A collaborative design method and device for a gear transmission system in a marine environment

Abstract

The application discloses a kind of collaborative design method and device of gear transmission system for marine environment, it is related to mechanical design field, comprising: the depth that gear transmission system works in marine environment is obtained, based on depth and first relationship, the environmental parameter of marine is calculated;According to environmental parameter and second relationship, the state parameter of lubricating oil used in gear transmission system is calculated;According to the state parameter of lubricating oil and the environmental parameter of marine, select initial gear material in material performance parameter database;According to the design requirement of gear transmission system, select initial configuration in configuration database;Initial gear material and initial configuration are used as initial condition, gear material and configuration are input to coupling performance prediction model to obtain performance index, under constraint condition, target function is solved iteratively using multi-objective optimization algorithm, to obtain the best gear material and configuration.The application overcomes the limitation of traditional separation type design, and can capture complex coupling relationship.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of mechanical design, in particular to a collaborative design method and device for a gear transmission system in marine environment. BACKGROUND

[0002] With the deepening of marine resource development, the performance requirements of the core components of underwater vehicles, deep-sea robots, and seabed operation platforms and other marine equipment are increasingly stringent. As the key component for power transmission in these equipment, the gear transmission system has been working in extreme marine environments such as high hydrostatic pressure, low temperature, and high salt mist corrosion for a long time. These environments pose a serious challenge to the reliability, life, and transmission efficiency of the system.

[0003] High hydrostatic pressure and low temperature can significantly change the mechanical properties of materials and the physical properties of lubricants. Low temperature can easily induce low-temperature brittleness of traditional steel, reducing its toughness; while high pressure puts higher requirements on the strength and fatigue resistance of materials. At the same time, the viscosity of lubricants is extremely sensitive to pressure and temperature: the increase of pressure will cause the viscosity to increase exponentially, and the decrease of temperature will also cause the viscosity to rise sharply. Such a dramatic change in viscosity directly interferes with the formation of elastohydrodynamic lubrication oil film in the gear meshing area. High viscosity not only increases the oil stirring loss and friction loss, reducing the transmission efficiency; more seriously, the oil film failure will exacerbate the tooth surface wear, and even cause galling failure, seriously affecting the contact stress distribution.

[0004] Currently, the design method of marine gear transmission system is usually a fragmented and experience-driven process. The designers often independently select materials, design geometric configurations, and determine lubrication schemes, lacking a unified collaborative framework to comprehensively evaluate the complex interactions between the three and the marine environment. Therefore, it is urgent to develop a collaborative design method that integrates the effects of marine environment, material performance, gear configuration, and lubrication characteristics. This method should systematically explore the optimal balance point between materials, configurations, and performance through multi-objective optimization means in a unified framework, and ultimately achieve performance breakthroughs in marine environment gear transmission systems. SUMMARY

[0005] The present application aims to solve the technical problems in the existing design method of marine gear transmission system, such as the disconnection between material selection, geometric configuration design, and lubrication analysis, the inability to effectively consider the comprehensive impact of high pressure and low temperature environment on the coupled performance of the system, and the resulting low reliability, low efficiency, and low optimization level of the design scheme. A collaborative design method and device for a gear transmission system in marine environment are proposed.

[0006] In a first aspect, the present application provides a collaborative design method for a gear transmission system in marine environment, comprising the following steps:

[0007] The material performance parameter database of the gear transmission system and the configuration database are constructed, the material performance parameter database includes gear materials and corresponding performance parameters, and the configuration database includes planetary gear transmission configurations and series and corresponding configuration parameters;

[0008] A first relationship between the depth of the ocean and environmental parameters and a second relationship between state parameters of lubricating oil and environmental parameters are constructed, a coupling performance prediction model of the gear transmission system is constructed, a target function including configuration parameters of the gear is constructed, and a constraint condition is set;

[0009] The depth at which the gear transmission system works in the ocean environment is obtained, the environmental parameters of the ocean are calculated based on the depth and the first relationship, the state parameters of the lubricating oil used in the gear transmission system are calculated according to the environmental parameters and the second relationship, the initial gear material is selected in the material performance parameter database according to the state parameters of the lubricating oil and the environmental parameters of the ocean, and the initial configuration is selected in the configuration database according to the design requirements of the gear transmission system.

[0010] The initial gear material and the initial configuration are taken as initial conditions, the gear material and the configuration are input into the coupling performance prediction model to obtain performance indexes, and the target function is iteratively solved under the constraint condition by using a multi-objective optimization algorithm to obtain the best gear material and configuration, so that the corresponding performance indexes meet or are better than the target performance indexes.

[0011] Preferably, the environmental parameters include the pressure and temperature of seawater, the first relationship includes a temperature function changing with the depth and a pressure function changing with the depth, the state parameters of the lubricating oil include viscosity, density, specific heat capacity and thermal conductivity, the second relationship includes a viscosity function changing with the environmental parameters, a density function changing with the environmental parameters, a specific heat capacity function changing with the environmental parameters and a thermal conductivity function changing with the environmental parameters, the viscosity function adopts a Roelands equation of viscosity-temperature-pressure, and the density function adopts a Dowson-Higginson equation of density-temperature-pressure.

[0012] Preferably, the gear material includes high-strength low-alloy steel, chromium-nickel-molybdenum alloy steel and austenitic stainless steel, the material parameters include elastic modulus, Poisson's ratio, yield strength, allowable contact stress, allowable bending stress, density and seawater corrosion resistance grade, the planetary gear transmission configuration includes an NGW type planetary gear transmission mechanism, an NWN type planetary gear transmission mechanism and an NN type planetary gear transmission mechanism, the configuration parameters include macro-geometric configuration parameters and micro-geometric configuration parameters, the macro-geometric configuration parameters include modulus, tooth number, pressure angle and spiral angle, the micro-geometric configuration parameters include tooth profile modification and tooth orientation modification, and the design requirements include transmission power, transmission ratio, transmission efficiency and service life.

