Hydrostatic bearing

Abstract

The present invention relates to a hydrostatic bearing, comprising a first throttle and a first pressure-bearing member. The first throttle is provided with a first pressure oil groove, and a first oil channel is provided in the first pressure oil groove, and the first oil channel can pump pressure oil into the first pressure oil groove; a first oil delivery groove is protruding and formed in the first pressure oil groove, and the pressure oil in the first pressure oil groove can flow into the first oil delivery groove; the first pressure-bearing member and the first throttle are arranged relative to each other along the axial direction of the shaft, and the first pressure-bearing member is in contact with the turntable; a first pressure-bearing cavity is provided on the side of the first pressure-bearing member away from the first throttle; the first oil delivery groove is connected to the first pressure-bearing cavity, and the oil in the first oil delivery groove can flow between the first pressure-bearing cavity and the turntable under the action of pressure. Since the inflow of pressure oil in the first oil delivery groove increases and the leakage decreases, the flow rate into the first pressure-bearing cavity will be larger, thereby making the flow rate of pressure oil between the first pressure-bearing cavity and the end face of the turntable larger, and the stiffness of the entire hydrostatic bearing is also higher.

Description

Technical Field

[0001] The present invention relates to the technical field of hydrostatic turntables, in particular to hydrostatic bearings. Background Art

[0002] Hydrostatic bearings are a type of bearing with excellent performance and widespread application. In existing technologies, the first throttle in a hydrostatic bearing is typically located within the first pressure-bearing cavity of the first pressure-bearing member. The first oil trough and the first pressure oil tank of the first throttle are both straight-cylinder structures and are arranged side by side. Consequently, when the pressurized oil in the first pressure oil tank is fed into the first oil delivery tank, one side of the first oil delivery tank receives the pressurized oil, while the other three sides of the first oil delivery tank overflow the pressurized oil to the periphery of the first oil delivery tank. This results in a low flow rate of the pressurized oil in the first oil delivery tank and reduced stiffness of the entire hydrostatic bearing. Summary of the Invention

[0003] Based on this, it is necessary to provide a hydrostatic bearing to address the technical problem that when the first throttle is arranged in the first pressure-bearing cavity of the first pressure-bearing part, and the first oil delivery groove and the first pressure oil delivery groove of the first throttle are both straight-cylinder structures, the flow rate of the pressure oil in the first oil delivery groove is small and the stiffness of the entire hydrostatic bearing is low.

[0004] 18. The hydraulic cylinder of claim 17, wherein the hydraulic cylinder has an inwardly extending portion for guiding the hydraulic cylinder inwardly along the axial direction of the shaft toward the oil pump, the hydraulic cylinder having the inwardly extending portion for guiding the hydraulic cylinder inwardly along the axial direction of the shaft toward the oil pump.

[0005] In one embodiment, the number of the first oil delivery grooves is at least two, and the at least two first oil delivery grooves are spaced apart and arranged in the groove cavity of the first pressure oil groove.

[0006] In one embodiment, there are multiple first throttles, and the multiple first throttles are spaced apart along the circumferential direction and axial direction of the shaft; and each first throttle is fixedly connected to a first pressure-bearing member along the circumferential direction of the shaft.

[0007] In one embodiment, the first throttle and the first pressure-bearing member to which the first throttle is fixedly connected have a stepped structure, and the highest point of the first end surface of the outer periphery of the first throttle is lower than the highest point of the second end surface of the first pressure-bearing member.

[0008] In one embodiment, the hydrostatic bearing further comprises a bearing inner ring, which is used to be sleeved on the outer circumference of the shaft, and the bearing inner ring is arranged between the first throttle and the first pressure-bearing member; the side wall of the bearing inner ring is engraved with a second throttle and a second pressure-bearing member; the second pressure-bearing member and the second throttle are arranged at intervals along the circumference of the shaft, and the second pressure-bearing member is used to abut against the shaft; the second pressure-bearing member is recessed inwardly along its thickness direction to form a second pressure-bearing cavity, and the second pressure-bearing cavity is arranged on the side of the second pressure-bearing member close to the shaft; the second throttle is connected to the second pressure-bearing cavity, and the second throttle can pump the pressure oil into between the second pressure-bearing cavity and the outer surface of the shaft.

[0009] In one embodiment, the second throttle is recessed inwardly along its thickness direction to form a second pressure oil groove, a second oil channel is provided in the second pressure oil groove, the second oil channel is used to communicate with an external oil delivery channel, and the second oil channel can pump the pressure oil into the second pressure oil groove; the second throttle is also recessed inwardly along its thickness direction to form a second oil delivery groove, the second oil delivery groove is spaced apart from the second pressure oil groove, and the pressure oil in the second pressure oil groove can flow into the second oil delivery groove under pressure; the second oil delivery groove is connected to the second pressure-bearing chamber.

[0010] In one embodiment, a second oil delivery channel is engraved on the side of the bearing inner ring facing away from the pressure oil groove, one end of the second oil delivery channel is connected to the second oil delivery groove, and the other end of the second oil delivery channel is connected to the second pressure-bearing chamber.

