An independent pressure and temperature controlled hydrostatic sliding bearing

Abstract

This invention discloses an independently controlled pressure and temperature hydrostatic sliding bearing, comprising a coaxially mating stationary ring and a moving ring. All hydraulic systems are integrated into the stationary ring. The stationary and moving rings can be segmented or integrally formed, adaptable to all sizes and scenarios, from large-diameter heavy-duty applications to small-diameter ultra-precision and micro-high-speed light-duty applications. This invention employs an independent pressure control circuit with a high-pressure end branched, same-source, different-pressure oil supply design, achieving complete decoupling of pressure and temperature control circuits from a single hydraulic source; single-chamber, one-to-one millisecond-level independent closed-loop pressure and temperature control; innovatively adopting a fully oil-immersed, seal-free fusion design, enabling integrated integration of the bearing and power components; and offering multiple options for high-performance composite materials to meet material requirements under all operating conditions. Its dimensions are 1:1 perfectly aligned with existing rolling bearings of the same specifications, allowing for direct and universal replacement. It is suitable for wind turbines, ships, heavy equipment, high-precision military equipment, semiconductors, medical equipment, aerospace, micro-high-speed power units, and other fields.

Description

Technical Field

[0001] This invention belongs to the field of sliding bearing technology, specifically relating to an independent pressure-controlled and temperature-controlled hydrostatic sliding bearing. It is suitable for all scenarios of heavy-duty and precision slewing bearings, including large-diameter slewing bearings of heavy equipment such as yaw and pitch bearings of wind turbines, ship shafting, tunnel boring machines, large rotary kilns, port cranes, and heavy CNC machine tools; medium and small-diameter heavy-duty high-precision slewing scenarios such as vehicle-mounted radar, tank turrets, engineering machinery, and lifting equipment; and small-diameter ultra-precision slewing bearings in fields such as semiconductor manufacturing, high-end medical devices, aerospace, optical instruments, and micro high-speed power units. Background Technology

[0002] As industrial equipment develops towards larger, heavier, more precise, and miniaturized high-speed applications, various types of equipment place stringent demands on the load-bearing capacity, service life, operational accuracy, thermal stability, and maintenance costs of core support bearings. Hydrostatic sliding bearings, with their core advantages such as non-contact rigid oil film support, wear-free operation, long lifespan, high load-bearing capacity, and low starting torque, have become a core technology direction for replacing traditional heavy-duty and high-speed rolling bearings. However, existing hydrostatic sliding bearings all suffer from fundamental bottlenecks that are difficult to overcome, and have yet to achieve large-scale engineering applications across all scenarios.

[0003] Currently, the mainstream yaw bearings for large-megawatt wind turbines use double-row back-to-back tapered roller bearings, while the mainstream pitch bearings use single-row four-point contact ball bearings. Both are integral ring forging structures, which not only present inherent barriers in processing and transportation but also suffer from inherent defects such as easy fatigue spalling of rolling elements, rapid grease failure, high maintenance costs, large starting torque, lag in pitch / yaw response, and weak shock resistance. Furthermore, the existing hydrostatic sliding bearing solution cannot achieve a 1:1 universal replacement with existing rolling bearings. Turbine manufacturers must redesign the original layout of the tower, nacelle, hub, and pitch drive, resulting in extremely high modification costs and preventing large-scale replacement.

[0004] In addition, in heavy-duty rotating applications with small and medium diameters, such as vehicle-mounted radar, tank turrets, and construction machinery, cross roller bearings are still the mainstream choice. However, they have three major drawbacks: First, they wear out quickly under frequent start-stop and alternating impact conditions, and the play increases continuously with the duration of use, leading to radar beam shift, reduced fire control aiming accuracy, and misalignment during hoisting. Second, they have weak resistance to overturning and impact, and are prone to roller breakage and raceway deformation under extreme conditions such as off-road bumps, strong crosswinds, and recoil after firing. Third, they have a slow response speed and cannot achieve millisecond-level dynamic correction, making it difficult to meet the core requirements of high-precision tracking and rapid alignment.

[0005] Meanwhile, extremely precise rotational applications with small diameters, such as semiconductor lithography machine pre-alignment stages, medical imaging equipment rotating frames, and satellite attitude control gyroscopes, place stringent demands on bearings at the nanometer and sub-arcsecond levels regarding rotational accuracy, response speed, and thermal stability. Existing imported precision crossed roller bearings, due to the hard contact friction of the metal rolling elements, have high starting torque and require a large-inertia servo motor drive. This results in slow servo closed-loop response, large overshoot, and positioning accuracy locked at ±0.5 arcseconds, unable to overcome the bottleneck of advanced processes at 7nm and below. Furthermore, wear and tear after 6-12 months of operation leads to accuracy degradation, necessitating downtime and replacement. Although air bearings have no friction, they have extremely stringent cleanliness requirements, low load-bearing stiffness, and poor impact resistance, requiring an ultra-clean air source system. This results in complex equipment structures and extremely high maintenance costs.

[0006] For micro high-speed power units with speeds above 50,000 RPM, the current mainstream solution is high-speed ceramic ball bearings. These bearings have inherent drawbacks such as short lifespan, high vibration, high noise, and rapid temperature rise, and cannot achieve maintenance-free operation throughout their entire lifespan. Existing micro hydrostatic bearing solutions, due to their complex structure, numerous sealing points, and the need for external hydraulic systems, cannot achieve integrated operation with the motor and have thus failed to achieve large-scale application.

[0007] Overall, existing hydrostatic sliding bearings generally suffer from eight core industry pain points: deep coupling between pressure control and temperature control circuits, resulting in mutual interference of parameters and inability to adjust them independently and accurately; inability to achieve independent control of a single chamber, leading to single-point failure causing overall machine failure; redundant and complex oil supply systems, making it impossible to reuse the existing hydraulic power source of the host machine; inherent physical boundaries between X-type and O-type double-row structures, making them irreplaceable; the inevitable formation of a wedge-shaped oil film under off-center load conditions, restricting bearing performance and lifespan; an irreconcilable core contradiction between independent control and simplified structure; inherent defects in the segmented sealing system, resulting in low integration of the hydraulic system and high leakage risk; and the lack of suitable solutions for light-load, micro-sized, high-speed scenarios, making integrated operation impossible. Summary of the Invention

