that the radius and helix angle of the spiral raceway can be adjusted according to actual needs. Compared with the traditional fixed radius raceway, a wider range of thrust increase can be achieved under the condition of unchanged input torque. By adjusting the radius of the spiral raceway and the helix angle through the particle swarm optimization algorithm, the axial thrust of the moving disk in the variable diameter force-increasing and pressurizing mechanism can be more effectively improved, thereby improving the overall force-increasing and pressurizing effect;

[0232] Furthermore, by optimizing the spiral raceway radius, spiral lead angle, input torque and other control parameters in the variable diameter force boosting mechanism, the optimal axial thrust can be achieved, thereby optimizing the vehicle brake boosting control system, which helps to improve the performance and stability of the brake system and ensure ideal braking effects under various driving conditions.

[0233] See also Fig. 9A vehicle brake boost control optimization device provided to meet one of the purposes of the present application includes a control parameter acquisition module 1100, a control model construction module 1200, a target condition acquisition module 1300, a control parameter optimization module 1400 and a brake control module 1500. Among them, the control parameter acquisition module 1100 is configured to respond to the vehicle brake boost control optimization instruction to obtain the spiral raceway radius, spiral lead angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque of the variable diameter boost and pressure mechanism corresponding to the target vehicle's variable diameter boost and pressure mechanism, wherein the center of the disk body is the center of the rotating disk and the movable disk in the variable diameter boost and pressure mechanism; the control model construction module 1200 is configured to construct a brake boost control model based on the spiral raceway radius, the spiral lead angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque of the variable diameter boost and pressure mechanism, wherein the brake boost control model characterizes the axial thrust of the movable disk in the variable diameter boost and pressure mechanism; the target condition acquisition module 1300 is configured to obtain the target output condition and boundary condition of the brake boost control model, wherein the boundary condition characterizes the preset threshold range of the axial displacement distance of the movable disk, The target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point is greater than the required pressure of the pressure-bearing part corresponding to the point; the control parameter optimization module 1400 is configured to initialize each particle in the particle population using a preset control parameter optimization algorithm, and determine the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output condition, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the spiral lead angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque; the brake control module 1500 is configured to determine the optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determine the optimal axial thrust of the moving disk in the variable diameter boost and pressure mechanism according to the optimal control parameter combination to act on the pressure-bearing part to complete the optimization of the vehicle brake boost control.

[0234] Based on any embodiment of this application, please refer to Fig.10 Another embodiment of the present application further provides an electronic device, which can be implemented by a computer device, such as Fig.10As shown, a schematic diagram of the internal structure of a computer device. The computer device includes a processor, a computer-readable storage medium, a memory, and a network interface connected via a system bus. Among them, the computer-readable storage medium of the computer device stores an operating system, a database, and computer-readable instructions. The database may store a control information sequence. When the computer-readable instructions are executed by the processor, the processor can implement a vehicle brake force boost control optimization method. The processor of the computer device is used to provide computing and control capabilities to support the operation of the entire computer device. The memory of the computer device may store computer-readable instructions. When the computer-readable instructions are executed by the processor, the processor can execute the vehicle brake force boost control optimization method of the present application. The network interface of the computer device is used to connect and communicate with a terminal. Those skilled in the art will understand that Fig.10 The structure shown in the figure is only a block diagram of a part of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied. The specific computer device may include more or fewer components than those shown in the figure, or combine certain components, or have a different arrangement of components.

[0235] In this embodiment, the processor is used to execute Fig. 9 The memory stores the program code and various data required to execute the above modules. The network interface is used to transmit data between user terminals or servers. The memory in this embodiment stores the program code and data required to execute all modules / submodules in the vehicle brake boost control optimization device of this application, and the server can call the program code and data of the server to execute the functions of all submodules.

[0236] The present application also provides a storage medium storing computer-readable instructions. When the computer-readable instructions are executed by one or more processors, the one or more processors execute the steps of the vehicle brake force boost control optimization method described in any embodiment of the present application.

