Hydrostatic bearing

Abstract

The application discloses a kind of liquid static pressure bearing, comprising: bearing and throttling device.Therein, bearing includes body and shaft core, body is provided with through hole, the both ends of through hole have first tapered cavity and second tapered cavity respectively, and along the direction away from second tapered cavity, the cross-sectional area of first tapered cavity gradually increases, along the direction away from first tapered cavity, the cross-sectional area of second tapered cavity gradually increases, shaft core is worn in through hole, shaft core includes front section shaft core and rear section shaft core, first tapered section is set on front section shaft core and is adapted to first tapered cavity, second tapered section is set on rear section shaft core and is adapted to second tapered cavity, between the outer peripheral surface of first tapered section and the inner wall surface of first tapered cavity, and between the outer peripheral surface of second tapered section and the inner wall surface of second tapered cavity, static pressure cavity is arranged.The application solves the problem that the rigidity of oil cannot be automatically adjusted according to the stress condition of bearing in the prior art.

Description

Technical Field

[0001] This application relates to the field of ultra-precision machine tool technology, and more specifically, to a hydrostatic bearing. Background Technology

[0002] Traditional rolling bearing elements, such as ball or roller bearings, have irregularities on their inner or outer rings. When each roller passes these irregularities, it deviates from its correct trajectory, and this deviation is transmitted to the supported component, making it difficult for the equipment to meet precision machining requirements. Hydrostatic bearings can replace traditional tapered roller bearings. They utilize hydrostatic pressure to support the load in a sliding bearing manner, offering numerous advantages over traditional rolling bearings and are widely used in the machinery manufacturing industry.

[0003] Compared to traditional rolling bearings, hydrostatic bearings offer superior load-bearing capacity: By carefully selecting the effective bearing area and throttling device, higher load-bearing capacity and oil film stiffness can be achieved. Hydrostatic bearings also boast high transmission efficiency: Due to pure liquid lubrication, the frictional resistance between contact surfaces is low, resulting in minimal power consumption and high transmission efficiency. Furthermore, hydrostatic bearings require lower structural precision: the oil chamber pressure depends on the average clearance across the entire chamber, rather than the minimum clearance at any given point. This averaging effect significantly reduces the impact of manufacturing errors. Finally, hydrostatic bearings have a long service life: operating under pure lubrication, the relative sliding surfaces are separated by a fluid film, preventing direct contact and thus eliminating wear issues.

[0004] However, existing hydrostatic bearings cannot automatically adjust the stiffness of the oil according to the stress conditions of the bearing. Summary of the Invention

[0005] The main objective of this application is to provide a hydrostatic bearing that at least solves the problem in the prior art that hydrostatic bearings cannot automatically adjust the stiffness of the oil according to the bearing's stress conditions.

[0006] According to one aspect of this application, a hydrostatic bearing is provided, comprising:

[0007] A bearing, comprising a body and a core, wherein the body has a through hole, and the two ends of the through hole have a first conical cavity and a second conical cavity respectively, and the cross-sectional area of ​​the first conical cavity gradually increases along the direction away from the second conical cavity, and the cross-sectional area of ​​the second conical cavity gradually increases along the direction away from the first conical cavity. The core is inserted into the through hole, and the core includes a front core and a rear core. The front core has a first conical segment adapted to the first conical cavity, and the rear core has a second conical segment adapted to the second conical cavity. Static pressure cavities are provided between the outer peripheral surface of the first conical segment and the inner wall surface of the first conical cavity, and between the outer peripheral surface of the second conical segment and the inner wall surface of the second conical cavity.

[0008] A throttle device is disposed on the outer peripheral surface of the body, and the throttle device includes:

[0009] The main body has a first side and a second side. A groove is formed on the first side of the main body, and a throttling boss is provided in the center of the groove. A first channel is provided on the throttling boss, and the first channel extends from the first side to the second side. A recess is provided on the second side of the main body, and the recess and the outer peripheral surface of the bearing body form an oil supply channel. The main body is also provided with an oil supply port, a first throttling channel and a second throttling channel. The oil supply port is connected to the oil supply channel and the second throttling channel.

[0010] A cover plate, which is disposed on the first side of the main body;

[0011] A thin film is disposed between the cover plate and the main body, and the thin film and the space of the groove located outside the throttling boss form a pressure stabilizing cavity, and the thin film and the cover plate form an adjustment cavity.

[0012] The first throttling channel is connected to the oil supply channel and the pressure stabilizing chamber at both ends, the second throttling channel is connected to the regulating chamber and the oil supply channel at both ends, and the first channel is connected to both the static pressure chamber and the oil supply channel.

