A multi-medium adapted hydrostatic and hydrodynamic pressure coupled fluid bearing assembly, system, rotary machine and method of operation

Abstract

This invention discloses a multi-media adaptable hydrostatic-dynamic coupling fluid suspension bearing assembly, system, rotating machinery, and operating method, belonging to the field of fluid suspension support technology. The bearing assembly includes a bearing body and a bearing housing forming a constant pressure fluid chamber. The working surface has axially arranged annular static pressure grooves and circumferentially distributed helical dynamic pressure grooves. At the intersection of their projections, fluid inlet micro-holes connecting to the constant pressure chamber are provided, forming a distributed matrix throttling network. The fluid inlet micro-holes include three forms: equal-diameter channels, classic Venturi, and simplified Venturi, flexibly adapting to conventional liquids, gas-liquid two-phase flows, and conventional gases. The bearing body has composite sealing components at both ends and an optional cooling system. This invention achieves multi-media compatible support through a unified core geometric framework and a mass-parameter adaptation system. Furthermore, the distributed micro-hole matrix and grid channel topology endow the bearing with parallel fault tolerance and passive flow pattern adjustment capabilities, significantly improving the bearing's adaptability to various operating conditions.

Description

Technical Field

[0001] This invention relates to the field of fluid suspension support technology, specifically to a dynamic-static-pressure coupled fluid suspension bearing assembly, system, rotating machinery, and operating method based on a unified core architecture geometric topology and achieving multi-media compatibility through mass parameter adaptation. Background Technology

[0002] Fluid suspension bearings utilize gas or liquid as a lubricating medium, forming a pressurized fluid film between the bearing and the spindle to achieve non-contact support. They offer significant advantages such as high speed, low friction, and long service life, and are widely used in high-end rotating equipment such as oil-free centrifugal compressors, ultra-precision machine tool spindles, and turbomachinery. Hybrid hydrostatic bearings combine the high precision of hydrostatic bearings with the strong load-bearing capacity of hydrostatic bearings. By optimizing structural parameters, they can effectively improve impact resistance and dynamic stability.

[0003] However, existing technologies still have the following core bottlenecks: First, they have narrow media adaptability. Traditional bearings are mostly designed for single media and lack a unified multi-media adaptability framework. When switching between gas, liquid, or gas-liquid two-phase flow, the stability of the fluid film is difficult to guarantee. Ordinary constant-diameter micropores cannot achieve effective gas-liquid mixing. Furthermore, their dynamic performance is insufficient. The parameters of the dynamic pressure groove and static pressure chamber are fixed, and the correction effect is poor under conditions such as sudden load changes and strong vibrations. Moreover, the sealing structure and support structure are designed independently, making it difficult to balance high rigidity and low leakage.

[0004] In this invention, the term "gas-liquid two-phase flow" refers to a fluid mixture in which the gas phase volume content is not higher than 30%, wherein the continuous phase is liquid and the dispersed phase is gas. Summary of the Invention

[0005] The purpose of this invention is to provide a multi-media adapted hydrostatic pressure coupled fluid suspension bearing assembly, system, rotating machinery, and operating method to solve the problems mentioned in the background art.

[0006] A multi-media adapted dynamic-static-pressure coupled fluid suspension bearing assembly includes: a bearing body, a bearing housing, and a media supply interface;

[0007] The bearing body and bearing housing cooperate to form a constant pressure fluid cavity; the bearing body has a working surface, on which are provided: annular static pressure grooves arranged along the axial direction and spiral dynamic pressure grooves distributed along the circumferential direction; the annular static pressure grooves and spiral dynamic pressure grooves intersect on the projection plane to form a grid-like groove network;

[0008] At the intersection of the projections of the annular static pressure groove and the spiral dynamic pressure groove, a fluid inlet microhole is provided that penetrates the bearing body. The fluid inlet microhole connects the fluid constant pressure chamber and the working surface. Multiple fluid inlet microholes form a distributed matrix throttling network distributed on the working surface.

[0009] The main channel for the fluid introduction micropore is selected from one of the following three structures:

[0010] The main channel of the equal-diameter channel micropore is a channel with an equal diameter.

[0011] A classic Venturi micropore has a constriction section, a throat, and a diffuser section in sequence along the flow direction;

[0012] Simplified Venturi micropores with constricted-isodiameter channels;

[0013] The bearing body is provided with composite sealing components at both ends.

[0014] As a further aspect of the present invention, the inlet end of the fluid introduction micropore is provided with a tapered guide section to reduce fluid introduction resistance.

[0015] As a further aspect of the present invention, it also includes a cooling system; the cooling system is a passive heat dissipation structure, or an internal flow channel integrated into the inner wall of the bearing housing, or an embedded independent module detachably assembled to the bearing housing, or the bearing assembly does not have the cooling system but relies solely on medium convection heat dissipation and body conduction heat dissipation.

[0016] As a further aspect of the present invention: the structural type of the fluid inlet micropore, the helix angle of the spiral dynamic pressure groove, and the number of labyrinth sealing grooves of the composite sealing assembly are all fixed values ​​selected according to the same preset medium type.

[0017] As a further aspect of the present invention: the fixed value selected according to the preset medium type satisfies at least one of the following correspondences:

[0018] When the preset medium type is gas, the fluid inlet micropore is selected from one of simplified Venturi micropore, equal diameter channel micropore and classic Venturi micropore, the helix angle of the spiral dynamic pressure groove is 20°-35°, and the number of labyrinth sealing grooves is 6-12.

[0019] When the preset medium type is liquid, the fluid inlet micropore is selected as equal diameter channel micropore, classic Venturi micropore or simplified Venturi micropore, the helix angle of the spiral dynamic pressure groove is 6°-20°, and the number of labyrinth sealing grooves is 3-8.

[0020] When the preset medium type is gas-liquid two-phase flow, the fluid inlet micropore is selected as a classic Venturi micropore, the helix angle of the spiral dynamic pressure groove is in the range of 15°-25°, and the number of labyrinth sealing grooves is 5-10.

[0021] As a further aspect of the present invention: the working area radius clearance between the bearing body and the mating spindle is set according to a preset medium type: when the medium is gas, a narrower clearance range is used; when the medium is liquid, a wider clearance range greater than the narrower clearance range is used; when the medium is a gas-liquid two-phase flow, a moderate clearance range between the narrower clearance range and the wider clearance range is used.

[0022] As a further aspect of the present invention: the medium supply interface is connected to the fluid constant pressure chamber, and the inlet pressure adjustment range of the fluid constant pressure chamber is 4-16 bar.

[0023] As a further aspect of the present invention: the cross-section of the annular static pressure groove (6) is semi-elliptical or arc-shaped, and the cross-section of the spiral dynamic pressure groove is semi-elliptical or arc-shaped.

[0024] As a further aspect of the present invention: the helix angle range of the spiral dynamic pressure groove is 6°-30°; and when the preset medium type adapted to the bearing assembly is gas, the helix angle range is 20°-35°; when the preset medium type is liquid, the helix angle range is 6°-20°; and when the preset medium type is gas-liquid two-phase flow, the helix angle range is 15°-25°.

[0025] As a further aspect of the present invention: when the preset medium is a liquid and its kinematic viscosity is greater than 1×10⁻³m² / s, the helix angle of the spiral dynamic pressure groove is in the range of 6°-20°, and for every 1×10⁻³m² / s increase in kinematic viscosity, the helix angle is reduced by 1°-3°.

