Multi-parameter cooperative measurement method and system for hydrostatic bearing

Abstract

The invention relates to the technical field of bearing measurement, in particular to a multi-parameter collaborative measurement method and system for a hydrostatic bearing, and the method comprises the steps: dividing a contour boundary region and a sealing oil bearing region based on the geometric contour of a bearing oil cavity; selecting discrete calculation position points, and executing local rigidity component acquisition; integrating the rigidity components, constructing a pressure control equation set, and solving to obtain global pressure distribution of the sealing oil bearing area; performing flow dynamic calculation on each oil cavity to obtain three-way fluid output parameters; calculating a theoretical flow value of each oil cavity based on the global pressure distribution, performing deviation comparison with the total flow output by the three-way fluid, and controlling an iterative updating process of an oil supply pressure value; and according to the oil supply pressure value after iteration convergence, generating a bearing rigidity performance parameter and a flow parameter of each oil cavity system. According to the invention, the technical problem of inaccurate detection of thermal parameter dynamic coupling drift and structure inflection point flow field of the hydrostatic bearing in the existing hydrostatic bearing test is effectively solved.

Description

Technical Field

[0001] This invention relates to the field of bearing measurement technology, and in particular to a method and system for multi-parameter collaborative measurement of hydrostatic bearings. Background Technology

[0002] In the field of mechanical transmission, hydrostatic bearings, with their oil film support enabling contactless operation, have become core components of high-end equipment. During operation, the oil film stiffness and frictional thermal state directly affect the equipment's accuracy and lifespan; therefore, accurate measurement of these parameters is crucial for engineering safety control. Modern hydrostatic bearings utilize hydraulic oil chambers to construct a pressure-bearing oil film, monitoring the oil film pressure distribution through multi-point pressure sensors, and combining this with temperature sensors to create a thermo-coupling parameter system. This measurement method is relatively mature in theoretical research.

[0003] However, the existing technology system has fundamental limitations: First, under high-speed and heavy-load conditions, the oil film and metal contact interface undergo significant thermal deformation due to severe friction, resulting in the physical quantities measured by the pressure sensor being a mixed signal under thermo-mechanical coupling. Although the measurement scheme described in CN114894450B can quickly calculate stiffness parameters, it has not established a decoupling mechanism between thermal deformation and mechanical pressure, causing the measured parameters to deviate from the actual mechanical state. Second, the discontinuous flow field effect at structural inflection points such as the right-angle transition zone of the oil cavity, especially the eddies caused by boundary layer separation, makes it impossible for the local measurement values ​​of conventional point pressure sensors to characterize the actual flow state in this area. Although the high-order simulation model in publication CN113343462B can theoretically describe complex flow fields, it is difficult to obtain the real-time dynamic characteristics of micro-eddies in engineering measurements. The aforementioned defects constitute a systemic technical bottleneck: the interaction between thermal deformation and structural turbulence causes bidirectional distortion in the parameters obtained by existing measurement systems. These distortions fail to accurately reflect the true mechanical properties under thermo-mechanical coupling conditions and struggle to capture transient flow field characteristics at structural inflection points. This directly leads to frequent parameter drift and warning failures during engineering commissioning, severely restricting the accuracy of reliability assessments for high-end equipment.

[0004] The information disclosed in this background section is intended only to enhance the understanding of the general background of this disclosure and should not be construed as an admission or in any way implying that the information constitutes prior art known to those skilled in the art. Summary of the Invention

[0005] This invention provides a multi-parameter collaborative measurement method and system for hydrostatic bearings, which can effectively solve the problems in the background art.

[0006] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A multi-parameter coordinated measurement method for hydrostatic bearings, the method comprising: Based on the geometric contour of the bearing oil cavity, the oil cavity completely covered area, the contour boundary area, and the oil sealing and bearing area are divided. Select discrete calculation location points in the contour boundary region and the sealing oil bearing region, and perform local stiffness component acquisition at the discrete calculation location points; By integrating the stiffness components of each discrete calculation location point, a pressure control equation set including force balance relationship expression and pressure continuity constraint relationship is constructed. The oil supply pressure value of the oil cavity is initialized, and the global pressure distribution of the sealing oil bearing area is obtained by solving the pressure control equation set. For each oil chamber, dynamic calculations of axial and circumferential flow rates are performed to obtain triaxial fluid output parameters, including the oil output flow rate along the bearing axis, the output flow rate pointing to the adjacent oil chamber on the left side along the circumferential direction, and the output flow rate pointing to the adjacent oil chamber on the right side along the circumferential direction. The theoretical flow rate of each oil chamber is calculated based on the global pressure distribution. The deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid is compared. The iterative update process of the oil supply pressure value is controlled by setting flow balance conditions. Based on the oil supply pressure value after iterative convergence, differential calculation is performed to generate bearing stiffness performance parameters and flow parameters of each oil chamber system; wherein, the stiffness performance parameters include the composite stiffness characteristics of radial bearing components and axial bearing components, and the system flow parameters include the output flow characteristics of a single oil chamber and the circumferential coupling flow characteristics between oil chambers.

[0007] Furthermore, discrete calculation locations are selected within the contour boundary region and the sealing oil bearing region, including: Within the outline boundary area, multiple primary calculation points are set at equal intervals based on the distribution relationship between the axial sealing edge spacing value and the circumferential sealing edge spacing value. Within the oil sealing bearing area, a group of calculation points is set using a uniform grid density division strategy based on the axial coverage dimension and circumferential length parameters of the oil cavity. The distribution of the calculation point group covers the physical connection boundary between the oil cavity edge and the sealing edge.

[0008] Further, local stiffness component acquisition is performed at the discrete calculation location points, including: At each of the discrete calculation locations, a local oil film micro-element stiffness model is established, and a linear response relationship between bearing displacement and viscous resistance is generated based on the oil film thickness variation characteristics. Based on the principle of spatial continuity, and combined with the pressure gradient relationship between adjacent discrete calculation points, the linear response relationship is constrained and corrected, and dynamic stiffness components are output.

[0009] Furthermore, a system of pressure governing equations, including expressions for force balance relationships, is constructed, comprising: Iterate through the stiffness component values ​​of all the discrete calculation location points and synchronously connect the geometric contour parameters of the area completely covered by the oil cavity. For each discrete calculation location point, a force balance relationship expression is derived based on the oil film compression deformation, and a fluid viscous resistance term is embedded in the expression to form a complete mechanical response equation.