[0013] Furthermore, the shaft core also includes an adjustment part disposed between the front shaft core and the rear shaft core, for at least adjusting the gap between the first tapered section and the first tapered cavity and the gap between the second tapered section and the second tapered cavity.

[0014] Furthermore, the adjustment part includes an adjustment pad, which has various models and different thicknesses. The various models of adjustment pads can be selectively installed between the front shaft core and the rear shaft core.

[0015] Furthermore, the static pressure chamber includes a first static pressure chamber and a second static pressure chamber. The first static pressure chamber is disposed between the outer peripheral surface of the first conical segment and the inner wall surface of the first conical cavity, and the second static pressure chamber is disposed between the outer peripheral surface of the second conical segment and the inner wall surface of the second conical cavity.

[0016] The throttle device includes a first throttle device and a second throttle device, wherein the first throttle device is connected to the first static pressure chamber and the second throttle device is connected to the second static pressure chamber.

[0017] Furthermore, both the first throttle and the second throttle include n units, and the n first throttles and the n second throttles are equally spaced on the outer peripheral surface of the body;

[0018] Both the first static pressure chamber and the second static pressure chamber include n, wherein the n first static pressure chambers are equally spaced on the inner wall surface of the first conical cavity, and the n second static pressure chambers are equally spaced on the inner wall surface of the second conical cavity;

[0019] n first throttles are connected to n first static pressure chambers in a one-to-one correspondence, and n second throttles are connected to n second static pressure chambers in a one-to-one correspondence;

[0020] Where n satisfies the relation: n≥2, and n∈N+.

[0021] Furthermore, n satisfies the relation: n≥3 and n≠4.

[0022] Furthermore, the body is provided with a first circumferential surface and a second circumferential surface at intervals along the axial direction. The first circumferential surface is provided with n first oil ports, and the oil supply ports of the n first throttles are connected to the n first oil ports in a one-to-one correspondence. Adjacent two first oil ports are connected through a first oil passage. The second circumferential surface is provided with n second oil ports, and the oil supply ports of the n second throttles are connected to the n second oil ports in a one-to-one correspondence. Adjacent two second oil ports are connected through a second oil passage.

[0023] The first oil passage is connected to the second oil passage through a third oil passage, and the main body is also provided with a main oil inlet passage, which is connected to the first oil passage and / or the second oil passage.

[0024] Furthermore, the oil supply channel includes a first flow channel and a second flow channel, which are concentrically arranged. The first flow channel is connected to the oil supply port, the second throttling channel, and the first throttling channel. The second flow channel is connected to the first flow channel and the first channel. The width of the first flow channel is greater than the width of the second flow channel.

[0025] Furthermore, a first static pressure channel is provided between the throttle and the first conical cavity, and the extending direction of the first static pressure channel is perpendicular to the conical surface of the first conical cavity; and / or,

[0026] A second static pressure channel is provided between the throttle and the second conical cavity, and the extension direction of the second static pressure channel is perpendicular to the conical surface of the second conical cavity.

[0027] Furthermore, the body is also provided with an oil outlet channel, which communicates with the through hole and is located between the first conical cavity and the second conical cavity.

[0028] Compared with the prior art, the diaphragm of the hydrostatic bearing of this application can monitor the pressure of the oil and automatically adjust the relative volume change between the pressure stabilizing chamber and the static pressure chamber according to the oil pressure to control the flow rate of the oil entering the static pressure chamber from the throttle, thereby dynamically adjusting the rigidity of the oil film in the static pressure chamber. Attached Figure Description

[0029] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0030] Figure 1 This is a schematic diagram of the hydrostatic bearing disclosed in this application from a first-view perspective.

[0031] Figure 2 This is a schematic diagram of the hydrostatic bearing disclosed in this application from a second-view perspective.

[0032] Figure 3 This is a cross-sectional view of the hydrostatic bearing disclosed in this application from one perspective;

[0033] Figure 4 This is a cross-sectional view of the hydrostatic bearing disclosed in this application from another perspective;

[0034] Figure 5 This is a schematic diagram of the bearing body disclosed in this application from a first-view perspective;

[0035] Figure 6This is a schematic diagram of the bearing body disclosed in this application from a second-view perspective;

[0036] Figure 7 This is a cross-sectional view of the bearing body disclosed in this application;

[0037] Figure 8 This is a schematic diagram of the first circumferential surface of the bearing body disclosed in this application;

[0038] Figure 9 This is a schematic diagram of the second circumferential surface of the bearing body disclosed in this application;

[0039] Figure 10 This is a schematic diagram of the structure of the throttle device disclosed in this application;

[0040] Figure 11 This is an exploded structural diagram of the throttle device disclosed in this application;

[0041] Figure 12 This is a schematic diagram of the main body of the throttle device disclosed in this application;

[0042] Figure 13 This is a schematic diagram of the cover plate of the throttle device disclosed in this application.

