Self-feedback surface throttling double-cone fluid hydrostatic bearing

Abstract

The invention discloses a self-feedback surface throttling double-cone fluid hydrostatic bearing, and relates to the field of precision machinery. The problems that in the prior art, a hydrostatic bearing feedback throttling structure is complex and is only suitable for liquid media are solved. The hydrostatic bearing is of a mirror symmetry structure, and the stator I and the stator II are fixed to the two sides of the stator III in a mirror symmetry mode to form a double-cone-shaped stator combination. The rotor I and the rotor II are fixed on two sides of the feedback ring in mirror symmetry; the feedback ring is positioned in the stator III, and a gap between the feedback ring and the stator III is an isobaric area; an axial adjacent gap between the stator I and the feedback ring is an axial feedback area I; a radial adjacent gap between the stator I and the feedback ring is a radial feedback region I; a bearing area I and a compensation area I are arranged between the rotor I and the stator I; the stator III is provided with a fluid inlet, and the fluid inlet, the isobaric area, the radial feedback area I, the axial feedback area I, the bearing area I and the compensation area I are communicated to form a medium channel. The method is suitable for various media and is suitable for more fields.

Description

Technical Field

[0001] This invention relates to the field of precision machinery, and specifically to a self-feedback surface throttling double-cone hydrostatic bearing. Background Technology

[0002] Hydrostatic bearings rely on an externally supplied fluid with a certain pressure flowing between the friction surfaces, which separates the moving parts of the bearing with a fluid film. The bearing is supported by the hydrostatic pressure of the fluid, which can reduce the influence of surface machining errors. This method has high motion accuracy and is widely used in industry.

[0003] Hydrostatic bearings are divided into two types: liquid hydrostatic bearings and gas hydrostatic bearings. In existing technologies, liquid hydrostatic bearings mainly employ two throttling methods: gap throttling and diaphragm throttling. Gap throttling requires complex flow channel fabrication and interference fit, resulting in a complex structural assembly. Diaphragm throttling can achieve high stiffness, but diaphragm consistency is difficult to guarantee, requiring different structures to adjust diaphragm stiffness and throttling gap, leading to complex design and poor versatility. Gas hydrostatic bearings mainly employ two throttling methods: orifice throttling and porous material throttling. Orifice throttling is more mature, involving separately fabricating a plunger with small holes and bonding it to the end of the bearing's gas path. Each bearing requires multiple plungers, and maintaining consistent diameter and bonding of the small holes on the plungers is difficult, easily causing air hammer when high-pressure gas is introduced. Porous material throttling devices use porous materials, but porous materials cannot guarantee uniform orifice size and consistent permeability, and the small pore size of porous materials makes them prone to clogging.

[0004] When the external load on a hydrostatic bearing changes, the bearing itself does not have the ability to regulate flow and pressure, and a throttling method with feedback capability is often required. In existing technologies, throttling methods with feedback capability include diaphragm throttling and self-feedback throttling. Diaphragm throttling requires the separate fabrication of a diaphragm throttler, which has a complex structure, and each hydrostatic bearing requires multiple diaphragm throttlers with consistent performance, making machining and assembly difficult. Existing self-feedback throttling methods require the fabrication of complex flow channels, often requiring appropriate fitting to achieve flow channel sealing, which is also complex to manufacture and adjust.

[0005] Currently, there is little research on combining surface throttling and self-feedback. US patent document US20070286537A1 proposes to process shallow grooves on the bearing surface as throttling devices, but it does not have feedback capability. Chinese invention patent document CN105697544A proposes to set oil grooves on hydrostatic spherical thrust bearings to realize gap self-feedback structure, but it does not have a surface throttling structure and is only suitable for liquid media. Summary of the Invention

[0006] This invention solves the problem of complex feedback throttling structures in existing hydrostatic bearings. It also overcomes the limitation that existing self-feedback throttling hydrostatic bearings are only suitable for liquid media.

