Bidirectional hydraulic feedback type tension-torsion hydrostatic bearing mechanism

Abstract

The application discloses a bidirectional hydraulic feedback type tension-torsion static pressure bearing mechanism, relates to the tension-torsion test technical field, and oil is supplied to two symmetrical static pressure oil cavities through a bidirectional hydraulic feedback type throttler; during work, oil flows to the liquid inlet of two liquid inlet guide columns, and part of oil from one liquid inlet guide column flows to the oil cavity through a liquid inlet throttling hole to form pressure oil, and the other part of oil flows to the oil cavity through a liquid outlet gap to release pressure; when the bearing rotating shaft approaches a certain static pressure oil cavity, the oil pressure of the corresponding oil cavity rises, the elastic diaphragm is pushed up to the other side to be elastically deformed, the distance between the elastic diaphragm and the other liquid inlet guide column is reduced, more oil flows to the liquid inlet throttling hole, the oil pressure of the other oil cavity is raised, the elastic diaphragm is reversely pushed back, and then the bearing rotating shaft is reversely pushed back, so that the bearing rotating shaft is in a balanced state, the deviation correction operation can be automatically completed, friction is reduced, the real modal response of the measured object can be truly reflected, and the service life is prolonged.

Description

Technical Field

[0001] This invention relates to the field of tension-torsion testing technology, and more particularly to a bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism. Background Technology

[0002] Tension-torsion testing is mainly used to simulate the tension-torsion environment of various mechanical, electrical, and electronic products on equipment such as ships, submarines, tanks, mobile artillery, aircraft, and bearings. Under certain special working conditions, the test equipment has a combined motion of tension and torsion. Tension-torsion refers to the periodic angular displacement motion of key components of aircraft and ships around the torsion axis while they are subjected to tensile force and torsional force.

[0003] The swing test bench is mainly used to perform swing, oscillation, and combined tests involving various parameters such as static angle, dynamic angle, and acceleration. Traditional tension-torsion load-bearing mechanisms mostly use bearing structures. However, the inherent clearance of bearing structures cannot be eliminated, and tension-torsion friction and wear will accelerate the shortening of bearing life. The frictional force generated by the relative motion of traditional test benches has a significant impact on accuracy and lifespan.

[0004] Existing tensile and torsional loads all use mechanical bearing structures, which employ a combination of sliding and rolling bearings. This results in high friction, which cannot accurately reflect the true modal response of the tested object. Furthermore, with prolonged use, mechanical wear due to bearing lifespan leads to extremely low lifespan.

[0005] How to reduce frictional resistance, accurately reflect the true modal response of the tested object, and improve its service life is a technical problem that needs to be solved. Summary of the Invention

[0006] This invention provides a bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism that automatically completes the correction operation, allowing the bearing shaft to automatically return to a balanced state. By reducing friction through an oil film, it accurately reflects the true modal response of the measured object. The specific solution is as follows:

[0007] A bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism includes a hydrostatic bearing support and a bearing shaft, wherein each end of the bearing shaft is supported by at least one of the hydrostatic bearing supports; the bearing shaft is used to mount the test piece.

[0008] The hydrostatic bearing support includes a mounting cavity for inserting the bearing shaft. The inner wall of the mounting cavity is provided with hydrostatic oil chambers. The number of hydrostatic oil chambers is even and they are symmetrically distributed in pairs in the circumferential direction of the mounting cavity.

[0009] Two symmetrically arranged hydrostatic oil chambers are supplied with oil through a bidirectional hydraulic feedback throttle. The bidirectional hydraulic feedback throttle includes a mounting housing, an elastic diaphragm, and two inlet guide posts. Each inlet guide post has an inlet throttle hole on its side wall. One end of each of the two inlet guide posts is fixed to the mounting housing. The elastic diaphragm is installed between the two inlet guide posts and forms a discharge gap with them. The outer periphery of the elastic diaphragm is installed on the mounting housing, dividing the interior of the mounting housing into two oil chambers. An outlet throttle hole is provided on the mounting housing, and the oil in the oil chambers is supplied to the two symmetrically arranged hydrostatic oil chambers through the outlet throttle hole.