[0043] The above figures include the following reference numerals:

[0044] 10. Bearing; 11. Body; 12. Shaft core; 13. Through hole; 20. Throttling device; 21. Main body; 22. Cover plate; 23. Diaphragm sheet; 31. First oil outlet channel; 32. Second oil outlet channel; 41. First oil port; 42. Second oil port; 43. First oil passage channel; 44. Second oil passage channel; 45. Third oil passage channel; 46. Main oil inlet channel; 80. Seal; 111. First conical cavity; 112. Second conical cavity; 113. First hydrostatic cavity; 114. Second hydrostatic cavity; 115. First hydrostatic channel; 116. Second hydrostatic channel; 121. Front section shaft core; 122. Rear shaft core; 123. Adjustment part; 201. First throttle; 202. Second throttle; 211. First side; 212. Second side; 213. Oil supply port; 214. First throttle channel; 215. Second throttle channel; 221. Arc-shaped boss; 222. Groove; 223. First sealing groove; 1211. First conical section; 1221. Second conical section; 2111. Groove; 2112. Throttling boss; 2113. First channel; 2114. Bearing boss; 2121. First flow channel; 2122. Second flow channel; 2123. Second sealing groove. Detailed Implementation

[0045] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0046] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0047] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0048] See Figures 1 to 13 As shown, according to an embodiment of this application, a hydrostatic bearing is provided, including: a bearing 10 and a throttle 20.

[0049] The bearing 10 includes a body 11 and a core 12. The body 11 has a through hole 13, and the two ends of the through hole 13 have a first conical cavity 111 and a second conical cavity 112, respectively. The cross-sectional area of ​​the first conical cavity 111 gradually increases in the direction away from the second conical cavity 112, and the cross-sectional area of ​​the second conical cavity 112 gradually increases in the direction away from the first conical cavity 111. The core 12 passes through the through hole 13 and includes a front core 121 and a rear core 122. The front core 121 has a first conical segment 1211 adapted to the first conical cavity 111, and the rear core 122 has a second conical segment 1221 adapted to the second conical cavity 112. Static pressure cavities are provided between the outer peripheral surface of the first conical segment 1211 and the inner wall surface of the first conical cavity 111, and between the outer peripheral surface of the second conical segment 1221 and the inner wall surface of the second conical cavity 112. A throttle 20 is disposed on the outer peripheral surface of the body 11. The throttle 20 includes a main body 21, a cover plate 22, and a diaphragm sheet 23. The main body 21 has a first side 211 and a second side 212. A groove 2111 is formed on the first side 211 of the main body 21. A throttling boss 2112 is provided in the center of the groove 2111. A first channel 2113 is provided on the throttling boss 2112, extending from the first side 211 to the second side 212. A recess is provided on the second side 212 of the main body 21. The recess and the outer peripheral surface of the bearing 10 body 11 form an oil supply channel. The main body 21 also has an oil supply port 213, a first throttling channel 214, and a second throttling channel 215. The oil supply port 213 is connected to both the oil supply channel and the second throttling channel 215. The cover plate 22 is disposed on the first side 211 of the main body 21. A diaphragm 23 is disposed between the cover plate 22 and the main body 21, and the space between the diaphragm 23 and the groove 2111 located outside the throttling boss 2112 forms a pressure stabilizing cavity, while the space between the diaphragm 23 and the cover plate 22 forms an adjusting cavity. The two ends of the first throttling channel 214 are respectively connected to the oil supply channel and the pressure stabilizing cavity, the two ends of the second throttling channel 215 are respectively connected to the adjusting cavity and the oil supply channel, and the first channel 2113 is connected to both the static pressure cavity and the oil supply channel.

[0050] In this embodiment, when the hydrostatic bearing is in operation, after the external oil circuit is connected to the throttle 20, the oil flows into the hydrostatic chamber through the throttle 20 and generates an oil film in the hydrostatic chamber, thus creating an oil film between the body 11 of the bearing 10 and the shaft core 12 of the bearing 10. At the same time, the throttle 20 of this embodiment can automatically adjust the stiffness of the oil film according to the force on the oil film.