[0013] As preferred, the coupling performance prediction model comprises a contact stress module, a bending stress module, a transmission efficiency module and a fatigue life module, the contact stress module and the bending stress module are respectively used for calculating the minimum oil film thickness and the film thickness ratio based on the elastohydrodynamic lubrication theory through the viscosity of lubricating oil, obtaining the dynamic load coefficient according to the film thickness ratio, combining the dynamic load coefficient with the configuration parameters and the load of the gear to calculate the contact stress of the tooth surface according to the ISO 6336 standard, and combining the dynamic load coefficient with the configuration parameters of the gear to calculate the bending stress; the transmission efficiency module is used for calculating the total loss power of the gear transmission system according to the ISO / RT 14179 standard, and calculating the transmission efficiency according to the total loss power; the fatigue life module is used for adopting the nominal stress method and combining the Miner linear cumulative damage theory to evaluate the fatigue life of the gear transmission system according to the ISO 6336 series standard.

[0014] As preferred, the objective function is:

[0015] ;

[0016] Wherein, represents the input vector of the objective function, is the modulus, and represent the number of teeth of a pair of gears, represents the helix angle, and b represents the tooth width, and represent the modification coefficient of a pair of gears; , , and respectively represent the first optimization function, the second optimization function, the third optimization function and the fourth optimization function, and min represents taking the minimum value, represents the contact stress, represents the transmission error, represents the system volume, represents the transmission efficiency;

[0017] The constraint conditions include strength constraints, geometric constraints and transmission performance constraints; the strength constraints include the tooth surface contact strength constraint, the pinion root tooth root bending strength constraint and the gear tooth root bending strength constraint;

[0018] The tooth surface contact strength constraint is:

[0019] ;

[0020] The pinion root tooth root bending strength constraint is:

[0021] ;

[0022] The bending strength constraint at the root of the large gear is:

[0023] ;

[0024] in, , and Let represent the tooth surface contact strength constraint function, the pinion root bending strength constraint function, and the gear root bending strength constraint function, respectively. , and This represents the minimum contact stress of the material, the minimum tooth root bending stress of the pinion, and the minimum tooth root bending stress of the gear. , and This indicates the allowable contact stress of the material, the allowable bending stress at the root of the pinion tooth, and the allowable bending stress at the root of the gear tooth.

[0025] Geometric constraints include addendum thickness constraints and center distance matching constraints. The addendum thickness constraint is as follows:

[0026] ;

[0027] The center distance matching constraint is:

[0028] ;

[0029] in, and Let these represent the tooth tip thickness constraint function and the center distance matching constraint function, respectively. Indicates the allowable tooth tip thickness. This indicates minimizing the tooth tip thickness. This represents minimizing the center distance. Indicates the allowable center distance. This indicates that tolerances are allowed;

[0030] Performance constraints include transmission efficiency constraints and transmission smoothness constraints. The transmission efficiency constraint is as follows: ;

[0031] The transmission smoothness constraint is: ;

[0032] in, and Let these represent the transmission efficiency constraint function and the transmission smoothness constraint function, respectively. This represents the minimum transmission efficiency. This indicates the maximum transmission error.

[0033] As a preferred choice, the multi-objective optimization algorithm adopts the NSGA-II algorithm. By setting the population size and the number of iterations, the algorithm uses a simulated binary crossover operator to perform non-dominated sorting and crowding distance calculation. After multiple generations of iteration, it finally converges to a stable Pareto optimal solution set. The best gear material and configuration are then selected from the Pareto optimal solution set.

[0034] Secondly, the present invention provides a collaborative design device for gear transmission systems oriented towards marine environments, comprising:

[0035] The database construction module is configured to build a material performance parameter database and a configuration database for the gear transmission system. The material performance parameter database includes gear materials and their corresponding performance parameters, and the configuration database includes planetary gear transmission configurations and stages and their corresponding configuration parameters.

[0036] The relationship building module is configured to build a first relationship between ocean depth and environmental parameters and a second relationship between lubricating oil state parameters and environmental parameters, build a coupling performance prediction model for the gear transmission system, build an objective function containing gear configuration parameters and set constraints.

[0037] The calculation module is configured to obtain the operating depth of the gear transmission system in the marine environment, calculate the marine environmental parameters based on the depth and a first relationship, calculate the state parameters of the lubricating oil used in the gear transmission system based on the environmental parameters and a second relationship, select the initial gear material from the material performance parameter database based on the lubricating oil state parameters and the marine environmental parameters, and select the initial configuration from the configuration database based on the design requirements of the gear transmission system.

[0038] The optimization module is configured to take the initial gear material and initial configuration as initial conditions, input the gear material and configuration into the coupled performance prediction model to predict the performance index, and use a multi-objective optimization algorithm to iteratively solve the objective function under constraints to obtain the optimal gear material and configuration, so that the corresponding performance index meets or exceeds the target performance index.

[0039] Thirdly, the present invention provides an electronic device including one or more processors; and a storage device for storing one or more programs, wherein when the one or more programs are executed by the one or more processors, the one or more processors implement the method as described in any implementation of the first aspect.

[0040] Fourthly, the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the method as described in any of the implementations of the first aspect.

[0041] Fifthly, the present invention provides a computer program product, including a computer program that, when executed by a processor, implements the method as described in any of the implementations in the first aspect.

[0042] Compared with the prior art, the present invention has the following beneficial effects:

[0043] (1) The collaborative design method for gear transmission systems for marine environments proposed in this invention improves the reliability of the design by establishing a dynamic bending stress model and a transmission efficiency model associated with the lubrication state, which can more accurately predict the mechanical performance and energy efficiency of the gear transmission system under real marine conditions.

[0044] (2) The collaborative design method for gear transmission systems for marine environments proposed in this invention transforms complex design problems into a standardized and repeatable calculation process, which greatly shortens the design cycle, reduces the reliance on physical prototypes and expensive experiments, and provides a quantitative and scientific basis for design decisions, significantly improving the design quality of core transmission components of marine equipment.

