CN215680603U - Sliding bearing and X-ray tube assembly - Google Patents

Abstract

The application relates to a slide bearing and X-ray tube assembly, the slide bearing includes: the mandrel comprises a mandrel main body and annular structures distributed on the outer side of the mandrel main body, wherein the annular structures are connected with the mandrel main body and have a distance with the mandrel main body; and the bearing sleeve is matched with the mandrel main body and the annular structure of the mandrel in shape, and at least three layers of gaps are formed between the mandrel and the bearing sleeve in the radial direction of the mandrel main body. The application provides a slide bearing passes through the loop configuration of dabber main part and cooperates with the bearing housing for form three layer at least clearances between dabber and the bearing housing in the radial direction of dabber main part, can be when improving slide bearing capacity and stability, increase the heat radiating area between bearing housing and the dabber.

Description

Sliding bearing and X-ray tube assembly

Technical Field

The application relates to the technical field of bearing equipment, in particular to a sliding bearing and an X-ray tube assembly.

Background

In production and life, sliding bearings are widely used in the fields of metallurgical industry, aerospace manufacturing, medical applications, and the like. For example, in the application of the sliding bearing in medical equipment, an X-ray tube is a core component of a medical diagnostic instrument (such as an X-ray machine and a CT), and during the operation of generating X-rays, electrons released by a cathode filament bombard the surface of an anode target to generate bremsstrahlung radiation, thereby generating the X-rays. In the process, the anode target generates a large amount of heat, which causes the temperature of the anode target to be too high, and thus there is a risk of melting, and therefore, in view of this, the anode target is usually connected with a bearing (e.g., a sliding bearing) to realize high-speed rotation of the anode target, and the heat generated by the anode target rotating at high speed is not too concentrated. The requirements of the rotary anode on the bearing capacity, stability and heat dissipation effect of the sliding bearing are higher, and the common sliding bearing cannot meet the requirements.

In view of the above problems, it is desirable to provide a sliding bearing with high stability, high bearing capacity and good heat dissipation effect.

SUMMERY OF THE UTILITY MODEL

An object of the present application is to provide a sliding bearing, including: the mandrel comprises a mandrel main body and annular structures distributed on the outer side of the mandrel main body, wherein the annular structures are connected with the mandrel main body, and a distance is reserved between the annular structures and the mandrel main body; and the bearing sleeve is matched with the mandrel main body and the annular structure of the mandrel in shape, and at least three layers of gaps are formed between the mandrel and the bearing sleeve in the radial direction of the mandrel main body.

In some embodiments, at least one region of the ring-like structure has a different thickness than regions of other regions of the ring-like structure.

In some embodiments, the bearing sleeve includes a raised structure located between the mandrel body and the ring structure, and a triple layer gap is formed between the mandrel body and the raised structure, between the ring structure and the raised structure, and between the ring structure and the bearing sleeve in a radial direction of the mandrel body.

In some embodiments, the width of any one of the at least three layers of gaps in the radial direction of the mandrel body is 10um to 30 um.

In some embodiments, at least one region of the raised structures has a different thickness than regions of other regions of the raised structures.

In some embodiments, a surface of the ring-shaped structure or a position of the bearing sleeve, which is matched with the shape of the mandrel main body and the ring-shaped structure of the mandrel, is provided with a notch.

In some embodiments, the mandrel includes a connecting member, the connecting member is sleeved on an outer wall of the mandrel main body, the ring-shaped structure is connected with the mandrel main body through the connecting member, and the connecting member is adapted to a first groove formed at an open end of the bearing sleeve.

In some embodiments, the sliding bearing includes a sealing member sleeved outside the mandrel body and connected to an open end of the bearing sleeve.

In some embodiments, the side wall of the sealing element, which is matched with the mandrel main body, is provided with a second groove.

Another object of the present application is to provide an X-ray tube assembly comprising: cathode filament subassembly, positive pole target subassembly, cathode filament subassembly, positive pole target subassembly set up relatively, positive pole target subassembly includes the target dish and supports the slide bearing of target dish, slide bearing includes: the mandrel comprises a mandrel main body and annular structures distributed on the outer side of the mandrel main body, the annular structures are connected with the mandrel main body, and a set distance is formed between the annular structures and the mandrel main body along the radial direction of the mandrel main body; the inner side of the bearing sleeve is provided with a convex structure; the bearing sleeve is assembled on the mandrel along the axial direction of the mandrel main body, the protruding structure is located between the mandrel main body and the annular structure, and the annular structure is located between the protruding structure and the bearing sleeve.

Drawings

The present application will be further explained by way of exemplary embodiments, which will be described in detail by way of the accompanying drawings. These embodiments are not intended to be limiting, and in these embodiments like numerals are used to indicate like structures, wherein:

FIG. 1 is a schematic structural view of a plain bearing according to some embodiments of the present application;

FIG. 2 is a schematic view of a plain bearing construction according to some embodiments of the present application;

FIG. 3 is a schematic cross-sectional view of a plain bearing along a radial direction of a mandrel body according to some embodiments of the present application;

FIG. 4 is a schematic illustration of a plain bearing according to some embodiments of the present application;

FIG. 5 is a schematic view of another plain bearing construction according to some embodiments of the present application;

FIG. 6 is a schematic view of another slide bearing construction according to some embodiments of the present application.