[0011] In one embodiment, the second oil delivery channel extends along the circumference of the bearing inner ring, and the second oil delivery channel is a semi-annular structure.

[0012] In one embodiment, the bearing inner ring is further engraved with a third oil delivery groove along its axial direction, and the third oil delivery groove is connected to the second oil delivery groove and the second oil delivery channel.

[0013] In one embodiment, there are multiple second throttles, and the multiple second throttles are arranged at intervals along the circumference of the bearing inner ring; the number of the second pressure-bearing member is adapted to the number of the second throttles.

[0014] In one embodiment, the hydrostatic bearing further includes a bearing outer ring, which is sleeved on the outer circumference of the bearing inner ring and interference fits with the bearing inner ring, and the bearing outer ring is detachably connected to the first throttle and the first pressure-bearing member.

[0015] In one embodiment, the outer ring of the bearing is engraved with a first oil delivery channel along its axial direction, one end of the first oil delivery channel is connected to the first oil delivery groove, and the other end of the first oil delivery channel is connected to the first pressure-bearing chamber.

[0016] In one embodiment, a third oil passage is engraved on the outer ring of the bearing, and the third oil passage is used to communicate with an external oil delivery channel, and the third oil passage is connected with the first oil passage and the second oil passage.

[0017] In one embodiment, the bearing outer ring includes an upper bearing outer ring and a lower bearing outer ring, the upper bearing outer ring and the lower bearing outer ring are arranged opposite to each other along the axial direction of the shaft, and the upper bearing outer ring and the lower bearing outer ring are detachably connected.

[0018] Beneficial effects of the present invention:

[0019] The present invention provides a hydrostatic bearing. When it is installed on the hydrostatic turntable shaft, since the first pressure oil groove is protruded into the cavity along its bottom wall and forms a first oil delivery groove with an annular hollow structure, the groove wall of the first oil delivery groove can form a small gap between the turntable end face with which it is installed and matched. Therefore, when the pressure oil in the first pressure oil groove flows into the first oil delivery groove under the action of gap throttling, the entire annular side wall of the first oil delivery groove serves as the oil delivery edge for the pressure oil to flow in. Moreover, since the pressure oil in the first oil delivery groove is blocked by the groove wall of the first oil delivery groove, the pressure oil is not easy to overflow from the first oil delivery groove to the outer periphery of the first oil delivery groove.

[0020] Therefore, compared with traditional methods, the first oil delivery trough of this hydrostatic bearing is surrounded by the side walls of the first pressure oil trough, so the oil delivery side of the first oil delivery trough becomes wider and the leakage side becomes shorter. Therefore, the input amount of pressure oil in the first oil delivery trough is larger and the leakage amount is smaller, which makes the flow rate of pressure oil flowing into the first pressure-bearing chamber larger, and thus the flow rate of pressure oil between the first pressure-bearing chamber and the turntable larger, and the stiffness of the entire hydrostatic bearing is also higher. At the same time, because the first throttle of this hydrostatic bearing is arranged outside the first pressure-bearing chamber, it can prevent the pressure oil overflowing from the first oil delivery trough from flowing into the first pressure-bearing chamber, and the overflow flow outside the first throttle does not affect the flow control effect of the first pressure-bearing chamber. The flow rate flowing into the first pressure-bearing chamber can be calculated based on the output flow rate of the first oil delivery trough, so the calculated value of the flow rate flowing into the first pressure-bearing chamber is also more accurate. Moreover, the first throttle is arranged independently of the first pressure-bearing chamber, and the working state of the first throttle is also more controllable. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 An exploded schematic diagram of a hydrostatic bearing provided in one embodiment of the present invention;

[0022] Figure 2 for Figure 1 The top view of the hydrostatic bearing after installation is shown;

[0023] Figure 3 for Figure 2 A cross-sectional view of the hydrostatic bearing at AA is shown;

[0024] Figure 4 for Figure 3 A partial enlarged view of position B of the hydrostatic bearing shown;

[0025] Figure 5 for Figure 1 A schematic diagram of a first throttle and a first pressure-bearing member of a hydrostatic bearing shown;

[0026] Figure 6 for Figure 5 A front view of the first throttle and the first pressure-bearing member of the hydrostatic bearing shown;

[0027] Figure 7 for Figure 5 A partial enlarged view of the first throttle at position C shown;

[0028] Figure 8 for Figure 1 Schematic diagram of the bearing inner ring, the second throttle and the second pressure-bearing member of the hydrostatic bearing shown;

[0029] Figure 9 for Figure 8 A partial cross-sectional view of the bearing inner ring, the second throttle and the second pressure bearing of the hydrostatic bearing is shown.