[0045] (3) The collaborative design method for gear transmission systems oriented to marine environment proposed in this invention provides a systematic design method that integrates marine environment, materials, geometry, lubrication and performance prediction, overcomes the limitations of traditional separate design, and can fully capture the complex coupling relationship between various factors. Attached Figure Description

[0046] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0047] Figure 1 This is a flowchart illustrating a collaborative design method for a gear transmission system for a marine environment, as an embodiment of this application.

[0048] Figure 2 Fitted surface plot of kinematic viscosity of VG320 lubricating oil for a collaborative design method of gear transmission system for marine environment in an embodiment of this application;

[0049] Figure 3 A simplified structural diagram of a gear transmission system for a collaborative design method of a gear transmission system for a marine environment, as described in an embodiment of this application.

[0050] Figure 4 A flowchart illustrating the transmission efficiency calculation of a collaborative design method for a gear transmission system oriented towards a marine environment, as exemplified by this application.

[0051] Figure 5 The main architecture diagram of the marine environment gear transmission system design and analysis software for the collaborative design method of gear transmission systems for marine environments, which is an embodiment of this application;

[0052] Figure 6 A parametric modeling interface diagram of a marine environment gear transmission system design and analysis software for a collaborative design method of a gear transmission system for a marine environment, as described in an embodiment of this application.

[0053] Figure 7 This is a schematic diagram of a collaborative design device for a gear transmission system for a marine environment, as described in an embodiment of this application.

[0054] Figure 8 A schematic diagram of the hardware structure of an electronic device provided in an embodiment of the present invention. Detailed Implementation

[0055] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this invention, and not all of them. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0056] Figure 1 This application illustrates a collaborative design method for a gear transmission system designed for marine environments, comprising the following steps:

[0057] S1. Construct a material performance parameter database and a configuration database for the gear transmission system. The material performance parameter database includes gear materials and their corresponding performance parameters, while the configuration database includes planetary gear transmission configurations and stages and their corresponding configuration parameters.

[0058] In specific embodiments, gear materials include high-strength low-alloy steel, chromium-nickel-molybdenum alloy steel, and austenitic stainless steel. Material parameters include elastic modulus, Poisson's ratio, yield strength, allowable contact stress, allowable bending stress, density, and seawater corrosion resistance. Planetary gear transmission configurations include NGW type planetary gear transmission mechanisms, NWN type planetary gear transmission mechanisms, and NN type planetary gear transmission mechanisms. Configuration parameters include macroscopic geometric configuration parameters and microscopic geometric configuration parameters. Macroscopic geometric configuration parameters include module, number of teeth, pressure angle, and helix angle. Microscopic geometric configuration parameters include tooth profile modification and tooth direction modification. Design requirements include transmission power, transmission ratio, transmission efficiency, and service life.

[0059] Specifically, the core of the embodiments of this application lies in constructing a digital model system that tightly couples environmental parameters, materials, configuration, lubrication, and system performance (contact stress, bending stress, transmission efficiency), and using a multi-objective optimization algorithm for global optimization. Therefore, a performance parameter database and a configuration database for gear transmission system materials are first established. The performance parameter database includes materials with excellent seawater corrosion resistance and high strength-to-weight ratio, such as high-strength low-alloy steel, chromium-nickel-molybdenum alloy steel, and austenitic stainless steel. Using this material performance parameter database, gear materials suitable for high pressure, low temperature, and seawater corrosion resistance can be selected based on the working conditions of the gear transmission system in a marine environment, and stored in the material performance parameter database for subsequent design selection. Example materials include commonly used high-strength, corrosion-resistant gear materials such as 42CrMoA, 18CrNiMo7-6, and aluminum bronze. The performance parameters in the material database include material parameters such as elastic modulus, Poisson's ratio, yield strength, allowable contact stress, allowable bending stress, density, and seawater corrosion resistance level.

[0060] The planetary gear types in the configuration database include at least NGW type planetary gear transmission mechanism, NWN type planetary gear transmission mechanism and NN type planetary gear transmission mechanism. The macroscopic geometric configuration parameters include module, number of teeth, pressure angle and helix angle, and the microscopic geometric configuration parameters include tooth profile modification and tooth direction modification.

[0061] S2, construct the first relationship between ocean depth and environmental parameters and the second relationship between lubricating oil state parameters and environmental parameters, construct a coupled performance prediction model for gear transmission system, construct an objective function including gear configuration parameters and set constraints.

[0062] In a specific embodiment, the environmental parameters include seawater pressure and temperature. The first relationship includes a temperature function that varies with depth and a pressure function that varies with depth. The lubricating oil's state parameters include viscosity, density, specific heat capacity, and thermal conductivity. The second relationship includes a viscosity function that varies with environmental parameters, a density function that varies with environmental parameters, a specific heat capacity function that varies with environmental parameters, and a thermal conductivity function that varies with environmental parameters. The viscosity function adopts the viscosity-temperature-pressure Roelands equation, and the density function adopts the Dowson-Higginson density-temperature-pressure equation.

[0063] Specifically, the environmental parameters of the target ocean are obtained, including the hydrostatic pressure and seawater temperature corresponding to the depth of the seawater, and temperature and pressure functions that vary with depth are constructed. The environmental parameters of the target ocean are determined by the operation of the gear transmission system at different depths in the ocean. Based on the environmental parameters of the ocean, viscosity, density, specific heat capacity and thermal conductivity functions of the lubricating oil as a function of the ocean environmental parameters are established. These functions can be used to calculate the values ​​of various state parameters of the lubricating oil under different pressure and temperature conditions.

[0064] By constructing temperature and pressure functions that vary with depth in the marine environment, and based on the different depths at which the gear transmission system operates, the corresponding environmental parameters can be calculated. For example, the pressure function of tropical seawater is shown in the following formula:

[0065] ;

[0066] in, Indicates the pressure of seawater. Atmospheric pressure Let the density of seawater be 1.025 × 10⁻⁶. 3 kg / m 3 g is the acceleration due to gravity, taken as 9.8 m / s². 2 h represents the depth of the seawater. The seawater flow velocity, The speed at which marine equipment moves relative to the seawater.