[0051] Specifically, the external oil circuit is connected to the oil supply port 213. Part of the oil flows from the oil supply port 213 into the regulating chamber through the second throttling channel 215. The other part of the oil flows into the oil supply channel and then flows into the pressure stabilizing chamber through the first throttling channel 214 and into the static pressure chamber through the first channel 2113. When the shaft 12 is not rotating, the shaft 12 or the body 11 will not apply pressure to the oil film, and the oil pressure in the pressure stabilizing chamber is relatively low. At this time, the diaphragm 23 is in contact with the throttling boss 2112 and blocks the opening of the first channel 2113, that is, the oil in the pressure stabilizing chamber cannot communicate with the static pressure chamber through the first channel 2113. At this time, the thickness and rigidity of the oil film are in their initial state. When the shaft 12 rotates, the shaft 12 or the body 11 applies pressure to the oil film. The oil in the static pressure chamber applies a reaction force to the oil in the oil supply channel, causing the oil entering the pressure stabilizing chamber to exert a thrust on the diaphragm 23. After being subjected to hydraulic pressure, the diaphragm 23 bends towards the regulating chamber. Depending on the magnitude of the hydraulic pressure, the degree of bending of the diaphragm 23 varies, thereby changing the relative volume between the static pressure chamber and the regulating chamber. This results in different flow rates of oil flowing out of the first channel 2113 in the pressure stabilizing chamber, ensuring that the thickness of the oil film in the static pressure chamber remains almost unchanged, thereby improving the rigidity of the oil film.

[0052] Furthermore, in this embodiment, to ensure sufficient contact between the oil film and the shaft core 12 of the bearing 10, the hydrostatic chamber is positioned between the outer surface of the first tapered section 1211 and the inner wall surface of the first tapered cavity 111, and between the outer surface of the second tapered section 1221 and the inner wall surface of the second tapered cavity 112. In this embodiment, for ease of assembly, the shaft core 12 is designed as a two-section shaft core, namely a front shaft core 121 and a rear shaft core 122. Both the front shaft core 121 and the rear shaft core 122 are provided with multiple fixing holes for fixing them together, allowing them to rotate synchronously.

[0053] Compared with the prior art, the diaphragm 23 of the hydrostatic bearing in this embodiment can monitor the pressure of the oil and automatically adjust the relative volume change between the pressure stabilizing chamber and the static pressure chamber according to the oil pressure to control the flow rate of the oil entering the static pressure chamber from the throttle 20, thereby dynamically adjusting the rigidity of the oil film in the static pressure chamber.

[0054] Furthermore, the shaft core 12 also includes an adjustment part 123, which is disposed between the front shaft core 121 and the rear shaft core 122, for at least adjusting the gap between the first tapered section 1211 and the first tapered cavity 111 and the gap between the second tapered section 1221 and the second tapered cavity 112.

[0055] Specifically, in this embodiment, the adjustment unit 123 can adjust the distance between the front shaft core 121 and the rear shaft core 122, thereby changing the gap between the first tapered section 1211 and the first tapered cavity 111, and the gap between the second tapered section 1221 and the second tapered cavity 112, thus changing the oil film thickness and stiffness within the gaps. In this embodiment, the adjustment unit 123 can be configured as two blocks that can move closer or further apart from each other. That is, by operating the drive member connected between the two blocks, the two blocks can be separated or moved closer together, thereby changing the oil film thickness.

[0056] Optionally, the adjustment part 123 includes an adjustment pad, which has a variety of different models and different thicknesses. The various models of adjustment pads can be selectively installed between the front shaft core 121 and the rear shaft core 122.

[0057] Specifically, when assembling the hydrostatic bearing, the thickness of the oil film can be adjusted appropriately according to the set rotational speed of the shaft core 12. That is, when the shaft core 12 rotates at a high speed and applies a large force to the oil film, a narrower adjusting shim can be installed to ensure the rigidity of the oil film. Conversely, when the shaft core 12 rotates at a low speed and applies a smaller force to the oil film, a thicker adjusting shim can be installed to ensure that there is no mechanical contact between the shaft core 12 and the body 11, thereby ensuring the accuracy of the hydrostatic bearing.

[0058] To ensure an oil film exists between the front shaft core 121, the rear shaft core 122, and the bearing 10 body 11, in this embodiment, the static pressure chamber includes a first static pressure chamber 113 and a second static pressure chamber 114. The first static pressure chamber 113 is located between the outer peripheral surface of the first conical section 1211 and the inner wall surface of the first conical cavity 111, and the second static pressure chamber 114 is located between the outer peripheral surface of the second conical section 1221 and the inner wall surface of the second conical cavity 112. The throttle device 20 includes a first throttle device 201 and a second throttle device 202. The first throttle device 201 communicates with the first static pressure chamber 113, and the second throttle device 202 communicates with the second static pressure chamber 114.

