A method and apparatus for controlling bearing creep based on variable interface performance

Abstract

This invention relates to the field of heavy-duty bearing design and application technology, specifically to a bearing creep control method and device based on variable interface performance. The device comprises an annular multifunctional variable interface layer between the bearing outer ring and the bearing housing. This interface layer is composed of stable anchoring units with high elastic modulus and high friction coefficient, and directional slip triggering units with low elastic modulus and low friction coefficient, periodically and alternately distributed along the circumference. The number of circumferential partitions is coprime to the number of bearing rollers, enabling directional, step-like triggering of controlled micro-creep. The surface of the interface layer is provided with a checkerboard or spiral groove network filled with a functional medium to achieve damping dissipation, lubrication protection, and stiffness regulation. An integrated grating displacement monitoring component is also included for graded judgment of creep state.

Description

Technical Field

[0001] This invention relates to the field of heavy-duty bearing design and application technology, specifically to a bearing creep control method and device based on variable interface performance. Background Technology

[0002] In heavy equipment fields such as wind power and tunnel boring machines, core bearings (e.g., wind turbine main shaft bearings, tunnel boring machine main drive bearings) generally face extreme working conditions: extremely low speeds or even long-term static load-bearing states, yet they must withstand enormous combined loads including radial, axial, and overturning moments. The load transfer mechanism of traditional rolling bearings has limitations: external loads are transferred to the raceways of the raceways via rollers, resulting in a high concentration of contact stress in a localized area directly beneath the rollers. Under low-speed or static heavy-load conditions, this continuous, highly localized contact stress easily leads to plastic deformation, early fatigue spalling, and even cracks on the raceway surface, severely limiting the bearing's load-bearing capacity and service life.

[0003] Current conventional techniques for improving bearing load capacity mainly focus on optimizing internal bearing geometry (such as increasing roller size and number, adopting high-load-bearing roller configurations, and optimizing raceway curvature) or selecting ultra-high-strength materials. However, these methods still face bottlenecks under low-speed, heavy-load conditions: on the one hand, geometric optimization is limited by installation space and manufacturing costs; on the other hand, improvements in material strength have marginal effects and cannot change the fundamental force transmission mechanism where loads are concentrated in local areas. Therefore, there is an urgent need for a design method that can innovate from the load distribution mechanism and significantly improve the stress state of low-speed, heavy-load bearings. Summary of the Invention

[0004] To address the aforementioned technical problems, this invention proposes a bearing creep control method and device based on variable interface performance. By actively designing and adjusting the mechanical properties of the interface between the bearing outer ring and the bearing housing, controlled creep is induced and utilized to achieve load equalization and significantly improve the bearing's load-bearing capacity.

[0005] The technical solution adopted in this invention is: a bearing controlled creep control device based on variable interface performance, which is set between the outer ring of the bearing and the bearing housing. The bearing creep control device is an annular multifunctional variable interface layer with elastic modulus gradient and friction coefficient gradient, which are synergistically coupled and distributed in the circumferential space and cover the entire outer ring of the bearing.

[0006] The multifunctional variable interface layer is composed of stabilizing anchoring units and directional slip triggering units periodically and alternately distributed along the circumferential contact surface of the bearing outer ring. The stabilizing anchoring unit is an integral structure with high elastic modulus and high coefficient of friction, and the directional slip triggering unit is an integral structure with low elastic modulus and low coefficient of friction. The number of circumferential partitions N of the multifunctional variable interface layer and the number of rollers Z of the corresponding bearing are coprime, where the number of circumferential partitions N is the total number of sets of the stabilizing anchoring units and the directional slip triggering units.

[0007] The surface of the multifunctional variable interface layer is provided with a network of grooves for filling and regulating the mechanical properties of the interface. The outer ring of the bearing and the bearing housing are provided with friction surfaces on the contact surfaces with the multifunctional variable interface layer to provide the interference of friction force.

[0008] As a preferred embodiment, the elastic modulus of the directional sliding trigger unit is... and coefficient of friction It needs to meet the target pressure When the slip critical point is reached, the specific constraint formula is as follows: The elastic modulus of the stable anchoring unit and coefficient of friction It is necessary to ensure that until There is no slippage under all pressures; the specific constraint formula is as follows: in, The interface coupling coefficient is... It is a non-linear exponent and its value range is The elastic modulus of the stable anchoring unit Elastic modulus of the directional slip trigger unit ratio / ≥3, the coefficient of friction of the stable anchoring unit coefficient of friction with directional sliding trigger unit value / >2.

[0009] As a preferred embodiment, the macroscopic equivalent elastic modulus in the multifunctional variable interface layer composed of stable anchoring units and directional sliding triggering units is... The following constraint formula must be satisfied: In the formula, h is the axial thickness of the multifunctional variable interface layer, and A c The nominal bearing area of ​​the multifunctional variable interface layer. This represents the maximum permissible radial stiffness loss ratio for the bearing system. This refers to the system stiffness of the bearing outer ring.

[0010] As a preferred embodiment, the stabilizing anchoring unit includes any one of diamond-silicon carbide composite material, a carbon-based film integrating strength and lubrication, molybdenum disulfide reinforced epoxy resin composite material, and carbon fiber reinforced polyimide composite material; the directional slip triggering unit includes any one of polytetrafluoroethylene modified epoxy resin composite material, hydrogenated nitrile rubber and resin blend material, and low-friction carbon-based film.

[0011] As a preferred embodiment, the groove network is a localized groove network with a checkerboard structure or a comprehensive spiral groove network with a striped structure; the number of groove networks within a single directional sliding trigger unit... Number of trench networks within a single stable anchoring unit The following constraint formula must be satisfied: In the formula, These represent the area ratios of the directional sliding trigger unit and the stable anchoring unit, respectively. These are the elastic moduli of the directional sliding trigger unit and the stable anchoring unit, respectively. is the trench network density enhancement factor, and its value ranges from 1.5 to 3.0.

[0012] Furthermore, the functional medium filling the trench network is one or more combinations of viscous fluid medium, solid lubricating medium, and compressible gas medium.

[0013] As a preferred embodiment, the nominal interference fit between the multifunctional variable interface layer and the bearing housing, used to provide the frictional interference fit, is... The following formula constraints must be met: In the formula, This is the prestress reduction factor, which reflects the proportional relationship between the prestress generated by the interference fit and the deformation required for slip triggering. It can be recommended to take a value based on the stress distribution characteristics of the interference fit surface and engineering experience. The specific value can be verified through finite element contact analysis: when the interference is If the soft region can still produce the expected slip under the ultimate load, then The value is reasonable. This refers to the trigger threshold for bearing raceway contact stress. denoted as , where is the elastic modulus of the directional sliding trigger unit, and h is the axial thickness of the multifunctional variable interface layer.