[0007] The present invention discloses a self-feedback surface throttling double cone hydrostatic bearing, the bearing comprising: a stator assembly and a rotor assembly, and the bearing further comprising a feedback loop; The stator assembly includes stator I, stator III, and stator II. Stator I and stator II are fixed symmetrically on both sides of stator III, forming a double-cone stator assembly. The rotor assembly includes rotor I and rotor II, which are fixed symmetrically on both sides of the feedback loop; The feedback loop is located inside stator III, and there is a gap between them, which is an isobaric region; A gap is left between the stator I and the feedback loop at their axially adjacent locations, and the gap is called axial feedback region I; a gap is left between the stator I and the feedback loop at their radially adjacent locations, and the gap is called radial feedback region I. Mirror-symmetrical to the above structure, a gap is left between the axial adjacent parts of the stator II and the feedback loop, and the gap is the axial feedback region II; a gap is left between the radial adjacent parts of the stator II and the feedback loop, and the gap is the radial feedback region II; The gap between rotor I and stator I is the load-bearing zone I and the compensation zone I; Mirror symmetry with the above structure, the gap between rotor II and stator II is the load-bearing area II and the compensation area II; The stator III is provided with a fluid inlet, which is connected to the isobaric zone. After the fluid flows into the isobaric zone from the fluid inlet, it is divided into two fluid paths. Fluid path one is radial feedback zone I, axial feedback zone I, bearing zone I, and compensation zone I; fluid path two is radial feedback zone II, axial feedback zone II, bearing zone II, and compensation zone II.

[0008] The design is further optimized so that the taper range of the double-cone stator assembly is 60°~120°.

[0009] In a further optimized design, rotor I, feedback loop, and rotor II have a coaxiality better than 0.002 mm; stator I, stator III, and stator II have a coaxiality better than 0.002 mm.

[0010] In a further optimized scheme, the radial feedback zone I is a toroidal gap, and the axial feedback zone I is a toroidal gap, with the widths of the two being the same or different.

[0011] In a further optimized design, the width of the annular gap is 10μm to 200μm.

[0012] In a further optimized scheme, the width of the bearing area I is 1-4 times the width of the annular gap of the radial feedback area I or the axial feedback area I.

[0013] In a further optimized scheme, the longitudinal cross-sectional width of the bearing area I is greater than that of the compensation area I, and the bearing area I and the compensation area I are adjacent to each other in a stepped shape.

[0014] In a further optimized scheme, the longitudinal cross-sectional width of the bearing area I is 2 to 3 times the longitudinal cross-sectional width of the compensation area I.

[0015] In a further optimized scheme, the width of the conical gap in the bearing area I is 5μm~50μm, and the width of the conical gap in the compensation area I is 2μm~30μm.

[0016] In a further optimized scheme, the fluid inlet is for gas, with a supply pressure between 0.2 MPa and 2 MPa; or, the fluid inlet is for liquid, with a supply pressure between 0.5 MPa and 5 MPa.

[0017] The advantages of this invention compared to the prior art are: In the hydrostatic bearing configuration described in this invention, axial feedback zone I and axial feedback zone II are used to feedback changes in axial load, and radial feedback zone I and radial feedback zone II are used to feedback changes in radial load.

[0018] In the hydrostatic bearing described in this invention, the radial feedback zone I, axial feedback zone I, load-bearing zone I, compensation zone I, radial feedback zone II, axial feedback zone II, load-bearing zone II, and compensation zone II constitute a self-feedback structure, realizing axial and radial self-compensation feedback, which makes the bearing have high stiffness in both the axial and radial directions and more stable operation.

[0019] The hydrostatic bearing configuration of this invention includes a compensation zone I and a load-bearing zone I between rotor I and stator I, with their adjacent sections forming a stepped gap. Similarly, a compensation zone II and a load-bearing zone II are provided between rotor II and stator II, also with their adjacent sections forming a stepped gap. This stepped gap constitutes a surface throttling structure, achieving the function of a throttling device in existing bearings. In other words, the hydrostatic bearing of this invention does not require a throttling device and can be used with both liquid and gaseous media. The surface throttling structure is simple, easy to process and assemble, and provides a wide operating pressure range without air hammer, significantly improving the bearing's load-bearing capacity.