[0010] The oil flows to the inlet of each of the two inlet guide columns. A portion of the oil enters from one of the inlet guide columns and flows through the inlet throttle hole to the oil chamber to form pressurized oil. The other portion of the oil flows through the drain gap to the oil chamber to release pressure.

[0011] When the bearing shaft approaches one of the hydrostatic oil chambers, the oil pressure in the corresponding oil chamber rises, causing the elastic diaphragm to be elastically deformed to the other side. The distance between the elastic diaphragm and the other inlet guide post decreases, allowing more oil to flow into the inlet throttling orifice, increasing the oil pressure in the other oil chamber, causing the elastic diaphragm to be pushed back in the opposite direction, and thus pushing the bearing shaft back in the opposite direction.

[0012] Optionally, the hydrostatic oil chamber includes an outer oil chamber and an inner oil chamber, each of which is provided in an even number and is symmetrically distributed in pairs in the circumferential direction of the mounting cavity;

[0013] The bidirectional hydraulic feedback throttle includes an outer throttle and an inner throttle. The outer throttle is used to supply oil to the outer oil chamber, and the inner throttle is used to supply oil to the inner oil chamber.

[0014] Optionally, the pressure in the inner oil chamber is higher than the pressure in the outer oil chamber. The inner oil chamber is used to improve the load-bearing capacity, and the outer oil chamber is used to improve the stiffness.

[0015] Optionally, the axial width of the inner oil cavity is greater than the axial width of the outer oil cavity.

[0016] Optionally, the hydrostatic bearing support includes an oil supply ring groove, an oil drain groove, and an oil drain hole, wherein the oil drain groove is disposed on both sides of the hydrostatic oil chamber in the axial direction;

[0017] The oil flows through the oil supply ring groove to the bidirectional hydraulic feedback throttle, and the oil discharged from the gap between the bearing shaft and the mounting cavity flows through the oil drain groove to the oil drain hole.

[0018] Optionally, a sealing cover is provided on the wall surface of the hydrostatic bearing support facing the bearing shaft, and a dust cover is provided on the wall surface away from the bearing shaft;

[0019] A sealing ring is installed on the sealing cover and is fixed to the end face of the hydrostatic bearing support by screws to seal the oil supply ring groove; the dust cover is a flexible felt for external dust protection.

[0020] Optionally, the hydrostatic bearing support is provided with support and fixation by a mounting bracket, which is fixed to the required mounting surface by screws.

[0021] Optionally, the hydrostatic bearing support is provided with a copper alloy coating inside to control the oil film gap and has repairability.

[0022] Optionally, the bearing shaft is equipped with an angle sensor for measuring the torsion angle.

[0023] This invention provides a bidirectional hydraulic feedback type tension-torsion hydrostatic bearing mechanism. An even number of hydrostatic oil chambers are arranged symmetrically in pairs along the circumferential direction on the inner wall of the mounting cavity. The two symmetrically arranged hydrostatic oil chambers are supplied with oil through a bidirectional hydraulic feedback type throttle. During operation, the oil flows to the inlets of two inlet guide columns. A portion of the oil entering from one inlet guide column flows through the inlet throttle hole to the oil chamber to form pressurized oil, while the other portion flows through the drain gap to the oil chamber to release pressure. When the bearing shaft approaches a certain hydrostatic oil chamber, the oil pressure in the corresponding oil chamber increases. The elastic diaphragm is pushed up to the other side, causing elastic deformation. The distance between the elastic diaphragm and the other inlet guide post decreases, allowing more oil to flow into the inlet throttling orifice. This increases the oil pressure in the other oil chamber, causing the elastic diaphragm to rebound in the opposite direction. Consequently, the bearing shaft rebounds in the opposite direction, bringing the bearing shaft to a balanced state. This allows for automatic correction, restoring the bearing shaft to its balanced state. A circumferentially uniformly distributed oil film is formed between the bearing shaft and the hydrostatic bearing support as a gap, reducing friction and thus accurately reflecting the true modal response of the measured object, thereby extending its service life. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0025] Figure 1 A schematic diagram of the overall structure of the bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism provided by the present invention;