[0014] As a preferred embodiment, a grating displacement monitoring component for detecting the deformation of a multifunctional variable interface layer is also provided. The grating displacement monitoring component includes a reflective grating ruler fixed to the end face of the bearing outer ring and a reading head fixed to the bearing housing end cover. The reading head is correspondingly provided with a tangential displacement monitoring channel and an axial displacement monitoring channel. The grating displacement monitoring component outputs a tangential displacement signal in real time. and axial displacement signal And simultaneously acquire load signals Its normal sampling frequency is 100Hz. When the displacement change rate of the multifunctional variable interface layer exceeds the threshold, high-speed sampling is automatically triggered. The high-speed sampling frequency is 1kHz to 5kHz. The constraint formula for the displacement threshold detection of the grating displacement monitoring component is as follows: ,in This represents the amount of compressive deformation generated in the soft zone when the load reaches the trigger stress—that is, the expected displacement amplitude of a normal controlled slip.

[0015] The beneficial effects of this invention are: To address the shortcomings of existing technologies, this invention provides a bearing creep control method and apparatus based on variable interface performance. Through optimized structural design, this invention achieves the following technical advantages: Firstly, this invention establishes a dual-gradient, multifunctional, variable interface layer with a spatially coordinated distribution of elastic modulus gradient and friction coefficient gradient between the outer ring of the bearing and the bearing housing. This layer forms stable anchoring units and directional slip triggering units, and ensures that the number of circumferential partitions in the interface layer is coprime with the number of bearing rollers. This actively induces the raceway to produce directional, step-like controlled micro-creep, achieving dynamic homogenization and circumferential migration of raceway contact stress. This transforms the traditional static localized load-bearing into dynamic traversal load-bearing, breaking through the load-bearing limit of traditional bearings from the perspective of force transmission mechanism. Theoretically, this increases the ultimate load-bearing capacity of low-speed, heavy-load bearings by more than 30%, effectively solving the technical problem that low-speed, heavy-load bearings are prone to raceway plastic deformation, early fatigue spalling, and even cracking due to the continuous concentration of contact stress in local areas of the raceway.

[0016] Secondly, this invention creates a groove network on the surface of the dual-gradient interface layer that matches the gradient distribution pattern, and fills the groove network with functional media such as viscous fluid, solid lubricant, or compressible gas. The damping dissipation, lubrication protection, and elastic support of the media are used to assist in the controlled creep process of the ring. Furthermore, the creep triggering timing and equivalent stiffness can be actively controlled by adjusting the gas medium pressure through an external gas source. This gives the interface layer the potential for intelligent control, while providing continuous lubrication reserves and impact buffers for the friction interface. This effectively solves the technical problems of instantaneous slippage impact, unexpected interface wear, and the insufficient control capability of traditional interface designs for creep processes and their inability to adapt to complex working conditions during controlled creep.

[0017] Thirdly, this invention determines the reasonable interference range between the interface layer and the bearing housing by comprehensively calculating the interference changes caused by load, temperature difference, and micro-flattening of the mating surfaces. At the same time, wear-resistant coating deposition or laser micro-texturing treatment is performed on the mating surfaces of the bearing outer ring and the bearing housing to set a stable basic friction coefficient. This achieves the collaborative design of the interface layer and the bearing mounting structure, ensuring that controlled creep is accurately triggered under the design stress threshold. It also improves the wear resistance of the mating surfaces and extends the overall service life of the interface system. This effectively solves the technical problems of poor interface layer anchoring effect, slip trigger failure, or creep runaway caused by unreasonable installation interference and fluctuations in the basic friction coefficient.

[0018] Fourth, this invention integrates a non-contact grating displacement monitoring system by installing reflective grating rulers and reading heads on the outer ring end face of the bearing and adjacent stationary components respectively. It adopts a dual-mode strategy of low-speed continuous sampling and high-speed triggered sampling to collect tangential, axial displacement and real-time load signals, realizing accurate identification of slip events and graded judgment of creep state. This provides accurate data support for the closed-loop control of controlled creep, and makes the operating status of the bearing system more monitorable and maintainable. It effectively solves the technical problems in traditional bearing design that make it impossible to grasp the interface slip state in real time, difficult to judge whether creep is triggered normally, and unable to detect and troubleshoot faults in a timely manner after anomalies occur.

[0019] Fifth, this invention concentrates all functional designs on the external interface layer between the bearing outer ring and the bearing housing, without altering the core structure of the bearing such as the raceway and rollers. It can be directly assembled and adapted to various existing high-load bearing configurations, significantly reducing engineering modification costs. At the same time, this design utilizes the creep phenomenon that still exists under low-speed / stationary conditions, transforming the harmful fretting wear under traditional working conditions into beneficial stress transfer dynamics. It cleverly solves the technical problems of the difficulty in establishing a lubricating film and severe wear in low-speed heavy-load bearings. It has unique adaptability to low-speed heavy-load working conditions such as wind turbine main shaft bearings and tunnel boring machine main drive bearings. It effectively solves the technical problems of traditional bearing performance improvement methods requiring optimization of internal geometric parameters or replacement of ultra-high-strength materials, which are limited by installation space and manufacturing costs and cannot be compatible with existing high-load bearing configurations. Attached Figure Description

[0020] 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 of the invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1(a) is a schematic diagram of stress concentration in a traditional bearing under heavy load, and (b) is a schematic diagram of the principle of stress homogenization achieved by controlled creep in this invention.

[0022] Figure 2 This is a schematic diagram of the structure of the present invention.

[0023] Figure 3 This is a 3D schematic diagram of a multifunctional variable interface layer, showing gradient patterns and trench networks.

[0024] Figure 4 These are comparison diagrams of the traditional structure and the present invention, wherein Figure a is a schematic diagram of the traditional structure, Figure b1 is a schematic diagram of the present invention, and Figure b2 is a schematic diagram of the specific structure of the present invention.

[0025] Figure 5 A schematic diagram showing the details of a localized trench network with a checkerboard structure and its medium filling.

[0026] Figure 6 A schematic diagram showing the overall spiral trench network with a striped structure and its medium filling details.

[0027] In the figure, 1-multifunctional variable interface layer, 2-stabilized anchoring unit, 3-directional sliding triggering unit, 4-bearing housing, 5-bearing outer ring, 6-roller, 7-groove network. Detailed Implementation

[0028] The present invention will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0029] It should be noted that, unless otherwise defined, the technical or scientific terms used herein should have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. The terms "a," "an," or "the," and similar words used in the specification and claims of this patent application do not express a limitation of quantity, but rather indicate the presence of at least one; terms such as "comprising" or "including" indicate that the elements or objects preceding "comprising" encompass the elements or objects listed following "comprising" or "including" and their equivalents, but do not exclude other elements or objects having the same function.