[0067] The formula for the temperature function is:

[0068] ;

[0069] in, This represents the temperature at a depth of h in the seawater.

[0070] Taking VG320 lubricating oil as an example, the viscosity function, density function, specific heat capacity function, and thermal conductivity function of the lubricating oil were obtained through experiments. The viscosity function of the lubricating oil was determined using the viscosity-temperature-pressure Roelands equation, as shown below:

[0071] ;

[0072] in, The value represents the viscosity of the lubricating oil, and T represents the temperature of the lubricating oil. For ambient temperature, For environmental viscosity, and These are the Roelands viscosity-pressure coefficient and viscosity-temperature coefficient, respectively. By measuring the viscosity of lubricating oil at different temperatures and pressures, and then fitting the data using the Roelands equation, the specific viscosity-pressure-temperature characteristics of the lubricant can be obtained. Ultimately, the ambient temperature, ambient viscosity, Roelands viscosity-pressure coefficient, and viscosity-temperature coefficient are determined. Figure 2 The results obtained from the VG320 lubricating oil test and the curve fitting results are shown.

[0073] The gear transmission system in the embodiments of this application includes a pressure equalizer to ensure that the pressure inside the gearbox is the same as that of the external environment. The density function is fitted to the VG320 lubricating oil using the Dowson-Higginson density-temperature-pressure equation, and the fitted equation is as follows:

[0074] ;

[0075] in, This indicates the density of the lubricating oil. ambient temperature The density of the lubricating oil.

[0076] Specific heat capacity and thermal conductivity can be measured experimentally. Specific heat capacity is measured using a differential scanning calorimeter (DSC 214 Polyma), and thermal conductivity is measured using a thermal conductivity meter (TC3000E).

[0077] S3, obtain the operating depth of the gear transmission system in the marine environment, calculate the marine environmental parameters based on the depth and the first relationship; calculate the state parameters of the lubricating oil used in the gear transmission system according to the environmental parameters and the second relationship; select the initial gear material from the material performance parameter database according to the lubricating oil state parameters and the marine environmental parameters; select the initial configuration from the configuration database according to the design requirements of the gear transmission system.

[0078] Specifically, during the design process, the temperature and pressure of the seawater are first calculated based on the depth, temperature, and pressure functions of the gear transmission system operating in the marine environment. Then, based on the seawater temperature and pressure, as well as the viscosity, density, specific heat capacity, and thermal conductivity functions of the lubricating oil, the viscosity, density, specific heat capacity, and thermal conductivity of the lubricating oil are further calculated.

[0079] Based on lubrication conditions and marine environmental parameters, gear materials suitable for high-pressure, low-temperature environments are selected, considering the material's toughness retention at low temperatures, its resistance to deformation under high pressure, and its comprehensive performance under the coupled effects of corrosion and wear. According to the design requirements of the gear transmission system, such as transmission power, transmission ratio, transmission efficiency, and service life, a suitable planetary gear transmission type or multi-stage planetary gear transmission configuration is selected. Taking a transmission ratio of 35.4 and a transmission efficiency greater than 80% as an example, a two-stage NGW type planetary gear can be selected, and its simplified structural diagram is shown below. Figure 3 As shown, this structure combines space efficiency with adaptability to extreme working conditions in deep-sea equipment, providing stable power support for complex underwater operations. Subsequently, appropriate modules, number of teeth, pressure angles, and helix angles were selected, and tooth profiles and directions were modified to adapt to the deep-sea environment.

[0080] Based on the above requirements, select an initial material and an initial configuration to form an initial design scheme. Establish a coupling performance prediction model for the gear transmission system related to the marine environment, comprehensively consider the thermal-fluid-structure coupling effect and the interaction effect of corrosion and wear, compare the results and conduct performance evaluation.

[0081] S4 uses the initial gear material and initial configuration as initial conditions, inputs the gear material and configuration into the coupled performance prediction model to predict the performance index, and uses a multi-objective optimization algorithm to iteratively solve the objective function under constraints to obtain the optimal gear material and configuration, so that the corresponding performance index meets or exceeds the target performance index.

[0082] In a specific embodiment, the coupled performance prediction model includes a contact stress module, a bending stress module, a transmission efficiency module, and a fatigue life module. The contact stress module and the bending stress module are used to calculate the minimum oil film thickness and the film thickness ratio based on the viscosity of the lubricating oil using the elastohydrodynamic lubrication theory. Based on the film thickness ratio, the dynamic load coefficient is obtained. The contact stress of the tooth surface is calculated by combining the dynamic load coefficient with the gear configuration parameters and load using the ISO 6336 standard. The bending stress is calculated by combining the dynamic load coefficient with the gear configuration parameters. The transmission efficiency module is used to calculate the total power loss of the gear transmission system using the ISO / RT14179 standard. The transmission efficiency is calculated based on the total power loss. The fatigue life module is used to evaluate the fatigue life of the gear transmission system using the nominal stress method combined with Miner's linear cumulative damage theory, according to the ISO 6336 series of standards.

[0083] In a specific embodiment, the objective function is:

[0084] ;

[0085] in, This represents the input vector to the objective function. For modulus, and Indicates the number of teeth in a pair of gears. b represents the helix angle, and b represents the tooth width. and This represents the coefficient of change for a pair of gears; , , and Let these represent the first, second, third, and fourth optimization functions, respectively, with min indicating the minimum value. Indicates contact stress, Indicates transmission error. Indicates the system volume. Indicates transmission efficiency;

[0086] Constraints include strength constraints, geometric constraints, and transmission performance constraints; strength constraints include tooth surface contact strength constraints, pinion root bending strength constraints, and gear root bending strength constraints.

[0087] The tooth surface contact strength constraint is:

[0088] ;

[0089] The bending strength constraint at the root of the pinion is:

[0090] ;

[0091] The bending strength constraint at the root of the large gear is:

[0092] ;

[0093] in, , and Let represent the tooth surface contact strength constraint function, the pinion root bending strength constraint function, and the gear root bending strength constraint function, respectively. , and This represents the minimum contact stress of the material, the minimum tooth root bending stress of the pinion, and the minimum tooth root bending stress of the gear. , and This indicates the allowable contact stress of the material, the allowable bending stress at the root of the pinion tooth, and the allowable bending stress at the root of the gear tooth.

