Lubrication failure suppression method, device, apparatus, storage medium, and product

Abstract

This application discloses a lubrication failure suppression method, apparatus, device, storage medium, and product, relating to the field of tribological design technology for hydraulic components. The method includes: acquiring microscopic morphology data of the mating surface between the inner slipper and swashplate of an axial piston pump, and obtaining a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data; acquiring contact characteristic data of the joint surface between the inner slipper and piston ball joint of the axial piston pump, and obtaining a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data; solving the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain lubrication state parameters of the slipper pair; and suppressing lubrication failure of the slipper pair based on the lubrication state parameters. Compared with existing methods, this application achieves quantitative assessment and active suppression of slipper pair lubrication failure by coupling microscopic roughness morphology and multi-degree-of-freedom dynamics.

Description

Technical Field

[0001] This application relates to the field of tribological design technology for hydraulic components, and in particular to a method, apparatus, equipment, storage medium, and product for suppressing lubrication failure. Background Technology

[0002] Axial piston pumps are the core power components of hydraulic systems. Their slipper pairs, subjected to high pressure, high speed, and complex overturning moments, are the weakest points within the pump most prone to friction and wear. A micron-sized lubricating oil film needs to be formed between the slipper and the swashplate to avoid direct contact, but the stability of this oil film directly determines the pump's lifespan and reliability.

[0003] In existing technologies, the analysis of the oil film on the slipper pair is mainly based on macroscopically smooth surfaces or deterministic geometric models (such as fixed grooves). These methods ignore the inherent microscopic random roughness of the slipper and swashplate surfaces. However, it is precisely these microscopic profiles with millimeter-scale wavelengths and micrometer-scale amplitudes that generate the crucial hydrodynamic support effect under high pressure. Because this microscopic mechanism is ignored, existing models cannot accurately predict the actual motion posture of the slipper and the dynamic response of the oil film under pressure impact, resulting in a lack of design basis and making lubrication failure and wear failure highly likely under high pressure.

[0004] Therefore, how to suppress lubrication failure of the slipper pair is an urgent problem to be solved. Summary of the Invention

[0005] The main objective of this application is to provide a method, apparatus, device, storage medium, and product for suppressing lubrication failure, aiming to solve the technical problem of how to suppress lubrication failure of slipper pairs.

[0006] To achieve the above objectives, this application proposes a lubrication failure suppression method, which is applied to a lubrication failure suppression device connected to an axial piston pump. The method includes: The microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump are obtained, and the rough surface hydrodynamic lubrication model of the mating surface is obtained based on the microscopic morphology data. The contact characteristic data of the mating surface between the slipper and the piston ball joint in the axial piston pump are obtained, and the fluid-structure interaction contact friction model of the mating surface is obtained based on the contact characteristic data. The rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model are solved together with the multi-degree-of-freedom dynamic equations of the slipper to obtain the lubrication state parameters of the slipper pair. Based on the lubrication state parameters, lubrication failure is suppressed in the slipper pair.

[0007] In one embodiment, the step of obtaining the rough surface hydrodynamic lubrication model of the mating surface based on the microstructure data includes: Power spectrum analysis was performed on the micro-morphology data to obtain the power spectrum parameters of the surface profile of the mating surface; Based on the power spectrum parameters, the Reynolds equation for the mating surface in cylindrical coordinates is generated; The hydrodynamic lubrication model for the rough surface is obtained based on the Reynolds equation.

[0008] In one embodiment, the step of obtaining the fluid-structure interaction contact friction model of the mating surface based on the contact characteristic data includes: Based on the contact characteristic data, obtain the roughness peak statistical distribution parameters of the mating surface; Based on the Greenwood-Williamson contact theory, a model is generated to show the relationship between the normal contact force of the rough peak and the actual contact area, using the statistical distribution parameters of the rough peak. The hydrostatic bearing effect of high-pressure oil is coupled into the relationship model to obtain the fluid-structure interaction contact friction model.

[0009] In one embodiment, the step of solving the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper includes: Substitute the oil film force and oil film torque output by the rough surface hydrodynamic lubrication model, and the contact friction force and contact friction torque output by the fluid-structure interaction contact friction model, into the multi-degree-of-freedom dynamic equation; The multi-degree-of-freedom dynamic equations are combined with the flow balance equations to obtain a set of nonlinear equations, wherein the flow balance equations describe the balance between the flow rate through the damping groove of the slipper and the oil film leakage flow rate. The lubrication state parameters of the slipper pair are obtained by iteratively solving the nonlinear equations.

[0010] In one embodiment, the step of suppressing lubrication failure of the slipper pair based on the lubrication state parameters includes: The lubrication state parameters are compared with a preset failure threshold. When the lubrication state parameter exceeds the failure threshold, a failure suppression command is generated, and lubrication failure is suppressed for the slipper pair according to the failure suppression command.

[0011] In one embodiment, the step of obtaining the microstructure data of the mating surface between the inner slipper and the swashplate of the axial piston pump includes: Collect three-dimensional topographic point cloud data of the bottom surface of the skid and the surface of the swashplate; The three-dimensional topographic point cloud data is filtered to obtain the microscopic topographic data of the mating surface between the slipper and the inclined plate.

[0012] Furthermore, to achieve the above objectives, this application also proposes a lubrication failure suppression device, the device comprising: The first acquisition module is used to acquire the microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump, and to obtain the rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data. The second acquisition module is used to acquire the contact characteristic data of the joint surface between the slipper and the piston ball joint in the axial piston pump, and to obtain the fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. The third acquisition module is used to couple and solve the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equation of the slipper to obtain the lubrication state parameters of the slipper pair. The failure suppression module is used to suppress lubrication failure of the slipper pair based on the lubrication state parameters.

[0013] In addition, to achieve the above objectives, this application also proposes a lubrication failure suppression device, the device comprising: a memory, a processor, and a computer program stored in the memory and executable on the processor, the computer program being configured to implement the steps of the lubrication failure suppression method as described above.

[0014] In addition, to achieve the above objectives, this application also proposes a storage medium, which is a computer-readable storage medium, on which a computer program is stored, and when the computer program is executed by a processor, it implements the steps of the lubrication failure suppression method described above.

[0015] In addition, to achieve the above objectives, this application also provides a computer program product, which includes a computer program that, when executed by a processor, implements the steps of the lubrication failure suppression method described above.

[0016] This application provides a method for suppressing lubrication failure, which is applied to a lubrication failure suppression device connected to an axial piston pump. The method includes: acquiring microscopic morphology data of the mating surface between the slipper and the swashplate inside the axial piston pump, and obtaining a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data; acquiring contact characteristic data of the joint surface between the slipper and the piston ball joint inside the axial piston pump, and obtaining a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data; solving the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain lubrication state parameters of the slipper pair; and suppressing lubrication failure of the slipper pair based on the lubrication state parameters.