[0030] The purpose of this invention is to provide a systematic method that, by implanting a specially designed multifunctional interface layer between the outer ring 5 of the bearing and the bearing housing 4, actively and controllably utilizes the microscopic slippage (controlled creep) of the bearing ring to achieve dynamic homogenization and migration of raceway contact stress, thereby breaking through the traditional load-bearing limit. This invention not only defines the core design theory and construction method of this interface layer, but also integrates structural designs to enhance its functionality and necessary collaborative monitoring elements.

[0031] Part 1: Design of Multifunctional Variable Interface Layer 1 This section aims to construct and design in detail the multifunctional variable interface layer 1 placed between the outer ring 5 of the bearing and the bearing housing. This layer is the core carrier for achieving the controlled creep function of this invention, and its design encompasses the following four aspects: 1. Construction and mechanism of dual-gradient functional matrix: The matrix properties of the multifunctional variable interface layer 1 are defined by two independent and co-designable spatial gradients: Elastic modulus (E) gradient: forms an alternating spatial distribution of "soft regions" (low modulus E1) and "hard regions" (high modulus E2). E2 / E1>3 to produce significant deformation differences.

[0032] Friction coefficient (μ) gradient: forming an alternating spatial distribution of "low μ region" (low friction coefficient μ1) and "high μ region" (high friction coefficient μ2), which is preferably coupled with the elastic modulus gradient in spatial distribution.

[0033] Synergistic Function Mechanism: The combination of "hard zone + high μ zone" constitutes the stable anchoring unit 2. It provides macroscopic rigid support and strong anti-slip resistance, ensuring the positioning accuracy and stability of the bearing under normal loads most of the time.

[0034] The combination of the "soft zone / low μ zone" constitutes the directional slip triggering unit 3, which is key to achieving controlled creep. Its low modulus characteristics allow it to generate larger local compressive deformation under load than the stable anchoring unit 2. This deliberately created periodic deformation mismatch alters the contact state, accumulates elastic strain energy, and creates driving potential energy and geometric tendency for the raceway to slip. Its low friction characteristics lower the threshold for slippage. When the local load reaches the design threshold, under the combined effect of the driving tendency provided by the "soft zone" and the reduced resistance of the "low μ zone," the raceway will preferentially undergo a small, step-like tangential slip (i.e., a controlled creep event) along the direction guided by this combined unit.

[0035] Hard / high μ region materials: High-modulus, high-friction materials can be selected, including but not limited to: Diamond-silicon carbide (DSiC) composite materials have an elastic modulus of over 48 GPa, and through surface texture design, their coefficient of friction against steel can be stabilized at 0.30–0.50. A carbon-based thin film that integrates strength and lubrication can achieve an elastic modulus of 15–65 GPa and a friction coefficient of 0.20–0.40 by adjusting its carbon bond structure. The molybdenum disulfide reinforced epoxy resin (MoS2 / EP) composite material has a significantly improved modulus compared to pure epoxy resin, and the coefficient of friction can be adjusted to 0.25-0.35 by adjusting the MoS2 content. The carbon fiber reinforced polyimide composite material has a measured modulus of 6 GPa. The surface is textured by micro-blasting, and the measured friction coefficient when rubbed against steel is around 0.32.

[0036] Soft / low μ region materials: Low-modulus, low-friction materials can be selected, including but not limited to: Polytetrafluoroethylene modified epoxy resin (PTFE / EP) composites can reduce the elastic modulus to 2-5 GPa and the coefficient of friction to 0.05-0.10. A high-performance hydrogenated nitrile butadiene rubber (HNBR) blend with resin has a measured modulus of 3.8 GPa. The surface is coated with a PTFE-filled film, resulting in a coefficient of friction of 0.06–0.10.

[0037] Low-friction carbon-based thin films, by doping with metal or non-metal elements, can achieve an adjustable elastic modulus of 4–15 GPa and a friction coefficient as low as 0.01–0.12.

[0038] Among the above material systems, the particularly preferred synergistic combination is the MoS2 and PTFE synergistic reinforced epoxy resin system, in which the MoS2 reinforced region is used as the stabilizing anchoring unit 2 and the PTFE reinforced region is used as the directional slip triggering unit 3. The two can be integrated and prepared on the same matrix through a partitioned curing process, which is more in line with the gradient design requirements of the present invention.

[0039] 2. Spatial design principles for gradient distribution: To ensure the stability, ergodicity, and effectiveness of controlled creep, the gradient distribution of the multifunctional variable interface layer 1 follows these criteria: Periodic alternating full-coverage distribution: The "hard area / high μ area" and the "soft area / low μ area" must be periodically alternating along the circumference of the contact surface (such as a checkerboard pattern or stripes) and cover the entire interface. The "star point" layout, which only sets stable anchoring elements 2 at a few points, is abandoned, as the latter will lead to uncontrollable macroscopic slippage and stiffness loss.

[0040] Periodic decoupling design: The geometric period (or number of partitions N) of the gradient distribution must follow a non-matching criterion with the number of bearing rollers 6 Z, meaning they should avoid being integer multiples of each other, and preferably be coprime numbers. This design ensures that during continuous controlled creep, the relative position of rollers 6 and the interface will undergo an irreversible phase shift, thus guaranteeing that every point on the entire raceway circumference can be traversed and supported and undergo stress transfer, fundamentally preventing localized stress lock-up.

[0041] The selection of the number of partitions N needs to be based on the outer diameter D of the bearing outer ring 5 and the circumferential design width of each directional slip trigger unit 3 / stabilizing anchor unit 2. (This value is usually determined based on deformation mismatch requirements and manufacturing processes, and ranges from approximately 5 to 20 mm). First, determine the initial value for the theoretical number of zones: Then, an integer coprime to the number of rollers Z near N0 is selected as the final partition number N, which should satisfy the engineering feasibility range (usually...). ).

[0042] 3. Theoretical design methods for key parameters To achieve the controlled creep function of "rigid support under normal load and directional slip under ultimate load", the core parameters of the multifunctional variable interface layer 1 need to be designed collaboratively. This invention proposes the following systematic design method, which clearly defines the selection criteria for the elastic modulus (E) and the coefficient of friction (μ) through a set of interrelated formulas and inequalities.

[0043] 3.1 Design Inputs and Objectives: Ultimate load condition: (N) is the maximum radial static load or quasi-static load on the bearing.

[0044] Ring-related dimensions: Outer ring outer diameter (mm), width (mm). The nominal bearing area can be calculated from this. (mm) 2 ).