[0026] Figure 2A top view of the bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism provided by the present invention;

[0027] Figure 3 for Figure 1 The longitudinal section of the bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism;

[0028] Figure 4 A longitudinal cross-sectional view of a specific embodiment of a hydrostatic bearing support;

[0029] Figure 5 This is a schematic diagram of the oil circuit principle of a two-way hydraulic feedback throttle.

[0030] Figure 6 A schematic diagram illustrating the bearing deviation of the rotating shaft;

[0031] Figure 7 This is a schematic diagram of an elastic diaphragm bulging upwards and deforming.

[0032] Figure 8 This is a schematic diagram showing how the bearing shaft returns to its center position.

[0033] The image includes:

[0034] Static pressure bearing support 1, mounting cavity 11, static pressure oil cavity 12, outer oil cavity 121, inner oil cavity 122, oil supply ring groove 13, oil drain groove 14, oil drain hole 15;

[0035] 2. Bearing shaft; 3. Two-way hydraulic feedback throttle; 31. Mounting housing; 31. Oil chamber; 312. Liquid outlet throttle orifice; 32. Elastic diaphragm; 321. Liquid discharge gap; 33. Liquid inlet guide post; 331. Liquid inlet throttle orifice; 332. Liquid inlet; 3.1. Outer throttle; 3.2.

[0036] 4. Sealing cover; 5. Dustproof cover; 6. Mounting bracket. Detailed Implementation

[0037] The core of this invention is to provide a bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism that automatically completes the correction operation, so that the bearing shaft automatically returns to a balanced state, and reduces friction through the oil film, thereby truly reflecting the real modal response of the tested object.

[0038] To enable those skilled in the art to better understand the technical solution of the present invention, the bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism of the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

[0039] Combination Figure 1 , Figure 2 , Figure 3As shown, the present invention provides a bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism, including a hydrostatic bearing support 1 and a bearing shaft 2. Both ends of the bearing shaft 2 are supported by at least one hydrostatic bearing support 1. At least two hydrostatic bearing supports 1 are provided, and at least one hydrostatic bearing support 1 is provided at each end of the bearing shaft 2, so that the ends of the bearing shaft 2 are supported by the hydrostatic bearing supports 1.

[0040] The bearing shaft 2 is used to mount the test piece. The test piece is fixed to the bearing shaft 2. The bearing shaft 2 can rotate relative to the hydrostatic bearing supports 1 at both ends, and can slide axially within a certain range. The direction of translation and sliding is as follows: Figure 2 In the X-axis direction, the two ends of the bearing shaft 2 are coaxial cylindrical structures, and the bearing shaft 2 rotates around the axis. The bearing shaft 2 can be a single integral structure or formed by splicing several segments. The bearing shaft 2 is forged as a whole to eliminate stress concentration. The bearing shaft 2 has connecting holes for installing bearing samples. The bearing shaft 2 has a hollow internal structure, which gives it high rigidity while reducing its weight and making it lightweight. The bearing shaft 2 is combined with two hydrostatic bearing supports 1, and a high-load-bearing hydrostatic oil film is established between the shaft and the shaft housing for bearing and guidance.