Detailed Description

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings used in the description of the embodiments will be briefly introduced below. It is obvious that the drawings in the following description are only examples or embodiments of the application, from which the application can also be applied to other similar scenarios without inventive effort for a person skilled in the art. Unless otherwise apparent from the context, or otherwise indicated, like reference numbers in the figures refer to the same structure or operation.

It will be understood by those within the art that the terms "first", "second", etc. in this application are used solely to distinguish one from another device, module, parameter, etc., and are not intended to imply any particular technical meaning, nor is the necessary logical order between them.

As used in this application and the appended claims, the terms "a," "an," "the," and/or "the" are not intended to be inclusive in the singular, but rather are intended to be inclusive in the plural unless the context clearly dictates otherwise. In general, the terms "comprises" and "comprising" merely indicate that steps and elements are included which are explicitly identified, that the steps and elements do not form an exclusive list, and that a method or apparatus may include other steps or elements.

This application is intended to cover any alternatives, modifications, equivalents, and alternatives that fall within the spirit and scope of the application, as defined by the appended claims. Furthermore, in the following detailed description of the present application, certain specific details are set forth in order to provide a better understanding of the present application. It will be apparent to one skilled in the art that the present application may be practiced without these specific details.

An X-ray apparatus is an apparatus for examination, diagnosis or radiotherapy of each part of a subject, in which an X-ray tube, which may be a vacuum diode operating at a high voltage, is a core component of an X-ray apparatus (e.g., an X-ray computed tomography apparatus). In particular, the X-ray tube may include a housing and a cathode and an anode disposed in the housing. The cathode may refer to a filament for emitting electrons. The anode may refer to a target material for receiving electron bombardment, also referred to as an anode target. In some embodiments, the housing may be a structure having a high vacuum inside. For example, the material of the housing may be glass, ceramic, or cermet. When high-energy high-speed electrons generated by a cathode of the X-ray tube bombard an anode target in the working process of the X-ray tube, the high-speed electrons reach the target surface of the anode target, the movement of the high-speed electrons is stopped, the kinetic energy of part of the high-speed electrons is converted into radiation energy, and the radiation is radiated out in the form of X-rays, and the radiation is called bremsstrahlung radiation. The other part of the high-speed electrons collide with the target surface of the anode target to generate a large amount of heat, so that the temperature of the target surface of the anode target is high. In order to prevent the anode target from being melted at a high temperature to extend its life, a bearing may be attached to one end of the anode target for enabling the anode target of the X-ray tube to rotate. On the one hand, the high-speed electrons collide with different positions of the anode target, so that the heat distribution of the anode target is uniform. On the other hand, the bearing can further transfer the heat on the anode target to achieve the heat dissipation effect. In some embodiments, the bearing may be a rolling bearing or a sliding bearing. The sliding bearing generally adopts a liquid metal bearing, and the liquid metal has excellent heat conductivity, so that compared with the traditional rolling bearing, the heat conduction efficiency of the anode target to a bearing system is improved, and the heat dissipation of the anode target is better assisted.

In some embodiments, the sliding bearing is generally formed by sleeving a bearing sleeve on a mandrel, wherein an inner wall of the bearing sleeve is matched with an outer wall of the mandrel, and a gap with a specific width is formed between the inner wall of the bearing sleeve and the outer wall of the mandrel, and a lubricating medium (such as liquid metal, water or air) is filled in the gap so that the bearing sleeve can rotate relative to the mandrel. In order to facilitate understanding of the specific structure of the slide bearing, the slide bearing 100 in fig. 1 is described as an example. FIG. 1 is a schematic illustration of a plain bearing according to some embodiments of the present application. As shown in fig. 1, the sliding bearing 100 may include a mandrel 110 and a bearing sleeve 120, wherein the bearing sleeve 120 is sleeved outside the mandrel 110 and has a shape matching with that of the mandrel 110. Specifically, a layer of gap 140 is formed between the inner wall of the bearing sleeve 120 and the outer wall of the mandrel 110, and the gap 140 is filled with a medium (e.g., liquid metal, water, oil, air, etc.) to reduce the sliding friction between the bearing sleeve 120 and the mandrel 110. When the sliding bearing 100 is in a rotating state, the bearing sleeve 120 rotates relative to the mandrel 110, and the medium in the gap 140 flows under the driving of the bearing sleeve 120 and the mandrel 110 and forms a dynamic pressure bearing oil film, so that a dynamic pressure effect is provided for the sliding bearing 100, and the bearing capacity and stability of the sliding bearing 100 are improved. Although the gap 140 between the bearing sleeve 120 and the mandrel 110 may provide a dynamic pressure effect by filling with a medium (e.g., liquid metal), the dynamic pressure effect provided by the medium in the gap 140 is limited, and there is a problem of insufficient bearing capacity when the sliding bearing 100 needs to bear a carrier of a large mass.