[0030] Figure markings: 100-first throttle; 110-first pressure oil groove; 111-first oil channel; 120-first oil delivery groove; 121-first oil delivery hole; 130-first end face; 200-first pressure-bearing member; 210-first pressure-bearing cavity; 211-second oil delivery hole; 220-second end face; 300-bearing inner ring; 310-second oil delivery channel; 311-third oil delivery hole; 320-third oil delivery groove; 400-second throttle; 410-second pressure oil groove; 411-second oil channel; 420-second oil delivery groove; 421-fourth oil delivery hole; 500-second pressure-bearing member; 510-second pressure-bearing cavity; 600-bearing outer ring; 610-bearing upper outer ring; 620-bearing lower outer ring; 630-first oil delivery channel; 640-third oil channel. DETAILED DESCRIPTION

[0031] To make the above-mentioned objects, features, and advantages of the present invention more readily apparent, specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. The following description sets forth numerous specific details to facilitate a full understanding of the present invention. However, the present invention can be implemented in many other ways than those described herein, and those skilled in the art may make similar modifications without departing from the scope of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0032] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0033] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0034] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0035] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0036] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intermediate element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be an intermediate element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only implementation methods.

[0037] See Figures 1 - 3 , Figure 1 An exploded schematic diagram of a hydrostatic bearing provided by an embodiment of the present invention is shown; Figure 2 Shown Figure 1 The top view of the hydrostatic bearing after installation is shown; Figure 3 Shown Figure 2The cross-sectional view of the hydrostatic bearing at AA shown in the figure; the hydrostatic bearing provided by one embodiment of the present invention comprises a first throttle 100 and a first pressure-bearing member 200. The first throttle 100 is used to be installed on the outer periphery of the shaft. The first throttle 100 is recessed inwardly along its thickness direction to form a first pressure oil groove 110. A first oil channel 111 is provided in the first pressure oil groove 110. The first oil channel 111 is used to communicate with an external oil delivery channel. The first oil channel 111 can pump pressure oil into the first pressure oil groove 110. The first pressure oil groove 110 is protruded into the cavity along its bottom wall and forms a first oil delivery groove 120 with an annular hollow structure. The pressure oil in the first pressure oil groove 110 can be pumped into the pressure oil groove 110. Under the action of force, the oil flows into the first oil delivery groove 120; the first pressure-bearing member 200 and the first throttle 100 are arranged opposite to each other along the axial direction of the shaft, and the end of the first pressure-bearing member 200 away from the first throttle 100 is used to abut against the turntable; the side of the first pressure-bearing member 200 away from the first throttle 100 is recessed inward along its thickness direction to form a first pressure-bearing cavity 210; the first oil delivery groove 120 is connected to the first pressure-bearing cavity 210, and the oil in the first oil delivery groove 120 can flow into between the first pressure-bearing cavity 210 and the turntable under the action of pressure.

[0038] When the hydrostatic bearing is installed on the hydrostatic turntable shaft, since the first pressure oil groove 110 protrudes into the cavity along its bottom wall and forms a first oil delivery groove 120 with an annular hollow structure, the groove wall of the first oil delivery groove 120 can form a small gap between the turntable end face with which it is installed. Therefore, when the pressure oil in the first pressure oil groove 110 flows into the first oil delivery groove 120 under the action of gap throttling, the entire annular side wall of the first oil delivery groove 120 serves as the oil delivery edge for the pressure oil to flow in. Moreover, since the pressure oil in the first oil delivery groove 120 is blocked by the groove wall of the first oil delivery groove 120, the pressure oil is not easy to overflow from the first oil delivery groove 120 to the outer periphery of the first oil delivery groove 120. Therefore, compared to conventional methods, the first oil delivery groove 120 of this hydrostatic bearing is surrounded by the sidewalls of the first pressure oil groove 110, resulting in a wider oil delivery edge and a shorter leakage edge. This results in a larger input volume of pressure oil within the first oil delivery groove 120 and a smaller leakage volume, resulting in a larger flow rate of pressure oil flowing into the first pressure-bearing chamber 210. This, in turn, increases the flow rate of pressure oil between the first pressure-bearing chamber 210 and the turntable end face, and also enhances the stiffness of the entire hydrostatic bearing. Furthermore, because the first throttle 100 of this hydrostatic bearing is disposed outside the first pressure-bearing chamber 210, it prevents overflowing pressure oil from the first oil delivery groove 120 from flowing into the first pressure-bearing chamber 210. The overflow flow of the first throttle 100 does not affect the flow control effect of the first pressure-bearing chamber 210. The flow rate flowing into the first pressure-bearing chamber 210 can be calculated using the output flow rate of the first oil delivery groove 120, resulting in a more accurate calculated value of the flow rate flowing into the first pressure-bearing chamber 210. Moreover, the first throttle 100 is arranged independently of the first pressure-bearing chamber 210 , and the working state of the first throttle 100 is more controllable.

[0039] It should be noted that: the unit of stiffness is N / um; that is, under what force will the hydrostatic bearing have a deformation of 1 um.

[0040] The following specifically describes the structure of the hydrostatic bearing. Please refer to Figures 4 - 9 , Figure 4 shows Figure 3 a partial enlarged view of the B part of the hydrostatic bearing shown; Figure 5 shows Figure 1 a schematic diagram of the first restrictor 100 and the first pressure-bearing member 200 of the hydrostatic bearing shown; Figure 6 shows [[ID=…]] Figure 5 the front view of the first restrictor 100 and the first pressure-bearing member 200 of the hydrostatic bearing shown; Figure 7 shows Figure 5 a partial enlarged view of the C part of the first restrictor 100 shown; Figure 8 shows Figure 1 a schematic diagram of the bearing inner ring 300, the second restrictor 400 and the second pressure-bearing member 500 of the hydrostatic bearing shown; Figure 9 is Figure 8 a partial cross-sectional view of the bearing inner ring 300, the second restrictor 400 and the second pressure-bearing member 500 of the hydrostatic bearing shown.