[0041] Combination Figure 4 As shown, the hydrostatic bearing support 1 includes a mounting cavity 11 for inserting the bearing shaft 2. The inner diameter of the mounting cavity 11 is slightly larger than the outer diameter of the cylindrical portions at both ends of the bearing shaft 2, allowing the bearing shaft 2 to be inserted. A hydrostatic oil cavity 12 is provided on the inner wall of the mounting cavity 11. The hydrostatic oil cavity 12 is a recessed structure located inside the mounting cavity 11, with the depth direction of the recess being the radial direction of the mounting cavity 11. An oil hole is provided within the recessed structure (usually on the bottom surface) to allow oil to enter.

[0042] Each hydrostatic oil chamber 12 is an independent structure. The number of hydrostatic oil chambers 12 is even, and they are symmetrically distributed in pairs around the circumference of the mounting cavity 11. At least two hydrostatic oil chambers 12 are provided, but four, six, or other numbers can also be used. The hydrostatic oil chambers 12 are evenly distributed around the circumference of the mounting cavity 11, and they adopt a symmetrical layout, satisfying both axisymmetry and central symmetry. The axis of central symmetry is the centerline of the mounting cavity 11, and the plane of axisymmetry is a cross-section along the radial direction of the mounting cavity 11.

[0043] Two symmetrically arranged hydrostatic oil chambers 12 are supplied with oil through a bidirectional hydraulic feedback throttle 3. The two symmetrical hydrostatic oil chambers 12 form a group. The bidirectional hydraulic feedback throttle 3 simultaneously supplies oil to the two hydrostatic oil chambers 12 in the group to provide static pressure and generate a pressure oil film with load-bearing capacity. The number of bidirectional hydraulic feedback throttles 3 is half the number of hydrostatic oil chambers 12.

[0044] Combination Figure 5 As shown, the bidirectional hydraulic feedback throttle 3 includes a mounting housing 31, an elastic diaphragm 32, and two inlet guide pillars 33. The mounting housing 31 is a shell structure, which can be a single complete shell or formed by splicing two parts. The interior of the mounting housing 31 is a cavity for oil to enter, and the mounting housing 31 can be configured as a cylindrical space. The elastic diaphragm 32 is fixedly installed to the inner wall of the mounting housing 31 around its perimeter. The elastic diaphragm 32 divides the inner cavity of the mounting housing 31 into two independent parts, forming two oil chambers 311. The elastic diaphragm 32 can undergo elastic deformation, thereby changing the volume of the two oil chambers 311. Figure 5 The structure shown is a longitudinal section. The area above the elastic diaphragm 32 is a chamber, and the area below the elastic diaphragm 32 is a chamber. Liquid can flow in the two chambers separately.

[0045] The liquid inlet guide posts 33 are mounted on the mounting housing 31. The ends of the two liquid inlet guide posts 33 are respectively fixed to the mounting housing 31. There is a gap between the two liquid inlet guide posts 33, and they do not directly contact each other. Figure 5 As shown, the two liquid inlet guide posts 33 have similar radial dimensions and their axes are aligned.

[0046] Each liquid inlet guide post 33 has a liquid inlet throttling hole 331 on its side wall. The liquid inlet throttling hole 331 is radially opened in the liquid inlet guide post 33. Each liquid inlet guide post 33 has at least one liquid inlet throttling hole 331, and each liquid inlet guide post 33 may have two or more liquid inlet throttling holes 331.

[0047] One end of each of the two liquid inlet guide posts 33 is fixed to the mounting housing 31. An elastic diaphragm 32 is installed between the two liquid inlet guide posts 33 and forms a drainage gap 321 with the liquid inlet guide posts 33. That is, the distance between the two liquid inlet guide posts 33 is greater than the thickness of the elastic diaphragm 32. The elastic diaphragm 32 forms a gap with the ends of the two liquid inlet guide posts 33 respectively, which allows oil to flow.