In order to ensure the bearing capacity of the sliding bearing 100, in some embodiments, the length of the core shaft 110 matched with the bearing sleeve 120 may be increased, but the length of the core shaft 110 matched with the bearing sleeve 120 is too large, so that the temperature difference between the two ends of the sliding bearing 100 is too large, and the temperature distribution unevenness of the two ends of the sliding bearing 100 causes thermal deformation of the components (for example, the core shaft 110 and the bearing sleeve 120), which easily causes the problem of the clamping stagnation at the matching position of the core shaft 110 and the bearing sleeve 120 or the shaking of the core shaft 110. In addition, when the sliding bearing 100 is applied to a rotating anode of an X-ray tube, where the target disk 130 is sleeved outside the bearing sleeve 120, the sliding bearing 100 absorbs and dissipates heat generated by the target disk 130, and the gap 140 between the spindle 110 and the bearing sleeve 120 can further absorb heat of the target disk 130, where the area of fit between the spindle 110 and the bearing sleeve 120 can be regarded as the heat dissipation area of the sliding bearing, but when the spindle 110 and the bearing sleeve 120 are fitted, only one layer of gap 140 is formed between the side wall of the spindle 110 and the inner wall of the bearing sleeve 120, and the heat dissipation area of the sliding bearing 100 is too small, and the heat dissipation effect is not good.

In order to solve the above problem, an embodiment of the present application provides a sliding bearing, which may include a mandrel and a bearing sleeve, wherein the mandrel includes a mandrel main body and a ring-shaped structure distributed outside the mandrel main body, the ring-shaped structure is connected to the mandrel main body, and the ring-shaped structure has a distance from the mandrel main body. The bearing sleeve is matched with the main body of the mandrel and the shape of the annular structure, and at least three layers of gaps are formed between the mandrel and the bearing sleeve in the radial direction of the main body of the mandrel. The annular structure, the mandrel main body and the bearing sleeve are matched to form at least three layers of gaps, and the dynamic pressure effect inside the sliding bearing can be effectively increased through media filled in the at least three layers of gaps, so that the bearing capacity of the sliding bearing is improved. In addition, the heat dissipation area between the mandrel and the bearing sleeve can be increased through the multi-layer gaps, and the heat dissipation capacity of the sliding bearing is further improved. Meanwhile, the length of the mandrel main body matched with the bearing sleeve can be shortened by arranging the annular structure, the temperature difference at two ends of the mandrel main body is reduced, the thermal deformation is prevented, and the stability of the sliding bearing is improved.

Some embodiments of the present application provide a sliding bearing, which can effectively solve the above-mentioned problems, and reference may be made to fig. 2 to 6 and the related description thereof for details of the sliding bearing.

FIG. 2 is a schematic illustration of a plain bearing according to some embodiments of the present application. As shown in fig. 2, the sliding bearing 200 may include a mandrel 210 and a bearing sleeve 220. In some embodiments, the bearing sleeve 220 has a geometric structure with a mounting cavity therein, one end of the bearing sleeve 220 is an open end, so that the spindle 210 can extend into the mounting cavity inside the bearing sleeve 220 through the open end, and the shape of the spindle 210 extending into the interior of the bearing sleeve 220 is matched with the shape of the mounting cavity inside the bearing sleeve 220, so that the bearing sleeve 220 can rotate relative to the spindle 210. In order to prevent the mandrel 210 and the bearing housing 220 from being worn greatly during the relative rotation, in some embodiments, the mandrel 210 and the bearing housing 220 may have a certain clearance at the matching position. In some embodiments, the gap may be filled with a corresponding medium to reduce the sliding friction between the bearing sleeve 220 and the mandrel 210, and the medium in the gap may provide a dynamic pressure effect for the sliding bearing 200, so as to improve the dynamic pressure effect of the sliding bearing 200. In some embodiments, the medium may be a gaseous medium or a liquid medium. Illustratively, the gaseous medium may include, but is not limited to, one or more of helium, nitrogen, argon, air, and the like. The liquid medium may include, but is not limited to, one or more of water, liquid metal, oil, and the like. Preferably, the medium is a liquid metal. The liquid metal alloy is generally composed of several low-melting-point metals such as gallium, tin and indium, is fluid at normal temperature, has a high boiling point (close to 2000 ℃), is not easy to volatilize, is metal, has good thermal conductivity, and can improve the heat dissipation effect of the sliding bearing 200 while providing a rotating dynamic pressure effect for the sliding bearing 200 by using the liquid metal as a gap filling medium.

In some embodiments, the mandrel 210 may comprise a mandrel body 212 and a ring-shaped structure 211 distributed outside the mandrel body 212, wherein the ring-shaped structure 211 is connected with the mandrel body 212, and the ring-shaped structure 211 is spaced apart from the mandrel body 212 in a radial direction of the mandrel body 212. In some embodiments, the mandrel body 212 may be a cylindrical structure, the ring-shaped structure 211 may be a circular ring-shaped or approximately circular ring-shaped structure, and the ring-shaped structures 211 are distributed along the circumferential side of the mandrel body 212, where the distance between the ring-shaped structure 211 and the mandrel body 212 in the radial direction of the mandrel body 212 may be understood as the distance between the inner wall of the ring-shaped structure 211 and the outer wall of the mandrel body 212. In some embodiments, the ring structure 211 may be disposed coaxially with the mandrel body 212 or may be disposed non-coaxially.