[0041] In one embodiment of the present invention, the number of the first oil supply grooves 120 of the hydrostatic bearing is at least two, and at least two first oil supply grooves 120 are arranged at intervals in the cavity of the first pressure oil groove 110. By providing at least two or more first oil supply grooves, the flow rate of the pressure oil finally flowing into the first pressure-bearing cavity 210 is larger, and the stiffness of the entire hydrostatic bearing is also higher.

[0042] In one specific embodiment, please refer to Figure 1 [[ID=3……]] Figures 5 - 7 In one embodiment of the present invention, the number of the first oil supply grooves 120 of the hydrostatic bearing is at least two, and at least two first oil supply grooves 120 are arranged at intervals in the cavity of the first pressure oil groove 110. By providing at least two or more first oil supply grooves, the flow rate of the pressure oil finally flowing into the first pressure-bearing cavity 210 is larger, and the stiffness of the entire hydrostatic bearing is also higher.

[0043] Please refer to Figure 1 and Figure 2 ​, in an embodiment of the present invention, the number of the first restrictors 100 of the hydrostatic bearing is multiple, and the multiple first restrictors 100 are respectively arranged at intervals along the circumferential and axial directions of the shaft; and a first pressure-bearing member 200 is fixedly connected along the circumferential direction of each first restrictor 100. Since there are multiple first restrictors 100, and each first restrictor 100 is arranged at intervals along the circumferential and axial directions of the shaft, and each first restrictor 100 is fixedly connected with a first pressure-bearing member 200 along the circumferential direction of the shaft, it is possible to form a group with a first restrictor 100 and a first pressure-bearing member 200 up and down. The upper first restrictor 100 supplies oil to the lower first pressure-bearing member 200, or the lower first restrictor 100 supplies oil to the upper first pressure-bearing member 200, so that the upper and lower first restrictors 100 and first pressure-bearing members 200 are staggered, reducing the oil circuit length and lowering the pipe loss; the oil pressures of the pressure oils on the upper and lower sides will also be more balanced during the up and down flow; at the same time, the structure of the entire hydrostatic bearing is relatively compact and convenient for installation.

[0044] In one specific embodiment, the number of the first restrictors 100 is 16. The 16 first restrictors 100 are arranged in two layers at intervals along the axial direction of the shaft, and the 8 first restrictors 100 in each layer are also arranged at intervals along the circumferential direction of the shaft, and the number of the first pressure-bearing members 200 is adapted to the number of the first restrictors 100. By forming a group with a first restrictor 100 and a first pressure-bearing member 200 up and down, 16 groups of first pressure-bearing assemblies are formed by the 16 first restrictors 100 and 16 first pressure-bearing members 200, and the stiffness of this hydrostatic bearing is increased by 39% compared with the stiffness of the straight-groove hydrostatic bearing.

[0045] In a specific test experiment, two hydrostatic bearings with an outer diameter of 690 mm, an inner diameter of 470 mm, and a single end face including eight groups (a total of 16 groups) of first restrictors 100 and first pressure-bearing members 200 up and down were designed. The total gap between the hydrostatic bearing and the end face of the hydrostatic turntable is 0.05 mm. The bearing pressure chamber areas and the oil-sealing edge gaps of the two bearings are the same, and the sizes of the oil supply grooves are also the same. The only difference is the first oil supply groove 120 and the first pressure oil groove 110. The first oil supply groove 120 and the first pressure oil groove 110 of one hydrostatic bearing are traditional straight-groove oil grooves, and the first oil supply groove 120 and the first pressure oil groove 110 of the other hydrostatic bearing are the "day"-shaped oil grooves provided by the present invention. The comparison is as follows:

[0046] Balanced position (mm) Full load position (mm) Full load magnitude (N) Stiffness N / μm Straight groove type oil groove 0.0239 0.0222 15000 8560 "Day”-shaped oil groove 0.0245 0.0233 15000 11930

[0047] Table 1

[0048] As can be seen from Table 1 above, under the same other conditions, the stiffness of the hydrostatic bearing provided by the present invention is increased by more than 39% compared with the stiffness of the traditional hydrostatic bearing.