[0048] The elastic diaphragm 32 is a high-rigidity diaphragm. The outer periphery of the elastic diaphragm 32 is installed on the mounting housing 31, dividing the interior of the mounting housing 31 into two oil chambers 311. The mounting housing 31 is provided with an outlet throttling orifice 312. Each oil chamber 311 is provided with at least one outlet throttling orifice 312. The oil in the oil chamber 311 is supplied to the two symmetrically arranged hydrostatic oil chambers 12 through the outlet throttling orifice 312.

[0049] The inlet throttling orifice 331 and the outlet throttling orifice 312 are respectively equipped with throttles. The function of the throttling orifice is to generate a pressure difference on both sides of the throttling orifice, provide control signals for other components, and delay local state changes in the hydraulic system to reduce oscillations.

[0050] Figure 5 The elastic diaphragm 32 shown is in its initial state, combined with Figure 5 As indicated by the arrows, the oil flowing in from the outside simultaneously flows to the inlets 332 of the two inlet guide columns 33. A portion of the oil entering from the inlet 332 of one inlet guide column 33 flows through the inlet throttle orifice 331 into the oil chamber 311 to form pressurized oil, while the other portion flows through the drain gap 321 into the oil chamber 311 to release pressure. The oil entering from each inlet guide column 33 has two destinations: one flows through the drain gap 321 into the oil chamber 311, and the other flows through the inlet throttle orifice 331 into the oil chamber 311.

[0051] When the bearing shaft 2 approaches a certain hydrostatic oil chamber 12, the oil pressure in the corresponding oil chamber 311 rises, causing the elastic diaphragm 32 to deform elastically to the other side. The distance between the elastic diaphragm 32 and the other inlet guide post 33 decreases, allowing more oil to flow into the inlet throttling orifice 331, increasing the oil pressure in the other oil chamber 311, and causing the elastic diaphragm 32 to rebound in the opposite direction, thereby causing the bearing shaft 2 to rebound in the opposite direction. After the elastic diaphragm 32 is squeezed from one side, the gap between the two sides of the elastic diaphragm 32 changes, with one side decreasing and the other side increasing. This changes the hydraulic resistance of the bidirectional hydraulic feedback throttling device 3, causing the flow rate on both sides of the elastic diaphragm 32 to change. This further increases the pressure difference between the two oil chambers based on the oil film gap shift, resulting in a higher load-bearing capacity.

[0052] Combination Figure 6 As shown, the bearing shaft 2 is offset downwards along the arrow in the figure due to gravity. The axis of the bearing shaft 2 is lower than the axis of the mounting cavity 11. The bearing shaft 2 is closer to the lower static pressure oil cavity 12 and farther away from the upper static pressure oil cavity 12, so that the upper and lower static pressure oil cavities 12 and the bearing shaft 2 have a gap difference. Since the upper and lower static pressure oil cavities 12 are connected to the same bidirectional hydraulic feedback throttle 3, one of the static pressure oil cavities 12 is supplied with oil by one oil cavity 311 of the bidirectional hydraulic feedback throttle 3, and the other static pressure oil cavity 12 is supplied with oil by the other oil cavity 311 of the bidirectional hydraulic feedback throttle 3.

[0053] Combination Figure 5 , Figure 6 As shown, with Figure 5 The upper oil chamber 311 is directed towards Figure 6 Oil is supplied to the upper static pressure oil chamber 12. Figure 5 The lower oil chamber 311 is directed towards Figure 6Oil is supplied to the lower hydrostatic oil chamber 12 (ignoring the left and right hydrostatic oil chambers 12). The flow resistance of the inlet throttle orifice 331 and the outlet throttle orifice 312 remains constant, while the flow rate changes depending on the oil pressure. The discharge gap 321 changes with the deformation of the elastic diaphragm 32, thus changing the flow resistance; the larger the gap, the smaller the flow resistance. The external oil pressure entering through the inlet 332 can be considered constant, therefore the amount of oil entering the oil chamber 311 through the inlet throttle orifice 331 remains constant, while the amount of oil entering the oil chamber 311 through the discharge gap 321 will change.