[0026] As a further aspect of the present invention: the composite sealing assembly includes a sealing boss and a labyrinth sealing groove formed on the sealing boss, wherein the protrusion height of the sealing boss is 2-6 μm higher than the working surface; the composite sealing assembly also includes a return groove disposed on the outside of the sealing boss and configured when fluid needs to be recovered, for collecting and guiding the leaked fluid back.

[0027] As a further aspect of the present invention: the number of channels in the labyrinth sealing groove ranges from 3 to 12; and when the preset medium type adapted to the bearing assembly is gas, the number of channels is 6 to 12; when the preset medium type is liquid, the number of channels is 3 to 8; and when the preset medium type is gas-liquid two-phase flow, the number of channels is 5 to 10.

[0028] As a further aspect of the present invention, the surface of the sealing boss is provided with a wear-resistant coating.

[0029] As a further aspect of the present invention, the configuration rule of the cooling system is as follows: when the temperature control accuracy requirement is ≤ ±2℃, the built-in flow channel or the embedded independent module is configured; when the allowable temperature fluctuation is ≥ ±3℃, the cooling system is not set up.

[0030] This invention also discloses a multi-media adapted hydrostatic-hydrostatic coupled fluid suspension bearing system, comprising:

[0031] The aforementioned bearing assembly;

[0032] A graded medium supply module, connected to the medium supply interface, is used to supply the fluid constant pressure chamber with a pressure adjustment range of 4-16 bar and a steady-state fluctuation of ≤±0.5 bar.

[0033] At least one sensor is used to detect bearing operating status parameters, said operating status parameters including at least one of spindle displacement, medium temperature, filtration pressure difference, and gas content;

[0034] The pre-processing module is located in the upstream pipeline of the graded media supply module, including a pre-filtration section with a filtration accuracy of ≤2μm and a pre-temperature control section that controls the initial temperature of the supplied liquid at 15℃~45℃.

[0035] The intelligent control module, which is communicatively connected to the sensor and the graded medium supply module, is used to: receive the operating status parameters; match the corresponding control strategy according to the preset medium type parameters; perform dynamic pressure compensation of the fluid constant pressure chamber to ensure that the compensation pressure does not exceed the range of 4-16 bar; and trigger an impurity cleaning warning when a filtration pressure difference ≥ 0.5 bar is detected.

[0036] Furthermore, the bearing system also includes an extreme condition monitoring unit for monitoring at least one parameter, namely, gas content and vibration acceleration. When the extreme condition monitoring unit detects that the gas content fluctuates by ≥10% within 10 minutes and the gas content reaches 15%-30% after the fluctuation, the intelligent control module activates the pressure fine-tuning mode to temporarily increase the pressure of the fluid constant pressure chamber to no more than 16 bar. If the gas content exceeds 30% after the fluctuation or the duration exceeds 10 minutes, the intelligent control module performs speed reduction or shutdown protection.

[0037] The present invention also discloses a rotating machine comprising the aforementioned bearing assembly or bearing system; the constant pressure fluid chamber of the bearing assembly is connected to the suspension medium supply system of the rotating machine; when the bearing assembly is equipped with the built-in flow channel or embedded independent module, the cooling system is connected to the cooling circuit of the rotating machine.

[0038] This invention also discloses an operating method for a multi-media adapted hydrostatic pressure coupled fluid suspension bearing assembly, applied to the aforementioned bearing assembly, comprising the following steps:

[0039] S1: Select the specific structure of the fluid inlet micropore according to the medium type and operating condition level of the application scenario: for conventional liquid conditions, use the equal-diameter channel micropore, the classic Venturi micropore, or the simplified Venturi micropore; for gas-liquid two-phase flow conditions or extreme conditions, use the classic Venturi micropore; for conventional gas conditions, use the simplified Venturi micropore, the equal-diameter channel micropore, or the classic Venturi micropore.

[0040] S2: Configure the cooling system according to the temperature control accuracy requirements: when the temperature control accuracy is ≤ ±2℃, configure the built-in flow channel or embedded independent module; when the temperature fluctuation is ≥ ±3℃, do not set up the cooling system.

[0041] S3: Set the initial pressure of the fluid constant pressure chamber and configure the pre-filter section (16) and the pre-temperature control section;

[0042] S4: Start the system, monitor operating parameters, and maintain stable operation within the preset normal operating range by relying on the autonomous correction effect of the dynamic-static-pressure coupled flow field of the bearing itself;

[0043] S5: When the load changes abruptly or the gas content of the gas-liquid two-phase flow fluctuates beyond the preset threshold, pressure compensation is initiated through the intelligent control module.

[0044] S6: When shutting down, first reduce the spindle speed to the preset safe range, then reduce the pressure in the constant pressure fluid chamber to 2-3 bar and maintain it for 5-10 minutes before cutting off the medium supply; under extreme conditions, extend the low pressure maintenance to 10-15 minutes. If a cooling channel is provided, the cooling system should continue to run for 15-25 minutes until the medium temperature drops back to 15℃-45℃.

[0045] Compared with the prior art, the beneficial effects of the present invention are:

[0046] This invention constructs a multi-field collaborative core framework consisting of a constant pressure fluid chamber, fluid inlet micro-orifices, an annular static pressure groove and a spiral dynamic pressure groove, and a composite sealing assembly. Based on this framework, a hierarchical design system of "medium type - operating condition level - parameter adaptation" is established. By subdividing the fluid inlet micro-orifices into three structural types—equal diameter channels, classic Venturi, and simplified Venturi—the micro-orifice type can be flexibly selected according to the medium characteristics and operating condition requirements to adapt to conventional liquid, gas-liquid two-phase flow, high-performance, extreme operating conditions, and conventional gas scenarios. Specifically, for conventional liquid operating conditions, equal diameter channels can be used to balance processing economy and low resistance performance, or classic or simplified Venturi structures can be used to further reduce inlet resistance by utilizing the rectifying effect of the Venturi structure. For conventional gas operating conditions, simplified Venturi micro-orifices are used to achieve stable flow in compressible fluids and avoid flow separation in the diffusion section, or equal diameter channels or classic Venturi structures can be used to adapt to different speeds and load requirements. Preferably, a tapered guide section can be provided at the micro-orifice inlet end to further reduce local resistance loss during fluid introduction. By forming a dynamic-static pressure coupling pressure field through the synergistic interaction of dynamic and static pressure grooves, high-rigidity support and inherent self-correcting capability are achieved. Precise leakage control is achieved through the composite structure of sealing bosses and labyrinth sealing grooves, and the coordinated adaptation of channel number and clearance. Three configurable cooling methods—no cooling channel, built-in channel, and embedded module—meet different temperature control accuracies and maintenance requirements. Furthermore, the topological combination of distributed matrix micropores and grid-like flow channels in the core architecture endows the bearing with two inherent passive mechanisms: first, parallel fault tolerance—the parallel pressure supply units formed by numerous micropores transform local failures into statistically smoothed degradation; second, confined passive dispersion—the grid channels apply geometrically forced flow pattern adjustment to heterogeneous clumps. These mechanisms collectively constitute the bearing's structural robustness when facing gas-liquid two-phase flow or working media containing impurities. The same core architecture of this invention can be widely adapted to gas, liquid, and gas-liquid two-phase flow media, covering conventional, high-performance, and extreme operating conditions, significantly improving flow film stiffness, self-correcting capability, and adaptability to extreme conditions. Simultaneously, the modular cooling design balances high-performance temperature control with engineering economy. This invention can be industrially applied in rotating machinery such as oil-free centrifugal compressors, ultra-precision machine tool spindles, turbomachinery, turboexpanders, and process screw compressors.