[0045] System stiffness constraint: the maximum allowable proportion of radial stiffness loss in the bearing system. (For example This indicates that the stiffness loss does not exceed 10%. This parameter is directly related to the macroscopic equivalent elastic modulus of the multifunctional variable interface layer 1. .

[0046] Stress migration trigger threshold: To avoid early failure caused by local stress concentration in the raceway, the contact stress value required to trigger stress migration is specified. (MPa). This is typically set as the contact fatigue limit of the raceway material. The value is S times (based on bearing industry design practice, for general industrial applications, S is a safety factor, and a recommended value is 0.75~0.85), i.e. Maximum expected contact pressure ( It can be calculated using Hertzian contact theory, or determined through engineering estimation based on the ratio of the bearing's rated static load to its ultimate load and with reference to the material's allowable contact stress.

[0047] Design parameters of multifunctional variable interface layer 1: area ratio of directional sliding trigger unit 3 / stable anchoring unit 2 , , Multifunctional variable interface layer 1 thickness (mm); Minimum modulus gradient ratio (like If the value is too small, close to 1, the performance of the soft-stabilized anchoring unit 2 will converge, failing to generate effective periodic deformation differences to drive directional slip. If... While a larger size would clearly differentiate functions, it could create difficulties in material matching and manufacturing. ).

[0048] 3.2 Core Formula System 1) System stiffness constraint equations Introducing the multifunctional variable interface layer 1 is equivalent to adding a parallel "spring" between the bearing and the bearing housing. To ensure that the bearing system still has sufficient support stiffness after the introduction of the multifunctional variable interface layer 1, the additional radial flexibility introduced by the presence of the multifunctional variable interface layer 1 must be limited in order to control the overall stiffness decay of the system.

[0049] Stiffness is defined as: The compressive stiffness of the multifunctional variable interface layer 1 can be expressed as: Assume the stiffness of the original bearing outer ring 5 (rigidly mounted) is... After introducing the multifunctional variable interface layer 1, the total stiffness of the system is Stiffness loss ratio is defined as follows: By combining the above relationships, we can solve for the... Requirements: (1) This formula is directly and rigorously derived from the stiffness series model and the definition of stiffness loss. It is a series spring problem in classical mechanics, with parameters... (Available from bearing manuals) and (Design goals) are determined. The lower limit is a fixed value.

[0050] 2) Physical criterion equation for controlled creep (local triggering condition) The essence of "controlled creep" is the triggering and control of microscopic slippage between the outer ring 5 of the bearing and the multifunctional variable interface layer 1. The physical conditions under which it occurs are precisely determined by the balance between the shear driving force and the maximum static friction force at the interface. These two factors are dominated by the elastic modulus and the coefficient of friction, respectively.

[0051] Consider a representative volume element on the multifunctional variable interface layer 1 (whether it's the directional slip triggering element 3 or the stable anchoring element 2). When the outer ring 5 of the bearing passes through the roller 6, the contact stress... When passed to this unit: Interface shear driving force The primary cause is the shear stress generated by the constrained Poisson expansion effect (lateral strain) of the compressed element. This stress is related to the axial strain of the element. Directly related, for a given geometry and Poisson's ratio, the core relationship can be simplified to: the driving shear stress is related to the applied pressure. The elastic modulus of the material in this region is directly proportional to the elastic modulus of the material. Inversely proportional. That is, for the same pressure... Modulus The lower the region, the greater the shear force generated. The larger.

[0052] Based on the constrained expansion model of a compressed elastic cylinder, the shear driving force can be characterized as: ,in The interface coupling coefficient is... As the exponent is close to 1 (typically reflecting nonlinear problems), the slip critical condition can be obtained: (2) Among them, the interface coupling coefficient This comprehensively reflects the constraint stiffness of the interface and the Poisson's ratio of the material. And the amplification effect of the geometry (aspect ratio) of the directional slip triggering unit 3 / stable anchoring unit 2 on the shear driving force; nonlinear exponent Characterizes the non-linearity of the relationship (usually) ).

[0053] and The determination can be made using the finite element simulation calibration method, and the steps are as follows: 1. Establish parameterized unit models: Construct finite element models representing the materials of directional slip trigger unit 3 and stable anchoring unit 2, including the bearing outer ring 5 segment, interface material elements and constraint bodies.

[0054] 2. Simulation Loading and Data Extraction: Applying a series of normal pressures to the model. And extract the tangential resultant force at the interface under each pressure. 3. Nonlinear fitting: based on the relational formula ( (area per unit), for data points By performing nonlinear least squares fitting, the design for this specific material and interface can be directly obtained. and The precise value.

[0055] 3) Parameter design inequalities of gradient functional regions Design of directional sliding trigger unit 3: its parameter combination It needs to meet the target pressure When the slip critical point is reached.

[0056] (3) To promote slip triggering, a "low modulus" is usually selected. "and "medium / low coefficient of friction" The combination of "".

[0057] Design of Stabilized Anchoring Unit 2: Its Parameter Combination It is necessary to ensure that until It does not slip under any pressure.

[0058] (4) To promote absolute anchoring, a "high modulus" is usually selected. "and "high coefficient of friction" The combination of "" must satisfy the following conditions. .

[0059] 4) Gradient Coordination and Equivalent Modulus Equation The directional sliding trigger unit 3 and the stabilizing anchoring unit 2 are connected in parallel in space to form an integrated multifunctional variable interface layer 1, whose macroscopic equivalent modulus is... It approximately follows the mixed law: (5) At the same time, in order to achieve a significant comparison of mechanical properties, the following must be met: (6) 3.3 Collaborative Design Process 1) Determine system constraints: Calculate the minimum equivalent modulus required for the multifunctional variable interface layer 1 according to formula (1). .

[0060] 2) Initial selection of parameters for the directional sliding trigger unit 3: Predetermine a relatively low coefficient of friction. (e.g., 0.1~0.2).

[0061] Will and calibration constants Substitute into formula (3) to solve or iterate to determine an elastic modulus that can satisfy the triggering condition. .Should It should be relatively low (usually in the range of 0.5 to 10 GPa).

[0062] 3) Calculate the lower limit of the parameters of stable anchoring element 2: Will and selected Substituting into formula (5), we can deduce the stiffness requirement of the system. .

[0063] According to the gradient requirement formula (6), calculate the gradient ratio required to satisfy the gradient requirement. .

[0064] Stable anchoring element 2 modulus Must meet: .

[0065] 4) Determine the friction coefficient of stable anchoring unit 2: To stabilize anchoring element 2, a relatively high coefficient of friction is pre-selected. (e.g., 0.40~0.70), and satisfying .

[0066] Will Substitute into formula (4) to perform anchorage verification to ensure that the inequality is strictly true.