[0049] Specifically, according to the gap throttling, the relationship between flow rate, gap height, pressure, etc. can be expressed as:

[0050]

[0051] Wherein, q is the flow rate of the pressurized oil flowing into the first pressure-bearing chamber 210; ΔP is the pressure difference between the first oil delivery groove 120 and the upper and lower ends of the first pressure-bearing chamber 210; L is the length of the first oil delivery groove 120; bi is the width of the first oil delivery groove 120; h is the height of the gap between the upper end surface of the first pressure-bearing member 200 and the lower end surface of the turntable; u is the dynamic viscosity of the pressurized oil;

[0052] By shifting the terms in this equation, we can get:

[0053]

[0054] Derivative the equation after the shift. We get:

[0055]

[0056] It can be seen from the above formula that when other conditions remain unchanged, the rate of change of h relative to q is inversely proportional to the size of the flow rate q. That is to say, the greater the flow rate, the smaller the rate of change of the height gap h. A smaller rate of change of the gap height means a higher stiffness. Therefore, when the hydrostatic bearing of the present application is adopted, due to the two first oil delivery grooves 120 and the first pressure oil groove 110, the first throttle 100 is formed into a "sun" shaped oil groove. The "sun" shaped oil groove increases the flow rate of the pressure oil in the first pressure-bearing chamber 210, so that the flow rate of the pressure oil between the first pressure-bearing chamber 210 and the turntable end face is larger, and the rate of change of the height gap h between the first pressure-bearing part 200 and the turntable end face is smaller, thereby making the stiffness of the entire hydrostatic bearing larger.

[0057] It should be noted that in some embodiments, the structural and geometric parameters of the multiple first throttles 100 and first pressure-bearing members 200 installed along the axial direction of the shaft may be the same or different. For example, the length, width, or height of the first pressure oil grooves 110 and first oil delivery grooves 120 between the multiple first throttles 100, and the number of first oil delivery grooves 120; and the length, width, or height of the first pressure-bearing chambers 210 between the multiple first pressure-bearing members 200 may be the same or different, and no limitation is imposed on this.

[0058] See also Figures 5 - 7In one embodiment of the present invention, the first throttle 100 of the hydrostatic bearing provided by the present invention and the first pressure-bearing member 200 to which it is fixedly connected have a stepped structure, and the highest point of the first end surface 130 of the outer periphery of the first throttle 100 is lower than the highest point of the second end surface 220 of the first pressure-bearing member 200. Because the highest point of the first end surface 130 of the outer periphery of the first throttle 100 is lower than the highest point of the second end surface 220 of the first pressure-bearing member 200, the pressure oil in the first pressure oil groove 110 is unlikely to overflow into the first pressure-bearing chamber 210 of the first pressure-bearing member 200. The pressure oil in the first pressure-bearing chamber 210 is transported only through the first oil delivery groove 120, so the flow rate flowing into the first pressure-bearing chamber 210 can be calculated based on the output flow rate of the first oil delivery groove 120, ultimately making the calculated value of the flow rate flowing into the first pressure-bearing chamber 210 more accurate.

[0059] See also Figure 1 、 Figure 3 、 Figure 8 and Figure 9 The hydrostatic bearing provided in one embodiment of the present invention further includes a bearing inner ring 300, which is configured to be sleeved around the outer circumference of the shaft and disposed between the first throttle 100 and the first pressure-bearing member 200. A second throttle 400 and a second pressure-bearing member 500 are engraved on the sidewall of the bearing inner ring 300. The second pressure-bearing member 500 and the second throttle 400 are spaced apart along the circumference of the shaft, and the second pressure-bearing member 500 is configured to abut the shaft. The second pressure-bearing member 500 is recessed inwardly along its thickness to form a second pressure-bearing cavity 510, which is disposed on a side of the second pressure-bearing member 500 close to the shaft. The second throttle 400 is in communication with the second pressure-bearing cavity 510, and the second throttle 400 is capable of pumping pressurized oil between the second pressure-bearing cavity 510 and the outer surface of the shaft. The pressure oil is delivered to the second pressure-bearing chamber 510 through the second throttle 400, so that the space between the second pressure-bearing chamber 510 and the outer surface of the shaft is filled with pressure oil, thereby reducing the wear of the outer surface of the shaft.

[0060] Since the second throttle 400 and the second pressure-bearing member 500 are directly engraved on the bearing inner ring 300 , the entire hydrostatic bearing does not need to be additionally connected with the second throttle 400 and the second pressure-bearing member 500 , and the structure of the entire hydrostatic bearing is also more compact.

[0061] In one specific embodiment, the structure of the second throttle 400 is a traditional straight groove type oil groove structure. Therefore, the engraving process of the second throttle 400 is relatively simple, and the cost of the entire hydrostatic bearing is relatively low. In another specific embodiment, the structure of the second throttle 400 is the "day" shaped oil groove structure provided by the present invention, which makes the flow rate of the pressure oil between the second pressure bearing cavity 510 and the outer surface of the shaft relatively large. The radial stiffness of the entire hydrostatic bearing is relatively large, and it can bear more radial loads. It should be noted that the structural selection of the second throttle 400 is not limited, and it can be adaptively modified according to the magnitude of the radial load to be borne.