[0020] The hydrostatic bearing described in this invention improves the convenience and applicability to various media by incorporating a self-feedback structure and a surface throttling structure, making it suitable for a wider range of fields. Attached Figure Description

[0021] Figure 1 A longitudinal sectional view of a self-feedback surface-throttling double-cone hydrostatic bearing provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of the fluid flow direction of a self-feedback surface throttling double cone hydrostatic bearing provided in an embodiment of the present invention; Reference numerals: Rotor I1; Stator I2; Stator III3; Feedback loop 4; Stator II5; Rotor II6; Isobaric zone 7; Fluid inlet 8; Compensation zone I9; Bearing zone I10; Radial feedback zone I11; Axial feedback zone I12; Radial feedback zone II13; Axial feedback zone II14; Bearing zone II15; Compensation zone II16. Detailed Implementation

[0022] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0024] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0025] Furthermore, the technical features involved in the different embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0026] It should be noted that some of the accompanying drawings are in a very simplified form and are not to scale, and are only used to facilitate and clearly illustrate the purpose of the embodiments of the present invention.

[0027] Implementation Method 1: Refer to Figure 1 and Figure 2This embodiment describes a self-feedback surface-throttling double-cone hydrostatic bearing. The bearing includes a stator assembly and a rotor assembly, and further includes a feedback loop 4. The stator assembly includes stator I2, stator III3, and stator II5. Stator I2 and stator II5 are fixed symmetrically on both sides of stator III3 to form a double-cone stator assembly. The rotor assembly includes rotor I1 and rotor II6, which are fixed symmetrically on both sides of the feedback loop 4. The feedback loop 4 is located inside the stator Ⅲ3, and there is a gap between them, which is the isobaric region 7; A gap is left between the stator I2 and the feedback ring 4 at their axially adjacent locations, and the gap is called the axial feedback region I12; a gap is left between the stator I2 and the feedback ring 4 at their radially adjacent locations, and the gap is called the radial feedback region I11; Mirror-symmetrical to the above structure, a gap is left between the stator II5 and the feedback ring 4 at their axially adjacent positions, the gap being the axial feedback region II14; a gap is left between the stator II5 and the feedback ring 4 at their radially adjacent positions, the gap being the radial feedback region II13; The gap between rotor I1 and stator I2 is the load-bearing zone I10 and the compensation zone I9; Mirror symmetry with the above structure, the gap between rotor II6 and stator II5 is the load-bearing area II15 and the compensation area II16; The stator Ⅲ3 is provided with a fluid inlet 8, which is connected to the isobaric zone 7. After the fluid flows into the isobaric zone 7 from the fluid inlet 8, it is divided into two fluid paths. One fluid path is the radial feedback zone Ⅰ11, the axial feedback zone Ⅰ12, the bearing zone Ⅰ10, and the compensation zone Ⅰ9. The other fluid path is the radial feedback zone Ⅱ13, the axial feedback zone Ⅱ14, the bearing zone Ⅱ15, and the compensation zone Ⅱ16.

[0028] In this embodiment, the fluid inlet 8 contains a hydrostatic bearing lubricating medium, which can be either a liquid or a gaseous medium.

[0029] In this embodiment, the isobaric zone 7 is an annular isobaric zone. After the hydrostatic bearing lubricating medium flows in from the fluid inlet 8 into this isobaric zone 7, it flows into two fluid paths at the same pressure. The other end of the two paths is connected to the outside.

[0030] In this embodiment, stator I2 and stator II5 are fixed to stator III3 by screws.

[0031] The rotor I1 and rotor II5 are fixed to the feedback loop 4 by screws.

[0032] In this embodiment, the radial feedback region I11 and the radial feedback region II13 have the same axial length, and are greater than 5 mm.