[0059] Specifically, the first throttle 201 is used to automatically adjust the rigidity of the oil film in the first static pressure chamber 113, and the second throttle 202 is used to automatically adjust the rigidity of the oil film in the second static pressure chamber 114, thereby improving the rotational accuracy of the front shaft core 121 and the rear shaft core 122 to a certain extent. At the same time, the arrangement of the first static pressure chamber 113 and the second static pressure chamber 114 avoids mechanical contact between the front shaft core 121 or the rear shaft core 122 and the body 11.

[0060] Furthermore, both the first throttle 201 and the second throttle 202 comprise n units, and the n first throttles 201 and n second throttles 202 are equally spaced on the outer peripheral surface of the body 11. Both the first static pressure chamber 113 and the second static pressure chamber 114 comprise n units, where the n first static pressure chambers 113 are equally spaced on the inner wall of the first conical cavity 111, and the n second static pressure chambers 114 are equally spaced on the inner wall of the second conical cavity 112. The n first throttles 201 are connected to the n first static pressure chambers 113 in a one-to-one correspondence, and the n second throttles 202 are connected to the n second static pressure chambers 114 in a one-to-one correspondence. Here, n satisfies the relationship: n≥2, and n∈N. + .

[0061] Specifically, the arrangement of the n first throttles 201 and n second throttles 202 on the outer circumferential surface of the body 11 ensures uniform force distribution on the shaft core 12, meaning the resultant force of the oil film bearing capacity on the shaft core 12 remains along the axial direction of the body 11. Furthermore, the n first static pressure chambers 113 surround the outer circumference of the first conical section 1211 to protect various parts of the outer circumference of the first conical section 1211 and prevent mechanical contact between the first conical section 1211 and the first conical cavity 111. Similarly, the n second static pressure chambers 114 surround the outer circumference of the second conical section 1221 to protect various parts of the outer circumference of the second conical section 1221 and prevent mechanical contact between the second conical section 1221 and the second conical cavity 112. Of course, the n first throttles 201 and n second throttles 202 individually control their respective static pressure chambers, so that the oil film rigidity within each static pressure chamber can be adjusted via the throttles 20.

[0062] Furthermore, n satisfies the relationship: n≥3 and n≠4. Specifically, if n≤2, that is, when the first throttle 201, the second throttle 202, the first static pressure chamber 113, and the second static pressure chamber 114 are all less than or equal to two, for example, when n is 2, the two oppositely arranged first throttles 201 and the two oppositely arranged second throttles 202 apply oil films in opposite directions, causing the shaft core 12 of the bearing 10 to be positioned between the oil films on both sides. If one of the first throttles 201 or one of the second throttles 202 fails, the other first throttle 201 or second throttle 202 pushes the oil film, causing the oil film to drive the shaft core 12 to move away from the throttle 20, thereby causing the shaft core 12 to abut against the body 11, resulting in the hydrostatic bearing seizing.

[0063] Similarly, when n is 4, since the four first throttles 201 and the four second throttles 202 are arranged in a square, if one of the first throttles 201 or one of the second throttles 202 fails, the remaining three first throttles 201 or second throttles 202 cannot generate a force opposite to the direction of movement of the shaft core 12, ultimately causing the shaft core 12 to make mechanical contact with the body 11. However, when n is 3 or 5 or greater than 5, when one first throttle 201 or second throttle 202 fails, the component force generated by the remaining throttles 20 near the shaft core 12 after the failure of the failed throttle 20 ensures that the shaft core 12 will not make contact with the body 11. That is, the oil film on the static pressure chamber controlled by the failed throttle 20 still has a certain rigidity under the combined action of the remaining throttles 20.

[0064] It is worth mentioning that in this embodiment, the first throttle 201 and the second throttle 202 are used. When the n first static pressure chambers 113 and the n second static pressure chambers 114 are all set at unequal intervals, the value of n can be 4, but different settings need to be adopted for each first throttle 201 and each second throttle 202.

[0065] In one specific embodiment, as shown in the appendix Figure 1 As shown, there are five of each of the following: the first throttle 201, the second throttle 202, the first static pressure chamber 113, and the second static pressure chamber 114. The first throttle 201 and the second throttle 202 are arranged side-by-side along the length of the body 11 of the bearing 10, so that the center of mass of the hydrostatic bearing is located on the axis of the body 11. Furthermore, having five of each type does not excessively increase manufacturing costs. Additionally, the structure of this embodiment ensures that even if one static pressure chamber or one throttle 20 fails, the bearing 10 will not seize and be damaged, thereby improving the protection of the hydrostatic bearing.

