Thrust bearing and transmission shaft assembly

Abstract

The invention relates to a thrust bearing and a transmission shaft assembly, and belongs to the technical field of screw drilling tools. The thrust bearing comprises a static ring; the movable ring comprises a base body and blades, the base body and the wall face of the static ring are oppositely arranged in a spaced mode, one ends of the blades are arranged on the wall face, close to the static ring, of the base body, the other ends of the blades extend towards the static ring, and the multiple blades are distributed in the circumferential direction of the base body at equal intervals. And a first channel for slurry to flow through is formed among any two adjacent blades, the base body and the static ring. Slurry is sucked into the bearing space through the blades, heat generated by sliding friction is effectively taken away through the slurry, the temperature of the surfaces of the moving ring and the static ring is reduced, and the service life of a product is prolonged.

Description

Technical Field

[0001] The present application relates to the technical field of screw drilling tools, and in particular to a thrust bearing and drive shaft assembly. Background Art

[0002] Screw drill tools are increasingly used in oil and gas extraction. They primarily consist of a motor assembly, a universal joint housing, a universal joint assembly, and a drive shaft assembly. The drive shaft assembly transmits the torque and speed generated by the motor to the drill bit, breaking the rock. The drive shaft assembly is a critical component in screw drill tools, and its performance directly impacts the tool's drilling efficiency and service life.

[0003] During conventional drilling, the weight on bit (WOB) is borne by the string bearing in the commonly used drive shaft assembly. Its structure and material properties generally meet drilling requirements. However, as drilling parameters increase, string bearing parts often break, significantly shortening the service life of the screw drill, severely impacting daily drilling operations and significantly increasing drilling costs.

[0004] Therefore, in drilling with enhanced drilling parameters, thrust bearings are used in the drive shaft assembly. Since the thrust bearing is a sliding friction structure, a large amount of friction heat will be generated under the working conditions of enhanced drilling parameters. After a large amount of friction heat is transferred to the friction surface of the thrust bearing, it cannot be cooled in time, resulting in the friction surface of the thrust bearing overheating and causing the bearing failure. As a result, the service life of the drive shaft assembly using the thrust bearing cannot meet the expected requirements. Summary of the Invention

[0005] The present application provides a thrust bearing and drive shaft assembly, which can solve the problem in the related art that the thrust bearing is prone to generate a large amount of friction heat under working conditions with enhanced drilling parameters, which in turn causes bearing failure and affects the service life of the drive shaft assembly.

[0006] First aspect: An embodiment of the present application provides a thrust bearing, comprising: a stationary ring; a dynamic ring, comprising a base and blades, wherein the base is opposite to the wall surface of the stationary ring and is arranged at intervals, one end of the blade is arranged on the wall surface of the base close to the stationary ring, and the other end extends toward the stationary ring, and there are multiple blades, which are equidistantly distributed around the circumference of the base, and a first channel for mud to flow through is formed between any two adjacent blades and the base and the stationary ring.

[0007] In some embodiments, an angle α is formed between a straight line connecting the centers of the two ends of the blade and the horizontal symmetry line of the dynamic ring, and the angle α is 30° to 70°.

[0008] In some embodiments, the cross-section of the blade is curved.

[0009] In some embodiments, a wear-resistant layer is provided on the end surface of the stationary ring that contacts the blades.

[0010] Second aspect: An embodiment of the present application provides a drive shaft assembly, including the thrust bearing as described above.

[0011] In some embodiments, it also includes: a transmission shaft, which is passed through the static ring and the dynamic ring of the thrust bearing; a fixing device, which fixes the thrust bearing on the transmission shaft, and the fixing device has a second channel for mud to flow in and a third channel for mud to flow out, and the two ends of the first channel are respectively connected to the second channel and the third channel.

[0012] In some embodiments, the fixing device includes two sets of mounting components, the two sets of mounting components are symmetrically mounted at both ends of the thrust bearing, and the second channel and the third channel are respectively formed in the two sets of mounting components.

[0013] In some embodiments, each group of the mounting components includes: a TC sleeve, which is sleeved on the drive shaft and has a first sub-channel formed therein; an adjustment sleeve, which is sleeved on the drive shaft and is located at one end of the TC sleeve, and has a second sub-channel formed therein; a spacer sleeve, which is sleeved on the drive shaft and is located at one end of the adjustment sleeve, and has a third sub-channel formed therein; and along the direction of mud flow, the first sub-channel, the second sub-channel and the third sub-channel are connected in sequence, and the second channel and the third channel both include the first sub-channel, the second sub-channel and the third sub-channel.