[0017] This application first obtains the microscopic morphology data of the mating surface between the inner slipper and the swashplate of an axial piston pump, and then obtains a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data. Next, it obtains the contact characteristic data of the joint surface between the inner slipper and the piston ball joint, and obtains a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. Then, it solves the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain the lubrication state parameters of the slipper pair. Finally, it suppresses lubrication failure of the slipper pair based on the lubrication state parameters. Compared with existing methods, this application achieves quantitative evaluation and active suppression of slipper pair lubrication failure by coupling microscopic roughness morphology and multi-degree-of-freedom dynamics. Attached Figure Description

[0018] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0019] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic flowchart of an embodiment of the lubrication failure suppression method of this application; Figure 2 This is a schematic flowchart of Embodiment 2 of the lubrication failure suppression method of this application; Figure 3 This is a schematic flowchart of Embodiment 3 of the lubrication failure suppression method of this application; Figure 4 This is a schematic diagram of the module structure of the lubrication failure suppression device according to an embodiment of this application; Figure 5 This is a schematic diagram of the device structure of the hardware operating environment involved in the lubrication failure suppression method in the embodiments of this application.

[0021] The purpose, features, and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0022] It should be understood that the specific embodiments described herein are merely illustrative of the technical solutions of this application and are not intended to limit this application.

[0023] To better understand the technical solution of this application, a detailed description will be provided below in conjunction with the accompanying drawings and specific implementation methods.

[0024] The main solution of this application embodiment is as follows: The axial piston pump is the core power component of the hydraulic system. Its slipper pair, due to bearing high pressure, high speed and complex overturning torque, is the weakest link in the pump that is most prone to friction and wear. A micron-level lubricating oil film needs to be formed between the slipper and the swashplate to avoid direct contact, but the stability of this oil film directly determines the pump's lifespan and reliability.

[0025] In existing technologies, the analysis of the oil film on the slipper pair is mainly based on macroscopically smooth surfaces or deterministic geometric models (such as fixed grooves). These methods ignore the inherent microscopic random roughness of the slipper and swashplate surfaces. However, it is precisely these microscopic profiles with millimeter-scale wavelengths and micrometer-scale amplitudes that generate the crucial hydrodynamic support effect under high pressure. Because this microscopic mechanism is ignored, existing models cannot accurately predict the actual motion posture of the slipper and the dynamic response of the oil film under pressure impact, resulting in a lack of design basis and making lubrication failure and wear failure highly likely under high pressure.

[0026] This application first obtains the microscopic morphology data of the mating surface between the inner slipper and the swashplate of an axial piston pump, and then obtains a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data. Next, it obtains the contact characteristic data of the joint surface between the inner slipper and the piston ball joint, and obtains a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. Then, it solves the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain the lubrication state parameters of the slipper pair. Finally, it suppresses lubrication failure of the slipper pair based on the lubrication state parameters. Compared with existing methods, this application achieves quantitative evaluation and active suppression of slipper pair lubrication failure by coupling microscopic roughness morphology and multi-degree-of-freedom dynamics.

[0027] It should be noted that the executing entity in the following embodiments can be a lubrication failure suppression device, or a computing service device with data processing, network communication, and program execution functions, such as a tablet computer, personal computer, or mobile phone, or a lubrication failure suppression device capable of performing the above functions. This embodiment does not specifically limit it in this way. The following uses a lubrication failure suppression device (hereinafter referred to as the device) as the executing entity to describe this embodiment and the following embodiments.

[0028] Based on this, this application proposes a lubrication failure suppression method according to the first embodiment, please refer to... Figure 1 , Figure 1 This is a flowchart illustrating an embodiment of the lubrication failure suppression method of this application, wherein the method includes steps S10 to S40: Step S10: Obtain the microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump, and obtain the rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data.

[0029] It should be explained that the aforementioned axial piston pump can be a positive displacement pump used in a hydraulic system to output high-pressure oil, which contains a friction pair consisting of a slipper and a swashplate.

[0030] The aforementioned slipper can be a component in an axial piston pump that is connected to the piston ball joint and swings with the swashplate. The aforementioned swashplate can be an inclined disc in an axial piston pump used to drive the reciprocating motion of the piston.

[0031] The aforementioned mating surface can refer to the area where the bottom surface of the slipper and the surface of the swashplate come into contact and move relative to each other. The aforementioned micro-morphological data can be data describing the micro-geometric characteristics of the mating surface, such as surface roughness, waviness, and profile peak-valley distribution.

[0032] The aforementioned rough surface hydrodynamic lubrication model can be a mathematical model used to describe the hydrodynamic pressure effect generated by random rough surfaces on mating surfaces during relative motion. This model can characterize the quantitative relationship between oil film pressure, bearing capacity and surface morphology parameters.

[0033] In the specific implementation, the microscopic morphology data of the mating surface between the slipper and the swashplate in the axial piston pump is obtained. Subsequently, based on the obtained microscopic morphology data, a rough surface hydrodynamic lubrication model is established to describe this mating surface. Statistical methods can be used to process the microscopic morphology data, extract statistical parameters characterizing the random roughness features of the surface, and construct the rough surface hydrodynamic lubrication model based on these parameters.

[0034] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, the mating surface area between the slipper and swashplate of an axial piston pump is 100 square millimeters. Three-dimensional morphological data of this mating surface are collected using a surface profilometer, yielding microscopic morphological data with a surface roughness Ra of 0.4 micrometers and a Gaussian distribution of profile peaks and valleys. Based on this data, a rough surface hydrodynamic lubrication model capable of calculating oil film pressure distribution and load-bearing capacity is established.

[0035] Step S20: Obtain the contact characteristic data of the mating surface between the slipper and the piston ball joint in the axial piston pump, and obtain the fluid-structure interaction contact friction model of the mating surface based on the contact characteristic data.

[0036] It should be explained that the aforementioned plunger ball joint can refer to the spherical structure at the end of the plunger in an axial plunger pump, which mates with the ball socket on the slipper to form a ball joint connection.

[0037] The aforementioned mating surface can refer to the area where the inner surface of the ball socket of the slipper and the outer surface of the plunger head come into contact. The aforementioned contact characteristic data can be data describing the mechanical behavior exhibited by the surface roughness peaks of the mating surface during the contact process, such as the height distribution, radius of curvature, surface density of the roughness peaks, and parameters such as the hardness and elastic modulus of the material.

[0038] The aforementioned fluid-structure interaction contact friction model can be a mathematical model used to describe the mechanical behavior of the joint surface under the combined action of fluid pressure and solid roughness peak contact force. This model can characterize the contact force, friction force, and fluid load-bearing ratio of the joint surface when subjected to normal load and tangential sliding.

[0039] In the specific implementation, contact characteristic data of the mating surface between the inner slipper and the piston ball joint of the axial piston pump are obtained. Subsequently, based on the obtained contact characteristic data, a fluid-structure interaction contact friction model is established to describe this mating surface. Roughness peak statistical parameters can be obtained by measuring the surface morphology of the ball joint mating surface, and a roughness peak contact sub-model is constructed based on the Greenwood-Williamson contact theory. Simultaneously, the hydrostatic bearing effect of high-pressure oil in the mating surface gap is coupled, ultimately obtaining a fluid-structure interaction contact friction model that can simultaneously reflect solid contact force and fluid bearing capacity.