[0008] Purpose of the invention

[0009] This invention addresses the aforementioned deficiencies of existing technologies by providing an independently controlled pressure and temperature hydrostatic sliding bearing. It fundamentally solves the industry pain points of pressure and temperature control parameter interference and oil supply system redundancy through a "single high-pressure source branched-path homogeneous pressure oil supply + single-medium dual-loop fully decoupled design." It resolves off-center load compensation and fault redundancy issues through "single-chamber one-to-one independent closed-loop control." It breaks the physical boundaries of the X / O type structure through "X-shaped structure full-dimensional three-dimensional pressure regulation." It eliminates wedge-shaped oil film defects through "millisecond-level pressure closed-loop to achieve uniform and equal-thickness oil film under all working conditions." It resolves the core industry contradiction between independent control and simplified structure through "shared return oil + one-way valve anti-crosstalk." It achieves this through a fully closed-loop sealing system, fully integrated hydraulic circuit, 1:1 universal replacement design, and segmented / With its integrated optional structure, multi-material compatibility options, and fully oil-immersed integrated design, it systematically solves all the core industry pain points of existing hydrostatic bearings. At the same time, it is equipped with a preferred implementation scheme of passive bore diameter adaptive pressure adjustment, covering light-load micro high-speed scenarios, fundamentally breaking through the engineering application bottlenecks of large hydrostatic bearings and micro hydrostatic bearings.

[0010] Definitions of core terms

[0011] 1. Independent high-pressure oil chamber: also known as hydraulic cushion, is an independent cavity opened on the mating surface of the stationary ring bearing to form a high-pressure bearing oil film. It is the core bearing unit of the hydrostatic bearing.

[0012] 2. Independent low-pressure temperature control cavity: This is an independent, enclosed cavity milled into the interior of the stationary ring base to contain the temperature control medium and achieve temperature regulation. Each independent low-pressure temperature control cavity spatially encloses at least one independent high-pressure oil cavity and is the core temperature control unit of the hydrostatic bearing.

[0013] 3. Independent pressure control circuit: Provides a complete hydraulic circuit with independent oil supply, independent pressure regulation and independent fault isolation for each independent high-pressure oil chamber. One circuit corresponds uniquely to one independent high-pressure oil chamber.

[0014] 4. Independent temperature control circuit: A complete hydraulic circuit provides independent medium circulation and independent temperature regulation for each independent low-pressure temperature control chamber. One circuit uniquely corresponds to one independent low-pressure temperature control chamber.

[0015] 5. Pressure control unit: The core actuator of the independent pressure control loop, integrating pressure regulation, pressure stabilization, pressure detection, and backflow prevention functions, is the core structure of active closed-loop pressure control.

[0016] 6. Temperature control unit: The core actuator of the independent temperature control loop, integrating flow regulation, temperature detection, and backflow prevention functions.

[0017] 7. Main line pressure relief valve: The preferred component for reducing pressure in the temperature-controlled oil supply main line. It is installed at the inlet of the temperature-controlled oil supply main line and is used to reduce the pressure of the high-pressure medium to the rated working pressure of the temperature control circuit in one go, so as to realize the pressure decoupling between the pressure control and the temperature control circuit.

[0018] 8. Segmented structure: The stationary or moving coil is a structure formed by splicing two or more arc segments of equal length along the circumference, which is suitable for large-diameter heavy-load working conditions.

[0019] 9. Integrated ring structure: The stationary or moving ring is a complete ring structure with no splicing, which is suitable for compact and ultra-precision working conditions with small to medium diameters.

[0020] 10. High-performance composite materials: Engineering composite materials with self-lubricating, wear-resistant, low thermal expansion and media corrosion-resistant properties are preferred base materials for bearing mating surfaces, including but not limited to PEEK, PEKK, PI, PPS and other types, which can be selected and adapted according to working conditions.

[0021] 11. Passive orifice adaptive pressure regulation: The preferred pressure regulation solution for light load scenarios. By changing the orifice ratio of the oil inlet and outlet of the independent high-pressure oil chamber, the working pressure of the oil chamber is accurately set by utilizing the fluid throttling principle. Relying on the pure fluid throttling effect, it can automatically adapt to load fluctuations and oil temperature changes. No electronic control components are required throughout the process. It is suitable for light load scenarios with constant or small fluctuations in load.

[0022] Technical solution

[0023] An independently controlled pressure and temperature hydrostatic sliding bearing includes a first ring assembly, a second ring assembly, an independent pressure control circuit group, and an independent temperature control circuit group. One of the first and second ring assemblies is a stationary ring, and the other is a moving ring; the stationary and moving rings are coaxially fitted to form a bearing mating surface that can rotate relative to each other.

[0024] All independent high-pressure oil chambers and independent low-pressure temperature control chambers are located on the stationary ring. The bearing mating surface has circumferentially evenly distributed independent high-pressure oil chambers, and the stationary ring contains multiple circumferentially distributed independent low-pressure temperature control chambers, each containing at least one independent high-pressure oil chamber. Each independent high-pressure oil chamber is equipped with an independent pressure control circuit, and each independent low-pressure temperature control chamber is equipped with an independent temperature control circuit.

[0025] Preferably, one independent pressure control loop corresponds to one independent high-pressure oil chamber, and one independent temperature control loop corresponds to one independent low-pressure temperature control chamber, realizing one-to-one independent closed-loop control of a single chamber.

[0026] Preferably, a temperature-controlled oil supply main line branches off from the high-pressure end of the independent pressure control loop. The working pressure of the temperature-controlled oil supply main line is lower than that of the independent pressure control loop. The temperature-controlled oil supply main line is further divided into multiple temperature-controlled oil supply branches, which are connected to each independent temperature control unit. The lubricating medium used in the independent pressure control loop is the same hydraulic medium used in the independent temperature control loop. Only one hydraulic power source is needed to supply oil to both the pressure control and temperature control loops simultaneously, and the original hydraulic system of the host machine can be directly reused. As a preferred method of pressure reduction, a main line pressure relief valve can be installed at the inlet of the temperature-controlled oil supply main line to generate a stable low-pressure oil supply through a one-time pressure reduction; alternatively, an integrated multi-pressure output hydraulic power source can be used to directly output the medium of the corresponding pressure level to achieve the same pressure decoupling effect.

[0027] Preferably, the independent pressure control circuit and the independent temperature control circuit within the same low-pressure temperature control chamber share the same return oil interface; there is no direct connection between the independent pressure control circuits, and they are physically isolated from each other; each shared return oil interface is connected to an independent return oil branch pipe, and all independent return oil branch pipes eventually converge into a single complete loop of low-pressure return oil main pipe; each independent return oil branch pipe is equipped with a one-way valve, and the one-way valve conducts from the corresponding circuit to the low-pressure return oil main pipe to prevent cross-pressure and cross-temperature between different circuits.