[0033] In this embodiment, the path of the liquid or gas medium in the hydrostatic bearing during operation is described below. Figure 2 As shown, the liquid or gas medium enters the isobaric zone 7 through the fluid inlet 8 and becomes a linear pressure source. A portion of the fluid flows through the first fluid path, sequentially through the radial feedback zone I11, the axial feedback zone I12, the bearing zone I10, and the compensation zone I9 to reach the outside. Another portion of the fluid flows through the second fluid path, sequentially through the radial feedback zone II13, the axial feedback zone II14, the bearing zone II15, and the compensation zone II16 to reach the outside.

[0034] The self-feedback surface-throttling double-cone hydrostatic bearing proposed in this embodiment uses axial feedback zones I and II to report changes in axial load, and radial feedback zones I and II to report changes in radial load. Therefore, no additional pressure feedback unit is required. This self-feedback structure enables continuous dynamic feedback and compensation during bearing operation. This structure is simple to manufacture, easy to assemble and adjust, and can automatically adjust the lubrication film pressure distribution according to changes in external load, achieving high support stiffness.

[0035] Implementation Method Two: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, the taper range of the double-cone stator assembly is 60°~120°.

[0036] In this embodiment, the taper of the tapered stator assembly can be in the range of 60° to 120°. If it is too large, the radial stiffness bearing capacity will be weak, and if it is too small, the axial stiffness bearing capacity will be weak.

[0037] In practical use, stators with different tapers can be selected according to different usage scenarios. When the axial load of the device is greater than the radial load during use, a stator with a taper range of 90° to 120° is preferred; when the radial load of the device is greater than the axial load during use, a stator with a taper range of 60° to 90° is preferred; when the axial load and radial load of the environment in which the device is located are comparable, a stator with a taper of 90° is preferred.

[0038] Implementation Method 3: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, rotor I1, feedback loop 4, and rotor II6 have a coaxiality better than 0.002 mm; stator I2, stator III3, and stator II5 have a coaxiality better than 0.002 mm.

[0039] In the hydrostatic bearing described in this embodiment, the coaxiality of stator I2, stator III3, and stator II5 with that of rotor I1, feedback ring 4, and rotor II6 is obtained by detecting the precision-machined rotating surface. If the coaxiality is too large, it will lead to poor bearing accuracy or even failure to rotate. In this embodiment, the coaxiality of stator I2, stator III3, and stator II5 with that of rotor I1, feedback ring 4, and rotor II6 is preferably set to be better than 0.002 mm.

[0040] Implementation Method Four: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, the radial feedback region I11 is a toroidal gap, and the axial feedback region I12 is a toroidal gap, and their widths may be the same or different.

[0041] Reference Figure 1 The hydrostatic bearing described in this embodiment has a mirror-symmetric structure. Therefore, the radial feedback zone II13 and the axial feedback zone II14 are also toroidal gaps. The radial feedback zone II13 and the radial feedback zone I11 have the same shape, and the axial feedback zone II14 and the axial feedback zone I12 have the same shape.

[0042] In this embodiment, the gaps in the radial feedback zone I11, radial feedback zone II13, axial feedback zone I12, and axial feedback zone II14 refer to their widths in a static state. These feedback zones constitute a self-feedback structure, used to provide feedback on the radial and axial load conditions of the hydrostatic bearing during operation. Therefore, during the operation of the hydrostatic bearing, the annular gap widths of the radial feedback zone I11, radial feedback zone II13, axial feedback zone I12, and axial feedback zone II14 vary according to the load conditions. When the rotor I1 and rotor II6 bear a downward axial load greater than an upward axial load, the annular gap width of the axial feedback zone II14 is greater than the annular gap width of the axial feedback zone I12; when the rotor I1 and rotor II6 bear a leftward load greater than a rightward load, the left gap of the radial feedback zone I11 and radial feedback zone II13 is smaller than its rightward gap.