[0047] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0048] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Furthermore, these drawings and textual descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concepts of this application to those skilled in the art through reference to specific embodiments.

[0049] Figure 1 This is a cross-sectional view of a bearing assembly provided in an embodiment of the present invention.

[0050] Figure 2 A radial cross-sectional view of a bearing provided for an embodiment of the present invention.

[0051] Figure 3 This is a schematic diagram of the structure of the fluid introduction micropore provided in an embodiment of the present invention.

[0052] Figure 4 This is a cooperative energy transfer path diagram provided for an embodiment of the present invention.

[0053] Figure 5 This is a schematic diagram of the gas-liquid two-phase flow mixing effect provided in an embodiment of the present invention.

[0054] Figure 6 This is a schematic diagram illustrating the eccentricity correction principle provided in an embodiment of the present invention.

[0055] Figure 7 This is a schematic diagram of the cooling system provided in an embodiment of the present invention.

[0056] Figure 8 This is a schematic diagram of the sealing assembly provided in an embodiment of the present invention.

[0057] Figure 9 This is a block diagram of intelligent control logic provided for an embodiment of the present invention.

[0058] In the diagram: 1. Bearing body; 2. Spindle; 3. Fluid constant pressure chamber; 5. Composite sealing assembly; 5-1. Sealing boss; 5-2. Labyrinth seal groove; 6. Annular static pressure groove; 7. Spiral dynamic pressure groove; 8. Return groove; 9. Media supply interface; 12. Fluid inlet micropore; 12-1. Equal diameter channel micropore; 12-2. Classic Venturi micropore; 12-3. Simplified Venturi micropore; 13. Bearing housing; 14. Cooling system; 14-1. Built-in flow channel; 14-2. Embedded independent module; 15. Extreme operating condition monitoring unit; 16. Pre-filter section; 17. Pre-temperature control section. Detailed Implementation

[0059] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, examples of which are illustrated in the drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings represent the same or identical elements.

[0060] Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0061] The specific implementation of the present invention will be described in detail below with reference to specific embodiments.

[0062] This invention achieves precise design adaptation for all scenarios, including conventional liquids, conventional gases, gas-liquid two-phase flows, high-performance applications, and even extreme working conditions, through a three-layer design framework consisting of a unified core geometric architecture, a subordinate parameter adaptation layer, and a configurable subordinate component layer. The following four typical embodiments detail the specific implementation of this invention for different application scenarios, such as conventional liquids, high-performance gases, extreme gas-liquid two-phase flows, and high-viscosity special media.

[0063] Example 1: Conventional Liquid Operating Conditions

[0064] This embodiment is applied to a hydraulic drive device or rotating machinery supported by an oil bearing that uses ISOVG32 hydraulic oil as the suspension medium. The diameter of the second journal of the main shaft is 80mm (which is within the conventional main shaft size range of 20-200mm), the rated speed is 12000r / min, the load is stable, and it is a conventional liquid working condition.

[0065] The bearing body 1 is installed inside the bearing housing 13, and the two fit together precisely to form a closed fluid constant pressure chamber 3, which provides a stable pressure foundation for the core structure. The working surface of the bearing body 1 is opposite to the spindle 2. On this surface, multiple annular static pressure grooves 6 are arranged axially, and spiral dynamic pressure grooves 7 are distributed circumferentially. Both have semi-elliptical cross sections, and their projections form an intersection point in space. At the intersection of the projections of the annular static pressure grooves 6 and the spiral dynamic pressure grooves 7, fluid inlet micro-holes penetrating the bearing body 1 are arranged. Multiple fluid inlet micro-holes form a distributed matrix throttling network distributed on the working surface.

[0066] Based on the adaptation logic of conventional liquid operating conditions, this embodiment selects a constant-diameter channel micropore 12-1, whose main channel has a constant-diameter structure. To reduce fluid introduction resistance, the inlet end of the micropore is preferably provided with a tapered guide section to guide the medium smoothly into the micropore and reduce turbulence disturbance. The micropore penetrates through the bearing body 1, with one end connected to the fluid constant pressure chamber 3 and the other end opening at the intersection of the working surfaces. The bearing body 1 has a composite sealing assembly 5 at both ends. This assembly, as the core sealing component, includes a sealing boss 5-1, a labyrinth sealing groove 5-2, and an optional reflux groove 8. In this embodiment, the sealing boss 5-1 is 4μm higher than the working surface, and the surface is coated with DLC coating using a "groove body first + overall spraying" process. According to the characteristics of the liquid medium, the labyrinth sealing groove 5-2 is adapted to have 5 channels and adopts a relatively wide sealing gap. The bearing housing 13 is equipped with a medium supply interface 9 that communicates with the constant pressure fluid chamber 3. An external pipeline includes a pre-filter section 16 and a pre-temperature control section 17. The pre-filter section 16 has a filtration accuracy of ≤2μm, and the pre-temperature control section 17 controls the initial temperature of the supplied liquid at 25℃. In this embodiment, the medium temperature control accuracy requires a temperature fluctuation of ≥±3℃. The pre-temperature control section 17 actively stabilizes the inlet medium temperature, and there is a good heat conduction path between the bearing body and the bearing housing. Therefore, the cooling system 14 adopts a channelless design, i.e., without additional channels, relying on "medium inlet temperature control + medium convection heat dissipation + body conduction heat dissipation" for temperature control.

[0067] Hydraulic oil, after being treated by the pre-filter section 16 and the pre-temperature control section 17 (meeting a filtration accuracy of ≤2μm and an initial temperature of 25℃), enters the constant pressure chamber 3 through the medium supply interface 9, forming a back pressure chamber with a stable pressure base (initial pressure 8 bar). During steady-state operation, pressure fluctuations are controlled within ≤±0.5 bar. Driven by pressure, the hydraulic oil is introduced into the working radius gap between the bearing body 1 and the spindle 2 through the equal-diameter channel micropores 12-1. As the spindle 2 begins to rotate, the hydraulic oil forms a static pressure bearing effect at the annular static pressure groove 6, and simultaneously forms a dynamic pressure effect under the pumping action of the spiral dynamic pressure groove 7. The two superimposed form a dynamic and static pressure coupled pressure field, forming a high-rigidity rotating fluid film. When the spindle 2 is subjected to a momentary load disturbance that causes a slight eccentricity, the pressure distribution of the grid flow field coupling becomes unbalanced, forming a pressure difference on the opposite side of the eccentric direction. This pressure difference pushes the spindle 2 back to the centered position, which is the inherent self-correction function. This mechanism is based on automatic pressure rebalancing of the coupled flow field in the grid domain. Its response speed depends on the characteristic time constant of the fluid film, and it can achieve effective correction at the millisecond level under typical operating conditions. The sealing boss 5-1 of the composite sealing assembly 5 and the labyrinth sealing groove 5-2 work together to effectively constrain the boundary of the fluid film, keeping the leakage at an extremely low level. The leaked fluid can be recovered through the return groove 8. Throughout the operation, heat is mainly dissipated through convective heat transfer of hydraulic oil and thermal conduction of the bearing body 1, with temperature fluctuations maintained within ±3.5℃, meeting the temperature control limit requirement of -10℃ to 60℃.