[0066] As attached Figures 7 to 9 As shown, the main body 11 has a first circumferential surface and a second circumferential surface spaced apart along the axial direction. The first circumferential surface has n first oil ports 41, and the oil supply ports 213 of the n first throttles 201 are connected one-to-one with the n first oil ports 41. Adjacent first oil ports 41 are connected through a first oil passage 43. The second circumferential surface has n second oil ports 42, and the oil supply ports 213 of the n second throttles 202 are connected one-to-one with the n second oil ports 42. Adjacent second oil ports 42 are connected through a second oil passage 44. The first oil passage 43 and the second oil passage 44 are connected through a third oil passage 45. The main body 11 also has a total oil inlet channel 46, which is connected to the first oil passage 43 and / or the second oil passage 44.

[0067] Specifically, along the axial direction of the body 11, the third oil passage 45 is opened from one side of the body 11 and communicates with the first oil passage 43, the second oil passage 44, and the main oil inlet passage 46. The main oil inlet passage 46 is opened on the outer periphery of the body 11 of the bearing 10 and communicates with the first oil passage 43. Further, the external oil passage is connected to the main oil inlet passage 46, and after the oil enters the main oil inlet passage 46, a portion of the oil flows into the first oil passage 43, and the oil in the first oil passage 43 flows into each of the first throttles 201. Another portion of the oil flows into the third oil passage 45, and after passing through the third oil passage 45, flows into the second oil passage 44, and finally flows into each of the second throttles 202. In this embodiment, both the first oil passage 43 and the second oil passage 44 are opened in the body 11 of the bearing 10. Compared with existing hydrostatic bearings, the hydrostatic bearing in this embodiment has a compact structure, and there is no interference between the flow channels. It is worth mentioning that when using the hydrostatic bearing, the opening of the third oil passage 45 on the body 11 needs to be plugged with an oil plug to prevent oil from leaking out through the opening of the third oil passage 45.

[0068] In addition, as attached Figure 10 To be continued Figure 12 As shown, the oil supply channel includes a first flow channel 2121 and a second flow channel 2122. The first flow channel 2121 and the second flow channel 2122 are concentrically arranged. The first flow channel 2121 is connected to the oil supply port 213, the second throttling channel 215 and the first throttling channel 214. The second flow channel 2122 is connected to the first flow channel 2121 and the first channel 2113. The width of the first flow channel 2121 is greater than the width of the second flow channel 2122.

[0069] Specifically, both the first flow channel 2121 and the second flow channel 2122 are annular flow channels, and the second flow channel 2122 is located outside the first flow channel 2121. After the external oil circuit is connected to the oil supply port 213, a portion of the oil flows into the regulating chamber through the second throttling channel 215, and another portion of the oil flows into the pressure stabilizing chamber through the first flow channel 2121 and the first throttling channel 214. The remaining oil flows into the static pressure chamber through the second flow channel 2122 and converges at the first channel 2113. Furthermore, the width of the first flow channel 2121 is set to be relatively large, while the width of the second flow channel 2122 is set to be relatively small. This ensures that the oil resistance in the first flow channel 2121 is lower than that in the second flow channel 2122, thereby guaranteeing a controllable ratio of oil flow from the pressure stabilizing chamber to the first channel 2113 and from the second flow channel 2122 to the first channel 2113 within a certain pressure range. This allows the throttle 20 to adjust the stiffness of the oil film within a certain range, as the pressure applied to the oil film by the bearing body 11 or shaft core 12 can be adjusted by the throttle 20. In one specific embodiment, the oil resistance in the second flow channel 2122 is 20 times that in the first flow channel 2121, so that the throttle 20 can still adjust the oil film in the static pressure chamber under a certain load force.

[0070] As attached Figure 3 and attached Figure 7 As shown, a first static pressure channel 115 is provided between the throttle 20 and the first conical cavity 111, and the extension direction of the first static pressure channel 115 is perpendicular to the conical surface of the first conical cavity 111.

[0071] In other words, after the oil flows into the first static pressure channel 115 through the throttle 20, it passes through a channel perpendicular to the conical surface of the first conical cavity 111. Because the impact direction of the oil is different from the extension direction of the first static pressure channel 115, the impact force of the oil is weakened by the first static pressure channel 115, and then it flows into the first static pressure chamber 113. The structure of this embodiment can prevent the oil from impacting the first static pressure chamber 113 for a long time, thus avoiding damage to the first static pressure chamber 113.

[0072] Optionally, a second static pressure channel 116 is provided between the throttle 20 and the second conical cavity 112, and the extending direction of the second static pressure channel 116 is perpendicular to the conical surface of the second conical cavity 112.