[0014] In some embodiments, it also includes: a half ring, which is connected to the groove of the transmission shaft; a retaining sleeve, one end of which is mounted on the transmission shaft and the other end is mounted on the half ring; a retaining ring, which is mounted on the retaining sleeve; and a fourth channel connected to the third channel is formed between the half ring, the retaining sleeve and the retaining ring.

[0015] In some embodiments, a positioning pin is connected to the half ring.

[0016] The beneficial effects of the technical solutions provided in the embodiments of the present application include: An embodiment of the present application provides a thrust bearing and drive shaft assembly. When the thrust bearing is used, the rotating blades of the moving ring will allow more mud to be sucked into the bearing space, which can effectively cool the heat generated by sliding friction, reduce the surface temperature of the moving ring and static ring parts, and improve the service life of the product. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0018] Figure 1 A schematic diagram showing a thrust bearing provided in an embodiment of the present application; Figure 2 A schematic diagram showing a transmission bearing assembly provided in an embodiment of the present application; In the figure: 1. static ring; 10. wear-resistant layer; 2. dynamic ring; 20. base; 21. blade; 3. first channel; 4. transmission shaft; 40. water cap; 41. sealing shell; 5. second channel; 6. third channel; 70. TC sleeve; 700. first sub-channel; 701. TC dynamic sleeve; 702. TC static sleeve; 71. adjustment sleeve; 710. second sub-channel; 711. outer adjustment sleeve; 712. inner adjustment sleeve; 72. spacer; 720. third sub-channel; 721. outer spacer; 722. inner spacer; 80. half ring; 800. positioning pin; 81. stop sleeve; 82. stop ring; 9. fourth channel. DETAILED DESCRIPTION

[0019] In order to enable those skilled in the art to better understand the present invention, the following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0020] The embodiment of the present application provides a thrust bearing and drive shaft assembly, which can solve the problem in the related art that the thrust bearing is prone to generate a large amount of frictional heat under conditions of enhanced drilling parameters, thereby causing bearing failure and affecting the service life of the drive shaft assembly.

[0021] See also Figures 1 to 2As shown, an embodiment of the present application provides a thrust bearing, comprising: a stationary ring 1 and a dynamic ring 22. The dynamic ring 22 includes a base 20 and blades 21. The base 20 is opposite to the wall of the stationary ring 1 and is arranged at intervals. One end of the blade 21 is arranged on the wall of the base 20 close to the stationary ring 1, and the other end extends toward the stationary ring 1. There are multiple blades 21, which are evenly distributed around the base 20. A first channel 3 for mud to flow through is formed between any two adjacent blades 21, the base 20, and the stationary ring 1. When the thrust bearing is in use, the dynamic ring 22 rotates, and the blades 21 draw more mud into the first channel 3. In the process of passing through the first channel 3, the mud will exchange heat with the friction surface of the base 20 of the dynamic ring 22 and the stationary ring 1. The mud carries away a large amount of heat generated by sliding friction on the friction surface, thereby cooling the friction surface.

[0022] Therefore, the present application, through the design of a specific blade 21 structure and first channel 3, allows mud to flow directly near the friction surface, promptly removing the heat generated by friction, significantly reducing the temperature of the friction surface, avoiding bearing failure due to overheating, and improving the reliability of the thrust bearing under conditions of enhanced drilling parameters. By solving the problem of thrust bearing failure due to overheating, the transmission shaft 4 assembly using this thrust bearing can maintain stable performance during operation, reducing the number of downtime maintenance due to bearing failure, thereby extending the service life of the transmission shaft 4 assembly and enabling it to meet the expected use requirements.

[0023] In the present application, it is also designed that an angle α is formed between the straight line formed by connecting the centers of the two ends of the blade 21 and the horizontal symmetry line of the dynamic ring 22, and the size of the angle α is 30°~70°. If the angle α is too small, close to 0°, the mud flow may be closer to being parallel to the horizontal symmetry line of the dynamic ring 22. Although the mud's passability may be guaranteed to a certain extent, the contact between the mud and the friction surface is not sufficient, and the cooling effect will be greatly reduced. If the angle α is too large, close to 90°, the mud will encounter greater resistance when passing through the first channel 3, resulting in poor mud flow, and may even affect the normal progress of drilling. Controlling the angle α between 30°~70° can achieve a better cooling effect while ensuring the smooth passage of the mud, achieving a balance between the cooling effect and the fluid resistance.