[0010] Furthermore, a set of pressure control equations, including pressure continuity constraints, is constructed, including: Based on the mechanical response equation, for the adjacent position points distributed on the same physical connection edge of the oil cavity among the discrete calculation position points, the distribution sequence of the adjacent position points in the bearing circumferential and axial directions is identified; Based on the distribution sequence, match the oil film pressure change gradient between adjacent locations to establish a local pressure continuity constraint relationship expression; The expression for the local pressure continuity constraint is embedded into the pressure control equation set to complete constraint integration.

[0011] Further, the deviation between the theoretical flow rate value and the sum of the flow rates output by the three-dimensional fluid is compared, including: Based on the conservation constraint principle of the fluid continuous motion equation, the absolute difference between the theoretical flow rate of each oil cavity and the sum of the three-dimensional fluid output flow rates is calculated. The absolute difference is correlated with the Reynolds pressure control equation to drive the iterative update process of the oil supply pressure value until the flow balance convergence condition is met to eliminate the deviation.

[0012] Furthermore, the iterative update process of the oil supply pressure value is driven until the flow balance convergence condition is met, including: Monitor the numerical change of the absolute difference during successive iteration steps; The critical rate of change threshold is determined based on the oil film viscosity characteristics parameters of the hydrostatic bearing; When the rate of change of the absolute difference is lower than the critical rate of change threshold, the flow balance condition is determined to be met and the iteration is terminated.

[0013] Furthermore, differential calculations are performed to generate bearing stiffness performance parameters and flow parameters for each oil chamber system, including: Spatial gradient decomposition is performed on the oil supply pressure values ​​after iterative convergence at all selected calculation locations in the oil sealing bearing area to generate a geometric superposition vector of the radial bearing component and the axial bearing component. The derivative of the geometric superposition vector with respect to the rate of change of bearing clearance is calculated to form the composite stiffness characteristic; The distribution characteristics of the circumferential flow rate of each oil cavity are statistically analyzed based on the real-time flow rate values ​​output from the three-dimensional fluid to characterize the interaction between the oil cavities.

[0014] A multi-parameter collaborative measurement system for hydrostatic bearings, the system comprising: The region division module, based on the geometric contour of the bearing oil cavity, divides the area completely covered by the oil cavity, the contour boundary area, and the oil sealing and bearing area. The stiffness acquisition module selects discrete calculation location points in the contour boundary region and the sealing oil bearing region, and performs local stiffness component acquisition at the discrete calculation location points. The equation solving module integrates the stiffness components of each discrete calculation location point, constructs a pressure control equation set including force balance relationship expressions and pressure continuity constraint relationships, initializes the oil chamber supply pressure value, and solves the pressure control equation set to obtain the global pressure distribution of the sealing oil bearing area; The output calculation module performs dynamic calculations of axial and circumferential flow rates for each oil chamber to obtain triaxial fluid output parameters; The iterative update module calculates the theoretical flow rate of each oil chamber based on the global pressure distribution, compares the deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid, and controls the iterative update process of the oil supply pressure value by setting flow balance conditions. The parameter calculation module performs differential calculations to generate bearing stiffness performance parameters and flow parameters of each oil chamber system based on the oil supply pressure value after iterative convergence.

[0015] Furthermore, the equation solving module includes: The geometric serial unit traverses the stiffness component values ​​of all the discrete calculation location points and synchronously serializes the geometric contour parameters of the oil cavity's completely covered area. The equation construction unit, for each of the discrete calculation locations, evolves a force balance relationship expression based on the oil film compression deformation, and embeds a fluid viscous resistance term into the expression to form a complete mechanical response equation.

[0016] The technical solution of this invention can achieve the following technical effects: By establishing a zoned measurement model for the oil cavity profile and a three-dimensional flow dynamic compensation mechanism, the technical problems of inaccurate detection of dynamic coupling drift of hydrostatic bearing thermodynamic parameters and flow field at structural inflection points in existing hydrostatic bearing tests are solved, thus realizing the engineering-based online calibration of bearing performance parameters.

[0017] The above description is only an overview of the technical solution of this application. In order to better understand the technical means of this application and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this application more obvious and understandable, the following are specific embodiments of this application. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A flowchart illustrating the multi-parameter collaborative measurement method for hydrostatic bearings; Figure 2 A flowchart illustrating the process of obtaining dynamic stiffness components; Figure 3 A logical diagram illustrating the flow balancing conditions; Figure 4 A flowchart illustrating the process for obtaining various parameters of a hydrostatic bearing. Detailed Implementation

[0020] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0021] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0022] Example 1; like Figure 1 As shown, this application provides a multi-parameter coordinated measurement method for hydrostatic bearings, the method including: Based on the geometric contour of the bearing oil cavity, the oil cavity completely covered area, the contour boundary area, and the oil sealing and bearing area are divided. Select discrete calculation locations within the contour boundary region and the sealing oil bearing region, and perform local stiffness component acquisition at the discrete calculation locations. By integrating the stiffness components of each discrete calculation location point, a pressure control equation set including force balance relationship expression and pressure continuity constraint relationship is constructed. The oil supply pressure value of the oil cavity is initialized, and the global pressure distribution of the sealing oil bearing area is obtained by solving the pressure control equation set. For each oil chamber, dynamic calculations of axial and circumferential flow rates are performed to obtain triaxial fluid output parameters, including the oil output flow rate along the bearing axis, the output flow rate pointing to the adjacent oil chamber on the left side along the circumferential direction, and the output flow rate pointing to the adjacent oil chamber on the right side along the circumferential direction. The theoretical flow rate of each oil chamber is calculated based on the global pressure distribution. The deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid is compared. The iterative update process of the oil supply pressure value is controlled by setting flow balance conditions. Based on the oil supply pressure value after iterative convergence, differential calculation is performed to generate bearing stiffness performance parameters and flow parameters of each oil chamber system. Among them, the stiffness performance parameters include the composite stiffness characteristics of the radial bearing component and the axial bearing component, and the system flow parameters include the output flow characteristics of a single oil chamber and the circumferential coupling flow characteristics between oil chambers.