[0028] Preferably, the core of the independent pressure control loop is a pressure control unit, which includes a variable throttle, a check valve, a single-chamber independent accumulator, and a pressure sensor. The high-pressure medium flows sequentially through the check valve, the single-chamber independent accumulator, and the variable throttle before entering the corresponding independent high-pressure oil chamber. The pressure sensor is located between the outlet of the variable throttle and the independent high-pressure oil chamber, and is electrically connected to an external controller via a built-in high-speed control bus, forming a single-chamber independent pressure closed-loop control with a pressure regulation response time ≤10ms. The core of the independent temperature control loop is a temperature control unit, which includes a variable throttle, a check valve, and a temperature sensor. The temperature-controlled medium flows sequentially through the check valve and the variable throttle before entering the corresponding independent low-pressure temperature control chamber. The temperature sensor is located inside the corresponding independent low-pressure temperature control chamber and is electrically connected to an external controller via a built-in high-speed control bus, forming a single-chamber independent temperature closed-loop control. Both types of variable throttle valve bodies adopt a circumferential double-layer sealing structure, with a sealing pressure not less than 1.5 times the maximum working pressure.

[0029] As a preferred implementation scheme for light-load scenarios, the working pressure of the independent high-pressure oil chamber can be passively adjusted by changing the orifice ratio of the inlet and outlet ports. The orifice ratio ranges from 1:1.2 to 1:10. Relying on the pure fluid throttling effect, it automatically adapts to load and oil temperature fluctuations without the need for any active electronic control components. It is suitable for micro high-speed, low-power light-load scenarios with constant load or fluctuation range ≤20%.

[0030] Preferably, the stationary and moving coils can be selected, depending on the operating conditions, as either a single-piece, seamless, closed-loop structure or a segmented structure consisting of two or more equal-length arc segments joined circumferentially. When using a segmented structure, each arc segment has at least one independently enclosed low-pressure temperature control cavity milled into it, with the temperature control cavities within the same arc segment interconnected. The independent low-pressure temperature control cavities of different arc segments are completely physically isolated, with no cross-arc medium communication channels. A concave-convex stop positioning structure is provided at the joint of adjacent arc segments, using an H7 / js6 transition fit, with a joint misalignment ≤0.01mm. When a segmented structure is adopted, the stationary ring is equipped with a segmented positioning and fastening retainer. The retainer has four sets of ring structures, two sets are arranged parallel to the axial vertical plane, and the other two sets are arranged on the upper and lower end faces respectively. Each set of ring structures is spliced ​​together from two semi-circular arc segments and embedded in the mounting groove of the stationary ring. The retainer and the base of the stationary ring are made of the same grade of material and their coefficients of thermal expansion are completely matched. The full-dimensional positioning of each arc segment is achieved by countersunk bolts.

[0031] Preferably, the bearing can adopt a single-row, double-row, or multi-row structure. When adopting a double-row structure, an X-shaped face-to-face conical arrangement is used, with independent high-pressure oil chambers and independent low-pressure temperature control chambers corresponding to the upper and lower rows. The control circuits of each row are independent and not connected to each other. The hydraulic main oil flow channels built into each stationary ring are arranged in layers, corresponding to the independent high-pressure oil chambers of the upper and lower rows respectively. They are circumferentially connected to form an independent high-pressure oil supply main oil circuit for the entire ring, which can realize full-dimensional three-dimensional pressure control of radial, axial, and overturning moment.

[0032] Preferably, the bearing mating surfaces offer three types of high-performance composite material options to meet the needs of various operating scenarios:

[0033] 1. Metal matrix composite high-performance composite material layer: The metal matrix is ​​alloy steel or titanium alloy, and the mating surface is composited with a high-performance composite wear-resistant layer; a nickel-based alloy transition layer is set between the wear-resistant layer and the metal matrix; the mating surface of the metal matrix is ​​laser roughened and dovetail-shaped locking grooves are processed to form a three-dimensional mechanical interlocking structure; an annular pressure distribution groove is opened around the independent high-pressure oil chamber to homogenize the oil film pressure distribution.

[0034] 2. Independent high-performance composite material functional plate floating structure: An independent high-performance composite material functional plate is set on the mating surface of the stationary ring. The independent high-pressure oil chamber, independent low-pressure temperature control chamber, pressure dividing groove and sealing groove are all integrally processed on the functional plate. The functional plate and the stationary ring matrix are non-rigidly connected and floatingly fitted, and an elastic material layer is set at the bottom.

[0035] 3. High-performance composite material monolithic structure: The moving coil and the stationary coil matrix are both integrally molded using the same grade of high-performance composite material, and their linear expansion coefficients are completely matched, so that the thermal deformation is synchronous and consistent under all working conditions.

[0036] As the optimal material selection, the high-performance composite material is preferably PEEK (polyetheretherketone). PEEK possesses excellent self-lubricating properties, wear resistance, resistance to media corrosion, and dimensional stability. Medical-grade and semiconductor-grade PEEK can meet the high requirements of cleanrooms, medical implants, and other demanding applications. Furthermore, PEEK can be molded through various processes such as cladding, injection molding, and precision machining, making it highly adaptable to mass production. When using a PEEK-metal composite solution, a nickel-based alloy transition layer is placed between the PEEK wear-resistant layer and the metal substrate to eliminate the difference in thermal expansion coefficients. The metal substrate bonding surface is pre-treated with laser roughening to form a micron-level rough structure, and a dovetail-shaped mesh locking groove is provided. The PEEK cladding layer is embedded in the locking groove to form a three-dimensional mechanical interlock, increasing the coating adhesion by more than 3 times. When using an independent PEEK functional board floating solution, there is no cladding interface or transition layer stress, eliminating the industry-wide problems of coating peeling and interface cracking at the source. The floating fit can completely release thermal expansion stress, and the oil film gap fluctuation can be stably controlled within ±0.002mm across the entire temperature range. When using a full PEEK homogeneous material solution, the thermal expansion coefficients of the moving and stationary coils are 100% matched, eliminating the oil film fluctuation and accuracy drift problems caused by the thermal expansion difference between dissimilar materials at the source, making it particularly suitable for ultra-precision scenarios.

[0037] Preferably, the built-in flow channel and valve mounting cavity inside the stationary ring base are integrally formed structures, including two processes: integral cutting / milling forming and integral fusion pre-embedded forming; all hydraulic control components and sensor wiring terminals are integrally built into the valve mounting cavity, with no exposed structures; the outer periphery of the stationary ring is a complete, continuous, smooth, closed-loop cylindrical surface, which can be covered with a continuous and uniform heat insulation layer. The heat insulation layer can adopt a composite structure such as anti-corrosion + heat insulation or stealth + heat insulation, depending on the working conditions.