[0024] Specifically, on the one hand, this design can guide the mud to form a certain spiral or oblique flow when passing through the first channel 3. This flow pattern allows the mud to more fully contact the friction surface of the base 20 of the dynamic ring 22 and the static ring 1, prolonging the residence time of the mud near the friction surface, thereby enhancing the heat exchange efficiency and more effectively removing the heat generated by friction. On the other hand, the existence of the angle α will cause the mud to generate a certain amount of turbulence during the flow. Turbulence can destroy the mud laminar boundary layer, making it easier for heat to transfer from the friction surface to the mud, further improving the cooling effect. For example, like in a river, if the water flow is a gentle laminar flow, the heat transfer efficiency is low; when the water flow forms vortices and turbulence, the heat transfer will be faster. With effective cooling and stable operation, the thrust bearing can avoid downtime and maintenance due to overheating and failure, thereby ensuring the continuity of drilling operations. Continuous drilling operations can improve drilling efficiency, shorten drilling cycles, and reduce drilling costs.

[0025] The blades 21 have a curved cross-section. This curved cross-section allows the slurry to flow more smoothly along the curved surface as it passes through the first channel 3 formed by adjacent blades 21, the base 20, and the stationary ring 1. Compared to flat blades 21, curved blades 21 guide the slurry into more streamlined streams, reducing turbulence and energy loss during the mud flow. This allows the mud to flow through the friction surface in a more stable and efficient manner, allowing for more complete heat exchange with the friction surface, removing more heat and significantly improving cooling efficiency. This is similar to setting up curved dikes in a river. Compared to straight dikes, curved dikes better guide the flow of water, making it smoother and reducing impact and energy consumption. In a thrust bearing, the curved blades 21 perform a similar function to dikes, guiding the slurry to flow more efficiently. Furthermore, the curved blades 21 can change the pressure distribution of the slurry within the channel, resulting in a more uniform flow distribution of the slurry within each first channel 3. This ensures that all areas of the friction surface between the base 20 of the dynamic ring 22 and the static ring 1 are adequately cooled, preventing local overheating. If the cross section of the blade 21 is flat, the mud flow in the channel may be unevenly distributed, resulting in insufficient cooling in some areas and excessive cooling in others.

[0026] In this application, during the drilling process, relative motion occurs between the stationary ring 1 and the blades 21, generating friction. To prevent wear on the end face of the stationary ring 1, a wear-resistant layer 10 is applied to the side of the stationary ring 1 that contacts the blades 21. This effectively resists friction and reduces the wear rate of the end face of the stationary ring 1. Without the wear-resistant layer 10, the end face of the stationary ring 1 would gradually wear over time, increasing the gap between the stationary ring 1 and the blades 21 and affecting the normal operation of the thrust bearing. The presence of the wear-resistant layer 10 extends the service life of the stationary ring 1, thereby reducing the number of repairs and replacements required due to wear of the stationary ring 1. This reduces drilling downtime and maintenance costs, improving drilling efficiency. For example, without the wear-resistant layer 10, the thrust bearing may require repair or replacement of the stationary ring 1 after a certain period of operation. However, with the wear-resistant layer 10, the maintenance interval can be extended several times. In addition, the wear-resistant layer 10 generally has a low coefficient of friction, which reduces the frictional resistance between the stationary ring 1 and the blades 21, thereby reducing the generation of frictional heat. Under the condition of enhanced drilling parameters, the generation of frictional heat will be more obvious. If there is no wear-resistant layer 10, a large amount of frictional heat will cause the temperature of the stationary ring 1 and the blade 21 to rise sharply, which may cause the bearing to overheat and fail.