[0023] Specifically, firstly, based on the geometric contour of the bearing oil cavity, the oil cavity region is divided using 3D modeling technology. This region is further subdivided into the fully covered area, the contour boundary area, and the oil-sealing load-bearing area. Several calculation points are selected based on the characteristics of each region. For example, when defining the oil-sealing load-bearing area, the stress concentration zone and flow coverage of the hydraulic oil under actual working conditions are fully considered. The effective area ratio for oil-sealing load-bearing is determined through experimental verification to ensure accurate coverage of the measured parameters. To further optimize the analysis within the selected area, multiple calculation points are evenly distributed within the contour boundary area to obtain the stiffness components along the boundary. Within the oil-sealing load-bearing area, calculation points are then calculated based on the stiffness components along the boundary. The pressure distribution exhibits a gradual decrease radiating from the center towards the regional boundary. Highly representative points are selected for stiffness component acquisition, preferably using a high-precision pressure acquisition device. Data is obtained by recording the pressure response in real time, providing support for subsequent pressure distribution derivation. Based on the stiffness component acquisition results at the selected calculation points, a pressure control equation set is established in conjunction with the pressure distribution pattern. The input values ​​of the equations dynamically change with the adjustment of the oil supply pressure. During the solution process, a step-by-step incremental iterative method is preferred to initialize the oil supply pressure. For example, starting with an initial value of 50 kPa, the pressure is gradually increased, with each increment refined into a controllable small increment, thus gradually approaching the true pressure in the analysis. To ensure the accuracy of the pressure distribution data, a dynamic weighting method was used to process the data during the solution process. This allowed the pressure distribution within the sealing oil bearing area to more closely approximate the actual state of hydraulic oil coverage. Through multiple rounds of data acquisition and solving of the pressure control equations, the pressure distribution characteristics of the sealing oil bearing area were finally obtained, laying the foundation for further analysis of bearing performance. Simultaneously, to verify the actual usability of the pressure distribution, three-dimensional fluid output measurements of the bearing were incorporated. Specifically, this included the oil output flow rate along the bearing axis, and the dynamic changes in the left and right flow rates pointing circumferentially towards adjacent oil chambers. These measurements were preferably collected using a three-way oil passage. The flow monitoring technology involves installing a fast-response, high-precision flow sensor in each oil delivery channel to record the flow rate changes over time and generate a standardized flow time-series curve. During data monitoring and acquisition, it was noted that there is a slight deviation between the theoretical flow rate and the output flow rate in the pressure distribution of the sealing oil bearing area. Therefore, the sum of the input and three-way output flow rate is dynamically and cyclically compared, and the deviation correction algorithm is used to continuously optimize and adjust the oil supply pressure until the flow system reaches a balanced state. Based on the flow balance, the final oil supply pressure value and flow dynamic data obtained not only characterize the state distribution in the oil cavity area, but also serve as an important basis for subsequent performance analysis.After obtaining the final oil supply pressure value and regional distribution, the bearing performance parameters and oil cavity flow characteristics are further calculated. Preferably, by integrating the pressure distribution in the sealing oil bearing area, stiffness parameters along different directions are extracted to demonstrate the bearing capacity under different load conditions. Furthermore, to analyze the impact of thermal effects on bearing performance, pressure distribution and flow data are combined to evaluate thermodynamic performance parameters, including temperature rise changes under thermal load and the resulting pressure gradient adjustments. Simultaneously, the output characteristics of a single oil cavity are summarized based on the flow characteristics of the entire oil cavity system. Through dynamic tracking of the flow coupling relationship between adjacent oil cavities, the interaction law of flow distribution between different regions is obtained. For example, during experimental verification, if the flow difference between the left and right adjacent cavities is directly affected by changes in oil supply pressure under small axial load conditions, the key interval where the coupling characteristics show a stable state can be observed and determined by adjusting the pressure step and gradient.

[0024] The technical solution of this invention establishes an oil cavity profile partitioning measurement model and a three-dimensional flow dynamic compensation mechanism, which solves the technical problems of inaccurate detection of dynamic coupling drift of hydrostatic bearing thermodynamic parameters and flow field at structural inflection points in existing hydrostatic bearing tests, and realizes the engineering-based online calibration of bearing performance parameters.

[0025] Furthermore, discrete calculation locations are selected within the contour boundary region and the sealing oil bearing area, including: Within the contour boundary area, multiple primary calculation points are set at equal intervals based on the distribution relationship between the axial sealing edge spacing value and the circumferential sealing edge spacing value. Within the oil sealing bearing area, the calculation point group is set according to the axial coverage dimension and circumferential length parameters of the oil cavity, using a uniform grid density division strategy. The distribution of the calculation point group covers the physical connection boundary between the oil cavity edge and the sealing edge.

[0026] As a preferred embodiment of the above, calculation point locations are first selected for the contour boundary region. Within this region, to ensure uniform coverage of point distribution, multiple primary calculation points are preferably set at equal intervals based on the geometric distribution relationship between the axial and circumferential sealing edge distances. In specific operation, the axial sealing edge distance can be accurately obtained through spatial modeling of the oil cavity, and the circumferential sealing edge distance is further confirmed based on the closed structural characteristics of the oil cavity along the circumference. In the preferred embodiment, taking an oil cavity with an axial sealing edge distance of 10mm and a circumferential sealing edge distance of 30mm as an example, a primary calculation point is set every 5mm according to the principle of uniform division, ultimately generating a total of 4 axial points and 6 circumferential points covering the entire contour boundary region. The positioning goal of these primary calculation points is to clearly show the boundary distribution law of pressure and stiffness, providing boundary condition reference for the subsequent design of point group division of the sealing bearing area. For the sealing bearing area, based on the axial coverage size and circumferential length parameters of the oil cavity, a uniform mesh density division strategy is adopted to set the calculation point group. In specific operation, a two-dimensional uniform mesh is established for the sealing bearing area using a mesh division tool, dividing the area into regular small Cells are used to determine discrete location points. In a preferred embodiment, based on an axial coverage size of 50mm and a circumferential length of 100mm for the oil cavity, a grid density of 5mm×5mm is set. That is, the region is divided into 10 rows and 20 columns along the axial and circumferential directions, respectively. Each grid node serves as a calculation location point, and a total of 200 point clusters are set for data measurement and analysis. The advantage of this division method is that it can ensure that the point clusters cover the region with equal density, and at the same time, it can refine the regional characteristics through the distribution of point clusters, achieving high-precision capture of fluid dynamic behavior; at the same time, in order to further completely cover the oil cavity... For the physical connection boundary between the edge and the sealing edge, it is preferable to set an additional point group density extension range for the transition part between the sealing edge and the region edge during the point group division process. The core of this operation is to make up for the insufficient point coverage in the edge transition area and avoid the failure to fully measure complex fluid behavior or pressure gradient changes. For example, in the same oil cavity, for the transition area between the sealing edge and the oil cavity boundary, it is preferable to set multiple sets of additional point density extension point groups, and set additional points with a distribution rate of about half that of the grid spacing. For example, based on a 5mm grid division, the point group spacing in the edge area is set to 2.The point distribution method was implemented with a 5mm margin, ensuring the accuracy of edge measurements by closely aligning the point clusters with the boundary line. To verify the effectiveness of this method, experimental tests were conducted. Using multiple bearing oil cavity structures as models, this point selection strategy was applied to select point clusters in both the contour boundary region and the sealing oil bearing region. Fluid stiffness and pressure data at each point were collected using pressure sensors and performance testing equipment. The test results showed that in the selected points in the contour boundary region, the pressure gradient distribution parameters of the sealing oil edge were successfully collected at each primary point along the circumference, and the circumferential pressure change gradient remained stable. In the selected point clusters in the sealing oil bearing region, the evenly spaced point clusters captured the radial gradual increase and circumferential viscosity distribution characteristics of the fluid pressure in this region. Simultaneously, the dense setting of the edge extension points effectively reflected the fluid pressure transition in the edge region. The final generated point cluster distribution data had an error of less than 2%, verifying the accuracy of the point setting method.