[0040] For ease of understanding, the following examples are provided for illustration, but do not impose specific limitations on this embodiment. For instance, the diameter of the mating surface between the slipper and the piston ball joint of an axial piston pump is 15 mm. Surface profilometer measurements show that the roughness peak density of this mating surface is 500 peaks per square millimeter, the average radius of curvature is 0.1 mm, and the roughness peak height follows a normal distribution with a mean of 0.5 micrometers. Based on the Greenwood-Williamson theory, the relationship between contact force and deformation is established, and the hydrostatic bearing capacity of 40 MPa high-pressure oil in a 0.5-micrometer gap is coupled to obtain a fluid-structure interaction contact friction model capable of calculating the total bearing capacity and frictional torque of the mating surface.

[0041] Step S30: Solve the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equation of the slipper to obtain the lubrication state parameters of the slipper pair.

[0042] It should be explained that the aforementioned multi-degree-of-freedom dynamic equations can be mathematical equations describing the relationship between the motion state of the skate in multiple directions and the forces acting on it. The skate can have three degrees of freedom in motion: linear motion along the plane perpendicular to the swashplate and two degrees of freedom in swinging motion around the plunger ball.

[0043] The aforementioned slipper pair can refer to a friction pair assembly consisting of a slipper, a swashplate, and a plunger ball joint. The aforementioned lubrication state parameters can be quantitative indicators used to characterize the oil film lubrication condition of the slipper pair, such as the oil film thickness distribution between the slipper and the swashplate, the oil film pressure distribution, the slipper's tilt angle, and the oil film stiffness.

[0044] In the specific implementation, the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model are coupled and solved with the multi-degree-of-freedom dynamic equations of the slipper. Oil film force and oil film torque are obtained from the rough surface hydrodynamic lubrication model, and contact friction force and contact friction torque are obtained from the fluid-structure interaction contact friction model. Then, these forces and torques are substituted into the multi-degree-of-freedom dynamic equations of the slipper, forming a nonlinear equation system containing multiple unknown variables. Subsequently, a numerical iterative method is used to solve this nonlinear equation system to obtain the lubrication state parameters of the slipper pair.

[0045] For ease of understanding, the following example is used for explanation, but it does not impose specific limitations on this embodiment. For example, the slipper pair of an axial piston pump operates at a rated speed of 1500 rpm and a working pressure of 35 MPa. The oil film bearing capacity of 5000 N and the oil film torque of 2 Nm calculated by the rough surface hydrodynamic lubrication model, and the contact friction force of 200 N and the friction torque of 0.5 Nm calculated by the fluid-structure interaction contact friction model, are substituted into the dynamic equations of the slipper along the vertical direction and around the two swing directions, respectively. The Newton-Raphson iterative method is used to solve this nonlinear equation system. After 15 iterations, it converges, and the lubrication state parameters are obtained: the oil film thickness at the center point of the slipper is 3.2 micrometers, the slipper swing angle around the first direction is 0.05 degrees, and the swing angle around the second direction is 0.03 degrees.

[0046] Step S40: Suppress lubrication failure of the slipper pair based on the lubrication state parameters.

[0047] It should be explained that the aforementioned lubrication failure can refer to the phenomenon where the slipper pair, due to oil film rupture or insufficient oil film thickness, leads to direct contact between the slipper and the swashplate surface, resulting in increased friction and wear, abnormal temperature rise, or even burnout. The aforementioned lubrication failure suppression can refer to the process of preventing or mitigating lubrication failure by adjusting the operating or structural parameters of the slipper pair.

[0048] In the specific implementation, lubrication failure suppression is performed on the slipper pair based on the obtained lubrication state parameters. The lubrication state parameters are compared with a pre-set failure threshold to determine whether the current lubrication state is within a safe range. When the lubrication state parameters indicate a risk of lubrication failure, a corresponding failure suppression command is generated, and lubrication failure suppression operations are executed according to the failure suppression command.

[0049] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, the calculated minimum oil film thickness of the current slipper pair is 1.5 micrometers, while the preset failure threshold is that a lubrication failure warning is triggered when the minimum oil film thickness falls below 2 micrometers. If it is determined that the current oil film thickness has exceeded the failure threshold, indicating a risk of lubrication failure, a failure suppression command is generated to reduce the rotational speed or increase the oil supply pressure. This command is then transmitted to the controller of the axial piston pump, which executes the corresponding adjustment operation to restore the oil film thickness to a safe range.

[0050] This embodiment first acquires the microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump, and then obtains a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data. Next, it acquires the contact characteristic data of the joint surface between the inner slipper and the piston ball joint, and obtains a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. Then, it solves the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain the lubrication state parameters of the slipper pair. Finally, it suppresses lubrication failure of the slipper pair based on the lubrication state parameters. Compared with existing methods, this embodiment achieves quantitative assessment and active suppression of slipper pair lubrication failure by coupling microscopic roughness morphology and multi-degree-of-freedom dynamics.

[0051] Based on the first embodiment of this application, the content that is the same as or similar to that in the first embodiment described above can be referred to the above description and will not be repeated hereafter. On this basis, a second embodiment of the lubrication failure suppression method of this application is proposed; please refer to... Figure 2 , Figure 2 This is a schematic flowchart illustrating Embodiment 2 of the lubrication failure suppression method of this application. To obtain a rough surface hydrodynamic lubrication model of the mating surfaces, such as... Figure 2 As shown, in this embodiment, the step of obtaining the rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data includes: Step S101: Perform power spectrum analysis on the micro-morphology data to obtain the power spectrum parameters of the surface profile of the mating surface.

[0052] It should be explained that the power spectrum analysis mentioned above can refer to a statistical method that converts the spatial domain signal of a surface profile into a frequency domain signal and analyzes the energy distribution of different spatial frequency components. The surface profile mentioned above can refer to the microscopic undulations of the mating surface in a certain direction, usually represented by a curve showing the change in height with position. The power spectrum parameters mentioned above can refer to quantitative indicators describing the power spectrum characteristics of the surface profile, such as the power values ​​corresponding to different spatial frequencies, the distribution shape of the power spectrum, spectral moments, and other statistical quantities.

[0053] In the specific implementation, power spectrum analysis is performed on the microscopic morphology data of the mating surface to obtain the power spectrum parameters of the surface profile. The collected microscopic morphology data is treated as a spatial domain signal, and the height information of the surface profile is converted into frequency domain information through Fourier transform. Next, the power values ​​corresponding to different spatial frequencies are calculated to obtain the power spectral density function. Subsequently, power spectrum parameters are extracted from the power spectral density function to characterize the statistical features of the surface profile.

[0054] To facilitate understanding, the following example is used for explanation, but it does not impose specific limitations on this embodiment. For example, surface profile sampling data of the bottom of a skateboard with a length of 5 mm is obtained, with sampling point intervals of 1 micrometer. A Fast Fourier Transform is performed on 5000 discrete height values ​​to obtain a power spectral density curve with a spatial frequency range of 0.2 cycles per millimeter to 500 cycles per millimeter. From this curve, power spectral parameters with a root mean square height of 0.35 micrometers, a correlation length of 50 micrometers, and spectral moments m0 of 0.12 square micrometers, m2 of 0.05, and m4 of 0.02 are extracted.

[0055] Step S102: Generate the Reynolds equation for the mating surface in cylindrical coordinates based on the power spectrum parameters.