In some embodiments, the ring structure 211 may be directly connected with the mandrel body 212. For example, the ring structure 211 may include an extension (not shown in fig. 2) that may be located between the ring structure 211 and the mandrel body 212. In some embodiments, the extension portion may be one or more rod-like structures, and when there are a plurality of rod-like structures, a plurality of ring-like structures may be spaced along a sidewall of the ring-like structure 211 opposite to the mandrel body 212. One end of the rod-like structure is connected to the ring-like structure 211 and the other end is connected to the mandrel body 212. In some embodiments, the extension portion may also be a circular ring structure, a peripheral side of the circular ring structure is connected to the annular structure 211, and a side wall corresponding to the aperture in the circular ring structure is connected to the mandrel main body 212.

In some embodiments, the ring-shaped structure 211 and the mandrel body 212 may also be connected by a connector 213. In some embodiments, the connecting member 213 may be a circular plate structure, the connecting member 213 is sleeved outside the mandrel main body 212, and an end of the annular structure 211 is connected to the connecting member 213, so as to connect the annular structure 211 and the mandrel main body 212. Here "attachment" means may include, but is not limited to, one or more of welding, riveting, bolting, bonding, and the like. In some embodiments, the ring structure 211, the mandrel body 212, and the connector 213 may also be an integrally formed structure.

In order to realize better fit connection between the bearing sleeve 220 and the mandrel 210, in some embodiments, the open end of the bearing sleeve 220 is provided with a first groove 270 matched with the connecting member 213, and the shape of the first groove 270 is matched with the shape of the connecting member 213. For example, the connecting member 213 has a circular plate structure, and accordingly, the first groove 270 has a circular groove shape. Taking the connecting member 213 as a circular plate structure and the shape of the first groove 270 as a circular groove as an example, the radius of the first groove 270 is larger than that of the connecting member 213. The radius of the connecting member 213 being smaller than the radius of the first groove 270 ensures that the bearing housing 220 can rotate relative to the spindle 210. In addition, the thickness (dimension in the axial direction of the spindle main body 212) of the connecting member 213 being smaller than the thickness (dimension in the axial direction of the spindle main body 212) of the first groove 270 also facilitates sealing of the sliding bearing 200.

In order to adapt the ring-shaped structure 211 and the mandrel body 212 of the mandrel 210 to the bearing sleeve 220, in some embodiments, the bearing sleeve 220 may comprise a raised structure 221, the raised structure 221 being located between the mandrel body 212 and the ring-shaped structure 211, that is, the raised structure 221 is located in the spacing between the mandrel body 212 and the ring-shaped structure 211. The annular structures 211, the protruding structures 221 and the mandrel main body 212 are arranged at intervals from outside to inside, and the outermost annular structure 211 is matched with the corresponding side wall of the mounting cavity of the bearing sleeve 220, wherein a first gap 240 is formed between the outer side of the annular structure 211 and the side wall of the mounting cavity of the bearing sleeve 220, a second gap 250 is formed between the inner side of the annular structure 211 and the outer side of the protruding structure 221, a third gap 260 is formed between the side wall of the mandrel main body 212 and the inner side of the protruding structure 221, and the first gap 240, the second gap 250 and the third gap 260 are distributed at intervals in a circular ring shape in the radial direction of the mandrel main body 212.

Fig. 3 is a schematic cross-sectional view of the sliding bearing shown in fig. 2 along the radial direction of the mandrel main body, and with reference to fig. 2 and 3, a first gap 240 is formed between the annular structure 211 and the side wall of the installation cavity of the bearing sleeve 220, a second gap 250 is formed between the inner side of the annular structure 211 and the outer side of the protruding structure 221, a third gap 260 is formed between the side wall of the mandrel main body 212 and the inner side of the protruding structure 221, the three gaps are all annularly arranged in the radial direction of the mandrel 210, the first gap 240 is located at the outer side, the second gap 250 is located in the middle, and the third gap 260 is located at the inner side.

The gap formed between the mandrel 210 and the bearing sleeve 220 is not limited to the first layer gap 240, the second layer gap 250, and the third layer gap 260, and may be formed in three or more layers in the radial direction of the mandrel main body 212. In some embodiments, when the number of the ring structures 211 is two, the ring structures 211 may include a first ring structure and a second ring structure, the inner diameter of the second ring structure being larger than the outer diameter of the first ring structure, the first ring structure being distributed on the circumferential side of the mandrel body 212, the second ring structure being distributed along the circumferential side of the first ring structure. The first ring structure is spaced from the mandrel body 212, and the second ring structure is spaced from the first ring structure. Correspondingly, the bearing sleeve 220 includes two protruding structures, which are respectively located at a distance between the first annular structure and the mandrel main body 212 and a distance between the second annular structure and the first annular structure. At this time, when the mandrel 210 is mated with the bearing housing 220, it is possible to realize five layers of gaps in the radial direction of the mandrel main body 212. By analogy, five or more layers of gaps can be formed when the mandrel 210 is matched with the bearing sleeve 220.

In some embodiments, the thickness of the multi-layer gap generated by the protruding structure 221 and the mandrel 210 may be the same or different, so as to reduce the manufacturing precision of the bearing sleeve 220 and the mandrel 210, thereby reducing the processing difficulty and the assembling difficulty of the sliding bearing 200. In some embodiments, the raised structure 221, the mandrel body 212, and the ring-shaped structure 211 may be coaxially arranged such that the thickness of the multi-layer gap created by the raised structure 221 in cooperation with the mandrel 210 is the same. The thickness of the gap here may be understood as the dimension of the gap in the radial direction of the mandrel body 212.