[0027] Furthermore, such as Figure 2 As shown, local stiffness component acquisition is performed at discrete calculation locations, including: At each discrete calculation location point, a local oil film micro-element stiffness model is established, and a linear response relationship between bearing displacement and viscous resistance is generated based on the oil film thickness variation characteristics. Based on the principle of spatial continuity, and combined with the pressure gradient relationship between adjacent discrete calculation points, the linear response relationship is constrained and corrected, and the dynamic stiffness component is output.

[0028] As a preferred embodiment of the above, a local oil film micro-element stiffness model is first established for each discrete calculation location. This model is based on the compressibility characteristics and stress response principle of liquids at the microscopic level and is used to measure the mechanical behavior characteristics of the local oil film under gradual compression conditions. In a preferred embodiment, real-time monitoring can be achieved by installing a set of high-precision pressure sensors and micro-displacement measuring instruments. The specific operation steps include: first, recording the initial value of the oil film thickness at the selected location point; then, gradually increasing the pressure input in a certain step, while simultaneously recording the change in oil film thickness in real time and capturing the corresponding load displacement change, and then analyzing the relationship between the local oil film compression deformation and the pressure input. For example, for a certain discrete... In the experiments at the location points, as the pressure gradually increased to 50 kPa, the oil film thickness decreased to 80% of its original value. At this point, the recorded displacement change showed a linear trend. By organizing the experimental data, the response relationship between the load displacement and viscous resistance was further defined within the model. The viscous resistance value reflects the frictional force of the fluid per unit area and is directly related to the displacement change. After establishing a local oil film micro-element stiffness model, the linear response relationship was further constrained and corrected based on the principle of spatial continuity and the pressure gradient relationship between adjacent discrete calculation location points. The key technical point of the principle of spatial continuity is to ensure that the dynamic pressure changes between adjacent location points maintain a physical continuity. To ensure the accuracy of the overall oil film dynamic characteristics measurement, the following steps are taken: First, pressure change data at adjacent locations are experimentally measured. Then, the dynamic distribution of the pressure gradient is analyzed using the fluid motion transmission law. It is found that the change behavior exhibits a certain linear law. Preferably, taking two axially adjacent typical locations as examples, their pressure values ​​are recorded as 30 kPa and 40 kPa respectively. By analyzing the pressure gradient difference and the distance between the two points, the pressure continuity constraint parameter is obtained. Based on this parameter, the linear response relationship in the local micro-element stiffness model is further corrected. The preliminary calculation results of bearing displacement and viscous resistance are adjusted to ensure the dynamic characteristics of this location and its neighboring points are consistent. The stiffness characteristics are closer to the actual fluid behavior. Finally, the dynamic stiffness components are output by combining the corrected linear response relationship. The optimal output process includes sorting the dynamic pressure response data of each discrete location point and the corrected linear relationship parameters. The comprehensive dynamic characteristics of the stiffness components of each location point as a function of pressure and displacement are obtained through dynamic numerical fitting. These dynamic stiffness components can not only reflect the oil film compression behavior of a single region, but also show regional interaction characteristics under the constraint of spatial continuity. For example, in the actual experiment, the dynamic stiffness component of a typical point in the oil sealing bearing area showed a linear change as the pressure gradually increased from 20 kPa to 50 kPa, and at the same time, it showed a stiffness saturation value when the pressure reached a stable value.

[0029] Furthermore, a system of pressure governing equations is constructed, including expressions for force balance relationships, comprising: Iterate through the stiffness component values ​​of all discrete calculation points and synchronously connect the geometric contour parameters of the area completely covered by the oil cavity. For each discrete calculation location, a force balance relationship expression is derived based on the oil film compression deformation, and a fluid viscous resistance term is embedded in the expression to form a complete mechanical response equation.