[0067] 5) Iterative optimization: If a feasible solution cannot be obtained in step 3 or 4, return to step 2 and adjust. or The initial values ​​are selected, and the process is repeated until all equations and inequalities (1)-(6) are satisfied simultaneously.

[0068] 3.4 Design Example (Brief Description) enter: Detailed calculation process: 1) From equation (1), we get .

[0069] 2) Take Substituting into equation (3) and solving, we get .

[0070] 3) From equation (5), we get From equation (6), we get Therefore .

[0071] 4) Take (satisfy Select Substituting into equation (4) for verification, we get 2.5 × (750 / 10.0)0.9 106 < (0.5 × 750) = 375, the anchoring condition is met.

[0072] in conclusion: The feasible parameter set is: directional sliding trigger unit 3 ; Stable anchoring unit 2 , This combination ensures that the system stiffness loss is less than 10%, and that directional slip is triggered by the directional slip triggering unit 3 at a contact stress of 600 MPa, while the stabilizing anchoring unit 2 remains anchored at 750 MPa.

[0073] 4. Design of the 7-functional structure of surface trench network To enhance the controllability of the controlled creep process, a trench network 7 adapted to the gradient distribution pattern can be designed on the surface of the multifunctional variable interface layer 1, and filled with a functional medium. The trench network 7 mainly comes in two forms corresponding to the gradient pattern: Localized grooves to adapt to checkerboard gradient patterns: In the independent "stabilizing anchoring unit 2" and "directional sliding triggering unit 3" units, groove patterns that match the function of the unit are designed respectively.

[0074] Integral spiral grooves adapted to striped gradient patterns: An integral spiral groove network is machined around the contact surface on the surface of a continuous striped gradient layer.

[0075] By filling and regulating fluid, solid, or gaseous media within the groove network, it is possible to actively or passively adjust the interfacial friction state, damping characteristics, and even local equivalent stiffness, thereby working in conjunction with gradient design to make the controlled creep process smoother and more controllable.

[0076] Viscous fluid medium (high-viscosity lubricating oil, grease, or specialized damping fluid): Viscous damping is formed by the shear resistance generated when the fluid, filling the groove network 7, undergoes microscopic relative motion at the interface. This damping force acts directly on the slip process, consuming slip kinetic energy and making the slip process smoother and more controllable, avoiding instantaneous impacts. During micro-slip, the fluid is dragged to the contact area, potentially generating small hydrodynamic pressures, which help to share some of the contact load, thereby assisting in reducing the driving force required to trigger further slip.

[0077] Solid lubricating medium: Pre-filling the groove network 7 with solid lubricants (such as graphene, molybdenum disulfide) or high-performance grease can provide continuous lubrication for the friction interface, reduce unexpected wear, and serve as an emergency lubrication reserve. Furthermore, the solid elastic particles can compensate for microscopic unevenness, provide stable elastic support, and act as a buffer under impact loads.

[0078] Gas lubrication medium (dry air, nitrogen, or other inert gas): The gas enclosed in the microcavities of the grooved network 7 has high compressibility. When the interface pressure changes, the gas volume is compressed or expanded, exhibiting a nonlinear gas spring effect. This effect can significantly absorb and store strain energy, delaying the rise of pressure peaks, thereby regulating the timing of slip triggering and the energy release process. If the microcavities of the grooved network 7 are connected to an external gas source through valves, the gas pressure inside the cavity can be actively regulated, thereby directly and actively changing the equivalent stiffness and load-bearing state of the multifunctional variable interface layer 1 in this region, achieving the most active creep control.

[0079] Furthermore, for the localized groove network 7 of the checkerboard gradient pattern, the number of groove networks 7 for the slip triggering unit and the stabilizing anchoring unit 2 follows the following design relationship: To achieve functional synergy between the sliding triggering unit 3 (sliding trigger) and the stable anchoring unit 2 (stable anchoring), the groove network 7 density of the directional sliding triggering unit 3 should be significantly higher than that of the stable anchoring unit 2. This is to meet the damping dissipation and stress homogenization requirements of the directional sliding triggering unit 3 during triggering sliding, while simultaneously preventing stiffness loss in the stable anchoring unit 2 due to excessive groove network 7. Let the number of groove network 7 within a single directional sliding triggering unit 3 be... The number of groove networks 7 within a single stable anchoring unit 2 is Then both should satisfy: In the formula: These represent the area proportions of the directional sliding trigger unit 3 and the stable anchoring unit 2, respectively. These are the elastic moduli of the directional sliding trigger unit 3 and the stable anchoring unit 2, respectively. The density enhancement factor of the trench network 7 reflects the additional requirements of the directional slip triggering unit 3 for damping dissipation and stress homogenization, and is usually taken as... .

[0080] Part Two: Elements of Collaborative Design To ensure the perfect implementation of the aforementioned core multi-functional variable interface layer 1, the following installation and application parameters need to be collaboratively designed and optimized: The multifunctional variable interface layer 1 and the bearing housing 4 adopt a calculated and optimized interference fit. The design goal is to provide sufficient initial prestress to enhance the anchoring effect of the "high μ zone" and the initial stiffness of the system. On the other hand, it ensures that this prestress will not hinder the controlled slip triggered by the directional slip triggering unit 3 under ultimate load.

[0081] The determination of interference fit needs to be based on the classical theory of rolling bearing fit design, taking into account the influence of factors such as load, temperature difference and micro-morphology of mating surfaces on the effective interference fit.

[0082] (1) Reduction in interference caused by load under radial load Under this action, the inner ring (or the race in this design) will generate circumferential tensile stress, causing its inner hole to expand, thereby reducing the initial interference fit. The amount of reduction can be estimated using the following empirical formula: when hour when hour In the formula: D is the outer diameter of the bearing outer ring 5, B is the width of the ring (mm), F r For the ultimate radial load (N), C 0r This is the basic static load rating of the bearing (N).

[0083] (2) Decrease in interference caused by temperature difference During operation, the bearing temperature is typically higher than the ambient temperature. The thermal expansion of the bearing races reduces the effective interference fit with the multifunctional variable interface layer 1. Let the temperature difference between the bearing interior and the external environment be... (°C), then the reduction in interference is: In the formula, Let be the coefficient of linear expansion of the bearing ring material. For bearing steel, D is the outer diameter of the ring (mm).

[0084] (3) Calculation of effective interference caused by micro-flattening of mating surfaces When using the press-fit method for assembly, the microscopic peaks on the mating surfaces are erased or flattened, resulting in an actual effective interference fit that is less than the nominal interference fit. According to GB / T 5371-2004 standard, the nominal interference fit... With effective overshoot The relationship is: In the formula, To match the arithmetic mean deviation (mm) of the surface profile. For the ground surface R a1 =0.0008-0.0016mm, R a2 =0.0016-0.0032mm, The minimum effective interference required is determined by the load and temperature difference. This represents the lower limit of nominal excess.