In some embodiments, when the bearing sleeve 220 rotates relative to the mandrel 210, the sliding friction is large due to the small thickness of the gap generated by the fit between the two, and the large thickness of the gap causes the front and rear ends of the bearing sleeve 220 to be greatly deviated in the axial direction of the mandrel main body 212, which affects the stability of the sliding bearing 200 in the working state. In order to reduce the sliding friction of the sliding bearing 200 in the operating state and to improve the stability of the sliding bearing 200, in some embodiments, the size of any one of the plurality of layers of gaps in the radial direction of the mandrel main body 212 may be between 3 μm and 60 μm. In some embodiments, any one of the plurality of layers of gaps may have a dimension in the radial direction of the mandrel body 212 of between 7 μm and 45 μm. In some embodiments, any one of the plurality of layers of gaps has a dimension in the radial direction of the mandrel body 212 of between 10 μm and 30 μm. In some embodiments, the size of any one of the plurality of layers of gaps in the radial direction of the mandrel body 212 may be between 15 μm and 25 μm. It should be noted that the size of the gap in the radial direction of the mandrel main body 212 is not limited to the above range, and may be larger or smaller than the above range, and the specific width may be adaptively adjusted according to the specific size and application scenario of the sliding bearing 200. For example, the width of the gap in the radial direction of the mandrel body 212 may be less than 3 μm, and it is sufficient that the bearing housing 220 can be rotated with respect to the mandrel 210.

In some embodiments, at least one of the at least three layers of gaps may be filled with a medium (e.g., liquid metal, air, oil, water, etc.), so as to reduce the sliding friction between the bearing sleeve 220 and the mandrel 210, and the medium in the gap may provide a better dynamic pressure effect for the sliding bearing 200 when rotating, thereby increasing the bearing capacity of the sliding bearing 200. For example only, the first gap 240, the second gap 250, and the third gap 260 are all filled with a medium. As another example, the first gap 240 is not filled with a medium, and the second gap 250 and the third gap 260 are filled with a medium. As another example, the first gap 240 and the second gap 250 may be filled with a dielectric, and the third gap 260 may be filled with a dielectric. As another example, the first gap 240 and the third gap 260 may be filled with a dielectric, and the second gap 250 may be filled with a dielectric.

In the sliding bearing 200 described above, the bearing sleeve 220 cooperates with the mandrel 210 to form a plurality of layers of gaps (e.g., the first gap 240, the second gap 250, and the third gap 260) distributed along the radial direction of the mandrel main body 212, compared with the sliding bearing 100 shown in fig. 1 with only one layer of gap 140, the dynamic pressure effect in the sliding bearing 200 can be effectively improved by the media filled in the plurality of layers of gaps, so that the bearing capacity of the sliding bearing 200 is improved. In addition, when the sliding bearing 200 is applied to the rotating anode of the X-ray tube, the annular structure 211 is arranged on the outer side of the mandrel main body 212 to be matched with the bearing sleeve 220, so that the bearing capacity of the sliding bearing 200 is improved, the axial length of the mandrel main body 212 matched with the bearing sleeve 220 is shortened, the temperature difference between two ends of the sliding bearing 200 is reduced, the temperature field distribution of the mandrel 210 and the bearing sleeve 220 is more uniform, the thermal deformation of the sliding bearing 200 caused by the large temperature difference between two ends of the sliding bearing 200 is obviously reduced, and the stability of the whole structure of the sliding bearing 200 is improved. By way of example only, when the sliding bearing 100 shown in fig. 1 and the sliding bearing 200 shown in fig. 2 have the same bearing capacity, the length of the core shaft main body 212 and the bearing bush 220 in the sliding bearing 200 can be at least shortened 1/4 relative to the length of the core shaft 110 and the bearing bush 120 in the sliding bearing 100, so as to effectively reduce the temperature difference between the two ends of the sliding bearing 200, reduce the thermal deformation of the sliding bearing 200, and improve the stability of the sliding bearing 200. In addition, the medium (e.g., liquid metal) in the multi-layer gap can absorb heat generated at the target disk 280, and the multi-layer gap can increase the heat dissipation area between the bearing sleeve 220 and the spindle 210, thereby improving the heat dissipation capability of the rotary anode.

It should be noted that the gaps in the sliding bearing 200 are not limited to the first gap 240, the second gap 250, and the third gap 260 distributed in the radial direction of the mandrel main body 212, and there are also gaps between the top ends of the mandrel main body 212 and the annular structure 211 and the inner wall where the bearing sleeve 220 is located, and between the upper surface of the connecting member 213 and the peripheral side thereof and the inner wall where the bearing sleeve 220 is located and the bottom end of the protruding structure 221, and for the convenience of distinguishing from the first gap 240, the second gap 250, and the third gap 260, the gaps may be referred to as end-face gaps, and the end-face gaps may communicate with at least one layer of the above-mentioned multiple layers of gaps distributed in the radial direction of the mandrel main body 212, so as to facilitate the filling of the medium. In some embodiments, the dimension of the end gap in the axial direction of the mandrel body 212 may be the same or different than the dimension of the first gap 240, the second gap 250, or the third gap 260 in the radial direction of the mandrel body 212.