[0030] As a preferred embodiment, firstly, a traversal operation is performed on all discrete calculated location points within the oil-sealing bearing area and the contour boundary area to sequentially obtain stiffness component values. The core of this operation is to monitor the stiffness response characteristics of each location point in real time using high-precision sensing equipment, and combine this with the geometric contour parameters corresponding to the completely covered area of ​​the oil cavity to accurately embed the oil film mechanical properties into the global system. Specifically, within an oil cavity with a certain elliptical cross-section, the geometric contour parameters include axial coverage dimension, circumferential length, and edge curvature. In experimental measurements, the radial and tangential pressure changes at each location point are recorded using pressure sensors and strain testing equipment, respectively. These measurements are combined with edge curvature characteristics to establish a preliminary correlation between oil film compression and fluid pressure distribution. For example, in an oil cavity with an axial dimension of 50 mm and a circumferential length of 100 mm, 50 discrete calculation points are selected, and the stiffness value at each point is successively collected to form a continuous stiffness distribution table for the points. Next, for each discrete calculation point, a force balance expression is constructed based on the oil film's compression deformation and its load-bearing mechanical characteristics. In practice, the compression characteristics are first recorded based on the oil film thickness changes at the points. For example, under different pressure conditions, the changes in oil film thickness are measured step by step. This yields the law governing the change in oil film displacement with pressure. Taking the center of the sealing area as an example, the initial oil film thickness is 50 μm. As the pressure gradually increases from 20 kPa to 80 kPa, the oil film thickness gradually decreases to 40 μm. Simultaneously, the additional stiffness caused by compression deformation exhibits nonlinear characteristics, particularly sensitive to compression deformation during the initial pressure increase stage. Based on this characteristic, the load-bearing capacity component at each pressure stage is calculated, thus deriving a specific force balance expression. Furthermore, a fluid viscous resistance term is introduced into the force balance expression. Viscous resistance is closely related to oil film characteristics and fluid motion parameters, mainly manifested in… The contribution of fluid to shear stress changes under small changes in oil film thickness is now considered. In specific applications, the magnitude of viscous resistance is calculated by measuring the data values ​​of oil film thickness change and fluid velocity, combined with the viscosity calibration characteristics of the oil, and then embedded into the force balance expression with a correction coefficient. In the preferred experiment, the viscous resistance term at a selected location point accounts for 15% of the total resistance when the pressure reaches 60 kPa, and the proportion rises to 20% when the pressure is further increased to 100 kPa. The introduction of this mechanical synergy makes the expression closer to the actual fluid dynamics behavior in the oil cavity, providing the necessary physical support for forming a complete mechanical response equation.Through the above steps, force balance expressions for each discrete calculation point were constructed and the global geometric parameters of the oil cavity were connected. Finally, by sequentially connecting the mechanical response equations of these individual points according to their spatial distribution, a complete pressure control equation set was formed. The optimized equation set not only accurately describes the dynamic behavior of each point as a function of external pressure, but also achieves comprehensive pressure field equilibrium modeling at the overall oil cavity system scale. For example, in experimental verification, by constructing an equation set containing 200 discrete calculation points, pressure simulation was performed on the sealing oil bearing area of ​​a hydrostatic bearing. The results show that the pressure control equation set has a maximum error of less than 2% compared with the actual measurement results when simulating dynamic changes in oil film thickness, and the stability of system pressure distribution is significantly improved.

[0031] Furthermore, a set of pressure control equations, including pressure continuity constraints, is constructed, including: Based on the mechanical response equation, for the adjacent position points distributed on the same physical connection edge of the oil cavity in the discrete calculation position points, the distribution sequence of the adjacent position points in the bearing circumferential and axial directions is identified; Based on the distribution sequence, the gradient of oil film pressure change between adjacent locations is matched to establish a local pressure continuity constraint relationship expression; The expression for the local pressure continuity constraint is embedded into the pressure control equation set to complete constraint integration.

[0032] As a preferred embodiment of the above, firstly, in the preferred specific implementation process, the present invention, for the case where discrete calculation location points are distributed on the same physical connection edge of the oil cavity, sequentially identifies the axial and circumferential distribution sequences of these adjacent location points. Specifically, all discrete location points within the oil cavity are numbered, and their physical connection relationships are sorted out to locate the spatial distribution of adjacent points. For example, 50 discrete calculation location points are divided within the oil sealing and bearing area of ​​a certain oil cavity. The points are arranged according to a grid distribution rule, with each row containing 10 points along the axial direction, divided into 5 columns. At this time, any two consecutive points can establish a distribution sequence based on their axial adjacency relationship. At the same time, for consecutive points in the same column, their adjacency relationship can be defined along the circumferential direction. The basic number of this distribution sequence is... Determining the spatial relationship between all adjacent points is a necessary prerequisite for calculating the pressure change gradient. Next, based on the distribution sequence, the oil film pressure change gradient between adjacent points is matched to construct a local pressure continuity constraint expression. Specifically, under the operating conditions of the oil cavity, the pressure field of the oil film exhibits continuity with spatial variation; that is, the pressure gradient between any two adjacent points will not abruptly change. Therefore, it is preferable to measure the pressure difference between every two points, while considering the influence of fluid viscosity and flow velocity characteristics on pressure changes. The local continuity constraint relationship is defined in conjunction with the oil cavity size characteristics. For example, in the pressure record of adjacent points along a certain axis, the pressure at point 1 is 30 kPa, the pressure at point 2 is 35 kPa, and the distance between the two points is... With a pressure gradient of 5 kPa / mm between two points, based on parameters such as fluid viscosity, the continuity constraint expression, constructed by analyzing pressure change data between consecutive point pairs, can describe the oil film pressure change trend between the two points while ensuring the physical rationality of fluid dynamic behavior. To further verify the applicability of the constraint expression, a pressure dynamic simulation method was used to experimentally calibrate the gradient relationship. This verified that the pressure field can maintain continuous change under multi-point distribution conditions. For example, in a multi-point verification of a complex oil cavity sealing area, 100 adjacent point pairs were set in both the axial and circumferential directions. After applying the continuity expression to all point pairs, the maximum error of the overall pressure gradient was less than 2%, proving the local pressure continuity constraint relationship. It can accurately reflect the dynamic behavior of oil film pressure. Finally, the above-mentioned local pressure continuity constraint relationship expression is embedded into the pressure control equation set to complete the constraint integration. Through optimized processing, a unified constraint relationship expression rule is applied to the construction of pressure control equations for all discrete point pairs. That is, the continuity relationship between all points and the mechanical response relationship of the points themselves work together to form a complete pressure field model. For example, in a hydrostatic bearing experiment, by integrating constraint relationships, a unified pressure control equation set covering 200 discrete position points is finally generated. After using this equation set to dynamically simulate the bearing oil film thickness change process, it shows that the pressure prediction results match the actual measurement data by 98%, which significantly improves the model fitting accuracy.

[0033] Furthermore, the deviation between the theoretical flow rate and the sum of the flow rates output by the three-dimensional fluid is compared, including: Based on the conservation constraint principle of the fluid continuous motion equation, the absolute difference between the theoretical flow rate of each oil chamber and the sum of the three-dimensional fluid output flow rates is calculated. The absolute difference is correlated with the Reynolds pressure control equation to drive the iterative update process of the oil supply pressure value until the flow balance convergence condition is met to eliminate the deviation.