[0068] The core technical principle of this embodiment lies in the formation of the dynamic-static pressure coupling pressure field and the autonomous correction mechanism of the inherent grid flow field of the core framework. The annular static pressure groove 6 in the grid flow field provides the basic static pressure bearing capacity, the magnitude of which is determined by the pressure of the fluid constant pressure chamber 3; the spiral dynamic pressure groove 7 uses the relative motion generated by the rotation of the main shaft to pump the fluid into the wedge-shaped convergence zone, generating a dynamic pressure effect much higher than the hydraulic pressure supplied. The two are coupled in space, forming a nonlinear superposition of stiffness, and its total stiffness is much higher than that of a single static or dynamic pressure bearing. When the main shaft 2 is eccentric, the grid flow field causes the fluid on the side with smaller gaps to be violently squeezed, and the pressure increases; the dynamic pressure effect on the side with larger gaps weakens, and the pressure decreases. The resulting pressure difference is opposite to the eccentricity direction, constituting a physical, fast-response inherent reset mechanism. The tapered guide section preferably set at the inlet end of the equal-diameter channel micro-hole 12-1 can further reduce the local resistance loss during fluid introduction. CFD simulation prediction shows that its inlet resistance can be reduced by 10%-15% compared with the traditional straight hole. The sealing boss 5-1 is designed to protrude 2-6μm above the working surface. Combined with the DLC coating, it helps reduce friction and wear while ensuring non-contact sealing.

[0069] This embodiment achieves stable support for conventional liquid media through a locked core framework. High spindle rotation accuracy enables millisecond-level rapid response. The design without cooling channels simplifies the system structure, reduces manufacturing costs, and avoids the problems of large space occupation and high cost associated with traditional integrated cooling jackets. The DLC coating and labyrinth groove structure of the composite sealing component 5 ensure long-term wear resistance and sealing reliability, guaranteeing the integrity of the sealing surface. This configuration fully demonstrates the robustness of the core framework of this invention and its engineering economy under normal operating conditions.

[0070] It should be noted that while constant-diameter micropores are preferred under conventional liquid conditions to balance processing economy and low resistance, those skilled in the art can replace the fluid inlet micropores with simplified or classic Venturi micropores according to actual operating requirements. In this case, due to the rectifying effect of the Venturi structure on the liquid boundary layer flow, its inlet resistance can be further reduced compared to constant-diameter channels, but its manufacturing cost increases accordingly. Therefore, as long as it does not deviate from the core concept of this invention—adapting the micropore structure to the medium characteristics to reduce inlet loss—it should be considered to fall within the protection scope of this invention.

[0071] Example 2: Gas Conditions

[0072] This embodiment is applied to an ultra-precision grinding machine spindle that uses nitrogen as the suspension medium. It is a gaseous working condition. The spindle journal diameter is 60mm, the rated speed is as high as 40000r / min, and extremely high rotational accuracy and rigidity are required.

[0073] The core structure formed by the bearing body 1 and the bearing housing 13 is the same as in Embodiment 1. Unlike Embodiment 1, this embodiment uses a simplified Venturi micro-orifice 12-3 for fluid inlet. This micro-orifice adopts a simplified Venturi structure of a contraction-equal diameter tube, which reduces flow resistance while ensuring stable gas inlet, making it suitable for conventional gas conditions. For specific applications (e.g., low-to-medium speed gas conditions), equal diameter channel micro-orifice 12-1 or classic Venturi micro-orifice 12-2 can be selected according to actual operating conditions. The labyrinth sealing groove 5-2 of the composite sealing assembly 5 is adapted to the gas medium characteristics with 10 channels and a narrow sealing gap. The sealing boss 5-1 protrudes 2μm above the working surface. The cross-section of the spiral dynamic pressure groove 7 is semi-elliptical, and its helix angle is adapted to 30° according to the gas medium. Due to the temperature control accuracy requirement of ≤±2℃, the cooling system 14 is configured as a built-in flow channel 14-1, which is integrated into the inner wall of the bearing housing 13, forming a continuous flow channel structure with excellent thermal conductivity. The intelligent control module and extreme condition monitoring unit 15 are integrated into the control system for real-time monitoring and dynamic adjustment of operating parameters. The pre-filter section 16 of the external pipeline has a filtration accuracy of ≤2μm, and the pre-temperature control section 17 precisely controls the initial gas supply temperature at 20℃±0.1℃.

[0074] High-pressure nitrogen gas, after precision filtration and temperature control, enters the constant pressure fluid chamber 3, with an initial pressure set at 8 bar. When the main shaft 2 rotates at an ultra-high speed of 40,000 r / min, the spiral dynamic pressure groove 7 generates a strong dynamic pressure pumping effect in the grid flow field, forming a local negative pressure zone at the micro-hole outlet, actively drawing gas from the constant pressure fluid chamber 3. The supply pressure of the constant pressure chamber, combined with the dynamic pressure suction effect, drives the gas to smoothly enter the working area radius gap through the simplified Venturi micro-holes 12-3. Its simplified Venturi structure avoids the flow separation and pressure fluctuations that may occur in the classic Venturi diffuser section under non-design conditions of compressible gas, achieving a passive flow enhancement effect positively correlated with the rotational speed at high speeds. This enhanced flow, combined with the static pressure effect of the annular static pressure groove 6, forms an extremely high-rigidity gas film. Based on the adaptation logic of ultra-high-speed application scenarios, as the rotational speed increases, the hydrodynamic pressure effect of the fluid increases non-linearly. In this embodiment, the "intelligent control module" simulates the control strategy of "the hydrodynamic pressure groove effect increases with increasing rotational speed, requiring coordinated adjustment of other parameters" by adjusting the air supply pressure and cooling flow rate, thus ensuring the continuity and stability of the gas film at high speeds. The adjustment range does not exceed the basic range of 20°-35° rise angle of the gas medium. The intelligent control module monitors the spindle displacement and temperature in real time and executes closed-loop control of "initial parameter preset - working status monitoring - dynamic multi-field compensation". When a local temperature rise caused by ultra-high-speed operation is detected, the cooling medium flow rate in the built-in flow channel 14-1 is immediately adjusted to accurately control the bearing temperature within the preset range, with a temperature control accuracy of ≤±2℃. At the same time, the intelligent control module also monitors the initial air supply temperature and filter pressure difference. When the filter pressure difference is ≥0.5 bar, the system triggers an impurity cleaning warning. If the warning is not issued within the specified time, the speed will automatically decrease.

[0075] In this embodiment, the simplified Venturi micropores 12-3 are designed for the low viscosity of the gas medium, avoiding pressure fluctuations and backflow that may be caused by the diffusion section in the classic Venturi structure. This achieves the lowest flow resistance while ensuring the uniformity of the introduced airflow. CFD simulations show that compared to complex structures, its gas introduction efficiency can be improved by more than 20%. Secondly, optimizing the helix angle of the spiral dynamic pressure groove 7 at ultra-high speed is crucial. An excessively large helix angle leads to a sharp increase in flow resistance and temperature rise, while an excessively small helix angle results in insufficient dynamic pressure effect. The intelligent control in this embodiment achieves nonlinear dynamic matching between the helix angle and rotational speed, working in conjunction with pressure compensation in the fluid constant pressure chamber and temperature control in the cooling system to ensure support stiffness and operational stability at ultra-high speeds. Finally, the precise temperature control of the built-in flow channel 14-1 eliminates the negative impact of thermal deformation on the spindle accuracy, achieving synergy between the mechanical field, flow field, and temperature field. Although the extreme condition monitoring unit 15 is not activated under these conventional high-performance conditions, it provides a monitoring basis for potential dynamic fluctuations.