[0094] Geometric constraints include addendum thickness constraints and center distance matching constraints. The addendum thickness constraint is as follows:

[0095] ;

[0096] The center distance matching constraint is:

[0097] ;

[0098] in, and Let these represent the tooth tip thickness constraint function and the center distance matching constraint function, respectively. Indicates the allowable tooth tip thickness. This indicates minimizing the tooth tip thickness. This represents minimizing the center distance. Indicates the allowable center distance. This indicates that tolerances are allowed;

[0099] Performance constraints include transmission efficiency constraints and transmission smoothness constraints. The transmission efficiency constraint is as follows: ;

[0100] The transmission smoothness constraint is: ;

[0101] in, and Let these represent the transmission efficiency constraint function and the transmission smoothness constraint function, respectively. This represents the minimum transmission efficiency. This indicates the maximum transmission error.

[0102] In a specific embodiment, the multi-objective optimization algorithm adopts the NSGA-II algorithm. By setting the population size and the number of iterations, it uses a simulated binary crossover operator to perform non-dominated sorting and crowding distance calculation. After multiple generations of iteration, it finally converges to a stable Pareto optimal solution set. The best gear material and configuration are selected from the Pareto optimal solution set.

[0103] Specifically, the gear transmission system coupled performance prediction model includes contact stress, bending stress, transmission efficiency, and fatigue life modules. The contact stress module, based on elastohydrodynamic lubrication theory, uses the working viscosity of the lubricant as input, combined with gear configuration parameters and loads, to calculate the contact stress on the tooth surface. The bending stress module, based on the ISO 6336 standard, establishes a functional relationship between the dynamic coefficient and the working viscosity of the lubricant, incorporating the influence of lubrication state on the system's dynamic behavior into the bending stress calculation, thus achieving coupled analysis of lubrication and bending stress. The transmission efficiency module calculates meshing friction loss based on the friction coefficient, which is determined by comprehensively considering the working viscosity of the lubricant, entrainment speed, slip-roll ratio, and oil film thickness calculated by elastohydrodynamic lubrication theory. The minimum oil film thickness is... The classic formula for calculating viscosity (Dowson-Higginson formula) is... Sucking speed The radius of curvature R and the load W are functions, as shown in the following equation:

[0104] ;

[0105] in, This refers to the viscosity-pressure coefficient of the lubricating oil. For the comprehensive elastic modulus.

[0106] Both the contact stress module and the bending stress module adopt the basic formula of the ISO 6336 standard. The expression for the contact stress module is:

[0107] ;

[0108] in, For the node region coefficient, The elastic coefficient, This is the overlap coefficient. This is the helix angle coefficient. The nominal tangential force on the pitch circle inside the end face. Let be the pitch circle diameter of the pinion, b be the working tooth surface width, and u be the gear ratio. For the use factor, This is the dynamic load factor. This is the inter-tooth load distribution factor. This is the tooth load distribution coefficient.

[0109] The expression for the bending stress module is:

[0110] ;

[0111] in, Normal modulus, It is the tooth profile coefficient. This is the stress correction factor. This is the helix angle coefficient. The inter-tooth load distribution factor is used for calculating bending strength. This is the tooth load distribution factor used for calculating bending strength. It is corrected for the effects of the marine environment on material properties, gear geometry, and multi-field coupling to ensure the accuracy of the calculation.

[0112] For dynamic load factor To model, establish an empirical or semi-empirical model, and This is related to the minimum film thickness ratio, as shown in the following formula:

[0113] ;

[0114] in, To comprehensively measure surface roughness. When In boundary lubrication, the probability of direct metal-to-metal contact increases, leading to intensified impact and vibration. The value is relatively high; when In (full film lubrication) mode, the lubricating film completely separates the tooth surfaces, resulting in smooth meshing. The value is low. (Through...) ← ← ← The chain is indirectly coupled with the viscosity of the lubricant.

[0115] Transmission efficiency is calculated using the ISO / RT 14179 standard to determine the power loss of a gear transmission system, such as... Figure 4As shown, based on the input power and some response parameters, the necessary parameters such as the force and speed of each component of the gear transmission system are calculated. Then, considering the influence of lubricating oil viscosity, material properties, and geometric parameters under the marine environment, the gear meshing loss power in the gear transmission system is calculated respectively. Oil stirring resistance loss power Bearing power loss and oil seal power loss The sum of their power values ​​is taken as the total power loss of the gear transmission system. Therefore, the transmission efficiency of the gear transmission system can be calculated, as shown in the following formula: ;

[0116] in, This refers to the input power.

[0117] The total thermal resistance of the gearbox housing in a marine environment Calculate the heat dissipation With total power loss Equal to estimate the temperature of the oil sump in the tank. The temperature change of the oil sump further affects the performance of the lubricating oil. By taking the temperature of the oil sump in the housing as the temperature of the lubricating oil, the state parameters of the lubricating oil are repeatedly calculated. After multiple iterations, a more accurate transmission efficiency of the gear transmission system is obtained.

[0118] In one example, power loss occurs during gear meshing. Includes external meshing power loss and internal meshing power loss The formula for the meshing power loss of planetary gears is: ,in, This represents the number of planetary gears.

[0119] The power loss due to air resistance during oil churning in planetary gears is: ;in, To reduce power loss due to air resistance during oil stirring, For oil churning losses in the sun gear, For the oil churning loss of the planetary gear, This is for the oil loss caused by the planetary carrier's stirring mechanism.

[0120] Bearing power loss Including no-load friction torque (Bearing air resistance and oil churning loss), radial load friction torque and axial load friction torque The calculation formula is as follows:

[0121] ;

[0122] in, This represents the bearing speed.

[0123] The power loss of the oil seal is: ;in, η is the frictional torque of the oil seal, and n is the rotational speed of the shaft.