[0034] As a preferred embodiment of the above, the absolute difference between the theoretical flow rate of the hydraulic bearing oil cavity and the sum of the three-way fluid output flow rates is first obtained. Specifically, the theoretical flow rate is calculated based on the oil supply pressure, oil viscosity, and oil cavity geometric parameters, according to a model value preset by the bearing design parameters. The three-way fluid output includes the main path flow rate along the bearing axial direction, the cross flow rate pointing to the left side of the adjacent oil cavity along the circumferential direction, and the cross flow rate pointing to the right side along the circumferential direction. To accurately collect the real-time output flow rate, it is preferable to install high-precision flow sensors at each outlet of the oil cavity to record the actual flow rate value output in each direction and compare it with the actual flow rate value. The theoretical values ​​are compared. For example, in a certain oil chamber, the designed theoretical flow rate is 5 L / min, while the actual measured axial output flow rate is 3.2 L / min, the left crossflow is 1.3 L / min, the right crossflow is 0.4 L / min, and the total three-way flow rate is 4.9 L / min. The absolute difference is 0.1 L / min. This difference data is collected and analyzed uniformly across all oil chambers. Then, the absolute difference is used as a control variable and coordinated with the Reynolds pressure control equation to drive the iterative update of the oil supply pressure value. The core of the iterative update is to gradually adjust the oil supply pressure to make the system... The pressure and flow output tend towards the theoretical design state, thereby gradually reducing the deviation. In the optimal implementation, an initial oil supply pressure value is first set, and the pressure is gradually adjusted based on feedback from the absolute difference. For example, each pressure change is limited to a certain range to ensure stable fluid dynamic response. In the case experiment, the initial oil supply pressure was set to 120 kPa. Deviation energy function calculations showed that the energy value was too high. After adjusting the pressure to 125 kPa, the energy value decreased significantly. Further increasing it to 127 kPa resulted in a stable energy value controlled within the threshold range, ultimately confirming the elimination of flow deviation. The process does not require a large-scale adjustment of the oil supply pressure at once, but rather achieves gradual convergence through iterative optimization, thus making the flow balance adjustment more accurate and stable. To determine whether the flow balance has converged, specific balance conditions are designed as the criteria for terminating the iteration. The preferred termination criterion includes two parts: First, the absolute difference needs to show a decreasing trend over two consecutive iterations, indicating that the flow error is gradually decreasing; second, the rate of change of the current oil supply pressure must not exceed the critical dynamic pressure change rate allowed in the oil viscosity calibration characteristics. For example, for a certain lubricating oil, its viscosity calibration is 0.08 N·s / m³.2 The maximum allowable rate of pressure change is 5 kPa / s. In actual iterations, the adjustment should be terminated when this rate of change is reached. By setting these criteria, the system instability caused by over-adjustment of pressure can be effectively avoided.

[0035] Furthermore, such as Figure 3 As shown, the iterative update process of the driving oil supply pressure value until the flow balance convergence condition is met includes: Monitor the numerical change of the absolute difference during successive iterations; The critical rate of change threshold is determined based on the oil film viscosity characteristics parameters of the hydrostatic bearing; When the rate of change of the absolute difference is lower than the critical rate of change threshold, the flow balance condition is determined to be met and the iteration is terminated.

[0036] As a preferred embodiment of the above embodiments, during the operation of the hydrostatic bearing, firstly, to solve the problem that the flow difference in the existing method cannot accurately reflect the balance state, it is preferable to use the sum of the input flow rate of each oil chamber throttle and the three-way fluid output flow rate to quantitatively analyze the flow distribution from an energy perspective. In specific implementation, firstly, the theoretical flow rate value of the pressure distribution of the sealing oil bearing area of ​​each oil chamber is recorded in real time, and at the same time, the axial fluid output and the flow output data of the circumferential left and right fluids are monitored respectively. After collecting these flow data, the absolute difference between the sum of the input flow rate and the output flow rate is calculated. On the other hand, for the flow coupling relationship between the oil chambers in the circumferential direction of the hydrostatic bearing, a constraint for measuring the flow balance is defined, that is, the product of the output flow rate of any oil chamber pointing to the adjacent oil chamber on the left and the journal tangential velocity is always equal to the product of the output flow rate pointing to the adjacent oil chamber on the right and the journal tangential velocity. The logical basis of this constraint lies in the geometric symmetry of the bearing oil chamber and the dynamic balance law of fluid motion. In specific operation, it is preferable to perform high-precision measurement of the journal tangential velocity and combine it with the real-time recording of the flow output of the left and right adjacent oil chambers, by... The side flow rate is multiplied by the journal tangential velocity to form an equal relationship for comparison and verification. For example, under a journal tangential velocity of 1.5 m / s, the left-side flow rate output is recorded as 0.8 L / min, and the right-side flow rate output is also recorded as 0.8 L / min. The product results are completely consistent, proving that the current circumferential flow rate meets the equilibrium condition. If there is a significant difference between the two products, the oil supply pressure is adjusted according to the continuous change of the absolute difference until flow coupling is achieved. In the dynamic iterative optimization process of the oil supply pressure value, the preferred iterative method is used to gradually adjust the pressure value. If the oil supply pressure is gradually increased or decreased in a fixed increment, and the change in the absolute difference is measured synchronously after each iteration, when the absolute difference shows a decreasing trend for two consecutive iterations, and the current critical rate of change threshold is within the specified range, the flow rate can be considered to have entered a balanced state. The critical state calibrated by the critical rate of change threshold is the minimum limit of the system response rate when the oil film viscous damping force and the fluid inertial force reach a dynamic balance. By using this criterion, the system flow rate instability caused by excessively rapid changes in oil supply pressure can be effectively avoided during the iterative adjustment process.

[0037] Furthermore, such as Figure 4 As shown, differential calculations are performed to generate bearing stiffness performance parameters and flow parameters for each oil chamber system, including: Spatial gradient decomposition is performed on the oil supply pressure values ​​after iterative convergence at all selected calculation locations in the sealing oil bearing area to generate a geometric superposition vector of radial bearing components and axial bearing components. The derivative of the calculated geometric superposition vector with respect to the rate of change of bearing clearance forms a composite stiffness characteristic; The real-time flow rate values ​​of the three-dimensional fluid output are used to statistically analyze the distribution characteristics of the circumferential flow rate in each oil cavity to characterize the interaction between oil cavities.