[0054] The bearing shaft 2 shifts downward under gravity, causing the lower hydrostatic oil chamber 12 to be compressed, increasing the pressure. This reduces the oil output from the lower liquid outlet throttling orifice 312, causing the elastic diaphragm 32 to bulge upward and undergo elastic deformation (e.g., Figure 7 (As shown in the diagram), the distance between the elastic diaphragm 32 and the upper inlet guide post 33 decreases, while the distance between the elastic diaphragm 32 and the lower inlet guide post 33 increases. The oil volume in the lower drain gap 321 increases, increasing the flow rate in the lower oil chamber 311, and consequently increasing the oil volume flowing out of the lower outlet throttling orifice 312. The oil volume in the upper drain gap 321 decreases, decreasing the flow rate in the upper oil chamber 311, and consequently decreasing the oil volume flowing out of the upper outlet throttling orifice 312. The pressure in the static pressure oil chamber 12 below the bearing shaft 2 increases, while the pressure in the static pressure oil chamber 12 above decreases, thus lifting the bearing shaft 2 upwards. Ultimately, the bearing shaft 2 returns to its intermediate state (as shown in the diagram). Figure 8 (As shown), it resists the axial displacement caused by gravity. The positional displacement of the bearing shaft 2 in other directions is restored to the intermediate state through the same principle.

[0055] The present invention utilizes the elastic diaphragm 32. The greater the deformation amplitude of the diaphragm 32, the greater the pressure difference between the two opposing hydrostatic oil chambers 12, resulting in a greater reverse thrust for correction. This reverse thrust corresponds to the degree of deviation of the bearing shaft 2, achieving an adaptive adjustment effect and realizing variable thrust regulation. The elastic diaphragm 32 can undergo elastic deformation, causing the drainage gaps 321 on both sides to increase and decrease respectively, resulting in a higher response speed.

[0056] Therefore, regardless of the circumferential direction of the bearing shaft 2, it can automatically return to a neutral equilibrium state through the adjustment of the bidirectional hydraulic feedback throttle 3, achieving the technical effect of automatic correction. A uniformly distributed oil film is formed circumferentially between the bearing shaft 2 and the hydrostatic bearing support 1 as a gap, reducing friction and thus accurately reflecting the true modal response of the measured object, while also extending its service life.

[0057] Based on the above technical solutions, combined with Figure 4As shown, the hydrostatic oil chamber 12 of the present invention includes an outer oil chamber 121 and an inner oil chamber 122. The outer oil chamber 121 and the inner oil chamber 122 are located at different positions in the axial direction. The outer oil chamber 121 and the inner oil chamber 122 are each set to an even number, and are symmetrically distributed in pairs in the circumferential direction of the mounting cavity 11. The number and size of the outer oil chamber 121 and the inner oil chamber 122 can be the same or different.

[0058] Correspondingly, the bidirectional hydraulic feedback throttle 3 includes an outer throttle 3.1 and an inner throttle 3.2. The outer throttle 3.1 is used to supply oil to the outer oil chamber 121, and the inner throttle 3.2 is used to supply oil to the inner oil chamber 122. (See attached diagram of the present invention.) Figure 4 , Figure 6 Taking the structure shown as an example, there are four outer oil chambers 121 and four inner oil chambers 122. The four outer oil chambers 121 are equipped with two outer throttles 3.1, and the four inner oil chambers 122 are equipped with two inner throttles 3.2.

[0059] Because it employs two layers of oil cavities, one inside and one outside the axis, the support range for the bearing shaft 2 is larger. Therefore, when the bearing shaft 2 is subjected to... Figure 3 When the torque is of a left-high-right-low or left-low-right-high type, the outer oil chamber 121 and the inner oil chamber 122 can provide better resistance. When the bearing shaft 2 is torn, combined with Figure 2 As shown, the torsion direction is torsion around the X-axis, torsion around the Y-axis, or a combination of torsion around the X-axis and the Y-axis. This will also cause the distance between the bearing shaft 2 and the static pressure oil chamber 12 to change. This can also be corrected by the bidirectional hydraulic feedback throttle 3.