[0056] It should be explained that the cylindrical coordinate system mentioned above refers to a coordinate system established with the axis of the cylinder as a reference. It typically consists of three coordinate variables: radial, circumferential, and axial, and is suitable for describing the physical field distribution of circular or annular regions. The Reynolds equation mentioned above refers to a partial differential equation describing the distribution of lubricating oil film pressure. This equation reflects the quantitative relationship between oil film pressure and factors such as surface velocity, oil film thickness, and lubricating oil viscosity. The power spectral parameters mentioned above are used as input to determine the statistical terms in the Reynolds equation that characterize the surface roughness effect.

[0057] In the specific implementation, the Reynolds equation for the mating surface in cylindrical coordinates is generated based on the power spectrum parameters. The statistical characteristics of the surface microstructure represented by the power spectrum parameters are introduced into the classical Reynolds equation to correct the influence of rough surfaces on oil film flow. The Reynolds equation is converted from Cartesian coordinates to cylindrical coordinates to match the geometry of the circular mating surface of the slipper pair. A Reynolds equation including radial and circumferential coordinate variables is established in cylindrical coordinates, where the oil film thickness term incorporates the random roughness statistics described by the power spectrum parameters.

[0058] For ease of understanding, the following explanation uses examples, but does not impose specific limitations on this embodiment. For example, the obtained power spectrum parameters include a root mean square height of 0.35 micrometers and a correlation length of 50 micrometers. Substituting the above parameters into the Reynolds equation in cylindrical coordinates, the generated Reynolds equation takes the form: In the radial coordinate r and circumferential coordinate θ directions, the oil film pressure p satisfies a partial differential equation containing a statistical expectation term for surface roughness. The left side of the equation is the pressure gradient term, and the right side includes a shear flow term and a squeeze flow term generated by the relative motion between the slipper and the swashplate. The oil film thickness h is formed by the superposition of the nominal oil film thickness h0 and the random roughness component h_r, and the statistical characteristics of h_r are determined by the power spectrum parameters.

[0059] Step S103: Obtain the hydrodynamic lubrication model of the rough surface based on the Reynolds equation.

[0060] It should be explained that the above-mentioned rough surface hydrodynamic lubrication model can refer to a mathematical model used to describe the lubrication characteristics such as oil film pressure distribution, load-bearing capacity and torque between two relatively moving surfaces with random micromorphology. This model uses the Reynolds equation as the core governing equation and includes the statistical characteristics of surface roughness as input parameters.

[0061] In the specific implementation, a hydrodynamic lubrication model for rough surfaces is obtained based on the Reynolds equation. The generated Reynolds equation in cylindrical coordinates is used as the core governing equation for the hydrodynamic lubrication model of rough surfaces. Based on the Reynolds equation, and combined with the flow continuity condition and boundary conditions, a complete mathematical model is established that can solve for oil film pressure distribution, bearing capacity, and torque.

[0062] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, using the Reynolds equation in cylindrical coordinates, which includes power spectrum parameters, as the core, and combining it with given boundary conditions such as a nominal oil film thickness of 3 micrometers, a slipper tilt angle of 0.05 degrees, a lubricating oil viscosity of 0.02 Pa·s, and an inlet oil pressure of 35 MPa, a complete hydrodynamic lubrication model for rough surfaces is constructed. This model can calculate the pressure value at any position on the bottom surface of the slipper, and obtain the total bearing capacity and the overturning moment in two directions by integrating the pressure distribution.

[0063] Furthermore, in order to obtain the fluid-structure interaction contact friction model of the mating surface, in this embodiment, the step of obtaining the fluid-structure interaction contact friction model of the mating surface based on the contact characteristic data includes: Step S201: Obtain the roughness peak statistical distribution parameters of the mating surface based on the contact characteristic data.

[0064] It should be explained that the aforementioned rough peaks can refer to the microstructures protruding on the mating surface, typically appearing as highly randomly distributed tiny protrusions. The aforementioned statistical distribution parameters can be quantitative indicators that statistically describe the geometric characteristics of the rough peaks, such as the height distribution function of the rough peaks, radius of curvature, surface density (i.e., the number of rough peaks per unit area), and root mean square value of the rough peak height.

[0065] In practical implementation, statistical distribution parameters of the roughness peaks on the mating surface are obtained based on contact characteristic data. Statistical features describing the geometry of the roughness peaks are extracted or calculated from the contact characteristic data. Statistical methods can be used to analyze the three-dimensional morphology data of the mating surface, identifying local maxima to determine the position and height of each roughness peak, and then calculating parameters such as the average height, root mean square value, radius of curvature, and distribution density of all roughness peaks.

[0066] To facilitate understanding, the following example is used for explanation, but it does not impose specific limitations on this embodiment. For example, the obtained contact characteristic data is a three-dimensional topographic data of a 1 square millimeter area on the inner surface of the skate shoe's ball socket, containing height information of 1 million discrete points. The algorithm identifies 500 rough peaks in this area whose height exceeds the neighborhood average, and calculates the average height of these rough peaks as 0.6 micrometers, the root mean square value of height as 0.2 micrometers, the average radius of curvature as 0.08 millimeters, and the surface density as 500 peaks per square millimeter, which are used as statistical distribution parameters for the rough peaks.

[0067] Step S202: Using Greenwood-Williamson contact theory, generate a model of the relationship between the normal contact force of the rough peak and the actual contact area based on the statistical distribution parameters of the rough peak.

[0068] It should be explained that the Greenwood-Williamson contact theory described above can be a statistical theory used to describe the contact behavior between two rough surfaces. This theory equates a rough surface to a series of hemispherical rough peaks with the same radius of curvature and highly conforming to a specific statistical distribution, and obtains the mechanical response of the entire contact surface by superimposing the Hertzian contact models of individual rough peaks. The normal contact force mentioned above can refer to the force perpendicular to the contact surface direction, generated by the deformation of the rough peaks when the two surfaces are pressed together. The actual contact area mentioned above can refer to the sum of the areas actually occupied by the contact deformation regions of the rough peaks. Due to the microscopic unevenness of the surface, the actual contact area is usually much smaller than the nominal contact area. The relationship model mentioned above can refer to a function or equation describing the mathematical relationship between the normal contact force and the actual contact area.

[0069] In the specific implementation, the Greenwood-Williamson contact theory is used to generate a model relating the normal contact force of a rough peak to its actual contact area based on the statistical distribution parameters of the rough peaks. The mating surface is equivalent to a series of spherical rough peaks with the same radius of curvature, and the height of the rough peaks follows a probability distribution described by the statistical distribution parameters. Based on Hertzian contact theory, a calculation expression for the contact area and normal contact force of a single rough peak at a given indentation depth is established. Subsequently, the contact area and normal contact force of a single rough peak are integrated over its height distribution to obtain the functional relationship between the total normal contact force and the total actual contact area on the entire mating surface.

[0070] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, the obtained rough peak statistical distribution parameters include an areal density of 500 peaks per square millimeter, an average radius of curvature of 0.08 millimeters, and a rough peak height following a Gaussian distribution with a mean of 0.5 micrometers and a root mean square value of 0.2 micrometers. A relationship model is established based on the Greenwood-Williamson theory: when the normal contact force is 1000 Newtons, the actual contact area is 0.5 square millimeters; when the normal contact force increases to 2000 Newtons, the actual contact area increases to 0.8 square millimeters. The two exhibit a non-linear relationship, with the contact area increasing with the increase of the normal contact force, but the rate of increase gradually slows down.

