A high wear resistant plastic alloy composite water-lubricated bearing and propeller

Abstract

The application discloses a kind of high wear-resistant plastic alloy composite water lubrication bearing and propeller, including rotor, bearing body and stator, and water lubrication gap is formed between the outer wall of stator and the inner wall of bearing body.The inner wall of bearing body is provided with annular pre-sand collecting groove, annular water inlet pressure equalizing groove, spiral sand guide groove and bearing converging groove, bearing converging groove is communicated with outside through radial sand discharge hole, annular sand discharge cavity, outer discharge channel, valve hole and deslagging long groove, one-way valve group is arranged in valve hole to guide and discharge sand-laden water flow and reduce shutdown backflow.Propeller includes first shell, second shell, third shell and shell body, and paddle cavity and paddle are arranged in shell body.Input horn, stator flow channel, paddle cavity and output horn form continuous variable cross-section water flow channel.Sand discharge ring guides sand-laden water flow in water lubrication gap to paddle cavity, and reduces the risk of backflow of sundries during reversing by non-return structure;Some embodiments can also be driven by external mechanical transmission to rotate shell body.

Description

Technical Field

[0001] This invention relates to water-lubricated bearings, and more particularly to a high wear-resistant plastic alloy composite water-lubricated bearing and a propeller. Background Technology

[0002] Water-lubricated bearings typically utilize a working water body to form a lubricating film between two relatively rotating support surfaces, reducing friction and wear. These bearings can be used in propellers, pump-jet propulsion devices, annular rotor assemblies, and other underwater rotating equipment for radial support, rotational guidance, and axial restraint of rotating components. For external rotor or annular rotor type underwater rotating equipment, the rotating component can be located on the outside and rotate synchronously with the equipment, while the stator or fixed support is located on the inside and remains relatively fixed. The bearing body is positioned between the rotating component and the stator, creating a water-lubricated gap between them.

[0003] In working environments such as rivers, nearshore areas, sewage, and silty water, the working water often contains particulate matter such as silt, fine sand, and debris. When these particles (impurities) enter the water-lubricated gaps, they easily cause abrasive wear between the relatively rotating support surfaces, leading to scratches on the bearing inner wall, increased clearance, localized uneven wear, and increased vibration. In severe cases, it can even cause bearing jamming or propeller instability. Especially in external rotor or annular rotor structures, bearings are typically housed within a limited annular space with a short axial dimension. The space for water flow channels, support structures, sand removal structures, and sealing structures is restricted. Once silt enters the water-lubricated gaps, if it cannot be collected and discharged in time, it easily circulates repeatedly within the short annular support area, exacerbating wear.

[0004] Existing water-lubricated bearings mostly employ smooth inner walls, ordinary straight grooves, ordinary annular grooves, or spiral grooves of equal depth. Smooth inner walls lack an active sand-guiding path, making it difficult to directionally remove silt entering the water-lubricated gap. Ordinary straight grooves have a single flow direction, making it difficult to accommodate sand-laden water flow from both ends of the bearing. While ordinary annular grooves can temporarily hold some silt, they easily lead to localized sand accumulation. Although spiral grooves of equal depth have a certain guiding effect, their sand-holding space and drainage capacity are insufficient near the silt accumulation area, making it difficult to achieve concentrated sand removal while maintaining the water film bearing area. Therefore, in sand-laden water environments, relying solely on ordinary groove structures is insufficient to balance water film stability and silt drainage capacity.

[0005] In addition, for external rotor or annular rotor water-lubricated bearings, the outer side of the bearing body usually needs to cooperate with the rotating components. If only radial sand discharge holes are set on the bearing body, but the annular sand discharge cavity, external discharge channel and axial slag discharge groove corresponding to the radial sand discharge holes are lacking, mud and sand may still remain in the mating area between the bearing body and the rotating components, causing poor sand discharge, contamination of the mating surface and additional wear.