[0062] Please refer to Figure 1 、 Figure 3 、 Figure 4 and Figure 8 For the hydrostatic bearing second throttle 400 provided by an embodiment of the present invention, a second pressure oil groove 410 is recessed inward along its thickness direction. A second oil passage 411 is provided in the second pressure oil groove 410. The second oil passage 411 is used to communicate with an external oil delivery channel, and the second oil passage 411 can pump pressure oil into the second pressure oil groove 410; the second throttle 400 is further recessed inward along its thickness direction to form a second oil delivery groove 420. The second oil delivery groove 420 is arranged at an interval from the second pressure oil groove 410. The pressure oil in the second pressure oil groove 410 can flow into the second oil delivery groove 420 under the action of pressure; the second oil delivery groove 420 is communicated with the second pressure bearing cavity 510. When the hydrostatic bearing is in use, when the second oil passage 411 pumps pressure oil into the second pressure oil groove 410, the pressure oil overflows from the second pressure oil groove 410 under the action of pressure and flows into the second oil delivery groove 420. The second oil delivery groove 420 then transports the pressure oil into the second pressure bearing cavity 510, so that the second pressure bearing cavity 510 and the outer surface of the shaft are filled with pressure oil, reducing the wear condition of the outer surface of the shaft.

[0063] It should be noted that when the second oil delivery groove 420 is arranged at an interval from the second pressure oil groove 410, this second throttle 400 is a traditional straight groove type oil groove structure. Through this second throttle 400, the cost of the entire hydrostatic bearing can be relatively low, and it is suitable for the hydrostatic turntable bearing with a relatively small radial load on the shaft and a relatively large lateral load.

[0064] Please refer to Figure 8 and Figure 9A second oil channel 310 is engraved on the side of the inner ring 300 of the hydrostatic bearing provided by one embodiment of the present invention, facing away from the pressure oil groove. One end of the second oil channel 310 communicates with the second oil groove 420, and the other end of the second oil channel 310 communicates with the second pressure-bearing chamber 510. By engraving the oil channel on the inner ring 300, the second throttle 400 and the second pressure-bearing member 500 are connected, eliminating the need for an additional oil channel and making the entire hydrostatic bearing structure more compact.

[0065] See also Figure 8 and ​ The second oil channel 310 of the hydrostatic bearing provided in one embodiment of the present invention extends circumferentially along the bearing inner ring 300 and has a semi-annular structure. Because the second oil channel 310 extends circumferentially along the bearing inner ring 300 and has a semi-annular structure, each second throttle 400 and its corresponding second pressure-bearing member 500 are paired and arranged at an 180-degree angle. This provides excellent processability for the entire hydrostatic bearing inner ring 300, effectively reducing manufacturing costs. Specifically, a fourth oil hole 421 is provided within the second oil groove 420. A third oil hole 311 is defined at one end of the second oil channel 310, which communicates with the second pressure-bearing chamber 510. The other end of the second oil channel 310 communicates with the fourth oil hole 421.

[0066] See also ​ and ​ The inner ring 300 of the hydrostatic bearing provided in one embodiment of the present invention further includes a third oil groove 320 along its axial direction. The third oil groove 320 is connected to both the second oil groove 420 and the second oil channel 310. Under pressure, the pressurized oil in the second oil groove 420 flows into the third oil groove 320, then into the second oil channel 310, ultimately flowing into the second pressure-bearing chamber 510. The third oil groove 320 stores and releases the pressurized oil, ensuring a relatively constant pressure for the pressurized oil that ultimately flows into the second pressure-bearing chamber 510. This reduces the rate of change in the thickness of the pressurized oil between the second pressure-bearing chamber 510 and the outer surface of the shaft.

[0067] See also ​ 、 ​ and ​The hydrostatic bearing provided in one embodiment of the present invention includes multiple second throttles 400, which are spaced apart circumferentially around the bearing inner ring 300. The number of second pressure-bearing members 500 matches the number of second throttles 400. By providing multiple second throttles 400 and spacing them apart circumferentially around the bearing inner ring 300, pressurized oil can be more effectively filled between the outer surface of the shaft in contact with the hydrostatic bearing and the second pressure-bearing members 500, effectively improving the radial stiffness and load capacity of the hydrostatic bearing.

[0068] By engraving the second throttle 400 and the second pressure-bearing member 500 on the side wall of the bearing inner ring 300, the parts of the radial bearing are completed by only one bearing inner ring 300, which not only makes the structure simple and compact, but also effectively reduces the manufacturing cost.

[0069] See also ​ The hydrostatic bearing provided in one embodiment of the present invention further includes a bearing outer ring 600. The bearing outer ring 600 is sleeved on the outer circumference of the bearing inner ring 300 and has an interference fit therewith. The bearing outer ring 600 is detachably connected to the first throttle 100 and the first pressure-bearing member 200. By sleeved on the outer circumference of the bearing inner ring 300 and detachably connected to the first throttle 100 and the first pressure-bearing member 200, the bearing outer ring 600 forms a sealed oil circuit with the bearing inner ring 300, thereby allowing pressurized oil to flow within the sealed second oil delivery channel 310. This also facilitates installation and disassembly of the entire hydrostatic bearing.

[0070] It should be noted that since the first throttle 100 and the first pressure-bearing member 200 are detachably connected to the bearing outer ring 600, when the first throttle 100 and the first pressure-bearing member 200 need to be replaced after long-term use and wear, or when the first throttle 100 and the first pressure-bearing member 200 are scratched by dry friction during startup and overload of the hydrostatic bearing and need to be replaced, the first throttle 100 and the first pressure-bearing member 200 can be detached from the bearing outer ring 600 and replaced. It can be seen that the first throttle 100 and the first pressure-bearing member 200 of the hydrostatic bearing provided by the present invention are replaceable functional panels, which not only reduces processing and use costs, but also achieves convenient maintenance.