[0076] This embodiment effectively suppresses spindle rotation errors under high-speed operating conditions, meeting the stringent requirements of ultra-precision machining for spindle rotation accuracy. The simplified Venturi micro-orifice optimizes the balance between flow resistance and stability for gas media. The combination of built-in flow channel 14-1 and intelligent control keeps temperature fluctuations within ±2℃, effectively suppressing thermal deformation errors. The early warning and protection mechanisms of the intelligent control module enhance system reliability. This configuration fully demonstrates the invention's ability to unleash the core architecture's potential through dynamic parameter adaptation in high-performance gas scenarios.

[0077] Example 3: Extreme Gas-Liquid Two-Phase Flow Conditions

[0078] This embodiment applies to a process screw compressor in the petrochemical field. The working medium is an oil-gas two-phase flow (with oil as the continuous phase and hydrocarbon gas as the dispersed phase). The diameter of the main shaft journal 2 is 150mm, and the rotation speed is 6000r / min. During the process, the gas content of the medium may rise sharply from 5% to 25% in a short time (≤10 minutes), which is an extreme working condition.

[0079] The core architecture remains unchanged. The fluid inlet micropores utilize classic Venturi micropores 12-2, whose standard Venturi structure is crucial for handling gas-liquid two-phase flow. The labyrinth sealing grooves 5-2 of the composite sealing assembly 5 are adapted to the characteristics of the gas-liquid two-phase flow medium, with an additional groove (9 grooves in total) added for extreme conditions, employing moderate gaps. The spiral dynamic pressure groove 7 has a preset rise angle of 20°, suitable for gas-liquid two-phase flow dominated by the liquid phase. The cooling system 14 is configured with an internal flow channel 14-1. The system integrates an extreme condition monitoring unit 15 for real-time monitoring of key fluctuation parameters such as gas content and vibration acceleration. The pre-filter section 16 of the external pipeline has a filtration accuracy ≤2μm, and the pre-temperature control section 17 controls the initial liquid supply temperature at 30℃.

[0080] The oil-gas two-phase mixture enters the constant pressure fluid chamber 3 via the supply system, with the initial pressure set at 10 bar. When the extreme condition monitoring unit 15 detects that the gas content rapidly increases from 5% to 25% within 10 minutes (gas content fluctuation ≥10%), and the gas content after the fluctuation reaches the range of 15%-30%, lasts for ≤10 minutes, and the spindle speed 2 is ≤15000 r / min, the intelligent control module is immediately triggered to start the pressure fine-tuning mode. This mode first temporarily increases the pressure in the constant pressure fluid chamber 3 from the usual 10 bar to 16 bar (within the range of 4-16 bar) to compensate for the decrease in fluid film stiffness caused by the increase in gas content; at the same time, the dynamic pressure effect is enhanced by adjusting the medium temperature or cooling flow rate.

[0081] Driven by pressure, the oil-gas mixture flows through classical Venturi micropores 12-2. The Venturi structure of the micropores generates high-speed flow and pressure changes at the throat, breaking the gas phase into tiny bubbles and dispersing them in the liquid phase. This active mechanism simultaneously couples with two inherent passive mechanisms of the core architecture:

[0082] Firstly, the confined passive dispersion of the grid-like channel system. As air masses pass through the intersecting network of dynamic and static pressure channels, they are repeatedly subjected to geometric compression, stretching, and cutting, passively splitting into smaller bubble-like flows driven by surface tension instability. This initial flow pattern adjustment is completed before entering the bearing gaps. This process is enforced by the channel topology and does not depend on high flow velocities.

[0083] Secondly, the distributed matrix micropores provide parallel fault tolerance. A large number of micropores form parallel pressure supply units at the grid intersection. When local gas phase accumulation causes the function of individual micropores to be momentarily limited, the surrounding micropores still maintain full-function pressure supply. The load-bearing capacity only undergoes a smooth decay, avoiding the risk of global instability caused by single-point failure in centralized pressure supply schemes.

[0084] The aforementioned passive mechanism, combined with the active breaking capability of the classic Venturi micropores and the intelligent control of pressure dynamic compensation, can effectively maintain the continuity and stiffness of the fluid film within the range of gas content fluctuations, and significantly expand the bearing's tolerance to gas-liquid two-phase flow.

[0085] After being processed by the aforementioned active and passive mechanisms, the microbubbles enter the dynamic and static pressure channel network with the fluid. The annular static pressure channel provides an axial pressure equalization channel, making the circumferential pressure distribution more uniform; the spiral dynamic pressure channel generates circumferential pumping flow, driving the microbubbles to move continuously with the mainstream, preventing them from stagnating and accumulating in local low-pressure areas. The intelligent control module synchronously monitors the filtration pressure difference, triggering an impurity cleaning warning when the pressure difference is ≥0.5 bar. If the gas content fluctuation exceeds the timeout or the gas content exceeds the extreme temporary limit of 30% after the fluctuation, the system will issue a warning and reduce the speed. If the speed reduction still exceeds 5 minutes, a shutdown protection will be implemented.

[0086] It is particularly important to note that when using classic Venturi micropores in gas-liquid two-phase flow conditions, while the throat acceleration effect enhances gas-phase fragmentation, it also carries the potential risk of cavitation. When the throat static pressure drops below the saturated vapor pressure of the medium due to excessively high flow velocity, cavitation bubbles may be generated, and their collapse in the diffusion section will cause cavitation damage to the micropore wall. Therefore, in the actual engineering implementation of this embodiment, the throat diameter and diffusion section angle of the Venturi micropores should be optimized hydrodynamically based on the specific properties of the medium (saturated vapor pressure, surface tension) and preset operating conditions (pressure supply range, upper limit of gas content fluctuation) to ensure that the minimum throat static pressure is higher than the saturated vapor pressure of the medium, or an anti-cavitation coating or material (such as diamond-like carbon coating, ceramicized layer) should be selected to ensure long-term operational reliability.

[0087] The key principle of this embodiment lies in the synergy of four mechanisms: "Venturi-enhanced mixing," "confined passive dispersion in the grid-like channel," "parallel fault tolerance of the distributed matrix micropores," and "dynamic pressure compensation." If the gas-liquid two-phase flow cannot be uniformly mixed before entering the bearing clearance, the gas phase easily coalesces to form large bubbles, leading to localized rupture of the flow film and the risk of bearing seizure. The classic Venturi micropores 12-2 utilize fluid dynamics principles to generate high shear force at the throat, dispersing the gas phase and achieving uniform mixing at the active level. The confined passive dispersion in the grid-like channel provides geometric adjustment of the flow pattern independent of flow velocity. The parallel fault tolerance of the distributed matrix micropores ensures that local gas phase aggregation does not diffuse into global instability. Furthermore, a sudden increase in gas content means a decrease in the effective viscosity of the fluid, resulting in a reduction in flow film stiffness. At this point, rapidly increasing the pressure in the constant pressure chamber can instantly increase the static pressure contribution, compensating for the stiffness loss caused by the decrease in viscosity, thereby maintaining the overall stiffness. These four mechanisms are indispensable and collectively ensure survivability under extreme operating conditions.

[0088] This embodiment enables the compressor to operate safely and stably under harsh process conditions with significant fluctuations in gas holdup in the gas-liquid two-phase flow, avoiding equipment damage and unplanned downtime caused by film rupture. The gas-liquid mixing effect of classic Venturi micro-orifices is significantly superior to that of traditional constant-diameter orifices; CFD simulations predict that film stability can be improved by more than 25%. The pressure compensation mechanism under extreme conditions effectively maintains film stiffness, and specialized early warning and shutdown logic ensure equipment safety when limits are exceeded. This configuration fully demonstrates the invention's specialized adaptability to extreme conditions.