[0038] Preferably, the bearing is provided with a double-layer semi-circular nitrogen seal structure at both ends, consisting of two sets of symmetrically arranged double-layer nested semi-circular cavities, each bridging the working surfaces of the moving and stationary rings; each set includes an inner first-layer sealing cavity and an outer second-layer sealing cavity, the two layers being independent and each equipped with a micro-positive pressure inert gas interface; an oil return port is provided at the bottom of the inner first-layer sealing cavity; during operation, the inner pressure > the outer pressure > atmospheric pressure, forming a three-stage gradient pressure seal. When a segmented structure is adopted, a closed-loop annular dynamic seal is provided on the bearing mating surface of each arc segment, enclosing the corresponding independent low-pressure temperature control cavity; a saddle-seam dynamic seal is provided at the splicing point of the adjacent arc segments, bridging the splicing gap of the annular dynamic seal, forming a sealing system without any breaks in the circumference; when an integrated ring structure is adopted, the saddle-seam dynamic seal is eliminated, and only the annular dynamic seal is retained.

[0039] Preferably, when the power component matched with the bearing is in a fully oil-immersed environment, the independent low-pressure temperature control chamber can be directly connected to and integrated with the internal oil chamber of the power component. There is no sealing structure between the two, and they share the same temperature control medium circulation loop, thereby realizing the integrated integration of the bearing and the power component.

[0040] Preferably, the bearing mounting dimensions are perfectly aligned 1:1 with existing rolling bearings of the same specification and type, allowing for direct in-situ replacement with zero cost for host machine modification.

[0041] Beneficial effects

[0042] 1. Single-source branching with different pressures from the same source, complete decoupling of dual circuits, resulting in a significant improvement in pressure and temperature control accuracy. The innovative design utilizes a high-pressure branching to generate high and low-pressure dual circuits, requiring only one hydraulic source to simultaneously supply oil to both the pressure and temperature control circuits. This allows for direct reuse of the host machine's original hydraulic system, resulting in zero cost for on-site modifications. Furthermore, it achieves complete decoupling of the pressure control and temperature control circuits from the source, ensuring that parameters do not interfere with each other. Under overturning moment conditions, oil film thickness fluctuations can be stably controlled within ±0.005mm, and the radial temperature difference of the entire bearing ring is ≤±0.3℃. Temperature control accuracy in small-diameter precision scenarios can reach ±0.05℃.

[0043] 2. One-to-one independent control per cavity, a qualitative leap in fault redundancy: Each circuit uniquely corresponds to a single cavity, with complete physical isolation, making each oil cavity and each temperature control cavity a completely independent operating unit. In the event of a single cavity failure, only the corresponding unit needs to be isolated; the remaining units can still operate normally, with a load-bearing capacity of over 90% of the rated value. Bearings can operate with a fault for 3-6 months, meeting the core requirements of high reliability and low maintenance frequency.

[0044] 3. Full-dimensional three-dimensional pressure regulation: A single X-type structure completely replaces the traditional X / O-type double-row bearing. The double-row X-type structure, combined with a single oil pad, provides millisecond-level independent pressure control, enabling full-dimensional three-dimensional pressure regulation. Under pure heavy-load conditions, its load-bearing rigidity reaches or even exceeds that of traditional O-type roller bearings; under overturning moment conditions, the diagonal oil pad provides millisecond-level differential pressure compensation, improving overturning resistance by more than 25% compared to traditional X-type bearings. It also retains the advantages of the X-type structure, such as strong self-aligning capability and high assembly tolerance. One structure covers all double-row bearing application scenarios.

[0045] 4. Millisecond-level response achieves uniform and consistent oil film thickness under all working conditions, eliminating wedge-shaped oil film defects at the source. The single oil pad independent pressure closed-loop response time is ≤10ms, which can dynamically adjust the oil supply pressure at the moment of occurrence of off-center load and impact load, so that the oil film thickness of all mating surfaces always remains uniform and consistent, eliminating wedge-shaped oil film defects at the source. The oil film stiffness is increased by more than 40%, and the bearing operating accuracy and service life are improved by orders of magnitude.

[0046] 5. Completely resolve the core industry contradiction between "independent control" and "simplified structure". The shared return oil interface design reduces the number of external interfaces by more than 50% and the number of leakage points by more than 75%. Combined with the return oil check valve design, it eliminates the problems of cross-pressure and cross-temperature from the structural source, which not only simplifies the structure, but also fully retains the core effect of independent control.

[0047] 6. A fully closed-loop sealing system and a fully integrated design completely eliminate leakage risks. The segmented structure uses a combination of annular dynamic seals and saddle-seam dynamic seals to form a seamless, closed-loop seal around the entire circumference. A double-layer gradient pressure nitrogen seal prevents crosstalk between internal and external media. All hydraulic components and wiring harnesses are internally mounted, with no exposed structures on the outer circumference of the stationary ring, reducing external leakage points by over 90%. The double-layer sealed valve body reduces internal leakage by over 99%.

[0048] 7. Dual structural forms + multiple material solutions, covering all scenarios and sizes. The segmented structure breaks through the barriers of large-diameter processing and transportation, while the integrated structure ensures the precision of small and medium diameters. Three types of high-performance composite material solutions are respectively adapted to three core scenarios: heavy-duty mass production, high reliability, and extreme precision. PEEK material is selected to balance performance and mass production. A single technology system covers all sizes and scenarios from wind power and tunnel boring machines to semiconductors and micro-power, significantly raising the market ceiling.

[0049] 8. Fully oil-immersed integrated design achieves high integration of bearing and power unit. For fully oil-immersed power systems, the low-pressure temperature control chamber and the internal oil chamber of the power component are connected without a seal, completely eliminating the need for sealing between the two and significantly reducing leakage points. At the same time, the internal oil chamber of the power component is used to expand the temperature control volume, which significantly improves temperature control stability and is particularly suitable for the mass production requirements of micro fully integrated power units. The preferred scheme of passive orifice diameter adaptive pressure regulation can further simplify the system structure in light-load scenarios and improve reliability.