[0237] The present application also provides a computer program product, including a computer program / instruction, which, when executed by one or more processors, implements the steps of the vehicle brake boost control optimization method described in any embodiment of the present application.

[0238] A person skilled in the art can understand that all or part of the processes in the above-mentioned embodiments of the present application can be implemented by instructing the relevant hardware through a computer program, and the computer program can be stored in a computer-readable storage medium. When the program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, the aforementioned storage medium can be a computer-readable storage medium such as a disk, an optical disk, a read-only memory (ROM), or a random access memory (RAM).

[0239] The above description is only a partial implementation method of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications should also be regarded as the scope of protection of the present application.

[0240] In summary, by optimizing the spiral raceway radius, spiral lead angle, input torque and other control parameters in the variable diameter force boosting mechanism, the optimal axial thrust can be achieved, and then the vehicle brake boosting control system can be optimized, which helps to improve the performance and stability of the brake system and ensure ideal braking effects under various driving conditions.

Claims

1. A vehicle brake boost control optimization method, characterized in that: include: In response to the vehicle brake boost control optimization instruction, the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center, and input torque of the variable diameter boost and pressure mechanism corresponding to the target vehicle are obtained, wherein the disc center is the center of the rotating disc and the moving disc in the variable diameter boost and pressure mechanism; According to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter force boosting and pressurizing mechanism, a brake force boosting control model is constructed, wherein the brake force boosting control model represents the axial thrust of the moving disc in the variable diameter force boosting and pressurizing mechanism; Obtaining the target output condition and boundary condition of the brake boost control model, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point is greater than the required pressure of the pressure-bearing part corresponding to the point; Initialize each particle in the particle population using a preset control parameter optimization algorithm, and determine the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the helix angle, the distance between the center of the spiral raceway and the center of the disk body, and the input torque; The optimal control parameter combination corresponding to the brake boost control model is determined based on the global optimal solution, and the optimal axial thrust of the moving disk in the variable diameter boost and pressure mechanism is determined based on the optimal control parameter combination to act on the pressure-bearing part to complete the optimization of the vehicle brake boost control.

2. The vehicle brake boost control optimization method according to claim 1, characterized in that: The step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism includes: Obtaining the spiral raceway radius, the spiral lead angle, and the distance between the spiral raceway center and the disk body center; Calculate and determine the square value of the distance between the center of the spiral raceway and the center of the disk body and the square value of the radius of the spiral raceway; Calculate and determine twice the product of the distance between the center of the spiral raceway and the center of the disk body and the radius of the spiral raceway to determine a first product; calculating and determining twice the product of the spiral raceway radius and the tangent value of the helix angle to determine a second product, calculating and determining a first ratio between the axial displacement distance of the moving plate and the second product, and calculating and determining a cosine value of the first ratio; Calculate and determine the third product between the first product and the cosine value of the first ratio, calculate and determine the square value of the distance between the center of the spiral raceway and the center of the disk body, the square value of the spiral raceway radius and the first sum of the third product, and determine the rolling body distribution radius in the variable diameter force increasing and pressurizing mechanism based on the square root value of the first sum.

3. The vehicle brake boost control optimization method according to claim 2, characterized in that: The step of constructing a brake boost control model according to the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism includes: Calculating and determining a fourth product between the rolling element distribution radius and the helix angle, and calculating and determining a tangent value of the fourth product; The axial thrust of the moving disk in the variable diameter force boosting and pressurizing mechanism is determined according to a second ratio between the input torque of the variable diameter force boosting and pressurizing mechanism and the tangent value of the fourth product, so as to construct the brake force boosting control model.