[0089] Example 4: Extreme Heavy Load Conditions for High-Viscosity Special Media

[0090] This embodiment is applied to a low-temperature turbo expander, which uses high-viscosity synthetic refrigeration oil (kinematic viscosity of about 5×10⁻³m² / s) as the suspension medium. The main shaft has a journal diameter of 100mm, a rotation speed of 30000r / min, and the load often changes abruptly (≥50%). It belongs to a special medium and extreme heavy load conditions.

[0091] The core architecture remains unchanged. The fluid inlet micropores utilize the classic Venturi micropore 12-2 design, but with a diameter appropriately increased compared to conventional liquid conditions. For the high-viscosity special medium of 5×10⁻³m² / s, a graded adaptation is required: the helix angle of the spiral dynamic pressure tank 7 is adjusted from the base helix angle of the liquid medium (within the 6°-20° range, taking the midpoint 15°) according to the rule of "decreasing the helix angle by 1°-3° for every 1×10⁻³m² / s increase in kinematic viscosity," ultimately preset to 8°. This low helix angle design effectively reduces the flow resistance of the high-viscosity fluid within the dynamic pressure tank, preventing overheating. The initial pressure of the fluid constant pressure chamber 3 follows the same rule, i.e., "decreasing by 0.5-2 bar for every 1×10⁻³m² / s increase in viscosity," decreasing from 8 bar for conventional liquids to 4 bar (still within the 4-16 bar range). This avoids a surge in power consumption caused by excessive shear force generated by the high-viscosity medium within a narrow gap. The labyrinth seal grooves 5-2 of the composite sealing assembly 5 are adapted to have 7 channels, with appropriately widened gaps. The cooling system 14 is configured with built-in flow channels 14-1 and is preset with a higher cooling medium flow rate to meet the heat dissipation requirements of special media.

[0092] High-viscosity refrigeration oil enters the constant pressure fluid chamber 3 after pre-filtration and temperature control, with an initial pressure of 4 bar. Due to the appropriately increased micropore diameter, the high-viscosity oil smoothly passes through the classic Venturi micropores 12-2 into the working area radius gap. The spindle 2 starts and accelerates to 30,000 r / min. Because the helix angle of the spiral dynamic pressure groove 7 has been optimized to 8°, the flow resistance of the high-viscosity oil within the groove is significantly reduced, avoiding excessive heat generated by excessive shearing. When a sudden load change occurs, the intelligent control module responds quickly, adding a compensation increment to the 4 bar base pressure. This, combined with the dynamic pressure effect generated by the low-helix-angle spiral dynamic pressure groove 7, jointly resists external impacts. Simultaneously, the cooling medium flow rate of the built-in flow channel 14-1 automatically increases, maintaining the bearing operating temperature within a safe range and ensuring that the oil viscosity does not drop excessively, maintaining a temperature control accuracy of ≤±2℃. If extreme heavy-load conditions persist for a long time, the intelligent control module can also activate pressure compensation to enhance the dynamic pressure effect and work in conjunction with the cooling system to achieve a closed-loop stiffness enhancement.

[0093] High-viscosity media mean that the fluid will generate huge shear forces when flowing in narrow gaps, leading to a surge in power consumption and temperature rise. Therefore, all parameters related to the flow must be adjusted in a coordinated manner: reducing the helical dynamic pressure channel helix angle to reduce flow resistance; reducing the pressure in the constant pressure chamber to reduce the shear power consumption in the static pressure chamber; and increasing the micro-orifice diameter to reduce the introduction resistance. This "resistance reduction" design is fundamental. On top of this, when encountering heavy load impacts, dynamic pressure compensation is used to temporarily increase the load-bearing capacity. This compensation pressure is not maintained indefinitely, thus achieving a dynamic balance between low power consumption and high load-bearing capacity. The strengthening of the cooling channels is to remove the unavoidable residual shear heat in time and maintain the stability of the oil viscosity. This entire adaptation logic strictly follows the graded adaptation rules for special media and integrates the pressure and temperature compensation algorithms of the intelligent control system.

[0094] This embodiment successfully achieved stable suspension support for high-viscosity special media under extreme heavy-load conditions. Through the coordinated adaptation of helix angle, constant pressure chamber pressure, and micropore diameter, the shear power consumption and temperature rise of the high-viscosity fluid were effectively controlled. The dynamic pressure compensation mechanism endowed the system with the ability to withstand sudden heavy-load impacts, significantly improving the operational stability and safety of the turbine machinery. Enhanced heat dissipation through built-in flow channels ensured the stability of the oil film temperature field, preventing thermal runaway. This configuration fully demonstrates the complete layered design concept of this invention, from the core architecture to the subordinate parameter adaptation layer, configurable component layer, and subordinate function optimization layer, achieving comprehensive coverage of the most complex operating conditions.

[0095] The above four embodiments demonstrate the precise adaptability of the present invention from different dimensions. To ensure the complete disclosure of the technical solution, the general technical features, supporting systems and implementation safeguards throughout all embodiments are described below. The medium supply interface (9) provided on the bearing housing (13) is connected to the external graded medium supply module at the system level. The graded medium supply module stably delivers the fluid medium with a pressure adjustment range of 4-16 bar and steady-state fluctuation ≤ ±0.5 bar to the fluid constant pressure chamber (3) through the medium supply interface (9), providing the bearing assembly with a fluid medium source with a predetermined pressure.

[0096] 1. Multi-field synergistic effect of the core architecture

[0097] In all embodiments, the energy transfer path follows a unified logic: the constant-pressure fluid enters the constant-pressure fluid chamber 3 after passing through the pre-filter section 16 and the pre-temperature control section 17; under the condition of main shaft rotation, the dynamic pressure pumping effect of the spiral dynamic pressure groove forms a local negative pressure in the micro-hole outlet region, actively drawing the medium in the constant-pressure chamber, which, combined with the supply pressure, forms an enhanced flow; the fluid is introduced into the working area radius gap through the selected fluid inlet micro-hole 12; the annular static pressure groove 6 and the spiral dynamic pressure groove intersect to form a gridded channel network, constituting a dynamic-static pressure coupled flow field. This gridded channel network and the distributed matrix micro-holes, as the irreducible skeleton of the core structure, endow the flow field with the following inherent functional characteristics: First, dynamic-static pressure coupled pressure field and autonomous correction. The annular static pressure groove and the spiral dynamic pressure groove form an internally coupled pressure gain through the micro-hole pressure supply at the grid intersection point. When the main shaft is eccentric, a restoring torque opposite to the eccentric direction is generated, realizing physical autonomous correction. Second, parallel fault tolerance and pressure homogenization of the distributed matrix micro-holes. Numerous micropores form parallel pressure supply units at grid intersections, transforming the risk of single-point failure into a statistically smoothed degradation, while simultaneously smoothing the pressure field spatially and eliminating pressure gradient singularities. Thirdly, the grid-based flow domain channels provide confined passive dispersion. The three-dimensional confined topology formed by the cross-network of dynamic and static pressure channels applies repeated geometric compression, stretching, and cutting to the heterogeneous clumps, enabling them to passively adjust their flow pattern before entering the load-bearing gap. The composite sealing component 5 constrains the flow field boundary, and leaked fluid is recovered via the return channel 8 or directly discharged. Under extreme conditions, the pressure in the constant pressure chamber 3 is dynamically adjusted by an intelligent control system, forming a stiffness-enhancing closed loop with the aforementioned inherent functions. Its mathematical model employs the Reynolds equation with coupled energy equations, combines the gas-liquid two-phase flow with the VOF model, and uses a sequential coupling method for multi-field coordination; dynamic load correction coefficients are introduced for extreme conditions to optimize simulation accuracy.