[0073] To prevent oil leakage from contaminating the hydrostatic bearing and to reduce the operating cost of the hydrostatic bearing, an oil outlet channel is provided on the body 11 in this embodiment. The oil outlet channel is connected to the through hole 13 and is located between the first conical cavity 111 and the second conical cavity 112.

[0074] Specifically, the oil outlet channel includes a first oil outlet channel 31 and a second oil outlet channel 32. The first oil outlet channel 31 and the second oil outlet channel 32 are interconnected. The first oil outlet channel 31 extends through the body 11 along the axial direction of the body 11 to return oil to one side of the first static pressure chamber 113 and the second static pressure chamber 114. The second oil outlet channel 32 extends through the body 11 in the radial direction and communicates with the through hole 13 to return oil to the other side of the first static pressure chamber 113 and the second static pressure chamber 114.

[0075] Furthermore, a support boss 2114 is provided in the groove 2111 of the throttle 20. The support boss 2114 is concentrically arranged with the throttle boss 2112 and located on the outer periphery of the throttle boss 2112. The support boss 2114 and the throttle boss 2112 have the same height to cooperate with the throttle boss 2112 in supporting the diaphragm sheet 23, thus preventing uneven stress on the diaphragm sheet 23 and causing damage to the diaphragm sheet 23. In this embodiment, the diaphragm sheet 23 is made of a metal diaphragm sheet with good ductility to extend the service life of the throttle 20.

[0076] Furthermore, the cover plate 22 is provided with an arc-shaped boss 221, and a groove 222 is provided on the end face of the arc-shaped boss 221. The groove 222 and the diaphragm sheet 23 form an adjustment cavity, and the groove 222 is connected to the second throttling channel 215.

[0077] Specifically, the arc-shaped boss 221 penetrates into the groove 2111 and abuts against the diaphragm 23. Oil enters the second throttling channel 215 through the oil supply port 213 and then enters the groove 222. The oil in the groove 222 applies hydraulic pressure to the diaphragm 23 to adjust the relative volume between the regulating chamber and the pressure stabilizing chamber. Furthermore, since the oil in the regulating chamber enters directly from the external oil passage, the pressure of the oil in the regulating chamber is only related to the pressure of the oil in the external oil passage and is unrelated to the bearing capacity of the oil film.

[0078] As attached Figure 12 and attached Figure 13 As shown, a first sealing groove 223 is provided between the cover plate 22 and the main body 21, and a second sealing groove 2123 is provided between the main body 21 and the outer peripheral surface of the bearing body 11. Both the first and second sealing grooves 223 contain sealing elements 80. Specifically, the cover plate 22 and the main body 21 are sealed by the first sealing groove 223 to prevent oil leakage from the regulating cavity. Similarly, the main body 21 and the bearing body 11 are sealed by the second sealing groove 2123 to prevent oil leakage from the oil supply channel. In this embodiment, the sealing element 80 includes a rubber sealing element 80.

[0079] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0080] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0081] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A hydrostatic bearing, characterized in that, include: A bearing (10) includes a body (11) and a shaft core (12). The body (11) has a through hole (13). The two ends of the through hole (13) have a first conical cavity (111) and a second conical cavity (112), respectively. Along the direction away from the second conical cavity (112), the cross-sectional area of ​​the first conical cavity (111) gradually increases, and along the direction away from the first conical cavity (111), the cross-sectional area of ​​the second conical cavity (112) gradually increases. The shaft core (12) passes through the through hole (13). The core (12) includes a front section core (121) and a rear section core (122). The front section core (121) is provided with a first conical segment (1211) adapted to the first conical cavity (111), and the rear section core (122) is provided with a second conical segment (1221) adapted to the second conical cavity (112). Static pressure cavities are provided between the outer peripheral surface of the first conical segment (1211) and the inner wall surface of the first conical cavity (111), and between the outer peripheral surface of the second conical segment (1221) and the inner wall surface of the second conical cavity (112). A throttle (20) is disposed on the outer peripheral surface of the body (11), and the throttle (20) includes: The main body (21) has a first side (211) and a second side (212). The first side (211) of the main body (21) has a groove (2111). A throttling boss (2112) is provided in the center of the groove (2111). A first channel (2113) is provided on the throttling boss (2112). The first channel (2113) extends from the first side (211) to the second side (212). A recess is provided on the second side (212) of the main body (21). The recess and the outer peripheral surface of the bearing (10) body (11) form an oil supply channel. The main body (21) is also provided with an oil supply port (213), a first throttling channel (214), and a second throttling channel (215). The oil supply port (213) is connected to the oil supply channel and the second throttling channel (215). A cover plate (22) is provided on the first side (211) of the main body (21); A thin film (23) is disposed between the cover plate (22) and the main body (21), and the space between the thin film (23) and the groove (2111) located outside the throttling boss (2112) forms a pressure stabilizing cavity, and the space between the thin film (23) and the cover plate (22) forms an adjusting cavity; Wherein, the two ends of the first throttling channel (214) are respectively connected to the oil supply channel and the pressure stabilizing chamber, the two ends of the second throttling channel (215) are respectively connected to the regulating chamber and the oil supply channel, and the first channel (2113) is connected to both the static pressure chamber and the oil supply channel; The shaft core (12) further includes an adjustment part (123), which is disposed between the front shaft core (121) and the rear shaft core (122) to at least adjust the gap between the first tapered section (1211) and the first tapered cavity (111) and the gap between the second tapered section (1221) and the second tapered cavity (112).