[0085] (4) Ensure maximum interference constraint for slip triggering The prestress generated by the interference fit should not hinder the directional slip trigger unit 3 from being triggered at the trigger stress. This results in a critical deformation. Therefore, the nominal interference... Also required: In the formula, This is the prestress reduction factor, which reflects the proportional relationship between the prestress generated by the interference fit and the deformation required for slip triggering. It can be recommended to take a value based on the stress distribution characteristics of the interference fit surface and engineering experience. The specific value can be verified through finite element contact analysis: when the interference is If the soft region can still produce the expected slip under the ultimate load, then The value is reasonable.

[0086] (5) Final nominal surplus The determination The final selected nominal overshoot All of the above conditions must be met. In engineering design, the minimum effective interference is usually calculated first based on the load and temperature difference. Then, the lower limit of the nominal interference is derived by considering the influence of surface roughness, and compared with the upper limit of the slip constraint. The selection principle is as follows: in, Anchored demand ( and The sum of these (and the surface flattening effect) is calculated by back-calculation. The value is determined by the slip trigger constraint. The specific value can be adjusted within this range according to the actual working conditions.

[0087] Pretreatment of the basic friction interface: Before installing the multifunctional variable interface layer 1, a wear-resistant coating is deposited or laser microtextured on the outer surface of the bearing outer ring 5 and / or the inner surface of the bearing housing 4. The aim is to establish a stable and appropriately sized basic coefficient of friction. This treatment not only improves the wear resistance of the metal body and extends the system life, but also provides a reliable and consistent performance benchmark for the design of gradient friction coefficients.

[0088] Basic friction coefficient The principles for determining: The value should be within the range of the friction coefficient of the directional sliding trigger unit 3. It is often advisable Its specific value can be controlled through surface treatment processes.

[0089] Part Three: Monitoring of Creep Status To enable verification, monitoring, and potential feedback control of controlled creep behavior, a high-precision displacement monitoring system is integrated.

[0090] The monitoring system consists of a non-contact optical grating displacement sensing system. High-precision reflective optical grating rulers and reading heads are installed on the end face of the outer ring 5 of the bearing and on adjacent stationary components (such as the end cover of the bearing housing 4), respectively, with at least two measurement directions: tangential (circumferential) and axial.

[0091] Monitoring principles and applications: 1. Data Acquisition and Slip Event Recognition The grating displacement sensing system outputs tangential displacement signals in real time. and axial displacement signal Synchronously acquire load signals Data acquisition employs a dual-mode strategy: continuous low-speed sampling (e.g., 100Hz) is used for trend monitoring; when the rate of displacement change exceeds a threshold, high-speed sampling (e.g., 1–5kHz) is automatically triggered to fully record the transient process of slip.

[0092] Identify single slip events from the raw displacement signal and extract the following feature parameters: tangential displacement. : Reflects the microscopic slippage of the raceway in the circumferential direction; axial displacement It reflects the axial displacement of the raceway (to aid in determining the direction); real-time load P: from the host control system or additional sensors.

[0093] 2. Design-provided benchmarks Triggering stress The designed sliding start threshold (e.g., 600 MPa) The elastic modulus of the directional sliding trigger unit 3 and multifunctional variable interface layer 1 thickness A theoretical reference value can be calculated: this This represents the amount of compressive deformation generated by the directional slip triggering unit 3 when the load reaches the trigger stress—that is, the expected displacement amplitude (e.g., 4 μm) of a normal controlled slip.

[0094] 3. Logic for determining state from data Step 1: Identify Slide Events A slip event is determined to have occurred when the tangential displacement exhibits a significant step change within a short period (e.g., a change exceeding 1 μm within 0.1 seconds) and remains stable before and after the change. Record the amplitude of this slip event. (Difference before and after the step jump); Slip direction angle Loads during slippage .

[0095] Step 2: Compare with the baseline to determine the status. The states are compared with the baseline, as shown in the table below: 4. Numerical judgment This is just a theoretical reference value. The actual slip amplitude will fluctuate within ±50% due to factors such as load distribution and medium damping, which is normal. Only when the amplitude significantly exceeds the normal fluctuation range (such as more than 2-3 times) is it considered abnormal.

[0096] Direction angle This is used to determine whether the sliding is "directional". If the sliding direction is chaotic (sometimes positive, sometimes negative, or obviously oblique), it indicates that the guiding function of the directional sliding trigger unit 3 has failed.

[0097] The timing of the load is an important criterion: if the slippage occurs frequently under loads far below the design trigger value, it indicates that the multifunctional variable interface layer 1 is "too soft" or has too low a coefficient of friction; if the slippage does not occur even under loads far exceeding the trigger value, it indicates that the slippage is "too hard".

[0098] To more clearly describe the specific structural composition of this bearing-controlled creep control device based on variable interface performance, in conjunction with the attached... Figure 1 -Appendix Figure 4 Description of the embodiment: Example 1: Static Multifunctional Variable Interface Layer Based on Checkerboard Gradient Pattern 1 This embodiment addresses the low-speed, heavy-load, relatively stable but impact-prone operating conditions of a 5MW wind turbine main shaft bearing, implementing an interface layer primarily based on passive control and long-term stability.

[0099] 1. Design Inputs and Parameter Determination: Input: Ultimate radial load Bearing dimensions bearing stiffness Allowing stiffness loss Contact fatigue limit of ring material .

[0100] Parameter calculation: Determine the safety factor Triggering stress The maximum contact pressure was calculated based on Hertzian contact theory. .set up , After finite element calibration, the interface coupling coefficient was determined. Based on the design process in Section 3.3, the feasible parameter combinations are calculated by combining formulas (1)-(6): the directional sliding trigger unit 3 must satisfy... The stable anchoring unit 2 must meet the following requirements: .

[0101] Calculate the baseline value for expected slip (for monitoring and judgment): In the formula, the slip efficiency coefficient The proportion of compressive deformation of the directional slip trigger unit 3 converted into tangential slip of the collar, as determined by finite element simulation, is considered. As a monitoring benchmark.

[0102] 2. Interface layer structure and preparation Matrices and gradient construction: A 5mm thick annular composite bushing was prepared. A square checkerboard pattern with a side length of 8mm was formed on its surface using a partitioned molding process.

[0103] Stabilizing anchoring unit 2: Utilizes carbon fiber reinforced polyimide composite material; actual measurement... The surface is textured by micro-blasting, and actual measurements show it can be effectively tested against steel. .