[0098] 2. Supporting Systems and Intelligent Control

[0099] All embodiments rely on a graded media supply module and an intelligent control module. The pressure adjustment range of the graded media supply module is 4-16 bar (temporary upper limit of 16 bar after compensation), with steady-state fluctuation ≤ ±0.5 bar, liquid supply filtration accuracy ≤ 2 μm, and initial liquid supply temperature 15℃-45℃; the pressure response speed under extreme conditions is improved by more than 30%. The intelligent control module executes closed-loop control of "initial parameter preset - working status monitoring - dynamic multi-field compensation" to realize the adaptation determination of the fluid inlet micro-hole 12 structure and the configuration of the cooling system 14, spindle 2 eccentric auxiliary correction, temperature compensation, and extreme condition special control, while simultaneously monitoring parameters such as initial liquid supply temperature and filtration pressure difference. The auxiliary correction function, as a supplement to the autonomous correction, is activated when the eccentricity exceeds the autonomous correction range: the displacement sensor collects eccentricity data, and the control module finely adjusts the pressure of the constant pressure chamber 3 according to the eccentricity range to form a pressure difference to assist in reset, working in conjunction with the autonomous correction.

[0100] 3. Process Implementation of Composite Sealing Components and Cooling System

[0101] The preferred process for the composite sealing component 5 is either "machining the tank first + overall spraying" or "substrate sinking - overall spraying" to apply the DLC coating. The steps include: machining the boss substrate to ensure height and flatness; machining the tank to create the labyrinth sealing groove 5-2 and the return groove 8; applying the DLC coating overall to achieve the required thickness; precision grinding to ensure the roughness of the boss's top surface; and annealing to release residual stress and extend the insulation time for products adapted to extreme conditions.

[0102] The cooling system 14 is manufactured and assembled as follows: There are no cooling channels, only ensuring good thermal conductivity of the bearing body; the built-in channel 14-1 is a continuous channel integrally machined on the inner wall of the bearing housing 13, with a smooth channel wall and a reasonably controlled gap with the fluid constant pressure chamber 3; the embedded independent module 14-2 has its body and channel machined separately, with the module interface precisely matched to the dedicated interface of the bearing housing 13, secured with bolts for easy disassembly and maintenance. After assembly, flow rate and temperature control accuracy are tested to ensure that design requirements are met.

[0103] To achieve the micrometer-level precision of the mesh channels and matrix micro-holes in the aforementioned core architecture, one or a combination of the following ultra-precision machining processes can be employed, but is not limited to: femtosecond laser direct writing, micro-electrical discharge machining, photolithography-electroforming-injection molding, or ultra-precision micro-drilling. To ensure geometric consistency of the matrix micro-holes during batch processing, a quality control strategy combining on-machine measurement or offline coordinate measuring machine / white light interferometry sampling is recommended. The selection of the specific machining methods described above falls within the scope of conventional engineering decisions made by those skilled in the art after becoming familiar with the architecture of this invention.

[0104] 4. Performance Verification and Scenario Constraints

[0105] All performance indicators of this invention are based on specific scenario constraints. The core performance indicator scenario constraints are based on a spindle journal diameter of 20-200mm and a kinematic viscosity of 0.1×10⁻⁻⁻⁶. 6 The basic boundary settings are -10×10⁻³m² / s and working pressure 4-16 bar. Extreme operating condition constraints include: load sudden change ≥50%, start-stop ≥3 times / hour, gas content fluctuation ≥10% / 10 minutes (≤30% after fluctuation), and medium temperature ≥60℃ or ≤-10℃. Medium compatibility constraints are: for gas-liquid two-phase flow, the normal gas content is ≤15%, and for extreme temporary conditions, it is ≤30% for a duration ≤10 minutes; oil is preferred as the continuous phase, and gas as the dispersed phase. Cooling system compatibility constraints are: for temperature control accuracy ≤±2℃, built-in flow channels are preferred; for ease of maintenance, embedded modules are preferred; and for temperature fluctuations ≥±3℃, no cooling flow channels are preferred.

[0106] Theoretical analysis and performance prediction are based on the Reynolds equation with coupled energy equations, the VOF model for gas-liquid two-phase flow, and a sequential coupling method using multi-field synergy, employing finite element / finite volume method three-dimensional simulation. CFD simulation prediction results under specific operating conditions show that the gas-liquid mixing uniformity of the classic Venturi micro-orifice 12-2 is more than 25% higher than that of the traditional capillary structure; the inlet resistance of the constant-diameter channel micro-orifice 12-1 can be reduced by 10%-15% under conventional liquid conditions (when a tapered guide section is provided at the inlet end); and the introduction efficiency of the simplified Venturi micro-orifice 12-3 can be improved by 15%-20% under conventional gas conditions. It should be noted that the performance gain achievable by the actual product will depend on engineering factors such as manufacturing precision, assembly tolerances, media cleanliness, and actual operating conditions. This invention reserves the right to calibrate the above simulation model using experimental data and optimize design parameters based on the calibrated model.

[0107] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within the present invention.

[0108] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A multi-media adapted hydrostatic-hydrostatic coupled fluid suspension bearing assembly, characterized in that, include: Bearing body (1), bearing housing (13) and media supply interface (9). The bearing body (1) and the bearing seat (13) cooperate to form a fluid constant pressure cavity (3); the bearing body (1) has a working surface, on which are provided: annular static pressure grooves (6) arranged along the axial direction and spiral dynamic pressure grooves (7) distributed along the circumferential direction; the annular static pressure grooves (6) and spiral dynamic pressure grooves (7) intersect on the projection plane to form a grid-like groove network; At the intersection of the projections of the annular static pressure groove (6) and the spiral dynamic pressure groove (7), a fluid inlet microhole (12) is provided that penetrates the bearing body (1). The fluid inlet microhole (12) connects the fluid constant pressure chamber (3) and the working surface. Multiple fluid inlet microholes form a distributed matrix throttling network distributed on the working surface. The main channel of the fluid inlet micropore (12) is selected from one of the following three structures: The micropore with equal diameter channel (12-1) has a main channel with equal diameter. The classic Venturi micropore (12-2) has a constriction section, a throat, and a diffuser section in sequence along the flow direction; Simplified Venturi micropores (12-3) with constricted-isodiameter channels; The bearing body (1) is provided with composite sealing components (5) at both ends.

2. The bearing assembly according to claim 1, characterized in that, The inlet end of the fluid inlet micropore (12) is provided with a tapered guide section to reduce fluid inlet resistance.

3. The bearing assembly according to claim 1, characterized in that, It also includes a cooling system (14); the cooling system (14) is a passive heat dissipation structure, or an internal flow channel (14-1) integrated into the inner wall of the bearing housing (13), or an embedded independent module (14-2) detachably assembled to the bearing housing (13), or the bearing assembly does not have the cooling system (14) but relies solely on medium convection heat dissipation and body conduction heat dissipation.

4. The bearing assembly according to claim 1, characterized in that, The structure type of the fluid inlet micropore (12), the helix angle of the spiral dynamic pressure groove (7), and the number of labyrinth sealing grooves of the composite sealing assembly (5) are all fixed values ​​selected according to the same preset medium type.