Since the medium in the gap has fluidity, the medium may flow out along the side wall of the mandrel body 212 during high-speed rotation of the sliding bearing 200, and in order to provide better sealing of the sliding bearing 200, in some embodiments, the sliding bearing 200 may further include a sealing member 230. In some embodiments, the sealing member 230 may be a plate-shaped or block-shaped structure, a middle region of the sealing member 230 is opened with an opening, the sealing member 230 is sleeved outside the spindle main body 212 through the opening and is connected to the open end of the bearing sleeve 220, and the size of the opening may be larger than the outer diameter of the spindle main body 212, so that the bearing sleeve 220 can rotate relative to the spindle 210. In some embodiments, the outer diameter of the seal 230 may be the same as the outer diameter of the open end of the bearing housing 220, or greater than the outer diameter of the open end of the bearing housing 220. In some embodiments, the sealing element 230 may be fixed to the open end of the bearing housing 220 by bolting, welding, riveting, or the like. On the one hand, the sealing member 230 can ensure the sealing property of the sliding bearing 200 and prevent the medium from flowing out. On the other hand, the seal 230 may prevent excessive axial displacement of the bearing housing 220 when rotating relative to the spindle 210.

In some embodiments, the surface of the ring-shaped structure 211 or the location where the bearing sleeve 220 fits the mandrel body 212 and the ring-shaped structure 211 of the mandrel 210 is provided with one or more notches (not shown in fig. 2). In some embodiments, the notches may be herringbone-shaped grooves, wedge-shaped grooves, or other shaped grooves. In some embodiments, the sidewall of the mandrel body 212, the sidewall of the ring-shaped structure 211, the sidewall of the protruding structure 221, or the sidewall of the mounting cavity of the bearing sleeve 220 corresponding to the first gap 240, the second gap 250, and the third gap 260 distributed along the radial direction of the mandrel body 212 may be provided with a notch, which may store a portion of the medium in the gap, and may prevent the medium in the sliding bearing 200 from leaking outwards along the sidewall of the mandrel body 212 to a certain extent, thereby achieving a self-sealing effect. In addition, the notches may store a certain amount of media, and the media stored in the notches may further enhance the dynamic pressure effect based on the wedge effect when the bearing sleeve 220 rotates relative to the spindle 210. In some embodiments, the top ends of the mandrel main body 212 and the annular structure 211 and the inner wall where the bearing sleeve 220 is located, the upper and lower surfaces and the peripheral side of the connecting member 213 and the inner wall where the bearing sleeve 220 is located or the bottom end of the protruding structure 221 may also be provided with notches, where the notches may prevent the annular structure 211, the mandrel main body 212 and the bearing sleeve 220 from moving and pressing against each other in the axial direction during the operation of the sliding bearing 200, and at the same time, may also reduce the risk of bearing seizure caused by thermal expansion of the annular structure 211, the mandrel main body 212 and the bearing sleeve 220 due to temperature increase to a certain extent. In some embodiments, a notch may also be provided on the surface of the seal 230 opposite the connector 213.

FIG. 4 is a schematic view of a plain bearing according to some embodiments of the present application. As shown in fig. 4, in some embodiments, one or more second grooves 231 are formed in the side wall of the seal 230 that mates with the mandrel body 212. In some embodiments, second groove 231 may be an annular groove along the sidewall of seal 230 that mates with the sidewall of mandrel body 212, or may be a plurality of non-communicating grooves along the sidewall of seal 230 that mates with the sidewall of mandrel body 212. In some implementations, the second groove 231 may be a notch in the shape of a human-shaped groove, a wedge-shaped groove, or the like. One or more second grooves 231 provided on the inner wall of the seal 230 may collect the medium as it flows outwardly along the outer wall of the mandrel body 212, thereby preventing leakage of the medium.

In order to reduce the difficulty of machining and assembling the mandrel 210 and the bearing sleeve 220 while allowing the bearing sleeve 220 to rotate relative to the mandrel 210, in some embodiments, at least one region of the ring-shaped structure 211 has a thickness that is different from the thickness of other regions of the ring-shaped structure 211. The thickness here refers to the dimension of the side wall of the ring-shaped structure 211 in the radial direction of the mandrel body 212. Correspondingly, the dimension of the ring-shaped structure 211 in the axial direction of the mandrel body 212 is the height of the ring-shaped structure 211. At least one region of the ring-shaped structure 211 may refer to a region of the ring-shaped structure 211 having a specific height range. For example, at least one region of the ring structure 211 may be a region within a range of 1/3-1/2 of the height of the ring structure 211. For another example, at least one region of the ring-shaped structure 211 may be a region above 3/4 of the height of the ring-shaped structure 211. For another example, at least one region of ring structure 211 may be a region below 1/3 of the height of ring structure 211. In some embodiments, the ring-shaped structure 211 may be of a shape that is increasing or tapering in thickness along the axial direction of the mandrel body 212. For example, the cross-sectional shape of the ring-shaped structure 511 shown in fig. 5 taken in a plane passing through the axis of the mandrel body 512 is trapezoidal. In other embodiments, the cross-sectional shape of the ring structure 511 taken in a plane passing through the axis of the mandrel body 512 may also be an inverted trapezoid. The cross-sectional shape of the annular structure 511 taken through the plane of the axis of the mandrel main body 512 is not limited to the trapezoidal shape, and may be other regular or irregular shapes such as a T-shape, an i-shape, and a circular arc shape. FIG. 6 is a schematic structural view of a plain bearing provided in accordance with some embodiments herein. As shown in fig. 6, the upper end of the ring structure 611 may be an arc-shaped end, and the arc-shaped end of the ring structure 611 may reduce the sliding friction between the bearing sleeve 620 and the ring structure 611, on the one hand, and may also facilitate the medium flow in the gap inside the sliding bearing 600, on the other hand. In some embodiments, the difference in thickness of at least one region of the ring structure 611 and the other regions of the ring structure 611 may also mean that the side wall of the ring structure 611 has recesses or protrusions, which may be uniformly or non-uniformly spaced at the side wall of the ring structure 611. In some embodiments, the thickness of all regions of the ring structure 611 may also be the same. For example, the cross-sectional shape of the ring-like structure 611 taken in a plane that is transverse to the axis of the mandrel body is rectangular as shown in FIG. 2.