[0104] Directional slip trigger unit 3: Utilizes a high-performance hydrogenated nitrile butadiene rubber (HNBR) blend with resin. Actual measurements... The surface is coated with a PTFE-filled film, as measured in actual tests. .

[0105] Periodic design: setting the number of circumferential partitions The number of bearing rollers 6 They are coprime, satisfying the non-matching criterion.

[0106] Trench network 7 structure implementation: The groove network 7 on the surface of the directional sliding trigger unit 3: Within each directional sliding trigger unit 3, a densely packed mesh groove network 7 with a depth of 0.1 mm and a width of 0.15 mm is laser-processed. The grooves are filled with high-viscosity damping silicone oil (viscosity > 10000 cSt). The groove network 7 density, calculated using the above formula, shows that the number of groove networks 7 on the surface of the directional sliding trigger unit 3 is 8 times that of the stable anchoring unit 2. This design generates high damping and a smooth process during sliding triggering.

[0107] The groove network 7 on the surface of the stabilizing anchoring unit 2: Within each stabilizing anchoring unit 2, an array of micro-pits with a depth of 0.05 mm is machined, and graphite-molybdenum disulfide composite solid lubricant is pre-placed within the pits. This design improves wear resistance while ensuring high-friction anchoring.

[0108] Implementation of collaborative elements: Basic friction interface: A tungsten carbide coating (HVOF) was prepared on the surface of the outer ring 5 of the bearing to obtain a stable and wear-resistant basic friction surface. Actual measurements showed... .

[0109] Interference fit design: Based on the above analysis and calculations, the optimized interference fit between the interface bushing and bearing housing 4 is 0.035mm. This value ensures that the initial prestress is sufficient to improve the system stiffness and anti-fretting ability, while calculations have verified that it will not hinder the directional sliding trigger unit 3 in... The sliding triggers the movement.

[0110] 3. Monitoring System Integration and Operation Process Monitoring System: A reflective optical encoder (accuracy 0.1μm) is installed on the non-load-bearing end face of the bearing outer ring 5, and a reading head is installed on the bearing housing end cover 4 to synchronously acquire the load signal of the fan main control system. Sampling Strategy: Continuous low-speed sampling at 100Hz, and triggering 5kHz high-speed sampling when the displacement change rate exceeds 0.5μm / ms, lasting for 0.5s.

[0111] Slip event recognition: when tangential displacement A step change exceeding 1 μm within 10 ms that stabilizes afterward is identified as a slip event, and the slip amplitude is recorded. Direction angle and trigger load .

[0112] Slip state judgment (design basis: °): Level I (Not Triggered): Load The duration exceeded 30 seconds, but no displacement step was detected. ).

[0113] Level II (Normal Trigger): Load reaches At that time, it appeared The step leap, °, and the displacement is stable after the step jump.

[0114] Level III (Abnormal Trigger): Meets any of the following conditions: ① (3 times the benchmark value); ② °;③ or .

[0115] Operating Process: Under rated wind speed, the system operates stably thanks to the support of the stable anchoring unit 2 and optimized interference fit. When encountering extreme gusts, local raceway stress increases sharply. If the high-stress point is located above the directional slip triggering unit 3, this unit triggers a step-like tangential slip in the raceway under deformation-driven and low-friction conditions. The damping silicone oil within the groove network 7 smooths this process. The monitoring system records slip events, and the stress peak shifts after slippage, preventing the accumulation of localized damage. Long-term operating data shows that this design effectively homogenizes the load and extends bearing life.

[0116] Example 2: Dynamic Active Multifunctional Variable Interface Layer Based on Striped Gradient Pattern 1 This embodiment addresses the working conditions where the spindle bearing of a high-precision test bench needs to frequently withstand varying load spectra and requires active adaptability, by implementing an intelligent interface layer that integrates external control.

[0117] 1. Design Inputs and Parameter Determination: Input: Ultimate radial load Bearing dimensions bearing stiffness Allowing stiffness loss Contact fatigue limit of ring material .

[0118] Parameter calculation: Determine the safety factor Triggering stress The maximum contact pressure was calculated based on Hertzian contact theory. Let f soft =0.4, f hard =0.6, After finite element calibration, the interface coupling coefficient was determined. Based on the design process in Section 3.3, the feasible parameter combinations are calculated by combining formulas (1)-(6): the directional sliding trigger unit 3 must satisfy... The stable anchoring unit 2 must meet the following requirements: .

[0119] Calculate the baseline value for expected slip (for monitoring and judgment): In the formula, the slip efficiency coefficient The proportion of compressive deformation of the directional slip trigger unit 3 converted into tangential slip of the collar, as determined by finite element simulation, is considered. As a monitoring benchmark.

[0120] 2. Interface Layer Structure and Active Control System Matrices and gradient construction: A ring bushing with a thickness of 3 mm was prepared, and its outer surface was covered with alternating soft and hard stripes of equal width (4 mm) in the circumferential direction.

[0121] The two stripes of the stable anchoring unit are made of aluminum bronze-based composite material. Actual measurement... Special surface roughening treatment, actual measurement .

[0122] The directional slip trigger unit has three stripes: the material is a blend of polyetheretherketone (PEEK) and elastomer, as measured in actual measurements. The surface contains lubricating components, as measured. .

[0123] Active control trench network 7 system: Groove network 7 design: A single-headed spiral groove network 7 (groove depth 0.2mm, groove width 0.3mm, pitch 8mm) is machined across the entire bushing surface. The two ends are connected to a media injection valve and an adjustable back pressure valve, respectively. It stores two media: Media A (silica nanoparticle suspension, viscosity 50cSt) and Media B (synthetic oil containing organic molybdenum additives, viscosity 15cSt), and integrates a high-pressure nitrogen injection function (pressure adjustable from 0.1 to 1.0MPa).

[0124] Implementation of collaborative elements: Basic friction interface: The outer surface of the bearing outer ring 5 is laser microtextured and coated with diamond-like carbon (DLC) to obtain... A stable, low-friction benchmark.

[0125] Dynamic interference adjustment: The initial mechanical interference is set to a relatively low value. The effective interference is dynamically adjusted by the medium pressure. When 1.0 MPa nitrogen is introduced, the microscopic expansion of the material of the directional slip trigger unit 3 can offset about 0.005 mm of interference, reducing the effective interference to 0.010 mm and promoting slip triggering.

[0126] 3. Monitoring and Working Process Monitoring system: integrates a grating displacement sensor (accuracy 0.1μm) and a strain gauge load sensor to collect tangential displacement, axial displacement and load in real time. The sampling strategy is the same as in Example 1.

[0127] Slip state judgment (design basis: °): Normal / light load conditions ( (The system is injected with medium A, and the interface layer is in a high-stiffness state. If a displacement of <0.5μm is detected at this time, it is determined to be in normal standby mode.)