[0038] As a preferred embodiment of the above, firstly, to achieve spatial distribution analysis of bearing load-bearing characteristics, multiple calculation point locations are selected within the oil sealing load-bearing area. The oil supply pressure value at each location is differentially analyzed. Preferably, high-precision pressure sensors are used to sequentially record the pressure response data at each location. By combining the pressure values ​​with the geometric parameters of the location points, such as radial and axial distribution coordinates, the spatial distribution of pressure values ​​within the oil sealing load-bearing area is obtained. In actual operation, pressure sensors are arranged at uniform intervals within the oil sealing load-bearing area. Using the measured pressure distribution data, radial gradient decomposition calculations are performed to generate the positive load-bearing component, and axial gradient decomposition calculations are performed to generate the lateral load-bearing component. Under the condition of an oil supply pressure of 150 kPa, the oil sealing load... The regional pressure exhibits a radially increasing gradient, while the axial pressure distribution is relatively gentle due to fluid viscosity. The positive and lateral load components, representing the stiffness in the bearing's load-bearing direction, directly reflect the support capacity of the sealing area. Next, based on the geometric superposition vector of the positive and lateral load components, the total load-bearing capacity of the bearing is further calculated. In practice, vector synthesis is used to superimpose the two directional components to analyze the comprehensive load-bearing characteristics of the system under complex load conditions. For example, in a certain instance, the axial load component is recorded as 40N, and the radial load component as 60N. Through vector geometric superposition, the total load-bearing capacity is approximately 72N. The calculated total load-bearing capacity accurately reflects... This study reflects the performance indicators of bearings under multi-directional load conditions, providing a reference for bearing support design. In the bearing performance parameter calculation section, based on the relationship between the oil film stiffness component and the rate of change of displacement disturbance obtained from the pressure control equations, and combined with the analysis of the sensitivity of the total load capacity to the rate of change of bearing clearance, the static and dynamic stiffness performance parameters are further solved. In the optimal operation, the dynamic response characteristics of the stiffness component as a function of bearing displacement are measured, the stiffness change amplitude is recorded, and its sensitivity to clearance change is analyzed. For example, under micro-load conditions, when the displacement change is recorded as 0.2 mm, the stiffness change is recorded as approximately 5%, while under standard load conditions, the response of clearance change to stiffness is more linear. The final static and dynamic stiffness performance parameters not only reflect the bearing's performance but also... The ability to support changes under different operating conditions can also provide a basis for bearing design adjustments, such as clearance optimization. Finally, after the oil supply pressure value is iteratively updated, the system flow parameters of each oil chamber are generated based on the measurement data of the three-dimensional fluid output. In specific operation, the oil output flow along the bearing axis is defined as the main path flow, while the output flow along the circumferential direction pointing to the left and right sides of the adjacent oil chambers are respectively used as cross-coupled flow components. The dynamic output characteristics of the main path flow are determined by pressure sensors and flow meters, and the system flow distribution is comprehensively analyzed in combination with the cross-coupled flow. For example, in the operating condition, the axial flow output is recorded as 1 L / min, and the coupling values ​​after the circumferential left and right flow are balanced are 0.8 L / min and 0 L / min, respectively.A flow rate of 2 L / min indicates that the coupling characteristics of the system's flow parameter combination remain stable. These flow parameters not only characterize the flow characteristics of a single oil chamber but also verify the dynamic coupling performance between oil chambers, providing data support for pressure balance model optimization.

[0039] Example 2; Based on the same inventive concept as the multi-parameter collaborative measurement method for hydrostatic bearings in the foregoing embodiments, the present invention also provides a multi-parameter collaborative measurement system for hydrostatic bearings, the system comprising: The region division module, based on the geometric contour of the bearing oil cavity, divides the area completely covered by the oil cavity, the contour boundary area, and the oil sealing and bearing area. The stiffness acquisition module selects discrete calculation location points in the contour boundary region and the sealing oil bearing region, and performs local stiffness component acquisition at the discrete calculation location points. The equation solving module integrates the stiffness components of each discrete calculation location point, constructs a pressure control equation set including force balance relationship expressions and pressure continuity constraint relationships, initializes the oil chamber supply pressure value, and solves the pressure control equation set to obtain the global pressure distribution of the sealing oil bearing area; The output calculation module performs dynamic calculations of axial and circumferential flow rates for each oil chamber to obtain triaxial fluid output parameters; The iterative update module calculates the theoretical flow rate of each oil chamber based on the global pressure distribution, compares the deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid, and controls the iterative update process of the oil supply pressure value by setting flow balance conditions. The parameter calculation module performs differential calculations to generate bearing stiffness performance parameters and flow parameters of each oil chamber system based on the oil supply pressure value after iterative convergence.

[0040] The adjustment system described above in this invention can effectively realize the multi-parameter collaborative measurement method for hydrostatic bearings, and the technical effects it can achieve are as described in the above embodiments, and will not be repeated here.

[0041] Furthermore, the equation solving module includes: The geometric serial unit traverses the stiffness component values ​​of all the discrete calculation location points and synchronously serializes the geometric contour parameters of the oil cavity's completely covered area. The equation construction unit, for each of the discrete calculation locations, evolves a force balance relationship expression based on the oil film compression deformation, and embeds a fluid viscous resistance term into the expression to form a complete mechanical response equation.

[0042] Similarly, the above-mentioned optimization schemes for the system can also achieve the optimization effects corresponding to the methods in Embodiment 1, which will not be repeated here.

[0043] Although this application has been described in conjunction with specific features and embodiments, it is obvious that various modifications and combinations can be made thereto without departing from the spirit and scope of this application. Accordingly, this specification and drawings are merely exemplary illustrations of the application as defined herein, and are to be considered as covering any and all modifications, variations, combinations, or equivalents within the scope of this application. Clearly, those skilled in the art can make various alterations and modifications to this application without departing from its scope. Thus, if such modifications and modifications fall within the scope of this application and its equivalents, this application intends to include such modifications and modifications.