[0124] The fatigue life module of this application employs the nominal stress method combined with Miner's linear cumulative damage theory to evaluate the fatigue life of gear transmission systems according to the ISO 6336 series standards. Under the action of the full-life-cycle load spectrum, the cumulative damage of the gear transmission system is calculated using the following formula:

[0125] ;

[0126] Where U represents the total cumulative damage. The damage degree is defined as the damage level under the i-th level load. The actual number of cycles under the i-th level load; Let U be the number of failure cycles corresponding to the i-th load level on the SN curve. When the cumulative damage degree U = 1.0, the gear transmission system is judged to have experienced fatigue failure; when U < 1.0, the corresponding fatigue life is the expected life under which the system can operate safely under this load spectrum.

[0127] The performance indicators obtained from the coupled performance prediction model are compared with the set target performance indicators, which include the target values ​​of transmission efficiency, contact stress, bending stress, and fatigue life. If the target performance indicators are not met, the materials, configurations, or combinations thereof are reselected or adjusted, and a multi-objective optimization algorithm is used for iterative calculation and evaluation until the results meet or exceed the target performance indicators.

[0128] In the multi-objective collaborative optimization process, the macroscopic geometric configuration parameters (such as module) of the gear are first constructed. Number of teeth , helix angle Tooth width b and change coefficient , The objective function is to simultaneously optimize conflicting engineering metrics—including minimizing contact stress. Transmission error and system volume And maximize transmission efficiency (Maximizing by taking negative values) Simultaneously, constraints are set to meet material strength requirements (tooth surface contact stress and tooth root bending stress do not exceed allowable values), geometric requirements (such as tooth tip thickness and center distance matching), and transmission performance (such as efficiency threshold and stability). The objective function is then input into an optimization platform based on the NSGA-II algorithm (such as the MATLAB Global Optimization Toolbox). By setting the population size and number of iterations, a simulated binary crossover operator is used for non-dominated sorting and crowding distance calculation. After multiple iterations, it finally converges to a stable Pareto optimal solution set. The final solution can be selected from this Pareto optimal solution set according to actual needs, and the objective function and constraints can be dynamically adjusted according to the specific scenario.

[0129] This application also presents a design and analysis software for a gear transmission system in a marine environment. This software is based on a high-level architecture (HLA) to build a collaborative design platform. It adopts a layered, multi-module design approach, including a user interaction layer, a core function layer, and a data management layer. The data management layer enables collaboration between these layers. Using Python as the core development language, it combines proprietary algorithms with third-party technology stacks to build a collaborative simulation platform. Figure 5 As shown. The user interaction layer integrates the software operation interface, parametric modeling visualization, and graphical result display functions. It uses the Qt framework to build the graphical user interface and connects to OpenGL 3D model generation tools to achieve dynamic visualization of design parameter input and results, such as... Figure 6 As shown; the core functional layer includes contact stress module, bending stress module, transfer efficiency module, and fatigue life module; the data management layer acts as a collaboration hub, storing parametric modeling data, importing graphics and calculation results through the SQLite database engine, and building a local model library (such as configuration database and material performance parameter database) to support rapid design iteration; this layer realizes real-time data transmission and reception with the user interaction layer and the core functional layer through API, such as feeding back optimization results to the visualization interface.

[0130] Further reference Figure 7 As an implementation of the methods shown in the above figures, this application provides an embodiment of a collaborative design device for gear transmission systems in marine environments. This device embodiment is similar to... Figure 1 Corresponding to the method embodiments shown, this device can be specifically applied to various electronic devices.

[0131] This application provides a collaborative design device for gear transmission systems in marine environments, comprising:

[0132] Database construction module 1 is configured to construct a material performance parameter database and a configuration database for a gear transmission system. The material performance parameter database includes gear materials and their corresponding performance parameters, and the configuration database includes planetary gear transmission configurations and stages and their corresponding configuration parameters.

[0133] Relationship building module 2 is configured to build a first relationship between ocean depth and environmental parameters and a second relationship between lubricating oil state parameters and environmental parameters, build a coupling performance prediction model for the gear transmission system, build an objective function containing gear configuration parameters and set constraints.

[0134] Calculation module 3 is configured to obtain the operating depth of the gear transmission system in the marine environment, calculate the marine environmental parameters based on the depth and a first relationship, calculate the state parameters of the lubricating oil used in the gear transmission system based on the environmental parameters and a second relationship, select the initial gear material from the material performance parameter database based on the lubricating oil state parameters and the marine environmental parameters, and select the initial configuration from the configuration database based on the design requirements of the gear transmission system.

[0135] Optimization module 4 is configured to take the initial gear material and initial configuration as initial conditions, input the gear material and configuration into the coupled performance prediction model to predict the performance index, and use a multi-objective optimization algorithm to iteratively solve the objective function under constraints to obtain the optimal gear material and configuration, so that the corresponding performance index meets or exceeds the target performance index.

[0136] Figure 8 This is a schematic diagram of the hardware structure of an electronic device provided in an embodiment of the present invention. For example... Figure 8 As shown, the electronic device of this embodiment includes a processor 801 and a memory 802; wherein the memory 802 is used to store computer execution instructions; and the processor 801 is used to execute the computer execution instructions stored in the memory to implement the various steps performed by the electronic device in the above embodiment. For details, please refer to the relevant descriptions in the foregoing method embodiments.

[0137] Alternatively, the memory 802 can be either standalone or integrated with the processor 801.

[0138] When the memory 802 is set up independently, the electronic device also includes a bus 803 for connecting the memory 802 and the processor 801.

[0139] This invention also provides a computer storage medium storing computer execution instructions, which, when executed by processor 801, implement the above method.

[0140] This invention also provides a computer program product, including a computer program that, when executed by a processor 801, implements the above-described method.

[0141] In the embodiments provided by this invention, it should be understood that the disclosed devices and methods can be implemented in other ways. For example, the device embodiments described above are merely illustrative; for instance, the division of modules is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple modules may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be indirect coupling or communication connection through some interfaces, devices, or modules, and may be electrical, mechanical, or other forms.