[0071] See also ​The outer ring 600 of a hydrostatic bearing provided in one embodiment of the present invention is engraved with a first oil channel 630 along its axial direction. One end of the first oil channel 630 communicates with the first oil groove 120, and the other end of the first oil channel 630 communicates with the first pressure-bearing chamber 210. When the hydrostatic bearing is in use, the pressurized oil in the first oil groove 120 is transported to the first pressure-bearing chamber 210 through the first oil channel 630. In one specific embodiment, each first throttle 100 and first pressure-bearing member 200 communicates with two first oil channels 630, reducing the adverse oil flow caused by blockage of a single first oil channel 630. Specifically, a first oil hole 121 is provided in the first oil groove 120, and a second oil hole 211 is provided in the first pressure-bearing chamber 210. One end of the first oil channel 630 communicates with the first oil hole 121, and the other end of the first oil channel 630 communicates with the second oil hole 211.

[0072] See also ​ A third oil passage 640 is engraved on the outer ring 600 of a hydrostatic bearing provided in one embodiment of the present invention. This third oil passage 640 communicates with the oil delivery channel, and further communicates with the first oil passage 111 and the second oil passage 411. By engraving the third oil passage 640 on the outer ring 600, the entire hydrostatic bearing's oil passages can be internally located. This not only shortens the oil passages, reduces oil pipe loss, and reduces manufacturing costs, but also improves the hydrostatic bearing's structural compactness and reduces the bearing's assembly volume.

[0073] See also ​ The outer ring 600 of a hydrostatic bearing provided in one embodiment of the present invention includes an upper outer ring 610 and a lower outer ring 620. The upper outer ring 610 and the lower outer ring 620 are disposed axially opposite each other and are detachably connected. By separating the upper outer ring 610 and the lower outer ring 620, the outer ring 600 is more conveniently mounted on the bearing inner ring 300.

[0074] In one specific embodiment, the end surfaces of the first pressure-bearing member 200 and the second pressure-bearing member 500 are coated with a wear-resistant coating material. This reduces wear when the first pressure-bearing member contacts the turntable end surface, and when the second pressure-bearing member 500 contacts the outer end surface of the shaft. This also optimizes the starting and emergency stopping performance of the hydrostatic bearing. In one specific embodiment, the coating material can be an Al-Sn-Cu coating. In other embodiments, the coating material can also be high-hardness ceramic particles, etc., without limitation.

[0075] In one specific embodiment, the end surfaces of the first restrictor 100 and the second restrictor 400 are coated with a wear-resistant coating material, so that the first restrictor 100 and the second restrictor 400 are not easily worn. In one specific embodiment, the coating material can be an Al-Sn-Cu coating. Of course, in other embodiments, the coating material can also be selected from high-hardness ceramic particles, etc., which is not limited to this.

[0076] It should be noted that, in other embodiments, all pressure-bearing surfaces of the hydrostatic bearing may also be coated with a wear-resistant coating material.

[0077] In one specific embodiment, the walls of the pressure oil grooves, oil delivery grooves, oil delivery channels, oil passages and oil delivery holes provided by the hydrostatic bearing are coated with an anti-rust coating, so that the hydrostatic bearing is not easily rusted during use.

[0078] See also ​ The hydrostatic bearing provided in one embodiment of the present invention is assembled from a first throttle 100, a first pressure-bearing member 200, a bearing inner ring 300, and a bearing outer ring 600. This facilitates the machining of the oil grooves, oil passages, and oil holes on the individual components, resulting in high manufacturability and low cost. Application of wear-resistant and rust-proof coatings to the pressure-bearing surfaces is also relatively easy. Furthermore, because the entire oil groove and oil passage are integrated into the bearing body, the overall structure is relatively compact, occupying less space.

[0079] It should be noted that any single component structure or different combination structures within the hydrostatic bearing can also be applied to hydrostatic guide rails or other hydrostatic structures without any limitation. For example, the structure in which the first throttle 100 and the first pressure-bearing member 200 cooperate with each other can be applied to hydrostatic guide rails.

[0080] The technical features of the above-mentioned embodiments can be combined arbitrarily. In order to make the description concise, not all possible combinations of the technical features in the above-mentioned embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0081] The above-described embodiments merely illustrate several implementations of the present invention, and while their descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent. It should be noted that a person skilled in the art would be able to make numerous variations and improvements without departing from the spirit of the present invention, all of which fall within the scope of protection of the present invention. Therefore, the scope of protection of the patent for this invention shall be determined by the appended claims.