[0128] Heavy load warning status ( ): The system switches to inject medium B, preparing to trigger.

[0129] Overload trigger state ( ): The system is injected with medium B and high-pressure nitrogen is introduced (pressure is positively correlated with load). If a displacement step of 4-11 μm (0.8 to 2 times the reference value) is detected. The determination that it was a Level II normal trigger indicates that the active control successfully promoted stress migration.

[0130] Anomaly detection: (3 times the baseline value) is judged as a Level III abnormal trigger (amplitude too large), indicating that the medium pressure is too high or the material of the directional sliding trigger unit 3 is aging.

[0131] like °, determined to be a Level III abnormal trigger (directional disorder), indicating uneven medium distribution or failure of stable anchoring unit 2.

[0132] like If there is still no slippage after 30 seconds, it is determined to be a Level I non-triggered condition, indicating that the medium has not been effectively switched or the control pressure is insufficient.

[0133] Intelligent Operation: The control system makes judgments based on real-time load and displacement signals. During the precision testing phase, the system maintains circulation of medium A, with the interface layer in a high-stiffness state. When the simulated load reaches a heavy-load condition, the system automatically switches to medium B + nitrogen mode, reducing interface friction and intelligently releasing local interference constraints, guiding the raceway to undergo the designed controlled slippage, achieving rapid stress homogenization. After the load decreases, the system switches back to medium A mode, stiffness is restored, and the raceway position is re-anchored. The entire process achieves closed-loop intelligent control through medium switching and pressure regulation, perfectly adapting to complex variable load test spectra.

[0134] It should be noted that although the present invention has been described through the above embodiments, the present invention may have many other embodiments. Without departing from the spirit and scope of the present invention, those skilled in the art can obviously make various corresponding changes and modifications to the present invention, but all such changes and modifications should fall within the scope of protection of the appended claims and their equivalents.

Claims

1. A bearing controlled creep control device based on variable interface performance, arranged between a bearing outer ring (5) and a bearing housing (4), characterized in that, The bearing controlled creep control device is an annular multifunctional variable interface layer (1) with elastic modulus gradient and friction coefficient gradient distributed in circumferential space and covering the entire outer ring (5) of the bearing. The multifunctional variable interface layer (1) is composed of a stable anchoring unit (2) and a directional sliding triggering unit (3) arranged in a periodic staggered pattern along the circumferential contact surface of the bearing outer ring (5). The stable anchoring unit (2) is an integral structure with high elastic modulus and high friction coefficient, and the directional sliding triggering unit (3) is an integral structure with low elastic modulus and low friction coefficient. The number of circumferential partitions N of the multifunctional variable interface layer (1) and the number of rollers (6) of the corresponding bearing are coprime numbers, where the number of circumferential partitions N is the total number of groups of the stable anchoring unit (2) and the directional sliding triggering unit (3). The surface of the multifunctional variable interface layer (1) is provided with a groove network (7) for filling and regulating the mechanical properties of the interface. The outer ring (5) of the bearing and the bearing seat (4) are provided with a friction surface for providing the interference of friction force on the contact surface with the multifunctional variable interface layer (1). The elastic modulus of the directional sliding trigger unit (3) and coefficient of friction It needs to meet the target pressure When the slip critical point is reached, the specific constraint formula is as follows: The elastic modulus of the stable anchoring unit (2) and coefficient of friction It is necessary to ensure that until There is no slippage under all pressures; the specific constraint formula is as follows: in, The interface coupling coefficient is... It is a non-linear exponent and its value range is The elastic modulus of the stabilizing anchoring unit (2) The elastic modulus of the directional sliding trigger unit (3) ratio / ≥3, the coefficient of friction of the stable anchoring unit (2) The coefficient of friction with the directional sliding trigger unit (3) ratio / >

2.

2. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, The macroscopic equivalent elastic modulus in the multifunctional variable interface layer (1) The following constraint formula must be satisfied: In the formula, h is the axial thickness of the multifunctional variable interface layer (1). A c The nominal bearing area of ​​the interface layer. This represents the maximum permissible radial stiffness loss ratio for the bearing system. The system stiffness of the bearing outer ring (5) is given.

3. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, The stabilizing anchoring unit (2) includes any one of diamond-silicon carbide composite material, a carbon-based film integrating strength and lubrication, a molybdenum disulfide reinforced epoxy resin composite material, and a carbon fiber reinforced polyimide composite material; the directional slip triggering unit (3) includes any one of polytetrafluoroethylene modified epoxy resin composite material, hydrogenated nitrile rubber and resin blend material, and a low-friction carbon-based film.

4. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, The groove network (7) is a localized groove with a checkerboard structure or an integral spiral groove with a striped structure; the number of groove networks (7) in a single directional sliding trigger unit (3) The number of trench networks (7) within a single stable anchoring unit (2) The following constraint formula must be satisfied: In the formula, The area ratios of the directional sliding trigger unit (3) and the stable anchoring unit (2) are respectively. The elastic moduli of the directional sliding trigger unit (3) and the stable anchoring unit (2) are respectively. The density enhancement factor of the trench network (7) is 1.5-3.

0.

5. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, The functional medium filled in the groove network (7) is one or more combinations of viscous fluid medium, solid lubricating medium, and compressible gas medium.

6. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, The nominal interference of the friction surface between the multifunctional variable interface layer (1) and the bearing housing (4) for providing friction interference. The following formula constraints must be met: In the formula, This is the prestress reduction factor, which reflects the proportional relationship between the prestress generated by the interference and the deformation required for slip triggering. This refers to the trigger threshold for bearing raceway contact stress. h is the elastic modulus of the directional sliding trigger unit (3), and h is the axial thickness of the multifunctional variable interface layer (1).

7. The bearing controlled creep control device based on variable interface performance according to claim 1, characterized in that, A grating displacement monitoring component for detecting the deformation of the multifunctional variable interface layer (1) is also provided. The grating displacement monitoring component includes a reflective grating ruler fixed to the end face of the bearing outer ring (5) and a reading head fixed to the end cover of the bearing seat (4). The reading head is provided with a tangential displacement monitoring channel and an axial displacement monitoring channel. The grating displacement monitoring component outputs a tangential displacement signal in real time. and axial displacement signal And simultaneously acquire load signals Its normal sampling frequency is 100Hz. When the displacement change rate of the multifunctional variable interface layer (1) exceeds the threshold, high-speed sampling is automatically triggered. Its high-speed sampling frequency is 1kHz to 5kHz. The constraint formula for the displacement threshold of the grating displacement monitoring component is: in The amount of compressive deformation generated in the soft zone when the load reaches the trigger stress.

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