[0050] The 1:1 universal replacement design eliminates the barrier to large-scale promotion. The installation dimensions of the entire series of bearings are completely aligned with those of rolling bearings of the same specifications. OEMs do not need to modify the original structure and can directly replace them to complete the performance upgrade, completely eliminating the core barrier to large-scale promotion. Attached Figure Description

[0051] Figure 1 This is a schematic diagram of the structure and oil circuit of the one-piece injection molded precision hydrostatic sliding bearing made entirely of PEEK material as described in Example 1; Figure 2 This is a simplified overall structural diagram of the yaw hydrostatic sliding bearing of the 16MW offshore wind turbine described in Example 2; Figure 3 This is a simplified hydraulic circuit diagram of the yaw hydrostatic sliding bearing of the 16MW offshore wind turbine described in Example 2.

[0052] Figure Labeling Explanation: 1 - Schematic diagram of PEEK integrated injection molded precision hydrostatic sliding bearing structure; 2 - Schematic diagram of PEEK integrated injection molded precision hydrostatic sliding bearing oil circuit; 3 - Fixed ring; 4 - Moving ring; 5 - Independent high-pressure oil chamber; 6 - Independent low-pressure temperature control chamber; 7 - Oil film; 8 - Pressure divider groove; 9 - High-pressure main oil supply circuit; 10 - Low-pressure main oil return circuit; 11 - Main circuit pressure relief valve; 12 - Temperature-controlled main oil supply circuit; 13 - Temperature-controlled branch oil supply circuit; 14 - Pressure control unit; 15 - Temperature control unit; 16 - Common return oil interface; 17 - Check valve; 18 - Upper drain; 19 - Lower drain; 20 - PEEK function board; 21 - Hydraulic oil circuit mounting cavity; 22 - Oil supply interface; 23 - Return oil interface; 24 - Control interface; 25 - End face segmented positioning and fastening retainer; 26 - Vertical segmented positioning and fastening retainer; 27 - Fixed ring arc segment; 28 - Moving ring arc segment; 29 - [Missing information - likely a section or part of the original text] - Annular dynamic seal 30 - Saddle-seam dynamic seal 31 - First nitrogen seal 32 - Second nitrogen seal 33 - Moving ring weld 34 - Moving ring joint 35 - Raised face 36 - Fluororubber elastic material layer Detailed Implementation

[0053] To clearly illustrate the technical solution of this invention, five typical scenario embodiments are selected for detailed explanation. All parameters have been theoretically calculated and verified in engineering, and are accurate and feasible for implementation.

[0054] Example 1: 12-inch wafer lithography machine pre-alignment stage with a one-piece injection-molded precision hydrostatic sliding bearing made entirely of PEEK material.

[0055] This embodiment is compatible with core semiconductor manufacturing equipment such as 12-inch wafer lithography machines and coating and developing machines. The core objective is to achieve sub-arcsecond positioning accuracy, nanometer-level oil film stability control, and zero precipitation in ISO Class 1 cleanrooms. In this embodiment, the stationary ring (3) is fixed relative to the lithography machine pre-alignment stage base, and the moving ring (4) rotates relative to the wafer carrier stage. Both are made of the same grade of semiconductor-grade high-purity PEEK material, and are integrally injection molded in the same batch and with the same process. The coefficient of thermal expansion is 100% matched, eliminating the accuracy drift caused by the thermal expansion difference of dissimilar materials from the root. The bearing adopts a single-row planar structure with an inner diameter of 200mm, an outer diameter of 300mm, and an axial height of 80mm. The stationary ring is equipped with two independent low-pressure temperature control chambers (6), and four independent high-pressure oil chambers (5) are evenly distributed in the circumference in an X-shape diagonal arrangement. Each independent low-pressure temperature control chamber encloses all four independent high-pressure oil chambers. It is equipped with four sets of independent pressure control circuits and two sets of independent temperature control circuits. The core of each circuit is a pressure control unit (14) and a temperature control unit (15).

[0056] 1. Core processes and structural design

[0057] The process employs a fusion-integrated pre-embedded molding process: pre-fabricated flow channel cores, standardized micro pressure / temperature control units, and EtherCAT high-speed control bus harnesses are precisely fixed to the injection mold cavity; PEEK raw materials from the same batch are melted at 380℃ and integrally molded under 120MPa injection pressure. After cooling, the core is extracted, directly forming a complete and smooth internal flow channel. The pre-embedded components are completely fused with the substrate as a whole. The finished product only requires mirror polishing of the mating surfaces and the addition of sealing components, with no additional machining processes throughout the entire process. The high-pressure oil supply main circuit (9) of the independent pressure control loop branches into a temperature-controlled oil supply main circuit (12), and the working pressure is stabilized at 0.8MPa after pressure reduction; in this embodiment, the main circuit pressure relief valve (11) is preferred to achieve one-time pressure reduction, and the original hydraulic vacuum adsorption system of the lithography machine can be directly reused. The temperature-controlled oil supply main circuit is split into multiple temperature-controlled oil supply branches (13), which are connected to each temperature control unit. Low-volatility electronic-grade anti-wear hydraulic oil is used as the common medium; the pressure and temperature circuits in the same independent low-pressure temperature control chamber share a common return oil interface (16), totaling 2 common return oil interfaces; each return oil branch pipe merges into the φ12mm low-pressure return oil main oil circuit (10), and each branch pipe is equipped with a stainless steel check valve (17) with an opening pressure of 0.008MPa. The pressure control unit is equipped with an ultra-high-speed pressure sensor with a response time ≤1ms and a pressure regulation response time ≤2ms; the temperature control unit is equipped with a PT1000 ultra-high precision temperature sensor with a detection accuracy of ±0.01℃; all components are connected to the lithography machine main controller through the built-in EtherCAT bus. The outer circumference of the stationary ring is a complete smooth cylindrical surface, covered with a 1mm thick anti-static clean heat insulation layer; the whole machine only reserves a unified oil supply interface (22), return oil interface (23), and control interface (24), and only three main interfaces need to be connected during on-site assembly.

[0058] 2. Sealing and mating surface design

[0059] Because of the integrated ring structure, the saddle-seam dynamic seal is eliminated, and only one complete closed-loop annular dynamic seal (29) is set. It is made of perfluoroether rubber and fits with the moving ring mating surface to form a fully circumferential closed system. Thanks to the complete synchronization of the deformation of the moving / stationary rings, the sealing surface is always in uniform contact, and the sealing life is more than 3 times longer than that of traditional composite materials. The bearing ends are equipped with a simplified double-layer semi-circular saddle-seam nitrogen seal, which is also made of PEEK material and integrally injection molded to form a three-level gradient pressure seal, which isolates the intrusion of micro dust in the clean room and avoids the volatilization of hydraulic medium to contaminate the wafer. The bearing mating surface, independent high-pressure oil chamber, and annular pressure distribution groove (8) are all integrally injection molded with the substrate; each independent high-pressure oil chamber is surrounded by an annular pressure distribution groove with a width of 3mm and a depth of 0.4mm to homogenize the oil film (7) pressure distribution.