[0142] The modules described as separate components may or may not be physically separate. The components shown as modules may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to implement the solution of this embodiment according to actual needs.

[0143] Furthermore, the functional modules in the various embodiments of this invention can be integrated into one processing unit, or each module can exist physically separately, or two or more modules can be integrated into one unit. The unit formed by the above modules can be implemented in hardware or in the form of hardware plus software functional units.

[0144] The integrated modules implemented as software functional modules described above can be stored in a computer-readable storage medium. These software functional modules, stored in a storage medium, include several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) or processor 801 to execute some steps of the methods of the various embodiments of this application.

[0145] It should be understood that the processor 801 described above can be a Central Processing Unit (CPU), or other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), etc. The general-purpose processor can be a microprocessor, or the processor 801 can be any conventional processor 801. The steps of the method disclosed in this invention can be directly manifested as the hardware processor 801 executing the steps, or as a combination of hardware and software modules within the processor 801 executing the steps.

[0146] The memory 802 may include high-speed RAM memory, and may also include non-volatile memory NVM, such as at least one disk storage device, and may also be a USB flash drive, portable hard drive, read-only memory, disk or optical disc, etc.

[0147] Bus 803 can be an Industry Standard Architecture (ISA), a Peripheral Component Interconnect (PCI) bus, or an Extended Industry Standard Architecture (EISA) bus, etc. Bus 803 can be divided into address bus, data bus, control bus, etc. For ease of illustration, the bus 803 in the accompanying drawings of this application is not limited to only one bus 803 or one type of bus 803.

[0148] The aforementioned storage medium can be implemented from any type of volatile or non-volatile storage device or a combination thereof, such as static random access memory (SRAM), electrically erasable programmable read-only memory (EEPROM), erasable programmable read-only memory (EPROM), programmable read-only memory (PROM), read-only memory (ROM), magnetic storage, flash memory, magnetic disk, or optical disk. The storage medium can be any available medium accessible to general-purpose or special-purpose computers.

[0149] An exemplary storage medium is coupled to a processor 801, enabling the processor 801 to read information from and write information to the storage medium. Alternatively, the storage medium can be an integral part of the processor 801. The processor 801 and the storage medium can reside in an application-specific integrated circuit (ASIC). Alternatively, the processor 801 and the storage medium can exist as discrete components in an electronic device or a host device.

[0150] Those skilled in the art will understand that all or part of the steps of the above-described method embodiments can be implemented by hardware related to program instructions. The aforementioned program can be stored in a computer-readable storage medium. When executed, the program performs the steps of the above-described method embodiments; and the aforementioned storage medium includes various media capable of storing program code, such as ROM, RAM, magnetic disks, or optical disks.

[0151] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A collaborative design method for gear transmission systems in marine environments, characterized in that, Includes the following steps: Construct a material performance parameter database and a configuration database for a gear transmission system. The material performance parameter database includes gear materials and their corresponding performance parameters, and the configuration database includes planetary gear transmission configurations and stages and their corresponding configuration parameters. A first relationship between ocean depth and environmental parameters, and a second relationship between lubricating oil state parameters and environmental parameters are constructed. The first relationship includes temperature and pressure functions varying with depth. The second relationship includes viscosity, density, specific heat capacity, and thermal conductivity functions varying with environmental parameters. The viscosity function adopts the Roelands viscosity-temperature-pressure equation, and the density function adopts the Dowson-Higginson density-temperature-pressure equation. A coupled performance prediction model for a gear transmission system is constructed, including a contact stress module, a bending stress module, a transmission efficiency module, and a fatigue life module. The contact stress module and the bending stress module are used to calculate the minimum oil film thickness and film thickness ratio based on the viscosity of the lubricating oil using elastohydrodynamic lubrication theory, respectively. The dynamic load factor is obtained from the film thickness ratio, and the contact stress on the tooth surface is calculated using the ISO 6336 standard in conjunction with the gear configuration parameters and load. The bending stress is calculated using the dynamic load factor in conjunction with the gear configuration parameters. The transmission efficiency module is used to calculate the contact stress on the tooth surface using ISO / RT. The ISO 14179 standard calculates the total power loss of a gear transmission system and then calculates the transmission efficiency based on this total power loss. The fatigue life module uses the nominal stress method combined with Miner's linear cumulative damage theory to evaluate the fatigue life of the gear transmission system according to the ISO 6336 series standards. It constructs an objective function containing gear configuration parameters and sets constraints. The objective function is: ； in, This represents the input vector to the objective function. For modulus, and Indicates the number of teeth in a pair of gears. b represents the helix angle, and b represents the tooth width. and This represents the coefficient of change for a pair of gears; , , and Let these represent the first, second, third, and fourth optimization functions, respectively, with min indicating the minimum value. Indicates contact stress, Indicates transmission error. Indicates the system volume. Indicates transmission efficiency; The depth at which the gear transmission system operates in the marine environment is obtained, and marine environmental parameters are calculated based on the depth and a first relationship; the state parameters of the lubricating oil used in the gear transmission system are calculated based on the environmental parameters and a second relationship; and an initial gear material is selected from the material performance parameter database based on the lubricating oil state parameters and the marine environmental parameters. According to the design requirements of the gear transmission system, an initial configuration is selected from the configuration database; Using the initial gear material and initial configuration as initial conditions, the gear material and configuration are input into the coupled performance prediction model to predict the performance index. Under the constraints, a multi-objective optimization algorithm is used to iteratively solve the objective function to obtain the optimal gear material and configuration, so that the corresponding performance index meets or exceeds the target performance index.

2. The collaborative design method for gear transmission systems oriented towards marine environments according to claim 1, characterized in that, The environmental parameters include seawater pressure and temperature; the lubricating oil's state parameters include viscosity, density, specific heat capacity, and thermal conductivity.