4. The vehicle brake boost control optimization method according to claim 1, characterized in that: The step of initializing each particle in the particle population by using a preset control parameter optimization algorithm and determining the global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions comprises: Initialize the current speed and current position of each particle in the particle swarm according to the target output condition and boundary condition of the brake boost control model using a preset control parameter optimization algorithm; Obtaining the current fitness value and the current individual optimal solution corresponding to each particle, and determining the current global optimal solution of the particle population according to the current fitness value and the current individual optimal solution; Determining the iteration position and iteration speed of each particle based on a preset particle speed formula, the target output condition and the boundary condition; Determine the latest fitness value corresponding to each particle according to the iteration position and the iteration speed, determine the individual optimal solution of each particle after iteration based on the iteration position, and determine the global optimal solution of the particle population corresponding to the control parameter combination according to the latest fitness value and the individual optimal solution after iteration; The above steps are repeated until a preset maximum number of iterations is met to determine the optimal control parameter combination corresponding to the global optimal solution.

5. The vehicle brake boost control optimization method according to claim 1, characterized in that: The steps of determining the optimal control parameter combination corresponding to the brake boost control model according to the global optimal solution, and determining the optimal axial thrust of the moving disk in the variable diameter boost pressure mechanism to act on the pressure-bearing part according to the optimal control parameter combination include: Inputting the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center and input torque of the variable diameter force boosting and pressurizing mechanism in the optimal control parameter combination into the brake boosting and pressurizing control model to determine the optimal axial thrust of the moving disc in the variable diameter force boosting and pressurizing mechanism; The optimal axial thrust of the moving disk is applied to the pressure-bearing member in the vehicle brake control system to optimize the vehicle brake force boost control.

6. The vehicle brake boost control optimization method according to claim 1, characterized in that: The radius of the spiral raceway is smaller than the radius of the moving disk; the spiral rise angle represents the angle at which the spiral raceway rises on the end surface of the disk, which determines the inclination of the spiral path of the spiral raceway.

7. The vehicle brake boost control optimization method according to any one of claims 1 to 6, characterized in that: The control parameter optimization algorithm is a particle swarm optimization algorithm, and the pressure-bearing part includes a brake caliper or a brake disc.

8. A vehicle brake boost control optimization device, characterized in that: include: A control parameter acquisition module is configured to respond to the vehicle brake boost control optimization instruction, obtain the spiral raceway radius, spiral lead angle, distance between the spiral raceway center and the disc center, and input torque of the variable diameter boost and pressure mechanism corresponding to the variable diameter boost and pressure mechanism of the target vehicle, wherein the disc center is the center of the rotating disc and the moving disc in the variable diameter boost and pressure mechanism; A control model building module is configured to build a brake boost control model based on the spiral raceway radius, the spiral lead angle, the distance between the spiral raceway center and the disc center, and the input torque of the variable diameter boost and pressure mechanism, wherein the brake boost control model represents the axial thrust of the moving disc in the variable diameter boost and pressure mechanism; a target condition acquisition module, configured to acquire a target output condition and a boundary condition of the brake boost control model, wherein the boundary condition represents a preset threshold range of the axial displacement distance of the moving disk, and the target output condition represents that within the preset threshold range of the axial displacement distance of the moving disk, the axial thrust of the moving disk at any point thereof is greater than the required pressure of the pressure-bearing member corresponding to the point; a control parameter optimization module, configured to initialize each particle in the particle population using a preset control parameter optimization algorithm, and determine a global optimal solution of the particle population corresponding to the control parameter combination according to the boundary conditions and the target output conditions, wherein each particle represents a control parameter combination constructed by the spiral raceway radius, the helix angle, the distance between the spiral raceway center and the disk center, and the input torque; The brake control module is configured to determine the optimal control parameter combination corresponding to the brake force boost control model according to the global optimal solution, and determine the optimal axial thrust of the moving disk in the variable diameter force boosting mechanism to act on the pressure-bearing part according to the optimal control parameter combination, so as to optimize the vehicle brake force boost control.

9. An electronic device, comprising a central processing unit and a memory, characterized in that: The central processing unit is used to call and run the computer program stored in the memory to execute the steps of the method according to any one of claims 1 to 7.

10. A computer-readable storage medium, characterized in that: It stores a computer program implemented according to the method described in any one of claims 1 to 7 in the form of computer-readable instructions, and when the computer program is called and executed by a computer, the steps included in the corresponding method are executed.

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