[0060] 3. General Replacement and Application Effects

[0061] This embodiment has installation dimensions that are perfectly aligned 1:1 with imported precision crossed roller bearings of the same specifications, allowing for direct in-situ replacement and performance upgrades at zero modification cost. A comparison of core performance characteristics is shown in the table below:

[0062] Operating friction torque 0.15 N·m 0.015 N·m 0.008 N·m Reduced by 94.7% Matching drive motor power 200W 50W 20W Reduced by 90% Rotary positioning accuracy ±0.5 arc seconds ±0.3 arc seconds ±0.15 arc seconds Increased by 233% radial runout 50nm 30nm 15nm Increased by 233% Oil film thickness fluctuation under all operating conditions / ±50nm ±5nm 900% increase Maintenance-free period 12 months 5 years 15 years Increased by 15 times Cleanroom Adaptability Level ISO Level 2 ISO Level 2 ISO Level 1 Increase by 1 level

[0063] This embodiment completely breaks through the two fundamental bottlenecks of advanced semiconductor processes: "high torque → high inertia → precision lock-up" and "poor material deformation → oil film fluctuation → precision drift". It fully meets the mass production requirements of advanced processes of 2nm and below, and a single 12-inch wafer production line can achieve a value gain of over 36 million yuan throughout its entire life cycle.

[0064] Example 2: Yaw hydrostatic sliding bearing for 16MW offshore wind turbine

[0065] This embodiment is adapted to the yaw bearing of a 16MW offshore ultra-large wind turbine, and its core requirements are heavy load, high salt spray, high reliability, and low maintenance frequency. The bearing adopts a double-sided symmetrical X-type face-to-face conical double-row structure, including an upper row (18) and a lower row (19). The mating surface is at an angle of 45° to the axis, the outer diameter is 7800mm, the inner diameter is 6500mm, and the axial height is 1200mm. The stationary ring is spliced ​​from 6 segments of stationary ring arc (27) of equal arc length. Each segment corresponds to a central angle of 60°. Each upper and lower row is equipped with 4 independent high-pressure oil chambers and 1 independent low-pressure temperature control chamber, for a total of 48 independent high-pressure oil chambers and 12 independent low-pressure temperature control chambers, and is equipped with 48 sets of pressure control circuits and 12 sets of temperature control circuits. The moving ring adopts a splicing structure of 2 segments of semi-circular arc (28). The splicing point forms a moving ring weld (33), and the splicing point of the stationary ring forms a stationary ring joint (34).

[0066] 1. Overall oil circuit design

[0067] A temperature-controlled oil supply main circuit branches off from the high-pressure main oil circuit, and the working pressure is stabilized at 1.2MPa after pressure reduction. In this embodiment, a pressure relief valve is preferred to achieve one-time pressure reduction, and 12 temperature-controlled oil supply branches are connected to each temperature control unit. No. 46 anti-wear hydraulic oil is used as the common medium, and the original hydraulic system of the blower can be directly reused. The pressure and temperature circuits within the same independent low-pressure temperature control chamber share a common return oil interface, totaling 12 common return oil interfaces. Each DN15 return oil branch pipe merges into the DN100 low-pressure return oil main circuit, and each branch pipe is equipped with a one-way valve with an opening pressure of 0.02MPa. The pressure control unit is equipped with a high-frequency response pressure sensor with a response time ≤5ms and a pressure regulation response time ≤10ms; the temperature control unit is equipped with a PT100 temperature sensor with a detection accuracy of ±0.1℃; all components are connected to the blower main controller via a built-in CAN bus. All valve assemblies and components are housed within the hydraulic circuit mounting cavity (21) milled into the stationary ring, with no exposed structures. The stationary ring is surrounded by a composite structure consisting of a 3mm polyurea anti-corrosion layer and a 5mm polyurethane insulation layer, adaptable to a wide temperature range of -40℃ to 60℃ at sea. The entire unit is equipped with uniform oil supply, return, and control interfaces on its exterior for easy on-site pipeline connection.

[0068] 2. Splicing, positioning, and sealing design

[0069] A concave-convex stop (35) is set at the splicing point of adjacent stationary arc segments for positioning, with a splicing misalignment of ≤0.01mm; four sets of segmented positioning and fastening retainers are configured, including two sets of end face segmented positioning and fastening retainers (25) and two sets of vertical face segmented positioning and fastening retainers (26), made of 42CrMo alloy steel, matching the thermal expansion coefficient of the substrate, and achieving full-dimensional positioning of each arc segment through countersunk bolts. Each stationary arc segment is equipped with a closed-loop annular dynamic seal in the upper and lower rows, made of polyurethane, which encloses the corresponding independent low-pressure temperature control cavity; a saddle-seam dynamic seal (30) is set at the splicing point of the annular dynamic seal, bridging the splicing gap of the annular dynamic seal, forming a sealing system without any breaks in the circumference. The bearing is equipped with a double-layer semi-circular nitrogen seal structure at both ends, including an inner first layer nitrogen seal (31) and an outer second layer nitrogen seal (32). The pressure of the inner sealing cavity is 0.15MPa and the outer pressure is 0.1MPa, forming a three-level gradient pressure seal to completely isolate the intrusion of marine salt spray. An oil return port is set at the bottom of the inner sealing cavity to recover a small amount of oil leakage from the end face.

[0070] 3. Mating surfaces and universal replacement design

[0071] The mating surfaces adopt an independent PEEK functional plate (20) floating structure. Each stationary ring arc segment corresponds to a 15mm thick PEEK functional plate. The independent high-pressure oil chamber, independent low-pressure temperature control chamber, pressure distribution groove, and sealing groove are all integrally machined on the PEEK functional plate. A 2mm thick fluororubber elastic material layer (36) is set between the PEEK functional plate and the 42CrMo alloy steel substrate. A 5mm wide and 0.5mm deep annular pressure distribution groove is set around each independent high-pressure oil chamber to homogenize the oil film pressure distribution. The installation dimensions of this embodiment are completely aligned 1:1 with the same specification double-row tapered roller bearing, and can be directly replaced in situ.

[0072] 4. Performance and Transportation Effectiveness

[0073] Invention Solution 26.8 tons 7.5 tons 34% Compatible with standard containers and conventional lifting operations Rolling bearings of the same specifications 40.6 tons 40.6 tons - Specialized transportation and ultra-large lifting are required.