Referring to fig. 2, in some embodiments, the thickness of at least one region in the raised structure 221 may be different from the thickness of regions in other regions in the raised structure 221. The thickness here refers to the dimension of the sidewall of the projection structure 221 in the radial direction of the mandrel body 212. Correspondingly, the dimension of the protruding structure 221 in the axial direction of the mandrel body 212 is the height of the protruding structure 221. The at least one region of the protrusion structure 221 may refer to a region of a specific height range of the protrusion structure 221. For example, at least one region of the raised structure 221 may be a region within a range of 1/3-1/2 of the height of the raised structure 221. For another example, at least one region of the raised structure 221 may be a region above 3/4 of the height of the raised structure 221. As another example, at least one region of the raised structure 221 may be a region below 1/3 of the height of the raised structure 221. In some embodiments, the raised feature 221 may be tapered or increasing in thickness along the axial direction of the mandrel body 212, for example, the cross-sectional shape of the raised feature 221 taken through the plane of the axis of the mandrel body 212 may be an inverted trapezoid, and in other embodiments, the cross-sectional shape of the raised feature 221 taken through the plane of the axis of the mandrel body 212 may also be a trapezoid. It should be noted that the cross-sectional shape of the projection structure 221 taken through the plane of the axis of the mandrel main body 212 is not limited to the trapezoid, but may be other regular or irregular shapes such as T-shaped, i-shaped, and arc-shaped. In some embodiments, the difference in thickness of at least one region of the raised structures 221 and the thickness of other regions of the raised structures 221 may also mean that the sidewalls of the raised structures 221 have recesses or protrusions thereon, which may be uniformly or non-uniformly spaced at the sidewalls of the raised structures. In some embodiments, the thickness of all regions of the raised structure 221 in the axial direction may also be the same. For example, the cross-sectional shape of the raised formation 221 taken in a plane through the axis of the mandrel body 212 may also be rectangular as shown in FIG. 2.

The sliding bearing 200 can be used in the field of medical CT apparatuses, for example, in X-ray apparatuses. Embodiments of the present disclosure also provide an X-ray tube assembly that may include a cathode filament assembly and an anode target assembly, wherein the cathode filament assembly and the anode target assembly are oppositely disposed. The cathode filament assembly may refer to a filament for emitting electrons. An anode target assembly (also referred to as a rotating anode) may refer to a target material for receiving electron bombardment. When high-energy high-speed electrons generated by the cathode filament assembly bombard a target disc of the anode target assembly in the working process of the X-ray tube assembly, the high-speed electrons reach the target surface of the target disc in the anode target assembly, the movement of the high-speed electrons is stopped, the kinetic energy of part of the high-speed electrons is converted into radiation energy, and the radiation is radiated out in the form of X rays and is called bremsstrahlung radiation. Another portion of the high-speed electrons collide with the target surface of the anode target assembly to generate a large amount of heat, so that the target surface temperature of the target disk is high. With continued reference to fig. 2, in some embodiments, the anode target assembly can include a target disk 280 and a slide bearing 200 supporting the target disk 280. In some embodiments, the sliding bearing 200 may include a mandrel 210 and a bearing sleeve 220 fitted to the mandrel 210, the bearing sleeve 220 being assembled to the mandrel 210 in an axial direction of the mandrel body 212. In some embodiments, the mandrel 210 may include a mandrel body 212 and a ring-shaped structure 211 distributed outside the mandrel body 212, the ring-shaped structure 211 being connected with the mandrel body 212, the ring-shaped structure 211 and the mandrel body 212 having a set spacing therebetween in a radial direction of the mandrel body 212. In some embodiments, the inner side of the bearing sleeve 220 is provided with a protrusion 221, the protrusion 221 is located between the mandrel main body 212 and the ring-shaped structure 211, and the ring-shaped structure 211 is located between the protrusion 221 and the bearing sleeve 220, such that a first gap 240 is formed between the outer side of the ring-shaped structure 211 and the sidewall of the mounting cavity of the bearing sleeve 220, a second gap 250 is formed between the inner side of the ring-shaped structure 211 and the outer side of the protrusion 221, and a third gap 260 is formed between the sidewall of the mandrel main body 212 and the inner side of the protrusion 221. In some embodiments, the target plate 280 may have a disk-shaped structure, a mounting opening is formed in a middle region of the target plate 280, and the target plate 280 is sleeved on an outer wall of the bearing sleeve 220 through the mounting opening and is fixedly connected to the bearing sleeve 220. The spindle 210 is coupled to the bearing sleeve 220, heat generated at the target disk 280 of the bearing sleeve 220 and the target disk 280 can be transferred to the sliding bearing 200, and a medium filled in the multi-layer gaps (e.g., the first gap 240, the second gap 250, and the third gap 260) of the sliding bearing 200 can absorb a portion of the heat of the target disk 280, thereby reducing the temperature of the target disk 280. In addition to the sliding bearing 200 enhancing heat dissipation through the media in the multi-layer gap, in some embodiments, the interior of the mandrel body 212 may be provided with a cooling medium. In some embodiments, the spindle body 212 may be a tubular structure with a hollow interior, and the spindle body 212 may be filled with a cooling medium to further absorb heat transferred from the absorption target disk 280. In some embodiments, the cooling medium may be water, alcohols, or other liquid mixtures with good thermal conductivity.