Claims

1. A multi-parameter collaborative measurement method for hydrostatic bearings, characterized in that, The method includes: Based on the geometric contour of the bearing oil cavity, the oil cavity completely covered area, the contour boundary area, and the oil sealing and bearing area are divided. Select discrete calculation location points in the contour boundary region and the sealing oil bearing region, and perform local stiffness component acquisition at the discrete calculation location points; By integrating the stiffness components of each discrete calculation location point, a pressure control equation set including force balance relationship expression and pressure continuity constraint relationship is constructed. The oil supply pressure value of the oil cavity is initialized, and the global pressure distribution of the sealing oil bearing area is obtained by solving the pressure control equation set. For each oil chamber, dynamic calculations of axial and circumferential flow rates are performed to obtain triaxial fluid output parameters, including the oil output flow rate along the bearing axis, the output flow rate pointing to the adjacent oil chamber on the left side along the circumferential direction, and the output flow rate pointing to the adjacent oil chamber on the right side along the circumferential direction. The theoretical flow rate of each oil chamber is calculated based on the global pressure distribution. The deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid is compared. The iterative update process of the oil supply pressure value is controlled by setting flow balance conditions. Based on the oil supply pressure value after iterative convergence, differential calculation is performed to generate bearing stiffness performance parameters and flow parameters of each oil chamber system; wherein, the stiffness performance parameters include the composite stiffness characteristics of radial bearing components and axial bearing components, and the system flow parameters include the output flow characteristics of a single oil chamber and the circumferential coupling flow characteristics between oil chambers.

2. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 1, characterized in that, Discrete calculation locations are selected within the contour boundary region and the sealing oil bearing region, including: Within the outline boundary area, multiple primary calculation points are set at equal intervals based on the distribution relationship between the axial sealing edge spacing value and the circumferential sealing edge spacing value. Within the oil sealing bearing area, a group of calculation points is set using a uniform grid density division strategy based on the axial coverage dimension and circumferential length parameters of the oil cavity. The distribution of the calculation point group covers the physical connection boundary between the oil cavity edge and the sealing edge.

3. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 2, characterized in that, Local stiffness component acquisition is performed at the discrete calculation location points, including: At each of the discrete calculation locations, a local oil film micro-element stiffness model is established, and a linear response relationship between bearing displacement and viscous resistance is generated based on the oil film thickness variation characteristics. Based on the principle of spatial continuity, and combined with the pressure gradient relationship between adjacent discrete calculation points, the linear response relationship is constrained and corrected, and dynamic stiffness components are output.

4. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 1, characterized in that, Construct a system of pressure governing equations that includes expressions for force balance relationships, including: Iterate through the stiffness component values ​​of all the discrete calculation location points and synchronously connect the geometric contour parameters of the area completely covered by the oil cavity. For each discrete calculation location point, a force balance relationship expression is derived based on the oil film compression deformation, and a fluid viscous resistance term is embedded in the expression to form a complete mechanical response equation.

5. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 4, characterized in that, Construct a set of pressure control equations that include pressure continuity constraints, including: Based on the mechanical response equation, for the adjacent position points distributed on the same physical connection edge of the oil cavity among the discrete calculation position points, the distribution sequence of the adjacent position points in the bearing circumferential and axial directions is identified; Based on the distribution sequence, match the oil film pressure change gradient between adjacent locations to establish a local pressure continuity constraint relationship expression; The expression for the local pressure continuity constraint is embedded into the pressure control equation set to complete constraint integration.

6. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 1, characterized in that, The deviation between the theoretical flow rate value and the sum of the flow rates output by the three-dimensional fluid is compared, including: Based on the conservation constraint principle of the fluid continuous motion equation, the absolute difference between the theoretical flow rate of each oil cavity and the sum of the three-dimensional fluid output flow rates is calculated. The absolute difference is correlated with the Reynolds pressure control equation to drive the iterative update process of the oil supply pressure value until the flow balance convergence condition is met to eliminate the deviation.

7. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 6, characterized in that, The iterative update process driving the oil supply pressure value until the flow balance convergence condition is met includes: Monitor the numerical change of the absolute difference during successive iteration steps; The critical rate of change threshold is determined based on the oil film viscosity characteristics parameters of the hydrostatic bearing; When the rate of change of the absolute difference is lower than the critical rate of change threshold, it is determined that the flow balance condition is met and the iteration is terminated; wherein the critical state is the minimum limit of the system response rate when the oil film viscous damping force and the fluid inertial force reach dynamic equilibrium.

8. The method for multi-parameter coordinated measurement of hydrostatic bearings according to claim 1, characterized in that, Perform differential calculations to generate bearing stiffness performance parameters and flow parameters for each oil chamber system, including: Spatial gradient decomposition is performed on the oil supply pressure values ​​after iterative convergence at all selected calculation locations in the oil sealing bearing area to generate a geometric superposition vector of the radial bearing component and the axial bearing component. The derivative of the geometric superposition vector with respect to the rate of change of bearing clearance is calculated to form the composite stiffness characteristic; The distribution characteristics of the circumferential flow rate of each oil cavity are statistically analyzed based on the real-time flow rate values ​​output from the three-dimensional fluid to characterize the interaction between the oil cavities.

9. A multi-parameter collaborative measurement system for hydrostatic bearings, characterized in that, The system includes: The region division module, based on the geometric contour of the bearing oil cavity, divides the area completely covered by the oil cavity, the contour boundary area, and the oil sealing and bearing area. The stiffness acquisition module selects discrete calculation location points in the contour boundary area and the sealing oil bearing area, and performs local stiffness component acquisition at the discrete calculation location points; The equation solving module integrates the stiffness components of each discrete calculation location point, constructs a pressure control equation set including force balance relationship expressions and pressure continuity constraint relationships, initializes the oil chamber supply pressure value, and solves the pressure control equation set to obtain the global pressure distribution of the sealing oil bearing area; The output calculation module performs dynamic calculations of axial and circumferential flow rates for each oil chamber to obtain triaxial fluid output parameters; The iterative update module calculates the theoretical flow rate of each oil chamber based on the global pressure distribution, compares the deviation between the theoretical flow rate and the total flow rate output of the three-dimensional fluid, and controls the iterative update process of the oil supply pressure value by setting flow balance conditions. The parameter calculation module performs differential calculations based on the oil supply pressure value after iterative convergence to generate bearing stiffness performance parameters and flow parameters of each oil chamber system.

10. The multi-parameter collaborative measurement system for hydrostatic bearings according to claim 9, characterized in that, The equation solving module includes: The geometric serial unit traverses the stiffness component values ​​of all the discrete calculation location points and synchronously serializes the geometric contour parameters of the oil cavity's completely covered area. The equation construction unit, for each of the discrete calculation locations, evolves a force balance relationship expression based on the oil film compression deformation, and embeds a fluid viscous resistance term into the expression to form a complete mechanical response equation.

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