[0027] In the present application, the material of the wear-resistant layer 10 includes but is not limited to cemented carbide and PDC composite sheets. Cemented carbide is an alloy material made of a hard compound of a refractory metal and a bonding metal through a powder metallurgy process, and has extremely high hardness and wear resistance. Its hardness can usually reach HRA80-93, which is much higher than that of ordinary steel. In the thrust bearing, a cemented carbide wear-resistant layer 10 is provided on the end face of the stationary ring 1 on the side in contact with the blade 21, which can effectively resist the friction and wear caused by relative movement during the drilling process. Even under conditions where drilling parameters are strengthened and friction is increased, the cemented carbide wear-resistant layer 10 can maintain its integrity for a long time, reduce the amount of wear on the end face of the stationary ring 1, ensure the stability of the fitting clearance between the stationary ring 1 and the blade 21, ensure the normal flow of mud in the first channel 3, and achieve effective cooling and lubrication. If the wear-resistant layer 10 has insufficient pressure resistance, it may deform under the action of pressure, resulting in a change in the fitting clearance, affecting the performance of the thrust bearing. For example, in a certain drilling operation, the static ring 1 made of ordinary materials suffers from severe rear end wear after running for a period of time, while the static ring 1 using a cemented carbide wear-resistant layer 10 has significantly reduced wear in the same period of time. The PDC composite sheet is composed of a polycrystalline diamond layer and a cemented carbide substrate. The polycrystalline diamond layer has extremely high hardness and wear resistance. Its hardness is close to that of natural diamond, and its wear resistance is dozens or even hundreds of times that of cemented carbide. Under conditions where drilling parameters are strengthened, the thrust bearing will generate a large amount of frictional heat. The PDC composite sheet wear-resistant layer 10 can conduct heat to the surrounding environment in a timely manner, reduce the temperature of the static ring 1 and the blade 21, and avoid bearing failure problems caused by overheating. This helps to improve the reliability and stability of the thrust bearing in high-temperature environments.

[0028] In some alternative embodiments, see Figure 1 and Figure 2An embodiment of the present application provides a drive shaft assembly including the aforementioned thrust bearing. During operation of the drive shaft assembly (4), slurry can flow in an orderly manner within the first channel (3), promptly removing heat generated by friction and effectively cooling the thrust bearing. Simultaneously, the slurry flow forms a lubricating film between the rotating ring (22) and the stationary ring (1), reducing direct contact and friction between them and reducing wear. An angle α is formed between the straight line connecting the centers of the two ends of the blade (21) and the horizontal symmetry line of the rotating ring (22), with the angle α ranging from 30° to 70°. This specific angle design guides the slurry flow within the first channel (3) in a more appropriate direction and speed. When the angle is within this range, the slurry can obtain optimal kinetic energy and flow direction, avoiding dead spots or turbulence, thereby improving cooling and lubrication efficiency. For example, if the angle is too small, the slurry flow may be too smooth and unable to effectively remove heat; if the angle is too large, the slurry flow may generate significant resistance, affecting flow efficiency. The cross-section of the blade (21) is curved, and this curved shape provides better mud guidance. The curved surface can make the mud flow more smoothly and reduce flow resistance. At the same time, it can also increase the contact area between the mud and the blades 21, further improving the mud's absorption and transfer efficiency of heat. Compared with the flat blades 21, the curved blades 21 can make the mud form a more stable flow state in the first channel 3, enhancing the cooling and lubrication effect. The end face of the stationary ring 1 on the side in contact with the blades 21 is provided with a wear-resistant layer 10. The wear-resistant layer 10 can resist the friction and wear between the blades 21 and the stationary ring 1, ensuring that the fitting clearance between the two remains relatively stable during long-term operation. A stable fitting clearance is the basis for the normal operation of the thrust bearing. It can ensure that the mud forms a stable flow in the first channel 3. At the same time, due to the reduced friction between the blades 21 and the stationary ring 1, the wear of the blades 21 will also be reduced accordingly. This reduces the number of repairs and replacements required due to component wear, and extends the service life of the thrust bearing and even the entire transmission shaft 4 assembly.