It should be noted that the application direction of the sliding bearing in the embodiment of the present specification is not limited to the field of the medical equipment (for example, the X-ray tube assembly) described above, and may also be used in other mechanical engineering equipment fields, for example, the fields of metallurgical industry equipment, aviation equipment, marine equipment, hydraulic engineering equipment, and the like.

The sliding bearing structure of the embodiment of the present application may bring beneficial effects including, but not limited to: (1) the annular structure, the mandrel main body and the bearing sleeve are matched with a plurality of layers of gaps, and the plurality of layers of gaps are filled with media, so that the dynamic pressure effect in the sliding bearing can be effectively increased, and the bearing capacity of the sliding bearing is improved; (2) the heat dissipation area between the core shaft and the bearing sleeve is increased by the multi-layer gaps, and the heat dissipation capacity of the sliding bearing is further improved; (3) through setting up ring structure can shorten dabber main part and bearing housing matched with length, reduce the temperature difference at dabber main part both ends, prevent heat altered shape, improve slide bearing's stability.

The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (10)

1. A plain bearing, comprising:

a mandrel (210), wherein the mandrel (210) comprises a mandrel body (212) and a ring-shaped structure (211) distributed outside the mandrel body (212), the ring-shaped structure (211) is connected with the mandrel body (212), and the ring-shaped structure (211) has a distance with the mandrel body (212); and

a bearing sleeve (220), the bearing sleeve (220) being form-fitted to the mandrel body (212) and the ring-shaped structure (211) of the mandrel (210), at least three layers of gaps being formed between the mandrel (210) and the bearing sleeve (220) in a radial direction of the mandrel body (212).

2. A plain bearing according to claim 1, characterized in that the thickness of at least one region in the ring-like structure (211) differs from the thickness of other regions in the ring-like structure (211).

3. A plain bearing according to claim 1, characterized in that the bearing sleeve (220) comprises a raised structure (221), the raised structure (221) being located between the mandrel body (212) and the ring-shaped structure (211), a triple-layer gap being formed in the radial direction of the mandrel body (212) between the mandrel body (212) and the raised structure (221), between the ring-shaped structure (211) and the raised structure (221), and between the ring-shaped structure (211) and the bearing sleeve (220).

4. A plain bearing according to claim 1, characterized in that the width of any one of the at least three layer gaps in the radial direction of the mandrel body (212) is 10-30 um.

5. A plain bearing according to claim 3, characterized in that the thickness of at least one region in the raised structure (221) differs from the thickness of regions of other regions in the raised structure (221).

6. A plain bearing according to claim 1, characterized in that the surface of the ring-shaped structure (211) or the bearing sleeve (220) is notched at a position adapted to the shape of the mandrel body (212) and the ring-shaped structure (211) of the mandrel (210).

7. The plain bearing according to claim 1, wherein the mandrel (210) comprises a connecting member (213), the connecting member (213) is sleeved on the outer wall of the mandrel main body (212), the ring-shaped structure (211) is connected with the mandrel main body (212) through the connecting member (213), and the connecting member (213) is adapted to the first groove (270) formed at the open end of the bearing sleeve (220).

8. A plain bearing according to claim 7, characterized in that the plain bearing comprises a seal (230), the seal (230) being sleeved outside the spindle body (212) and being connected with the open end of the bearing sleeve (220).

9. A plain bearing according to claim 8, wherein the side wall of the seal (230) cooperating with the mandrel body (212) is provided with a second groove (231).

10. An X-ray tube assembly comprising: cathode filament subassembly, positive pole target subassembly, cathode filament subassembly, positive pole target subassembly relative setting, positive pole target subassembly includes target disc (280) and supports the slide bearing of target disc (280), its characterized in that, the slide bearing includes: a mandrel (210), the mandrel (210) comprising a mandrel body (212) and a ring-shaped structure (211) distributed outside the mandrel body (212), the ring-shaped structure (211) being connected with the mandrel body (212), the ring-shaped structure (211) and the mandrel body (212) having a set spacing therebetween in a radial direction of the mandrel body (212); the inner side of the bearing sleeve (220) is provided with a convex structure (221); the bearing sleeve (220) is assembled on the mandrel (210) along the axial direction of the mandrel main body (212), the protruding structure (221) is located between the mandrel main body (212) and the annular structure (211), and the annular structure (211) is located between the protruding structure (221) and the bearing sleeve (220).

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