5. The bearing assembly according to claim 4, characterized in that, The fixed value selected based on the preset media type satisfies at least one of the following correspondences: When the preset medium type is gas, the fluid inlet micropore (12) is selected from one of the simplified Venturi micropore (12-3), the equal diameter channel micropore (12-1), and the classic Venturi micropore (12-2), the helix angle of the spiral dynamic pressure groove (7) is 20°-35°, and the number of labyrinth sealing grooves is 6-12. When the preset medium type is liquid, the fluid inlet microhole (12) is selected as equal diameter channel microhole (12-1), classic Venturi microhole (12-2) or simplified Venturi microhole (12-3), the helix angle range of the spiral dynamic pressure groove (7) is 6°-20°, and the number of labyrinth sealing grooves is 3-8. When the preset medium type is gas-liquid two-phase flow, the fluid inlet micro-hole (12) is selected as the classic Venturi micro-hole (12-2), the helix angle of the spiral dynamic pressure groove (7) is 15°-25°, and the number of labyrinth sealing grooves is 5-10.

6. The bearing assembly according to claim 1, characterized in that, The medium supply interface (9) is connected to the fluid constant pressure chamber (3), and the inlet pressure adjustment range of the fluid constant pressure chamber (3) is 4-16 bar.

7. The bearing assembly according to claim 1, characterized in that, The cross-section of the annular static pressure groove (6) is semi-elliptical or arc-shaped, and the cross-section of the spiral dynamic pressure groove (7) is semi-elliptical or arc-shaped.

8. The bearing assembly according to claim 1, characterized in that, The helix angle range of the spiral dynamic pressure groove (7) is 6°-30°; and when the preset medium type adapted to the bearing assembly is gas, the helix angle range is 20°-35°; when the preset medium type is liquid, the helix angle range is 6°-20°; when the preset medium type is gas-liquid two-phase flow, the helix angle range is 15°-25°.

9. The bearing assembly according to claim 8, characterized in that, When the preset medium is a liquid and its kinematic viscosity is greater than 1×10⁻³m² / s, the helix angle of the spiral dynamic pressure groove (7) is in the range of 6°-20°, and the helix angle is reduced by 1°-3° for every 1×10⁻³m² / s increase in kinematic viscosity.

10. The bearing assembly according to claim 1, characterized in that, The composite sealing assembly (5) includes a sealing boss (5-1) and a labyrinth sealing groove (5-2) formed on the sealing boss (5-1). The protrusion height of the sealing boss (5-1) is 2-6 μm higher than the working surface. The composite sealing assembly (5) also includes a return groove (8) disposed on the outside of the sealing boss (5-1) and configured when fluid needs to be recovered, for collecting and guiding the leakage fluid back.

11. The bearing assembly according to claim 10, characterized in that, The number of channels in the labyrinth sealing groove (5-2) ranges from 3 to 12; and when the preset medium type adapted to the bearing assembly is gas, the number of channels is 6 to 12; when the preset medium type is liquid, the number of channels is 3 to 8; and when the preset medium type is gas-liquid two-phase flow, the number of channels is 5 to 10.

12. The bearing assembly according to claim 10, characterized in that, The surface of the sealing boss (5-1) is provided with a wear-resistant coating.

13. The bearing assembly according to claim 3, characterized in that, The configuration rules for the cooling system (14) are as follows: when the temperature control accuracy requirement is ≤ ±2℃, the built-in flow channel (14-1) or the embedded independent module (14-2) is configured; when the allowable temperature fluctuation is ≥ ±3℃, the cooling system (14) is not set up.

14. A multi-media adapted hydrostatic-hydrostatic coupling fluid suspension bearing system, characterized in that, include: The bearing assembly according to any one of claims 1-13; A graded medium supply module is connected to the medium supply interface (9) and is used to supply the fluid constant pressure chamber (3) with a pressure adjustment range of 4-16 bar and a steady-state fluctuation of ≤±0.5 bar. At least one sensor is used to detect bearing operating status parameters, said operating status parameters including at least one of spindle displacement, medium temperature, filtration pressure difference, and gas content; The pre-processing module is located in the upstream pipeline of the graded media supply module, including a pre-filtration section (16) with a filtration accuracy of ≤2μm and a pre-temperature control section (17) that controls the initial temperature of the supply liquid at 15℃~45℃. The intelligent control module is connected in communication with the sensor and the graded medium supply module, and is used to: receive the operating status parameters; match the corresponding control strategy according to the preset medium type parameters; perform dynamic pressure compensation of the fluid constant pressure chamber (3) so that the compensation pressure does not exceed the range of 4-16 bar; and trigger impurity cleaning warning when the filter pressure difference is detected to be ≥0.5 bar.

15. The bearing system according to claim 14, characterized in that, It also includes an extreme condition monitoring unit (15) for monitoring at least one parameter among gas content and vibration acceleration; when the extreme condition monitoring unit (15) detects that the gas content fluctuates by ≥10% within 10 minutes and the gas content reaches 15%-30% after the fluctuation, the intelligent control module starts the pressure fine-tuning mode to temporarily increase the pressure of the fluid constant pressure chamber (3) to no more than 16 bar; if the gas content exceeds 30% after the fluctuation or the duration exceeds 10 minutes, the intelligent control module performs speed reduction or shutdown protection.

16. A rotating machine, characterized in that, The bearing assembly comprises any one of claims 1-13 or the bearing system according to claim 14 or 15; the constant pressure chamber (3) of the bearing assembly is connected to the suspension medium supply system of the rotating machinery; when the bearing assembly is configured with the built-in flow channel (14-1) or the embedded independent module (14-2), the cooling system (14) is connected to the cooling circuit of the rotating machinery.

17. A method for operating a multi-media adapted hydrostatic pressure coupled fluid suspension bearing assembly, applied to the bearing assembly according to any one of claims 1-13, characterized in that, Includes the following steps: S1: Select the specific structure of the fluid inlet micropore (12) according to the medium type and operating condition level of the application scenario: for conventional liquid conditions, select the equal diameter channel micropore (12-1), the classic Venturi micropore (12-2), or the simplified Venturi micropore (12-3); for gas-liquid two-phase flow conditions or extreme conditions, select the classic Venturi micropore (12-2); for conventional gas conditions, select the simplified Venturi micropore (12-3), the equal diameter channel micropore (12-1), or the classic Venturi micropore (12-2). S2: Configure the cooling system (14) according to the temperature control accuracy requirements: when the temperature control accuracy is ≤ ±2℃, configure the built-in flow channel (14-1) or the embedded independent module (14-2); when the temperature fluctuation is ≥ ±3℃, do not set up the cooling system (14). S3: Set the initial pressure of the fluid constant pressure chamber (3) and configure the pre-filter section (16) and the pre-temperature control section (17). S4: Start the system, monitor operating parameters, and maintain stable operation within the preset normal operating range by relying on the autonomous correction effect of the dynamic-static-pressure coupled flow field of the bearing itself; S5: When the load changes abruptly or the gas content of the gas-liquid two-phase flow fluctuates beyond the preset threshold, pressure compensation is initiated through the intelligent control module. S6: When shutting down, first reduce the spindle speed to the preset safe range, then reduce the pressure of the fluid constant pressure chamber (3) to 2-3 bar and maintain it for 5-10 minutes before cutting off the medium supply; under extreme conditions, extend the low pressure to 10-15 minutes, and if a cooling channel is provided, the cooling system continues to run for 15-25 minutes until the medium temperature drops to 15℃-45℃.

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