[0074] This embodiment has a rated static load of 120,000 kN and a starting torque of ≤500 N·m, which is more than 95% lower than that of rolling bearings; the oil film thickness fluctuation under all operating conditions is ≤±0.003 mm, and the radial temperature difference of the entire circle is ≤±0.3℃; it can operate with a fault for 6 months in a single cavity failure, meeting the design requirements of 25 years of maintenance-free operation for offshore wind power.

[0075] Example 3: 10MW Onshore Wind Turbine Pitch Hydrostatic Sliding Bearing

[0076] This embodiment is adapted to the pitch bearing of a 10MW onshore wind turbine, and its core requirements are to meet the needs of frequent start-stop, millisecond-level pitch response, and resistance to alternating loads. The bearing adopts a single-row conical structure with a 30° angle between the mating surface and the axis, an outer diameter of 1800mm, an inner diameter of 1400mm, and an axial height of 220mm. The stationary ring adopts a three-segment structure with equal arc length, totaling 18 independent high-pressure oil chambers and 6 independent low-pressure temperature control chambers, equipped with 18 pressure control circuits and 6 temperature control circuits.

[0077] 1. Overall oil circuit and structural design

[0078] The temperature-controlled oil supply main route is generated from the high-pressure end, and the working pressure is stabilized at 1.0MPa after pressure reduction. In this embodiment, the pressure reduction is achieved by a pressure relief valve on the main route, using No. 32 low-pour-point anti-wear hydraulic oil and reusing the original hydraulic station of the wind turbine pitch control. A shared return oil design is used with a return oil check valve to prevent cross-pressure and cross-temperature. The pressure regulation response time is ≤5ms, which is suitable for rapid pitch adjustment. The outer periphery of the stationary ring is covered with an epoxy zinc-rich anti-corrosion layer and a rock wool insulation layer composite structure, which is suitable for a wide onshore temperature range of -35℃ to 55℃. The splice uses concave-convex stop positioning and is equipped with two sets of positioning and fastening retainers on the upper and lower end faces. The mating surface is made of PEEK-42CrMo composite material, with a 2.5mm thick PEEK wear-resistant layer clad and equipped with a three-level interface strengthening process. An annular pressure distribution groove is set to homogenize the oil film pressure. Double-layer nitrogen seals are set at both ends of the bearing to isolate the intrusion of outdoor sand, dust, rain and snow.

[0079] 2. Application Effects

[0080] This embodiment has a rated static load of 45,000 kN and a starting torque of ≤80 N·m, which is more than 90% lower than that of rolling bearings, completely eliminating the pitch "backlash" and "jamming" problems; the pitch response speed is improved by more than 80%, the wind energy utilization coefficient Cp value is improved by 2.5%, and the annual power generation of the unit is improved by more than 3%; the design life is ≥20 years, and the operation and maintenance cost is reduced by more than 75%.

[0081] Example 4: Medium-speed hydrostatic sliding bearing for vehicle-mounted radar

[0082] This embodiment is adapted to military vehicle-mounted active phased array radar, and its core requirements are high-precision tracking, high shock resistance, extreme wide temperature range, stealth, and lightweight design. The bearing adopts a single-row conical structure with an outer diameter of 750mm, an inner diameter of 600mm, and an axial height of 180mm. Both the stationary and moving rings adopt an integrated full-ring structure, with 24 independent high-pressure oil chambers and 8 independent low-pressure temperature control chambers evenly distributed circumferentially, and is equipped with 24 pressure control circuits and 8 temperature control circuits.

[0083] 1. Overall Design

[0084] The temperature-controlled oil supply main route is generated by a branch at the high-pressure end, and the working pressure is stabilized at 1.0MPa after pressure reduction. In this embodiment, the pressure reduction is achieved by a pressure relief valve on the main route, using No. 32 low-pour-point anti-wear hydraulic oil and reusing the original hydraulic system of the vehicle. The pressure regulation response time is ≤5ms, which is suitable for rapid tracking requirements. All components are built-in, and the outer periphery of the stationary ring is covered with a radar-wave stealth coating + aerogel insulation layer composite structure, which can adapt to extreme temperature differences of -55℃ to 70℃. The mating surfaces are made of PEEK-TC4 titanium alloy composite material, which is non-magnetic and lightweight. The saddle-seam dynamic seal is eliminated, and only the annular dynamic seal is retained, resulting in a simple and reliable structure.

[0085] 2. Application Effects

[0086] Rated static load 12000kN, starting torque ≤40N・m, which is more than 95% lower than that of rolling bearings; radar beam offset ≤0.01° under strong crosswind and off-road bumpy conditions; anti-overturning moment capability is improved by more than 30%; can operate stably with faults for 12 months, meeting the 15-year maintenance-free requirement of military equipment.

[0087] Example 5: Integrated hydrostatic sliding bearing for a 500W 50000 RPM high-speed micro motor

[0088] This embodiment is adapted to a miniature high-speed brushless motor, and it addresses the pain points of traditional high-speed rolling bearings, such as short lifespan, high vibration, and low integration. It adopts a preferred solution combining passive aperture adaptive voltage regulation and a fully oil-immersed, seal-free design. The bearing has an inner diameter of 8mm, an outer diameter of 16mm, and an axial height of 6mm. The stationary ring is integrally formed with the motor housing, and the moving ring is integral with the motor rotor. The motor has a rated power of 500W, a rated speed of 50,000rpm, and a total rotor weight of 18g. It features a fully oil-immersed structure, with the bearing temperature control chamber completely connected to the motor's internal oil chamber, and no sealed structure.

[0089] 1. Pressure control and oil circuit design

[0090] This embodiment adopts a passive orifice adaptive pressure regulation design, which relies on the pure fluid throttling effect to achieve automatic pressure adaptation without electronic components. It does not require the configuration of active control components such as variable throttle, pressure sensor, and controller. Under dynamic working conditions such as axial load fluctuation, oil temperature change, vibration and shock, it can automatically maintain the stability of oil film pressure and thickness.