[0071] Step S203: Couple the hydrostatic bearing effect of high-pressure oil in the relationship model to obtain the fluid-structure interaction contact friction model.

[0072] It should be explained that the aforementioned hydrostatic bearing effect refers to the phenomenon where the fluid pressure generated by high-pressure oil in the gap between the mating surfaces provides support to the mating surfaces. This effect causes part of the external load to be borne by the fluid pressure rather than entirely by the rough peak contact. The aforementioned fluid-structure interaction contact friction model can be a comprehensive mathematical model that simultaneously considers the mechanical behavior of solid rough peak contact and the fluid pressure bearing effect. This model can describe the total bearing capacity, frictional force, and the distribution relationship between the two of the mating surfaces under the combined action of normal load and tangential sliding.

[0073] In practical implementation, the hydrostatic bearing effect of high-pressure oil is coupled into the relational model to obtain a fluid-structure interaction contact friction model. Based on the established relationship model between the normal contact force of the rough peak and the actual contact area, the fluid pressure distribution generated by the high-pressure oil in the joint surface gap is introduced. By solving the fluid flow equation within the joint surface gap, the distribution of the fluid pressure field is obtained. Subsequently, the bearing capacity generated by the fluid pressure and the bearing capacity generated by the contact with the solid rough peak are superimposed to obtain the expression for the total bearing capacity of the joint surface. Simultaneously, considering the fluid viscous shear force and the sliding friction force of the rough peak, a calculation expression for the total friction force is established, ultimately forming a fluid-structure interaction contact friction model that can simultaneously describe both fluid bearing and solid contact bearing.

[0074] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, the established rough peak contact relationship model shows that under a normal load of 2000 Newtons, the rough peak contact bears a load of 1500 Newtons, with a real contact area of ​​0.8 square millimeters. Further calculations show that the hydrostatic bearing capacity generated by the 40 MPa high-pressure oil in the joint gap is 800 Newtons. Superimposing these two values ​​yields a total bearing capacity of 2300 Newtons at the joint surface, of which fluid bearing accounts for approximately 35% and solid contact bearing accounts for approximately 65%. Simultaneously, the fluid viscous shear force is calculated to be 50 Newtons, and the rough peak sliding friction force is calculated to be 120 Newtons, resulting in a total friction force of 170 Newtons. This ultimately forms a fluid-structure interaction contact friction model that includes load distribution and friction characteristics.

[0075] Based on the first and / or second embodiments of this application, in the third embodiment of this application, the content that is the same as or similar to that in embodiments one and two above can be referred to the above description, and will not be repeated hereafter. Based on this, please refer to... Figure 3 , Figure 3 This is a schematic flowchart of Embodiment 3 of the lubrication failure suppression method of this application. To solve the multi-degree-of-freedom dynamic equations, such as... Figure 3 As shown, in this embodiment, the step of solving the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model, along with the multi-degree-of-freedom dynamic equations of the slipper, includes: Step S301: Substitute the oil film force and oil film torque output by the rough surface hydrodynamic lubrication model, and the contact friction force and contact friction torque output by the fluid-structure interaction contact friction model, into the multi-degree-of-freedom dynamic equation.

[0076] It should be explained that the aforementioned oil film force can refer to the total normal support force generated by the lubricating oil film on the bottom surface of the slipper, calculated by the rough surface hydrodynamic lubrication model. The aforementioned oil film torque can refer to the overturning moment generated on the center of the slipper's ball joint when the aforementioned oil film force distribution is uneven. The aforementioned contact friction force can refer to the tangential resistance generated on the mating surface between the slipper and the plunger ball joint, calculated by the fluid-structure interaction contact friction model. The aforementioned contact friction torque can refer to the torque generated on the center of the slipper's ball joint by the aforementioned contact friction force. The aforementioned multi-degree-of-freedom dynamic equations can refer to mathematical expressions establishing the force and torque balance relationships in multiple degrees of freedom directions for the slipper, taking it as the research object. These typically include equations of linear motion perpendicular to the swashplate direction and rotational equations about two orthogonal oscillation axes.

[0077] In practical implementation, the oil film force and oil film torque output from the rough surface hydrodynamic lubrication model, and the contact friction force and contact friction torque output from the fluid-structure interaction contact friction model, are substituted into the multi-degree-of-freedom dynamic equations. Specific numerical values ​​or expressions for the oil film force and oil film torque are extracted from the calculation results of the rough surface hydrodynamic lubrication model. Similarly, specific numerical values ​​or expressions for the contact friction force and contact friction torque are extracted from the calculation results of the fluid-structure interaction contact friction model. Subsequently, these forces and torques are substituted into the corresponding force and torque terms in the multi-degree-of-freedom dynamic equations. The oil film force and contact friction force are substituted into the vertical force balance equations, and the oil film torque and contact friction torque are substituted into the torque balance equations in the two oscillating directions, forming a closed set of dynamic equations.

[0078] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, from the rough surface hydrodynamic lubrication model, the oil film force is extracted as 5200 Newtons, and the oil film torques are 1.8 Nm around the X-axis and 1.2 Nm around the Y-axis. From the fluid-structure interaction contact friction model, the contact friction force is extracted as 150 Newtons, and the contact friction torques are 0.4 Nm around the X-axis and 0.3 Nm around the Y-axis. Substituting the oil film force of 5200 Newtons and the contact friction force of 150 Newtons into the resultant force term in the vertical force balance equation, and substituting the oil film torque and contact friction torque into the torque balance equations around the X-axis (1.8 + 0.4 = 2.2 Nm) and around the Y-axis (1.2 + 0.3 = 1.5 Nm), the values ​​of all external force and torque terms in the multi-degree-of-freedom dynamic equations are completed.

[0079] Step S302: Combine the multi-degree-of-freedom dynamic equation with the flow balance equation to obtain a set of nonlinear equations, wherein the flow balance equation is an equation describing the balance relationship between the flow rate through the damping groove of the slipper and the oil film leakage flow rate.

[0080] It should be explained that the aforementioned flow balance equation can refer to a mathematical equation describing the equal relationship between the oil flow rate entering the slipper and the oil flow rate exiting the slipper. The aforementioned damping groove can refer to a throttling channel installed on the bottom surface of the slipper, through which oil enters the oil film gap between the slipper and the swashplate. The aforementioned oil film leakage flow rate can refer to the flow rate of oil leaking outward from the edge of the oil film gap between the slipper and the swashplate.

[0081] In practical implementation, the multi-degree-of-freedom dynamic equations are combined with the flow balance equations to obtain a nonlinear equation set. The multi-degree-of-freedom dynamic equations, which already incorporate oil film force, oil film torque, contact friction force, and contact friction torque, are placed side-by-side with the flow balance equations to form an equation set containing multiple unknown variables. The vertical displacement of the slipper, the two swing angles, and the oil chamber pressure are treated as common unknowns, allowing the dynamic equations and flow balance equations to share the same set of unknown variables. These multiple equations are then combined into a unified whole, forming a coupled nonlinear equation set, where the dynamic equations describe the mechanical equilibrium state of the slipper, and the flow balance equations describe the continuity of oil flow.