[0060] Specifically, the pressure in the inner oil cavity 122 is higher than the pressure in the outer oil cavity 121. The inner oil cavity 122 is used to increase the load-bearing capacity, while the outer oil cavity 121 is used to increase the stiffness. That is, the inner oil cavity 122 is mainly used to bear gravity, while the outer oil cavity 121 is mainly used to resist torsion.

[0061] In one embodiment, the axial width of the inner oil cavity 122 is greater than the axial width of the outer oil cavity 121, and the difference in support capacity between the inner and outer layers is achieved by setting different widths.

[0062] Combination Figure 4 As shown, Figure 3The structure of the static pressure bearing support 1 on the left is shown, while the static pressure bearing support 1 on the right is arranged symmetrically with it. The static pressure bearing support 1 includes an oil supply ring groove 13, an oil drain groove 14, and an oil drain hole 15. The oil drain groove 14 is located on both sides of the static pressure oil chamber 12 in the axial direction. Each static pressure bearing support 1 is provided with two oil drain grooves 14. The oil drain groove 14 is a deep groove arranged in the radial direction. The oil flows out from the static pressure oil chamber 12 (outer oil chamber 121 and inner oil chamber 122) and enters the gap between the bearing shaft 2 and the mounting cavity 11. When it flows into the oil drain groove 14, the oil is discharged.

[0063] The oil flows through the oil supply ring groove 13 to the bidirectional hydraulic feedback throttle 3, supplying oil to each bidirectional hydraulic feedback throttle 3 from the outside. The oil discharged from the gap between the bearing shaft 2 and the mounting cavity 11 flows through the oil drain groove 14 to the oil drain hole 15, and is finally discharged to the outside.

[0064] Combination Figure 1 , Figure 4 As shown, a sealing cover 4 is provided on the wall surface of the hydrostatic bearing support 1 facing the bearing shaft 2, and a dust cover 5 is provided on the wall surface away from the bearing shaft 2. The sealing cover 4 is installed on the end face of the hydrostatic bearing support 1 to seal the high-pressure oil. A sealing ring is installed on the sealing cover 4 and is fixed to the end face of the hydrostatic bearing support 1 by screws to seal the oil supply ring groove 13. The dust cover 5 is made of flexible felt and is used for external dust protection to prevent dust from entering the gap between the hydrostatic bearing support 1 and the bearing shaft 2 and affecting the performance of the hydrostatic oil film.

[0065] Combination Figure 1 As shown, the static pressure bearing support 1 is supported and fixed by the mounting support 6. The mounting support 6 is fixed to the required mounting surface by screws. The mounting support 6 is equipped with a flange and is fixed by bolts.

[0066] The hydrostatic bearing support 1 has a copper alloy coating inside to control the oil film gap and is repairable.

[0067] Furthermore, an angle sensor can be installed on the bearing shaft 2 to measure the torsion angle and accurately measure the torsion state of the bearing shaft 2.