[0091] Two independent high-pressure oil chambers are symmetrically arranged on the upper and lower end faces of the stationary ring, corresponding to the upper and lower supports of the rotor, respectively. Each independent high-pressure oil chamber has one oil inlet and one oil outlet. The diameter of the oil inlet on the lower bearing side is 0.8mm, and the diameter of the oil inlet on the upper non-bearing side is 0.6mm. The diameters of the upper and lower oil outlets are both 1.2mm. The difference in the diameter of the upper and lower oil inlets creates a basic axial pressure difference, precisely balancing the static weight of the 18g rotor. At the same time, relying on the throttling matching characteristics of the oil inlet and outlet, adaptive pressure regulation is achieved under working conditions: when the axial load increases, the oil film gap decreases, the oil outlet throttling effect is enhanced, and the oil chamber pressure automatically increases; when the axial load decreases, the oil film gap increases, the oil flow rate increases, and the oil chamber pressure automatically decreases. There is no electronic control intervention throughout the process; the pressure dynamic adaptation is achieved purely by the physical structure.

[0092] A single hydraulic power source outputs a constant pressure of 0.5MPa, which is directly connected to the oil inlet of two independent high-pressure oil chambers. Under steady-state conditions, the working pressure of the lower high-pressure oil chamber is stable at 0.5MPa, and the working pressure of the upper high-pressure oil chamber is stable at 0.48MPa. The axial buoyancy just balances the rotor's weight, and the oil film thickness is stably controlled at 5μm±0.5μm under all working conditions.

[0093] The temperature control medium uses 1cSt low-viscosity perfluoropolyether oil, which is the same hydraulic medium as the high-pressure bearing medium. After the temperature control circuit is depressurized to 0.2MPa from the high-pressure end, it directly enters the internal cavity of the motor and is fully connected to the independent low-pressure temperature control cavity of the bearing, realizing integrated temperature control of the bearing, motor stator and rotor. The steady-state temperature rise of the whole unit is ≤5℃. In this embodiment, the main circuit pressure relief valve is preferred to realize the pressure reduction of the temperature control circuit, and the corresponding pressure can also be directly output through an integrated multi-pressure hydraulic source.

[0094] 2. Integration and Application Effects

[0095] Only one PTFE spring-loaded dynamic seal is retained on the motor output shaft. There is no sealing structure between the bearing and the motor, creating a fully enclosed positive pressure oil immersion environment. All oil circuits are integrally injection molded with the motor housing, and the overall dimensions are completely consistent with those of high-speed rolling bearings of the same specifications, allowing for direct and universal replacement.

[0096] Vibration acceleration 1.2g 0.08g Reduced by 93.3% Operating noise 65dB 32dB Reduced by 50.8% Mean Time Between Failures 3000 hours 50,000 hours Increased by 15.7 times Temperature rise 35℃ 5℃ Reduced by 85.7%

[0097] This embodiment achieves zero control components, zero additional seals, and integrated design for micro high-speed motor bearings, with a cost that is only 1 / 5 of that of imported ceramic ball bearings. It is particularly suitable for applications such as drones, medical high-speed centrifuges, and industrial high-speed spindles.

Claims

1. An independent pressure and temperature controlled hydrostatic slide bearing, characterized in that It includes a first ring assembly, a second ring assembly, an independent pressure control circuit group, and an independent temperature control circuit group; one of the first ring assembly and the second ring assembly is a stationary ring, and the other is a moving ring, which are coaxially fitted to form a bearing mating surface; multiple independent high-pressure oil chambers are opened on the bearing mating surface of the stationary ring, and at least two independent low-pressure temperature control chambers are opened inside the stationary ring, each of which contains at least one independent high-pressure oil chamber; each independent high-pressure oil chamber is configured with an independent pressure control circuit, and each independent low-pressure temperature control chamber is configured with an independent temperature control circuit.

2. The independent hydrostatic pressure and temperature controlled sliding bearing of claim 1, wherein, Each independent pressure control circuit corresponds uniquely to an independent high-pressure oil chamber, and each independent temperature control circuit corresponds uniquely to an independent low-pressure temperature control chamber.

3. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 2, characterized in that, The high-pressure end of the independent pressure control circuit branches off to a temperature-controlled oil supply main circuit, the working pressure of which is lower than that of the independent pressure control circuit. The temperature-controlled oil supply main circuit is further divided into multiple temperature-controlled oil supply branches, which are connected to each independent temperature control unit. The lubrication medium of the independent pressure control circuit is the same hydraulic medium as the temperature control medium of the independent temperature control circuit.

4. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, The independent pressure control circuit and the independent temperature control circuit in the same low-pressure temperature control chamber share the same return oil interface; there is no direct connection between the independent pressure control circuits; each shared return oil interface is connected to an independent return oil branch pipe, and all independent return oil branch pipes converge into the entire low-pressure return oil main pipe; each independent return oil branch pipe is equipped with a check valve, and the direction of the check valve is from the corresponding circuit to the low-pressure return oil main pipe.

5. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, The core of the independent pressure control loop is the pressure control unit, which includes a variable throttle, a one-way valve, a single-chamber independent accumulator, and a pressure sensor; the core of the independent temperature control loop is the temperature control unit, which includes a variable throttle, a one-way valve, and a temperature sensor; both the pressure sensor and the temperature sensor are electrically connected to an external controller via a built-in high-speed control bus.

6. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, The stationary coil and the moving coil can be either an integral whole-coil structure or a segmented structure consisting of two or more equal-length arc segments spliced ​​together circumferentially. When a segmented structure is used, the independent low-pressure temperature control cavities within each arc segment are independent of each other and physically isolated, with no cross-arc segment medium connection channels.

7. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, The bearing adopts a single-row, double-row, or multi-row structure; when adopting a double-row structure, it adopts an X-shaped face-to-face conical arrangement, with independent high-pressure oil chambers and independent low-pressure temperature control chambers set in the upper and lower rows respectively, and the corresponding control circuits are independent of each other; each stationary ring has a built-in hydraulic main oil flow channel set in layers, corresponding to the independent high-pressure oil chambers in the upper and lower rows respectively.

8. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, The bearing mating surface adopts one of the following three types of high-performance composite material structures: The first type is a metal matrix composite high-performance composite material layer, with a transition layer and mechanical interlocking structure between the two; the second type is an independent high-performance composite material functional plate set on the side of the bearing mating surface, with the high-performance composite material functional plate and the stationary ring matrix having a floating mating structure, and an elastic material layer set at the bottom; the third type is that both the moving ring and the stationary ring matrix are integrally molded using the same grade of high-performance composite material.

9. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, When the power components are in a fully oil-immersed environment, the independent low-pressure temperature control chamber can be directly connected to the internal oil chamber of the power components, sharing the same temperature control medium circulation loop.

10. The independently controlled pressure and temperature hydrostatic sliding bearing according to claim 1, characterized in that, Its installation dimensions are perfectly aligned 1:1 with the corresponding type of rolling bearing of the same specification, and it can be directly replaced.

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