[0043] The changes in the aforementioned different feedback zones cause corresponding changes in the flow rate of the hydrostatic bearing lubricating medium within the corresponding feedback zone, which in turn leads to pressure changes in the corresponding compensation zone, further altering the stress on the rotor assembly and ultimately increasing the stiffness of the hydrostatic bearing. Specifically: When the axial load changes: When the rotor assembly of the hydrostatic bearing is subjected to a downward axial load, the rotor assembly moves downward relative to the stator assembly, the gap in the axial feedback zone I12 increases, the flow rate of the fluid medium to the axial feedback zone I12 increases, the pressure in the bearing zone I10 and the compensation zone I9 increases, the rotor I experiences a greater upward resultant force, the gap in the axial feedback zone II14 decreases, the flow rate of the fluid medium to the axial feedback zone II14 decreases, the pressure in the bearing zone II15 and the compensation zone II16 decreases, the rotor II experiences a less downward resultant force, and the rotor assembly as a whole receives a greater upward resultant force to resist the downward axial load, giving the hydrostatic bearing greater axial stiffness.

[0044] When the radial load changes: When the hydrostatic bearing rotor assembly is subjected to a rightward radial load, the rotor assembly moves to the right relative to the stator assembly, causing the gap in the right radial feedback zone I11 to increase. This leads to an increase in the flow rate of the fluid medium in the right radial feedback zone I11 and radial feedback zone II13, and an increase in the pressure in the right bearing zone I10, compensation zone I9, bearing zone II15, and compensation zone II16. The rotor assembly experiences a larger resultant force to the left, while the gap in the left radial feedback zone I11 decreases. Consequently, the flow rate of the fluid medium flowing through the left radial feedback zone I11 and radial feedback zone II13 decreases, and the pressure in the left bearing zone I10, compensation zone I9, bearing zone II15, and compensation zone II16 decreases. The rotor assembly experiences a smaller resultant force to the right, and the rotor assembly as a whole experiences a larger resultant force to the left to resist the rightward axial load, giving the hydrostatic bearing greater radial stiffness.

[0045] Implementation Method 5: Refer to Figure 1 This embodiment is an optimized design of embodiment four. In this embodiment, the width of the annular gap is 10μm to 200μm.

[0046] If the gap width of the radial feedback zone I11, radial feedback zone II13, axial feedback zone I12, and axial feedback zone II14 in the hydrostatic bearing described in this embodiment is set too large, the feedback effect will be poor or even lost. If it is set too small, it will be difficult to process and adjust. Therefore, it is preferable to set the width of the radial feedback zone I11 to 10μm~200μm to achieve the feedback purpose.

[0047] Implementation Method Six: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, the width of the bearing area I10 is 1-4 times the width of the annular gap of the radial feedback area I11 or the axial feedback area I12.

[0048] The hydrostatic bearing described in this embodiment has a mirror-symmetric structure, that is, the bearing area II15 is 1-4 times the annular gap width of the radial feedback area II13 or the axial feedback area II14.

[0049] When the fluid medium enters the bearing area I10 from the axial feedback area I12 and enters the bearing area II15 from the axial feedback area II14, the flow velocity decreases and the pressure increases, thereby promoting the transport of the fluid medium.

[0050] Implementation Method Seven: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, the longitudinal cross-sectional width of the bearing area I10 is greater than the longitudinal cross-sectional width of the compensation area I9, and the adjacent parts of the bearing area I10 and the compensation area I9 are stepped.

[0051] Reference Figure 1 The hydrostatic bearing described in this embodiment has a mirror-symmetric structure, that is: the longitudinal cross-sectional width of the bearing area II15 is greater than the longitudinal cross-sectional width of the compensation area II16, the bearing area II15 and the compensation area II16 are adjacent to each other in a stepped shape, the bearing area II15 and the bearing area I10 have the same shape, and the compensation area II16 and the compensation area I9 have the same shape.

[0052] The above-described structural features define the hydrostatic bearing in its static state. During operation, these features will change.