3. The collaborative design method for gear transmission systems oriented towards marine environments according to claim 1, characterized in that, The gear materials include high-strength low-alloy steel, chromium-nickel-molybdenum alloy steel, and austenitic stainless steel. The material parameters include elastic modulus, Poisson's ratio, yield strength, allowable contact stress, allowable bending stress, density, and seawater corrosion resistance. The planetary gear transmission configurations include NGW type planetary gear transmission mechanisms, NWN type planetary gear transmission mechanisms, and NN type planetary gear transmission mechanisms. The configuration parameters include macroscopic geometric configuration parameters and microscopic geometric configuration parameters. The macroscopic geometric configuration parameters include module, number of teeth, pressure angle, and helix angle. The microscopic geometric configuration parameters include tooth profile modification and tooth direction modification. The design requirements include transmission power, transmission ratio, transmission efficiency, and service life.

4. The collaborative design method for gear transmission systems oriented towards marine environments according to claim 1, characterized in that, The constraints include strength constraints, geometric constraints, and transmission performance constraints; the strength constraints include tooth surface contact strength constraints, pinion root tooth root bending strength constraints, and gear tooth root bending strength constraints. The tooth surface contact strength constraint is: ； The bending strength constraint at the root of the pinion is: ； The bending strength constraint at the root of the large gear is: ； in, , and Let represent the tooth surface contact strength constraint function, the pinion root bending strength constraint function, and the gear root bending strength constraint function, respectively. , and This represents the minimum contact stress of the material, the minimum tooth root bending stress of the pinion, and the minimum tooth root bending stress of the gear. , and This indicates the allowable contact stress of the material, the allowable bending stress at the root of the pinion tooth, and the allowable bending stress at the root of the gear tooth. The geometric constraints include tooth tip thickness constraints and center distance matching constraints. The tooth tip thickness constraint is as follows: ； The center distance matching constraint is: ； in, and Let these represent the tooth tip thickness constraint function and the center distance matching constraint function, respectively. Indicates the allowable tooth tip thickness. This indicates minimizing the tooth tip thickness. This represents minimizing the center distance. Indicates the allowable center distance. This indicates that tolerances are allowed; The performance constraints include transmission efficiency constraints and transmission smoothness constraints. The transmission efficiency constraints are as follows: ; The transmission smoothness constraint is: ; in, and Let these represent the transmission efficiency constraint function and the transmission smoothness constraint function, respectively. This represents the minimum transmission efficiency. This indicates the maximum transmission error.

5. The collaborative design method for gear transmission systems oriented towards marine environments according to claim 1, characterized in that, The multi-objective optimization algorithm adopts the NSGA-II algorithm. By setting the population size and number of iterations, it uses a simulated binary crossover operator to perform non-dominated sorting and crowding distance calculation. After multiple generations of iteration, it finally converges to a stable Pareto optimal solution set. The best gear material and configuration are selected from the Pareto optimal solution set.

6. A collaborative design device for gear transmission systems in marine environments, characterized in that, include: The database construction module is configured to construct a material performance parameter database and a configuration database for a gear transmission system. The material performance parameter database includes gear materials and their corresponding performance parameters, and the configuration database includes planetary gear transmission configurations and stages and their corresponding configuration parameters. The relationship construction module is configured to construct a first relationship between ocean depth and environmental parameters, and a second relationship between lubricating oil state parameters and environmental parameters. The first relationship includes temperature and pressure functions varying with depth. The second relationship includes viscosity, density, specific heat capacity, and thermal conductivity functions varying with environmental parameters. The viscosity function uses the Roelands viscosity-temperature-pressure equation, and the density function uses the Dowson-Higginson density-temperature-pressure equation. A coupled performance prediction model for the gear transmission system is constructed. This model includes a contact stress module, a bending stress module, a transmission efficiency module, and a fatigue life module. The contact stress and bending stress modules are used to calculate the minimum oil film thickness and film thickness ratio based on the lubricating oil viscosity using elastohydrodynamic lubrication theory. The dynamic load factor is obtained from the film thickness ratio. The contact stress is calculated using ISO 6336 standard, combining the dynamic load factor with the gear configuration parameters and load to calculate the contact stress on the tooth surface. The bending stress is calculated using the dynamic load factor and gear configuration parameters. The transmission efficiency module is used to calculate the bending stress using ISO / RT... The ISO 6336 standard calculates the total power loss of a gear transmission system and then calculates the transmission efficiency based on this total power loss. The fatigue life module uses the nominal stress method combined with Miner's linear cumulative damage theory to evaluate the fatigue life of the gear transmission system according to the ISO 6336 series standards. It constructs an objective function containing gear configuration parameters and sets constraints. The objective function is: ； in, This represents the input vector to the objective function. For modulus, and Indicates the number of teeth in a pair of gears. b represents the helix angle, and b represents the tooth width. and This represents the coefficient of change for a pair of gears; , , and Let these represent the first, second, third, and fourth optimization functions, respectively, with min indicating the minimum value. Indicates contact stress, Indicates transmission error. Indicates the system volume. Indicates transmission efficiency; The calculation module is configured to obtain the operating depth of the gear transmission system in a marine environment, calculate marine environmental parameters based on the depth and a first relationship, calculate the state parameters of the lubricating oil used in the gear transmission system according to the environmental parameters and a second relationship, select an initial gear material from the material performance parameter database according to the lubricating oil state parameters and the marine environmental parameters, and select an initial configuration from the configuration database according to the design requirements of the gear transmission system. The optimization module is configured to take the initial gear material and initial configuration as initial conditions, input the gear material and configuration into the coupled performance prediction model to predict the performance index, and use a multi-objective optimization algorithm to iteratively solve the objective function under the constraints to obtain the optimal gear material and configuration, so that the corresponding performance index meets or exceeds the target performance index.

7. An electronic device, comprising: One or more processors; Storage device for storing one or more programs. When the one or more programs are executed by the one or more processors, the one or more processors implement the method as described in any one of claims 1-5.

8. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the program is executed by the processor, it implements the method as described in any one of claims 1-5.

9. A computer program product, comprising a computer program, characterized in that, When the computer program is executed by a processor, it implements the method as described in any one of claims 1-5.

Images