[0029] In this embodiment, the drive shaft 4 assembly also includes: a drive shaft 4 and a fixing device. The drive shaft 4 is inserted through the static ring 1 and the dynamic ring 22 of the thrust bearing; the fixing device fixes the thrust bearing to the drive shaft 4. The fixing device has a second channel 5 for mud to flow in and a third channel 6 for mud to flow out. The two ends of the first channel 3 are connected to the second channel 5 and the third channel 6 respectively. The fixing device firmly fixes the thrust bearing to the drive shaft 4, preventing the thrust bearing from shifting or loosening during operation. This stable fixing method can ensure that the relative position between the static ring 1 and the dynamic ring 22 of the thrust bearing is always accurate. The first channel 3 is formed by adjacent blades 21, the base 20 and the static ring 1. Its unique structure allows mud to better penetrate the contact surface between the dynamic ring 22 and the static ring 1 during flow, forming a uniform lubricating film. The second channel 5 and the third channel 6 provide smooth paths for the entry and exit of mud, ensuring that the mud can fully cover the entire working area of ​​the thrust bearing, reducing direct contact and friction between the dynamic ring 22 and the static ring 1, reducing wear, and extending the service life of the thrust bearing. The first channel 3 is connected with the second channel 5 and the third channel 6 to form a complete mud circulation channel. During the operation of the drive shaft 4, mud can enter from the second channel 5 and flow through the first channel 3 and the third channel 6 in sequence to achieve continuous circulation. This circulating flow can continuously remove the heat generated by friction in the thrust bearing, effectively reducing the bearing temperature, preventing performance degradation and damage due to overheating, and ensuring that the drive shaft 4 assembly operates stably at an appropriate temperature.

[0030] In this embodiment, the fixing device includes two sets of mounting components, which are symmetrically mounted at both ends of the thrust bearing. The second channel 5 and the third channel 6 are respectively formed within the two sets of mounting components. The two sets of mounting components are symmetrically mounted at both ends of the thrust bearing, so that the second channel 5 and the third channel 6 are also symmetrically distributed. This symmetrical layout ensures that mud can enter and exit the thrust bearing at a uniform flow rate and pressure. The second channel 5 serves as the mud inlet channel, and the third channel 6 serves as the mud outlet channel. The two channels cooperate to form a complete mud circulation path. During operation of the drive shaft 4, the mud continuously circulates within the thrust bearing, providing continuous cooling and lubrication. Compared with single-channel or asymmetric channel designs, the dual-channel design improves the mud circulation efficiency and enhances the cooling and lubrication effects, keeping the thrust bearing in good working condition. When mud flows through the second channel 5, it forms a uniform flow distribution within the thrust bearing, fully covering the contact area between the dynamic ring 22 and the static ring 1, removing heat generated by friction, and preventing local overheating. At the same time, the uniform mud flow can also better form a lubricating film, reduce the direct contact and wear between the dynamic ring 22 and the static ring 1, and increase the service life of the thrust bearing.

[0031] Furthermore, the symmetrical mounting arrangement effectively disperses the stress and vibration generated during operation of the drive shaft 4. When the drive shaft 4 is subjected to axial or radial forces, the symmetrical mounting assembly evenly distributes the stress throughout the fixture and drive shaft 4 structure, preventing stress concentration and localized damage. Furthermore, the symmetrical mounting arrangement improves the overall rigidity and stability of the fixture, reduces displacement and deformation caused by vibration, and ensures the relative positional accuracy between the thrust bearing and the drive shaft 4, thereby enhancing the operational reliability and transmission accuracy of the drive shaft 4.