[0068] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism, characterized in that, It includes a static pressure bearing support (1) and a bearing shaft (2), with each end of the bearing shaft (2) supported by at least one of the static pressure bearing supports (1); the bearing shaft (2) is used to mount the test piece; The static pressure bearing support (1) includes an installation cavity (11) for inserting the bearing shaft (2). The inner wall of the installation cavity (11) is provided with static pressure oil cavities (12). The number of static pressure oil cavities (12) is even and they are symmetrically distributed in pairs in the circumferential direction of the installation cavity (11). Two symmetrically arranged hydrostatic oil chambers (12) are supplied with oil through a bidirectional hydraulic feedback throttle (3); the bidirectional hydraulic feedback throttle (3) includes a mounting housing (31), an elastic diaphragm (32), and two inlet guide posts (33); each inlet guide post (33) has an inlet throttle hole (331) on its side wall; one end of each of the two inlet guide posts (33) is fixed to the mounting housing (31), and the elastic diaphragm (32) is installed on the two inlet guide posts (33). Between the liquid guide columns (33), and forming a drain gap (321) with the liquid inlet guide column (33); the outer periphery of the elastic diaphragm (32) is installed on the mounting shell (31), dividing the interior of the mounting shell (31) into two oil chambers (311), and the mounting shell (31) is provided with an outlet throttling hole (312), through which the oil in the oil chamber (311) is supplied to the two symmetrically arranged hydrostatic oil chambers (12) respectively; The oil flows to the inlet (332) of the two inlet guide columns (33). A portion of the oil enters from one of the inlet guide columns (33) and flows to the oil chamber (311) through the inlet throttle hole (331) to form pressurized oil. The other portion of the oil flows to the oil chamber (311) through the drain gap (321) to release pressure. When the bearing shaft (2) approaches a certain hydrostatic oil chamber (12), the oil pressure in the corresponding oil chamber (311) rises, causing the elastic diaphragm (32) to be elastically deformed to the other side. The distance between the elastic diaphragm (32) and the other inlet guide post (33) decreases, allowing more oil to flow into the inlet throttle orifice (331), increasing the oil pressure in the other oil chamber (311), causing the elastic diaphragm (32) to be pushed back in the opposite direction, and thus pushing the bearing shaft (2) back in the opposite direction.

2. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 1, characterized in that, The static pressure oil chamber (12) includes an outer oil chamber (121) and an inner oil chamber (122). The outer oil chamber (121) and the inner oil chamber (122) are each set to an even number, and are symmetrically distributed in pairs in the circumferential direction of the mounting cavity (11). The bidirectional hydraulic feedback throttle (3) includes an outer throttle (3.1) and an inner throttle (3.2). The outer throttle (3.1) is used to supply oil to the outer oil chamber (121), and the inner throttle (3.2) is used to supply oil to the inner oil chamber (122).

3. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 2, characterized in that, The pressure in the inner oil cavity (122) is higher than the pressure in the outer oil cavity (121). The inner oil cavity (122) is used to improve the load-bearing capacity, and the outer oil cavity (121) is used to improve the stiffness.

4. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 3, characterized in that, The axial width of the inner oil cavity (122) is greater than the axial width of the outer oil cavity (121).

5. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 1, characterized in that, The hydrostatic bearing support (1) includes an oil supply ring groove (13), an oil drain groove (14) and an oil drain hole (15), wherein the oil drain groove (14) is provided on both sides of the hydrostatic oil chamber (12) in the axial direction; The oil flows through the oil supply ring groove (13) to the bidirectional hydraulic feedback throttle (3), and the oil discharged from the gap between the bearing shaft (2) and the mounting cavity (11) flows through the oil drain groove (14) to the oil drain hole (15).

6. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 5, characterized in that, A sealing cover (4) is provided on the wall surface of the static pressure bearing support (1) facing the bearing shaft (2), and a dust cover (5) is provided on the wall surface away from the bearing shaft (2); A sealing ring is installed on the sealing cover (4), and the oil supply ring groove (13) is sealed by screws on the end face of the hydrostatic bearing support (1); the dust cover (5) is a flexible felt for external dust protection.

7. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 1, characterized in that, The static pressure bearing support (1) is supported and fixed by the mounting support (6), which is fixed to the required mounting surface by screws.

8. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 1, characterized in that, The hydrostatic bearing support (1) has a copper alloy coating inside to control the oil film gap and has repairability.

9. The bidirectional hydraulic feedback tension-torsion hydrostatic bearing mechanism according to claim 1, characterized in that, The bearing shaft (2) is equipped with an angle sensor for measuring the torsion angle.

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