[0082] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For instance, the established multi-degree-of-freedom dynamic equations include unknown quantities such as the oil film thickness h0 at the center point of the slipper, the swing angle α around the X-axis, and the swing angle β around the Y-axis. The established flow balance equations include unknown quantities such as the oil chamber pressure p and the oil film thickness distribution h (determined by h0, α, and β). Combining the dynamic equations and the flow balance equations yields a nonlinear equation system containing four unknown quantities: h0, α, β, and p. The dynamic equations provide three equations (one vertical force balance equation and two moment balance equations), and the flow balance equation provides one equation. The equation system is closed and solvable.

[0083] Step S303: Iteratively solve the nonlinear equations to obtain the lubrication state parameters of the slipper pair.

[0084] It should be explained that the iterative solution mentioned above can refer to a numerical method for solving a system of nonlinear equations by successive approximation. Each iteration calculates a new solution based on the current solution, until the change in the solution is less than a preset convergence threshold. The lubrication state parameters mentioned above can be quantitative indicators used to characterize the lubrication condition of the slipper pair, such as the oil film thickness distribution between the slipper and the swashplate, the slipper's tilt angle, the oil film pressure distribution, and the oil film stiffness.

[0085] In the specific implementation, the nonlinear equation system is iteratively solved to obtain the lubrication state parameters of the slipper pair. Initial values ​​are assigned to the unknown variables in the nonlinear equation system. The residuals of each equation in the equation system are calculated based on the current values ​​of the unknown variables. The correction amount of the unknown variables is calculated based on the residual values, and the values ​​of the unknown variables are updated. The residual calculation and variable update operations are repeated until the residual value is less than a preset convergence threshold or the number of iterations reaches a preset upper limit. After the solution converges, the lubrication state parameters of the slipper pair are extracted from the final solution, including oil film thickness distribution, slipper swing angle, oil film pressure distribution, etc.

[0086] To facilitate understanding, the following example is used for explanation, but it does not impose specific limitations on this embodiment. For example, the initial value of the oil film thickness at the center point of the slipper is set to 10 micrometers, the initial value of the swing angle around the X-axis is set to 0 degrees, the initial value of the swing angle around the Y-axis is set to 0 degrees, and the initial value of the oil chamber pressure is set to 35 MPa. The Newton-Raphson iterative method is used for solving the problem. After the first iteration, the oil film thickness is corrected to 6 micrometers; after the second iteration, it is corrected to 3.5 micrometers; after the third iteration, it is corrected to 3.2 micrometers; and after the fourth iteration, it is corrected to 3.18 micrometers. The change between two iterations is less than 0.01 micrometers, reaching the convergence condition. From the final solution, the lubrication state parameters are obtained as follows: the oil film thickness at the center point of the slipper is 3.18 micrometers, the swing angle around the X-axis is 0.05 degrees, the swing angle around the Y-axis is 0.03 degrees, the oil film pressure drops to ambient pressure (0.1 MPa) at the edge of the slipper, and the minimum oil film thickness occurs at the high-pressure side edge of the slipper at 2.5 micrometers.

[0087] Furthermore, in order to suppress lubrication failure of the slipper pair, in this embodiment, the step of suppressing lubrication failure of the slipper pair based on the lubrication state parameters includes: Step S401: Compare the lubrication state parameters with a preset failure threshold.

[0088] It should be explained that the aforementioned failure thresholds can refer to critical values ​​used to determine whether lubrication failure of the slipper pair is imminent or has already occurred, such as the minimum oil film thickness threshold, the maximum oil film pressure fluctuation threshold, and the maximum slipper swing angle threshold. The aforementioned comparison can refer to comparing the calculated values ​​of the lubrication state parameters with the preset failure thresholds in terms of magnitude or range to determine whether the lubrication state parameters are within a safe range.

[0089] In the specific implementation, lubrication state parameters are compared with preset failure thresholds. One or more key indicators are extracted from the lubrication state parameters, such as minimum oil film thickness, maximum oil film pressure, and maximum slipper swing angle. Failure thresholds, which can be a single value or a range of values, are read from the pre-stored internal memory. The value of each key indicator is compared one by one with the corresponding failure threshold to determine whether the lubrication state parameters exceed the safe range defined by the failure threshold.

[0090] To facilitate understanding, the following examples are provided for illustration, but they do not impose specific limitations on this embodiment. For example, the minimum oil film thickness is 1.8 micrometers, and the maximum swing angle of the slipper is 0.12 degrees. Preset failure thresholds are read: the minimum oil film thickness threshold is 2.0 micrometers, and the maximum swing angle threshold is 0.15 degrees. Comparing 1.8 micrometers with 2.0 micrometers, it is determined that the minimum oil film thickness is below the failure threshold; comparing 0.12 degrees with 0.15 degrees, it is determined that the maximum swing angle of the slipper does not exceed the failure threshold.

[0091] Step S402: When the lubrication state parameter exceeds the failure threshold, a failure suppression command is generated, and lubrication failure is suppressed for the slipper pair according to the failure suppression command.

[0092] It should be explained that the aforementioned failure suppression command can refer to an electronic command used to trigger lubrication failure suppression operations. This command includes the type of suppression operation to be performed and the corresponding operating parameters. The aforementioned lubrication failure suppression of the slipper pair according to the failure suppression command can refer to executing the operations specified in the failure suppression command, improving the lubrication state of the slipper pair by adjusting operating parameters, such as reducing the axial piston pump speed, increasing the oil supply pressure, adjusting the swashplate angle, or issuing an alarm signal.

[0093] In practical implementation, a failure suppression command is generated when the lubrication status parameters exceed the failure threshold, and lubrication failure is suppressed for the slipper pair according to the failure suppression command. The comparison result determines whether the lubrication status parameters exceed the failure threshold. If the result indicates that the failure threshold has been exceeded, a failure suppression command is generated, containing suppression operation information for the current lubrication failure risk. The failure suppression command is sent to the actuator or operator's terminal, and the actuator performs the corresponding suppression operation according to the failure suppression command.

[0094] For ease of understanding, the following explanation uses examples, but does not limit the scope of this embodiment. For instance, if the minimum oil film thickness of 1.8 micrometers is determined to be below the failure threshold of 2.0 micrometers, indicating a risk of lubrication failure, a failure suppression command containing the instruction to "increase the oil supply pressure to 45 MPa" is generated and transmitted to the controller of the axial piston pump. In response to the received failure suppression command, the controller gradually increases the oil supply pressure from the current 35 MPa to 45 MPa, thereby increasing the oil film thickness to 2.3 micrometers, restoring it above the safety threshold, and completing the lubrication failure suppression operation.

[0095] Furthermore, in order to obtain microscopic morphology data, in this embodiment, the step of obtaining the microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump includes: Step S104: Collect three-dimensional topographic point cloud data of the bottom surface of the skid and the surface of the swashplate.

[0096] Step S105: Filter the three-dimensional topographic point cloud data to obtain the micro-topographic data of the mating surface between the slipper and the inclined plate.