[0032] In the present application, each set of mounting components includes: a TC sleeve 70, an adjustment sleeve 71, and a spacer sleeve 72. The TC sleeve 70 is sleeved on the transmission shaft 4, and includes a TC dynamic sleeve 701 and a TC static sleeve 702. The TC dynamic sleeve 701 is threadedly connected to the two ends of the transmission shaft 41, and the TC static sleeve 702 is sleeved on the outer circle of the TC dynamic sleeve 701, and a first sub-channel 700 is formed between the TC dynamic sleeve 701 and the TC static sleeve 702; the adjustment sleeve 71 is sleeved on the transmission shaft 4 and is located at one end of the TC sleeve 70, and the adjustment sleeve 71 includes an outer adjustment sleeve 711 and an inner adjustment sleeve 712, and the inner adjustment sleeve 712 is sleeved on the outer circle of the transmission shaft 4, and the outer adjustment sleeve 711 is sleeved on the outer circle of the inner adjustment sleeve 712, and a second sub-channel 710 is formed between the outer adjustment sleeve 711 and the inner adjustment sleeve 712; the spacer sleeve 72 is sleeved Mounted on the transmission shaft 4 and located at one end of the adjustment sleeve 71, the spacer 72 comprises an outer spacer 721 and an inner spacer 722. The inner spacer 722 is sleeved onto the transmission shaft 4, the dynamic ring 22 is sleeved onto the transmission shaft 4 at the end of the inner spacer 722, the static ring 1 is sleeved onto the outer circumference of the inner spacer 722, and finally the outer spacer 721 is sleeved onto the outer circumference of the dynamic ring 22. The spacer 72, together with the dynamic ring 22 and the static ring 1, forms a third sub-channel 720 within the spacer 72. Along the direction of mud flow, the first sub-channel 700, the second sub-channel 710, and the third sub-channel 720 are sequentially connected. The second channel 5 and the third channel 6 both comprise the first sub-channel 700, the second sub-channel 710, and the third sub-channel 720. They are sequentially connected along the direction of mud flow. This graded channel design precisely guides the flow of mud, allowing it to flow through different parts of the thrust bearing along a predetermined path. During the operation of the drive shaft 4, the mud first enters the first sub-channel 700 to cool and lubricate the TC sleeve 70. It then enters the second and third sub-channels 710 and 720, respectively, to cool and lubricate other key parts of the thrust bearing. This ensures that the entire thrust bearing is adequately cooled and lubricated, effectively reducing bearing temperature and wear. After the mud passes through the thrust bearing and flows through the first channel 3, it exits the third sub-channel 720, the second sub-channel 710, and the first sub-channel 700 on the third channel 6. The three symmetrically arranged sub-channels together form a complete mud circulation channel, increasing the contact area and contact time between the mud and the thrust bearing. Compared to a single-channel design, the coordinated operation of multiple channels improves the cooling efficiency of the mud, more quickly removes heat generated by friction, prevents performance degradation and damage caused by overheating, and ensures that the drive shaft 4 system operates stably at an appropriate temperature. In addition, at both ends of the transmission shaft 4, one end is used to connect to the drill bit, and the other end is connected to the water cap 40. The TC sleeve 70 is connected close to the drill bit and the water cap 40 respectively. The mud enters from one end of the water cap 40 and flows out from one end of the drill bit.

[0033] In this embodiment, the transmission shaft 4 assembly further includes: a half ring 80, a stopper sleeve 81, and a stopper ring 82. The half ring 80 is connected to the groove of the transmission shaft 4 via a connected positioning pin 800; one end of the stopper sleeve 81 is sleeved on the transmission shaft 4, and the other end is sleeved on the half ring 80; the stopper ring 82 is sleeved on the stopper sleeve 81; and a fourth channel 9 connected to the third channel 6 is formed between the half ring 80, the stopper sleeve 81, and the stopper ring 82. Specifically, the third channel 6 is located between the first sub-channel 700 and the second sub-channel 710. The fourth channel 9 is connected to the third channel 6, so that the flow path of the mud is further extended and expanded. During the outflow process, the mud passes through the third sub-channel 720 and the second sub-channel 710 in sequence and then enters the fourth channel 9, which can cool and lubricate more parts of the transmission shaft 4 assembly. This multi-channel series design increases the contact area and time between the mud and the drive shaft 4 and surrounding components, improves the cooling and lubrication efficiency, ensures that the entire drive shaft 4 assembly can be fully cooled during operation, reduces heat accumulation caused by friction, and reduces the wear rate of components.

[0034] The half ring 80 is connected to the groove of the transmission shaft 4 via a locating pin 800. The retaining sleeve 81 is fitted onto the transmission shaft 4 at one end and onto the half ring 80 at the other end. The retaining ring 82 is fitted onto the retaining sleeve 81. Finally, a sealing housing 41 is mounted over the TC sleeve, retaining ring 82, and adjustment sleeve 71. This multi-component assembly and connection creates a stable support structure. During operation of the transmission shaft 4, the components cooperate with each other, effectively dissipating the stress and vibration generated by the transmission shaft 4, reducing displacement and deformation caused by vibration, and improving the operational stability of the transmission shaft 4. Furthermore, the assembly and connection between the half ring 80, retaining sleeve 81, and retaining ring 82 form a multi-layer sealing structure. The retaining sleeve 81 fits over the transmission shaft 4 and half ring 80, and the retaining ring 82 fits over the retaining sleeve 81. The tight fit between these components effectively prevents slurry from leaking out of the channel. Compared to a single sealing structure, the multi-layer sealing structure provides a better sealing effect, reduces the risk of slurry leakage, ensures that slurry flows along the designated path within the channel, and improves the cooling and lubrication effect. Furthermore, because the half ring 80, retaining sleeve 81, retaining ring 82, and other components utilize a modular design and are assembled by fitting together and connecting with locating pins 800, these components can be easily disassembled to inspect the channel, clean out mud deposits, or replace damaged components when maintenance or repair is required on the transmission shaft 4 assembly. This easy-to-assemble and disassemble design greatly simplifies the maintenance and repair process, reducing repair time and labor costs.