[0053] The self-feedback surface-throttling double-cone hydrostatic bearing proposed in this embodiment forms a stepped gap between rotor I and stator I; similarly, a stepped gap is also formed between rotor II and stator II. The surface-throttling structure formed by the two stepped gaps can achieve the function of a throttling device in existing bearings, eliminating the need for an additional throttling device. This structure is simple to manufacture and easy to assemble and adjust. Furthermore, this structure is suitable for both gaseous and liquid hydrostatic bearing lubrication media. When using gas lubrication, a higher supply pressure can be used than in different air-bearing systems without generating air hammer, thereby achieving a higher load-bearing capacity.

[0054] Implementation Method 8: Refer to Figure 1 This embodiment is an optimized design of embodiment seven. In this embodiment, the longitudinal cross-sectional width of the bearing area I10 is 2 to 3 times the longitudinal cross-sectional width of the compensation area I9.

[0055] The hydrostatic bearing described in this embodiment has a mirror-symmetric structure, that is: the longitudinal cross-sectional width of the bearing area II15 is 2 to 3 times the longitudinal cross-sectional width of the compensation area II16, the bearing area I10 and the bearing area II15 have the same shape, and the compensation area I9 and the compensation area II16 have the same shape.

[0056] The above structure is defined as the structure of the hydrostatic bearing under static conditions.

[0057] In this embodiment, when the ratio of the longitudinal cross-sectional width of the bearing area I10 to the longitudinal cross-sectional width of the compensation area I9 of the hydrostatic bearing is less than 2, the surface throttling effect will be greatly reduced. When the ratio is greater than 3, air hammer phenomenon is likely to occur. Therefore, this embodiment proposes a preferred method to set the longitudinal cross-sectional width of the bearing area I10 to 2 to 3 times the longitudinal cross-sectional width of the compensation area I9.

[0058] Implementation Method Nine: Refer to Figure 1 This embodiment is an optimized design of embodiment seven. In this embodiment, the width of the conical gap in the bearing area I10 is 5μm~50μm, and the width of the conical gap in the compensation area I9 is ​​2μm~30μm.

[0059] The hydrostatic bearing described in this embodiment has a mirror-symmetric structure, that is, the width of the conical gap in the bearing area II15 is 5μm~50μm, and the width of the conical gap in the compensation area II16 is 2μm~30μm.

[0060] In this embodiment, the hydrostatic bearing is preferably configured such that the width of the conical gap between the bearing area I10 and the bearing area II15 is limited to 5μm to 50μm, and the width of the conical gap between the compensation area I9 and the compensation area II16 is limited to 2μm to 30μm.

[0061] In the hydrostatic bearing described in this embodiment, the gap in the compensation zone I9 (compensation zone II16) is smaller than that in the bearing zone I10 (bearing zone II15). Therefore, the fluid medium has a higher pressure when it is in the bearing zone I10 (bearing zone II15), and the pressure drop in the gap decreases when it flows into the compensation zone I9 (compensation zone II16), thereby providing support stiffness and load-bearing capacity without a throttle.

[0062] Implementation Method 10: Refer to Figure 1 This embodiment is an optimized design of embodiment one. In this embodiment, the fluid inlet 8 receives gas with a supply pressure between 0.2 MPa and 2 MPa; or, the fluid inlet 8 receives liquid with a supply pressure between 0.5 MPa and 5 MPa.

[0063] When the hydrostatic bearing described in this embodiment is lubricated with a gas medium, the bearing has the advantages of high speed, precision, and low friction. The gas supply pressure can be selected between 0.2MPa and 2MPa according to different stiffness and load requirements without causing air hammer. When lubricated with a liquid medium, the bearing has the advantages of high stiffness, large load capacity, and good damping. The gas supply pressure can be selected between 0.5MPa and 5MPa according to different stiffness and load requirements.

[0064] The structure of the hydrostatic bearing claimed in this invention also includes reasonable combinations or equivalent substitutions of the optimized solutions defined in the above embodiments.