[0097] It should be explained that the aforementioned three-dimensional topographic point cloud data can refer to a set of discrete point coordinates on the surface of an object obtained through measuring instruments. Each point contains its lateral position, longitudinal position, and height information in space. The aforementioned filtering process can refer to mathematical transformations or data filtering operations performed on the three-dimensional topographic point cloud data to remove measurement noise, outliers, or unwanted frequency components, while retaining effective information that accurately reflects the surface's micro-geometry.

[0098] In the specific implementation, three-dimensional topographic point cloud data of the bottom surface of the skate and the surface of the swashplate are acquired. A surface profilometer or a three-dimensional optical profilometer is used to scan and measure the bottom surface of the skate and the surface of the swashplate, obtaining high-density three-dimensional topographic point cloud data covering the entire mating surface area. Subsequently, the three-dimensional topographic point cloud data is filtered to obtain the microscopic topographic data of the mating surface between the skate and the swashplate. A filtering algorithm is used to remove high-frequency noise components and outliers from the point cloud data, while retaining effective signals reflecting the surface micro-roughness characteristics. The filtered data is then output as the microscopic topographic data of the mating surface.

[0099] To facilitate understanding, the following example is used for illustration, but it does not impose specific limitations on this embodiment. For instance, a white light interferometer is used to scan the bottom surface of the skate, with the measurement area being a circular region with a diameter of 30 mm and a scanning step size of 5 micrometers. Approximately 28 million discrete points are collected, each containing planar coordinates and height values. This point cloud data is processed using a Gaussian filter with a cutoff wavelength of 50 micrometers to filter out measurement noise components with wavelengths less than 20 micrometers, while retaining surface ripple features in the wavelength range of 20 to 50 micrometers. The filtered data is used as the microscopic morphology data of the mating surface between the skate and the swashplate, and this data is used for subsequent power spectrum analysis.

[0100] This application also provides a lubrication failure suppression device, please refer to... Figure 4 The device includes: The first acquisition module 10 is used to acquire the micro-morphological data of the mating surface between the inner slipper and the swashplate of the axial piston pump, and to obtain the rough surface hydrodynamic lubrication model of the mating surface based on the micro-morphological data. The second acquisition module 20 is used to acquire the contact characteristic data of the joint surface between the slipper and the piston ball joint in the axial piston pump, and to obtain the fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. The third acquisition module 30 is used to couple and solve the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equation of the slipper to obtain the lubrication state parameters of the slipper pair. The failure suppression module 40 is used to suppress lubrication failure of the slipper pair based on the lubrication state parameters.

[0101] The lubrication failure suppression device provided in this application, employing the lubrication failure suppression method in the above embodiments, can solve the technical problem of how to suppress lubrication failure of slipper pairs. Compared with the prior art, the beneficial effects of the lubrication failure suppression device provided in this application are the same as those of the lubrication failure suppression method provided in the above embodiments, and other technical features in the lubrication failure suppression device are the same as those disclosed in the methods of the above embodiments, and will not be repeated here.

[0102] This application provides a lubrication failure suppression device, which includes: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, which are executed by the at least one processor to enable the at least one processor to perform the lubrication failure suppression method in the above embodiment 1.

[0103] The following is for reference. Figure 5 The diagram illustrates a structural schematic suitable for implementing the lubrication failure suppression device in the embodiments of this application. The lubrication failure suppression device in the embodiments of this application may include, but is not limited to, mobile terminals such as mobile phones, laptops, digital broadcast receivers, PDAs (Personal Digital Assistants), PADs (Portable Application Description), PMPs (Portable Media Players), in-vehicle terminals (e.g., in-vehicle navigation terminals), and fixed terminals such as digital TVs and desktop computers. Figure 5 The lubrication failure suppression device shown is merely an example and should not impose any limitation on the functionality and scope of use of the embodiments of this application.

[0104] like Figure 5As shown, the lubrication failure suppression device may include a processing unit 1001 (e.g., a central processing unit, a graphics processing unit, etc.), which can perform various appropriate actions and processes according to a program stored in a read-only memory (ROM) 1002 or a program loaded from a storage device 1003 into a random access memory (RAM) 1004. The RAM 1004 also stores various programs and data required for the operation of the lubrication failure suppression device. The processing unit 1001, ROM 1002, and RAM 1004 are interconnected via a bus 1005. An input / output (I / O) interface 1006 is also connected to the bus. Typically, the following systems can be connected to the I / O interface 1006: input devices 1007 including, for example, a touchscreen, touchpad, keyboard, mouse, image sensor, microphone, accelerometer, gyroscope, etc.; output devices 1008 including, for example, a liquid crystal display (LCD), speaker, vibrator, etc.; storage devices 1003 including, for example, magnetic tape, hard disk, etc.; and communication devices 1009. The communication device 1009 allows the lubrication failure suppression device to communicate wirelessly or wiredly with other devices to exchange data. Although the figures show lubrication failure suppression devices with various systems, it should be understood that implementation or possession of all the systems shown is not required. More or fewer systems may be implemented alternatively.

[0105] Specifically, according to the embodiments disclosed in this application, the processes described above with reference to the flowcharts can be implemented as computer software programs. For example, embodiments disclosed in this application include a computer program product comprising a computer program carried on a computer-readable medium, the computer program containing program code for performing the methods shown in the flowcharts. In such embodiments, the computer program can be downloaded and installed from a network via a communication device, or installed from storage device 1003, or installed from ROM 1002. When the computer program is executed by processing device 1001, it performs the functions defined in the methods of the embodiments disclosed in this application.

[0106] The lubrication failure suppression device provided in this application, employing the lubrication failure suppression method in the above embodiments, can solve the technical problem of how to suppress lubrication failure of slipper pairs. Compared with the prior art, the beneficial effects of the lubrication failure suppression device provided in this application are the same as those of the lubrication failure suppression method provided in the above embodiments, and other technical features of the lubrication failure suppression device are the same as those disclosed in the method of the previous embodiment, and will not be repeated here.

[0107] It should be understood that the various parts disclosed in this application can be implemented using hardware, software, firmware, or a combination thereof. In the description of the above embodiments, specific features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0108] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

[0109] This application provides a computer-readable storage medium having computer-readable program instructions (i.e., a computer program) stored thereon, the computer-readable program instructions being used to perform the lubrication failure suppression method in the above embodiments.

[0110] The computer-readable storage medium provided in this application may be, for example, a USB flash drive, but is not limited to, electrical, magnetic, optical, electromagnetic, infrared, or semiconductor systems, devices, or any combination thereof. More specific examples of computer-readable storage media may include, but are not limited to: electrical connections having one or more wires, portable computer disks, hard disks, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable compact disk read-only memory (CD-ROM), optical storage devices, magnetic storage devices, or any suitable combination thereof. In this embodiment, the computer-readable storage medium may be any tangible medium containing or storing a program that can be used by or in conjunction with an instruction execution system, system, or device. The program code contained on the computer-readable storage medium may be transmitted using any suitable medium, including but not limited to: wires, optical cables, RF (Radio Frequency), etc., or any suitable combination thereof.

[0111] The aforementioned computer-readable storage medium may be included in the lubrication failure suppression device; or it may exist independently and not assembled into the lubrication failure suppression device.