[0035] In the description of this application, it should be noted that the terms "upper" and "lower" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0036] It should be noted that, in this application, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprising a ..." does not exclude the presence of other identical elements in the process, method, article or device comprising the element.

[0037] The foregoing is merely a list of specific embodiments of the present application, intended to enable those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application is not limited to the embodiments shown herein, but is intended to conform to the broadest scope consistent with the principles and novel features of the present application.

Claims

1. A thrust bearing, characterized in that: It includes: static ring (1); A dynamic ring (2) includes a base (20) and blades (21), wherein the base (20) is opposite to the wall surface of the static ring (1) and is arranged at intervals, one end of the blade (21) is arranged on the wall surface of the base (20) close to the static ring (1), and the other end extends toward the static ring (1), and there are multiple blades (21) that are equidistantly distributed around the base (20) in the circumferential direction, and a first channel (3) for mud to flow through is formed between any two adjacent blades (21), the base (20) and the static ring (1).

2. A thrust bearing according to claim 1, characterized in that: An included angle α is formed between a straight line formed by connecting the centers of the two ends of the blade (21) and the horizontal symmetry line of the dynamic ring (2), and the size of the included angle α is 30° to 70°.

3. A thrust bearing according to claim 2, characterized in that: The cross section of the blade (21) is arranged in a curved surface.

4. A thrust bearing according to claim 1, characterized in that: The end surface of the stationary ring (1) in contact with the blades (21) is provided with a wear-resistant layer (10).

5. A transmission shaft assembly, characterized in that: Comprising the thrust bearing according to any one of claims 1 to 4 above.

6. The transmission shaft assembly according to claim 5, characterized in that: Also includes: A transmission shaft (4) passing through the static ring (1) and the dynamic ring (2) of the thrust bearing; A fixing device fixes the thrust bearing on the transmission shaft (4), the fixing device having a second channel (5) for mud to flow in and a third channel (6) for mud to flow out, and two ends of the first channel (3) are respectively connected to the second channel (5) and the third channel (6).

7. The transmission shaft assembly according to claim 6, characterized in that: The fixing device comprises two sets of mounting components, the two sets of mounting components are symmetrically mounted at both ends of the thrust bearing, and the second channel (5) and the third channel (6) are respectively formed in the two sets of mounting components.

8. The transmission shaft assembly according to claim 7, characterized in that: Each set of the installation components includes: A TC sleeve (70) is sleeved on the transmission shaft (4) and has a first sub-channel (700) formed therein; an adjusting sleeve (71) which is sleeved on the transmission shaft (4) and located at one end of the TC sleeve (70), and a second sub-channel (710) is formed inside the adjusting sleeve (71); a spacer sleeve (72) which is sleeved on the transmission shaft (4) and located at one end of the adjustment sleeve (71); a third sub-channel (720) is formed inside the spacer sleeve (72); And along the mud flow direction, the first sub-channel (700), the second sub-channel (710) and the third sub-channel (720) are connected in sequence, and the second channel (5) and the third channel (6) both include the first sub-channel (700), the second sub-channel (710) and the third sub-channel (720).

9. The transmission shaft assembly according to claim 6, characterized in that: Also includes: A half ring (80) connected in a groove of the transmission shaft (4); A stopper sleeve (81), one end of which is sleeved on the transmission shaft (4) and the other end of which is sleeved on the half ring (80); A retaining ring (82) is sleeved on the retaining sleeve (81); A fourth channel (9) communicating with the third channel (6) is formed between the half ring (80), the stop sleeve (81), and the stop ring (82).

10. The transmission shaft assembly according to claim 9, characterized in that: A positioning pin (800) is connected to the half ring (80).

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