Claims

1. A self-feeding surface throttling dual-taper fluid static pressure bearing, the bearing comprising: The stator assembly and the rotor assembly are characterized in that the bearing further comprises a feedback ring (4); The stator assembly comprises a stator I (2), a stator III (3), and a stator II (5), the stator I (2) and the stator II (5) are fixed on both sides of the stator III (3) in mirror image symmetry, forming a double-cone stator assembly; The rotor assembly comprises a rotor I (1) and a rotor II (6), the rotor I (1) and the rotor II (6) are fixed on both sides of the feedback ring (4) in mirror image symmetry; The feedback ring (4) is located in the stator III (3), and a gap is left between the two, which is an equal pressure area (7); A gap is left between the axial adjacent part of the stator I (2) and the feedback ring (4), which is an axial feedback area I (12); a gap is left between the radial adjacent part of the stator I (2) and the feedback ring (4), which is a radial feedback area I (11); In mirror image symmetry with the above structure, a gap is left between the axial adjacent part of the stator II (5) and the feedback ring (4), which is an axial feedback area II (14); a gap is left between the radial adjacent part of the stator II (5) and the feedback ring (4), which is a radial feedback area II (13); The gap between the rotor I (1) and the stator I (2) is a bearing area I (10) and a compensation area I (9); In mirror image symmetry with the above structure, the gap between the rotor II (6) and the stator II (5) is a bearing area II (15) and a compensation area II (16); The stator III (3) is provided with a fluid inlet (8), the fluid inlet (8) is communicated with the equal pressure area (7), and the fluid flows into the equal pressure area (7) from the fluid inlet (8), then is divided into two fluid paths, wherein the fluid path one is the radial feedback area I (11), the axial feedback area I (12), the bearing area I (10), and the compensation area I (9); the fluid path two is the radial feedback area II (13), the axial feedback area II (14), the bearing area II (15), and the compensation area II (16).

2. A self-feedback surface-restricted dual-taper hydrostatic bearing according to claim 1, wherein, The taper range of the double-cone stator assembly is 60°-120°.

3. A self-feedback surface-restricted dual-taper hydrostatic bearing according to claim 1, wherein, The coaxiality of the rotor I (1), the feedback ring (4), and the rotor II (6) is better than 0.002mm; the coaxiality of the stator I (2), the stator III (3), and the stator II (5) is better than 0.002mm.

4. A self-feedback surface-restricted dual-taper hydrostatic bearing according to claim 1, wherein, The radial feedback area I (11) is an annular gap, the axial feedback area I (12) is an annular gap, and the widths of the two are the same or different.

5. A self-feeding surface throttling dual-taper fluid static pressure bearing according to claim 4, wherein, The width of the annular gap is 10μm-200μm.

6. A self-feedback surface-restricted dual-taper hydrostatic bearing according to claim 1, wherein, The width of the bearing area I (10) is 1-4 times the width of the annular gap of the radial feedback area I (11) or the axial feedback area I (12).

7. A self-feeding surface throttling dual-taper fluid static pressure bearing according to claim 1, wherein, The longitudinal section width of the bearing area I (10) is greater than the longitudinal section width of the compensation area I (9), and the adjacent part of the bearing area I (10) and the compensation area I (9) is in a stepped shape.

8. A self-feeding surface throttling dual-taper fluid static pressure bearing according to claim 7, wherein, The longitudinal section width of the bearing area I (10) is 2-3 times the longitudinal section width of the compensation area I (9).

9. A self-feeding surface-restricted dual-taper hydrostatic bearing according to claim 7, wherein, The width of the conical gap of the bearing area I (10) is 5μm-50μm, and the width of the conical gap of the compensation area I (9) is 2μm-30μm.

10. A self-feedback surface-restricted dual-taper hydrostatic bearing according to claim 1, wherein, The fluid inlet (8) is for gas, and the gas supply pressure is between 0.2 MPa and 2 MPa; or, the fluid inlet (8) is for liquid, and the liquid supply pressure is between 0.5 MPa and 5 MPa.

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