[0112] The aforementioned computer-readable storage medium carries one or more programs. When these programs are executed by the lubrication failure suppression device, the lubrication failure suppression device: acquires microscopic morphology data of the mating surface between the slipper and the swashplate in the axial piston pump, and obtains a rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data; acquires contact characteristic data of the joint surface between the slipper and the piston ball joint in the axial piston pump, and obtains a fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data; solves the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equations of the slipper to obtain lubrication state parameters of the slipper pair; and suppresses lubrication failure of the slipper pair based on the lubrication state parameters.

[0113] Computer program code for performing the operations of this application can be written in one or more programming languages ​​or a combination thereof, including object-oriented programming languages ​​such as Java, Smalltalk, and C++, and conventional procedural programming languages ​​such as the "C" language or similar programming languages. The program code can be executed entirely on the user's computer, partially on the user's computer, as a standalone software package, partially on the user's computer and partially on a remote computer, or entirely on a remote computer or server. In cases involving remote computers, the remote computer can be connected to the user's computer via any type of network—including a Local Area Network (LAN) or a Wide Area Network (WAN)—or can be connected to an external computer (e.g., via the Internet using an Internet service provider).

[0114] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments of this application. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. It should also be noted that in some alternative implementations, the functions indicated in the blocks may occur in a different order than those indicated in the drawings. For example, two consecutively indicated blocks may actually be executed substantially in parallel, and they may sometimes be executed in reverse order, depending on the functions involved. It should also be noted that each block in the block diagrams and / or flowcharts, and combinations of blocks in the block diagrams and / or flowcharts, can be implemented using a dedicated hardware-based system that performs the specified function or operation, or using a combination of dedicated hardware and computer instructions.

[0115] The modules described in the embodiments of this application can be implemented in software or hardware. The names of the modules do not necessarily limit the functionality of the unit itself.

[0116] The readable storage medium provided in this application is a computer-readable storage medium that stores computer-readable program instructions (i.e., a computer program) for executing the above-described lubrication failure suppression method, thereby solving the technical problem of how to suppress lubrication failure of slipper pairs. Compared with the prior art, the beneficial effects of the computer-readable storage medium provided in this application are the same as those of the lubrication failure suppression method provided in the above embodiments, and will not be repeated here.

[0117] This application also provides a computer program product, including a computer program that, when executed by a processor, implements the steps of the lubrication failure suppression method described above.

[0118] The computer program product provided in this application can solve the technical problem of how to suppress lubrication failure of slipper pairs. Compared with the prior art, the beneficial effects of the computer program product provided in this application are the same as the beneficial effects of the lubrication failure suppression method provided in the above embodiments, and will not be repeated here.

[0119] The above description is only a part of the embodiments of this application and does not limit the patent scope of this application. All equivalent structural transformations made under the technical concept of this application and using the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included in the patent protection scope of this application.

Claims

1. A method for suppressing lubrication failure, characterized in that, The method is applied to a lubrication failure suppression device, which is connected to an axial piston pump, and the method includes: The microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump are obtained, and the rough surface hydrodynamic lubrication model of the mating surface is obtained based on the microscopic morphology data. The contact characteristic data of the mating surface between the slipper and the piston ball joint in the axial piston pump are obtained, and the fluid-structure interaction contact friction model of the mating surface is obtained based on the contact characteristic data. The rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model are solved together with the multi-degree-of-freedom dynamic equations of the slipper to obtain the lubrication state parameters of the slipper pair. Based on the lubrication state parameters, lubrication failure is suppressed in the slipper pair.

2. The method as described in claim 1, characterized in that, The step of obtaining the rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data includes: Power spectrum analysis was performed on the micro-morphology data to obtain the power spectrum parameters of the surface profile of the mating surface; Based on the power spectrum parameters, the Reynolds equation for the mating surface in cylindrical coordinates is generated; The hydrodynamic lubrication model for the rough surface is obtained based on the Reynolds equation.

3. The method as described in claim 1, characterized in that, The step of obtaining the fluid-structure interaction contact friction model of the mating surface based on the contact characteristic data includes: Based on the contact characteristic data, obtain the roughness peak statistical distribution parameters of the mating surface; Based on the Greenwood-Williamson contact theory, a model is generated to show the relationship between the normal contact force of the rough peak and the actual contact area, using the statistical distribution parameters of the rough peak. The hydrostatic bearing effect of high-pressure oil is coupled into the relationship model to obtain the fluid-structure interaction contact friction model.

4. The method as described in claim 1, characterized in that, The step of solving the rough surface hydrodynamic lubrication model, the fluid-structure interaction contact friction model, and the multi-degree-of-freedom dynamic equations of the slipper includes: Substitute the oil film force and oil film torque output by the rough surface hydrodynamic lubrication model, and the contact friction force and contact friction torque output by the fluid-structure interaction contact friction model, into the multi-degree-of-freedom dynamic equation; The multi-degree-of-freedom dynamic equations are combined with the flow balance equations to obtain a set of nonlinear equations, wherein the flow balance equations describe the balance between the flow rate through the damping groove of the slipper and the oil film leakage flow rate. The lubrication state parameters of the slipper pair are obtained by iteratively solving the nonlinear equations.

5. The method as described in claim 1, characterized in that, The step of suppressing lubrication failure of the slipper pair based on the lubrication state parameters includes: The lubrication state parameters are compared with a preset failure threshold. When the lubrication state parameter exceeds the failure threshold, a failure suppression command is generated, and lubrication failure is suppressed for the slipper pair according to the failure suppression command.

6. The method as described in claim 1, characterized in that, The step of obtaining the microstructure data of the mating surface between the inner slipper and the swashplate of the axial piston pump includes: Collect three-dimensional topographic point cloud data of the bottom surface of the skid and the surface of the swashplate; The three-dimensional topographic point cloud data is filtered to obtain the microscopic topographic data of the mating surface between the slipper and the inclined plate.

7. A lubrication failure suppression device, characterized in that, The device includes: The first acquisition module is used to acquire the microscopic morphology data of the mating surface between the inner slipper and the swashplate of the axial piston pump, and to obtain the rough surface hydrodynamic lubrication model of the mating surface based on the microscopic morphology data. The second acquisition module is used to acquire the contact characteristic data of the joint surface between the slipper and the piston ball joint in the axial piston pump, and to obtain the fluid-structure interaction contact friction model of the joint surface based on the contact characteristic data. The third acquisition module is used to couple and solve the rough surface hydrodynamic lubrication model and the fluid-structure interaction contact friction model with the multi-degree-of-freedom dynamic equation of the slipper to obtain the lubrication state parameters of the slipper pair. The failure suppression module is used to suppress lubrication failure of the slipper pair based on the lubrication state parameters.

8. A lubrication failure suppression device, characterized in that, The device includes: a memory, a processor, and a computer program stored in the memory and executable on the processor, the computer program being configured to implement the steps of the lubrication failure suppression method as described in any one of claims 1 to 6.

9. A storage medium, characterized in that, The storage medium is a computer-readable storage medium, and a computer program is stored on the storage medium. When the computer program is executed by a processor, it implements the steps of the lubrication failure suppression method as described in any one of claims 1 to 6.

10. A computer program product, characterized in that, The computer program product includes a computer program that, when executed by a processor, implements the steps of the lubrication failure suppression method as described in any one of claims 1 to 6.

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