2. The hydrostatic bearing according to claim 1, characterized in that, The adjustment part (123) includes an adjustment pad, which has a variety of different models. The thickness of the adjustment pads of the various models is different, and the adjustment pads of the various models can be selectively installed between the front shaft core (121) and the rear shaft core (122).

3. The hydrostatic bearing according to claim 1, characterized in that, The static pressure chamber includes a first static pressure chamber (113) and a second static pressure chamber (114). The first static pressure chamber (113) is disposed between the outer peripheral surface of the first conical segment (1211) and the inner wall surface of the first conical cavity (111). The second static pressure chamber (114) is disposed between the outer peripheral surface of the second conical segment (1221) and the inner wall surface of the second conical cavity (112). The throttle (20) includes a first throttle (201) and a second throttle (202), the first throttle (201) being connected to the first static pressure chamber (113) and the second throttle (202) being connected to the second static pressure chamber (114).

4. The hydrostatic bearing according to claim 3, characterized in that, The first throttle (201) and the second throttle (202) each include n units, and the n first throttles (201) and the n second throttles (202) are evenly spaced on the outer peripheral surface of the body (11); The first static pressure chamber (113) and the second static pressure chamber (114) each include n, wherein the n first static pressure chambers (113) are equally spaced on the inner wall surface of the first conical cavity (111), and the n second static pressure chambers (114) are equally spaced on the inner wall surface of the second conical cavity (112); n first throttles (201) are connected to n first static pressure chambers (113) in a one-to-one correspondence, and n second throttles (202) are connected to n second static pressure chambers (114) in a one-to-one correspondence; Where n satisfies the relation: n≥2, and n∈N + .

5. The hydrostatic bearing according to claim 4, characterized in that, n satisfies the following relationship: n≥3 and n≠4.

6. The hydrostatic bearing according to claim 4, characterized in that, The body (11) is provided with a first circumferential surface and a second circumferential surface at intervals along the axial direction. The first circumferential surface is provided with n first oil ports (41) at intervals. The oil supply ports (213) of the n first throttles (201) are connected to the n first oil ports (41) in a one-to-one correspondence. Adjacent two first oil ports (41) are connected through a first oil passage (43). The second circumferential surface is provided with n second oil ports (42). The oil supply ports (213) of the n second throttles (202) are connected to the n second oil ports (42) in a one-to-one correspondence. Adjacent two second oil ports (42) are connected through a second oil passage (44). The first oil passage (43) and the second oil passage (44) are connected through the third oil passage (45), and the main body (11) is also provided with a total oil inlet passage (46), which is connected to the first oil passage (43) and / or the second oil passage (44).

7. The hydrostatic bearing according to any one of claims 1 to 6, characterized in that, The oil supply channel includes a first flow channel (2121) and a second flow channel (2122). The first flow channel (2121) and the second flow channel (2122) are concentrically arranged. The first flow channel (2121) is connected to the oil supply port (213), the second throttling channel (215) and the first throttling channel (214). The second flow channel (2122) is connected to the first flow channel (2121) and the first channel (2113). The width of the first flow channel (2121) is greater than the width of the second flow channel (2122).

8. The hydrostatic bearing according to any one of claims 1 to 6, characterized in that, A first static pressure channel (115) is provided between the throttle (20) and the first conical cavity (111), and the extending direction of the first static pressure channel (115) is perpendicular to the conical surface of the first conical cavity (111); and / or, A second static pressure channel (116) is provided between the throttle (20) and the second conical cavity (112), and the extension direction of the second static pressure channel (116) is perpendicular to the conical surface of the second conical cavity (112).

9. The hydrostatic bearing according to any one of claims 1 to 6, characterized in that, The body (11) is also provided with an oil outlet channel, which is connected to the through hole (13) and located between the first conical cavity (111) and the second conical cavity (112).

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