Claims

1. A hydrostatic bearing, characterized in that: The hydrostatic bearing comprises: a first throttle, the first throttle being mounted on the outer periphery of the shaft, the first throttle being recessed inwardly along its thickness direction to form a first pressure oil groove, a first oil channel being provided in the first pressure oil groove, the first oil channel being configured to communicate with an external oil delivery channel, the first oil channel being capable of pumping pressure oil into the first pressure oil groove; the first pressure oil groove being configured to protrude into the cavity along its bottom wall to form a first oil delivery groove having an annular hollow structure, the pressure oil in the first pressure oil groove being capable of flowing into the first oil delivery groove under pressure; A first pressure-bearing member, wherein the first pressure-bearing member and the first throttle are arranged opposite to each other along the axial direction of the shaft, and the end of the first pressure-bearing member facing away from the first throttle is used to abut against the turntable; the side of the first pressure-bearing member facing away from the first throttle is recessed inwardly along its thickness direction to form a first pressure-bearing cavity; the first oil delivery groove is connected to the first pressure-bearing cavity, and the pressure oil in the first oil delivery groove can flow between the first pressure-bearing cavity and the turntable under the action of pressure.

2. The hydrostatic bearing according to claim 1, characterized in that: The number of the first oil delivery grooves is at least two, and the at least two first oil delivery grooves are arranged in the groove cavity of the first pressure oil groove at intervals.

3. The hydrostatic bearing according to claim 1 or 2, characterized in that: There are multiple first throttles, and the multiple first throttles are spaced apart along the circumferential direction and the axial direction of the shaft; and each first throttle is fixedly connected to a first pressure-bearing member along the circumferential direction of the shaft.

4. The hydrostatic bearing according to claim 3, characterized in that: The first pressure-bearing member to which the first throttle is fixedly connected has a stepped structure, and the highest point of a first end surface of an outer periphery of the first throttle is lower than the highest point of a second end surface of the first pressure-bearing member.

5. The hydrostatic bearing according to claim 1, wherein: The static pressure bearing further includes a bearing inner ring, the bearing inner ring is used to be sleeved on the outer circumference of the shaft, and the bearing inner ring is arranged between the first throttle and the first pressure bearing member; The side wall of the inner ring of the bearing is engraved with a second throttle and a second pressure-bearing member; the second pressure-bearing member and the second throttle are arranged at intervals along the circumference of the shaft, and the second pressure-bearing member is used to abut against the shaft; the second pressure-bearing member is recessed inwardly along its thickness direction to form a second pressure-bearing cavity, and the second pressure-bearing cavity is arranged on the side of the second pressure-bearing member close to the shaft; the second throttle is connected to the second pressure-bearing cavity, and the second throttle can pump the pressure oil into between the second pressure-bearing cavity and the outer surface of the shaft.

6. The hydrostatic bearing according to claim 5, characterized in that: The second throttle is recessed inwardly along its thickness direction to form a second pressure oil groove, and a second oil channel is provided in the second pressure oil groove. The second oil channel is used to communicate with an external oil delivery channel, and the second oil channel can pump the pressure oil into the second pressure oil groove; the second throttle is also recessed inwardly along its thickness direction to form a second oil delivery groove, and the second oil delivery groove is spaced apart from the second pressure oil groove. The pressure oil in the second pressure oil groove can flow into the second oil delivery groove under pressure; the second oil delivery groove is connected to the second pressure-bearing chamber.

7. The hydrostatic bearing according to claim 6, characterized in that: A second oil delivery channel is engraved on the side of the bearing inner ring away from the second pressure oil groove. One end of the second oil delivery channel is connected to the second oil delivery groove, and the other end of the second oil delivery channel is connected to the second pressure chamber.

8. The hydrostatic bearing according to claim 7, characterized in that: The second oil delivery channel extends along the circumference of the bearing inner ring, and the second oil delivery channel is a semi-annular structure.

9. The hydrostatic bearing according to claim 8, characterized in that: The bearing inner ring is further engraved with a third oil delivery groove along its axial direction, and the third oil delivery groove is communicated with the second oil delivery groove and the second oil delivery channel.

10. The hydrostatic bearing according to any one of claims 5 to 9, characterized in that: There are multiple second throttles, and the multiple second throttles are arranged at intervals along the circumference of the bearing inner ring; the number of the second pressure-bearing parts is adapted to the number of the second throttles.

11. The hydrostatic bearing according to claim 6, wherein: The hydrostatic bearing further includes a bearing outer ring, which is sleeved on the outer circumference of the bearing inner ring and interference fits with the bearing inner ring. The bearing outer ring is detachably connected to the first throttle and the first pressure-bearing member.

12. The hydrostatic bearing according to claim 11, wherein: The outer ring of the bearing is engraved with a first oil delivery channel along its axial direction. One end of the first oil delivery channel is connected to the first oil delivery groove, and the other end of the first oil delivery channel is connected to the first pressure-bearing chamber.

13. The hydrostatic bearing according to claim 11, wherein: A third oil passage is engraved on the outer ring of the bearing. The third oil passage is used to communicate with an external oil delivery channel, and the third oil passage is communicated with the first oil passage and the second oil passage.

14. The hydrostatic bearing according to any one of claims 11 to 13, characterized in that: The bearing outer ring includes an upper bearing outer ring and a lower bearing outer ring. The upper bearing outer ring and the lower bearing outer ring are arranged opposite to each other along the axial direction of the shaft, and the upper bearing outer ring and the lower bearing outer ring are detachably connected.

Images