[0006] Existing propellers are typically designed based on the propeller blades, motor rotor, casing guide, and overall installation space, with water-lubricated bearings often serving only as support components installed inside the propeller. For conventional propellers, the inlet, outlet, and internal flow channels of the propeller casing primarily serve propulsion efficiency, without redesigning the entire flow channel, throat, bearing water supply, and sediment removal structure around the water-lubricated bearing that rotates on the outer ring and is fixed on the inner ring. Especially in structures where the outer ring rotates and the inner ring is fixed, the fixed inner ring or stator is located in the middle of the propeller's flow channel. If it is not designed as an integral part of the fixed inner ring throat core, it may increase flow resistance and make it difficult to utilize its fixed characteristics to provide active water supply, flushing, and sediment removal functions for the bearing water film and sediment discharge.

[0007] For shaftless rim-type propellers or external rotor propellers, if only a uniform cross-section shell or a common cylindrical guide shell is used, the water flow is prone to flow deviation, local backflow, or uneven velocity distribution before entering the blade working area. If the throat is too small or the diffuser section is poorly designed, it can easily lead to restricted water intake, cavitation, increased noise, or flow separation at the outlet. Especially in waters containing sediment, when there is a lack of coordinated design between the outlet flow field and the bearing sediment discharge path, even if sediment discharge channels, collection channels, and discharge holes are set inside the bearing, the discharged sediment-containing water flow may still experience secondary deposition or backflow at the shell window, near the blade root, or in the outlet diffuser area.

[0008] Furthermore, in practical use, propellers typically have a main propulsion direction and a reverse maneuvering direction. The main propulsion direction usually requires high propulsion efficiency, large thrust, and good sediment removal capability; the reverse direction usually only needs to meet functions such as low-speed reversing, parking, positioning, getting out of trouble, or short-term reverse clearing. If the propeller is designed as a completely symmetrical bidirectional flow channel, it may be difficult to balance the efficiency of the main propulsion direction and the sediment removal effect at the outlet; if it is designed as a unidirectional flow channel, it may lack the necessary reverse low-speed maneuvering and reverse disturbance clearing capabilities.

[0009] Therefore, how to achieve timely and effective sand removal, thereby improving the wear resistance and sand removal capacity of water-lubricated bearings in sandy water environments, is a technical problem that needs to be solved. Summary of the Invention

[0010] In view of the above-mentioned defects of the prior art, the technical problem to be solved by the present invention is to provide a high wear-resistant plastic alloy composite water-lubricated bearing and a propeller. The high wear-resistant plastic alloy composite water-lubricated bearing still has good sand guiding and sand discharge capabilities after being installed in the housing, which can reduce the retention of mud and sand in the water lubrication gap and assembly mating area, thereby reducing abrasive wear and improving the stability and reliability of the bearing in sandy water environment.

[0011] To achieve the above objectives, the present invention provides a high wear-resistant plastic alloy composite water-lubricated bearing, comprising a rotor, a bearing body, and a stator. The rotor is non-rotatably mounted on the bearing body, while the bearing body is rotatably mounted on the stator. A water-lubricating gap is formed between the outer wall of the stator and the inner wall of the bearing body, and the water-lubricating gap is used to accommodate water to form a water film. The inner wall of the bearing body is also provided with a spiral sand guide groove and a bearing collection groove. The two sides of the bearing collection groove are respectively connected to one end of the corresponding spiral sand guide groove, and the other end of the spiral sand guide groove extends spirally along the inner wall of the bearing body. The bearing converging groove is also connected to one end of the radial sand discharge hole, and the other end of the radial sand discharge hole passes through the bearing body and is connected to the annular sand discharge cavity. The annular sand discharge cavity is set inside the rotor, and the rotor is also provided with an external discharge channel, which is directly or indirectly connected to the outside of the rotor to discharge impurities from the rotor.

[0012] As a further improvement of the present invention, a spline is provided on the inner wall of the rotor, and a spline groove is provided on the outer wall of the bearing body. The rotor is fitted onto the bearing body and the spline is inserted into the spline groove.

[0013] As a further improvement of the present invention, the two ends of the bearing body are respectively assembled and fixed with end caps, and the end caps are respectively equipped with a first sealing gasket and a second sealing gasket. The first sealing gasket and the second sealing gasket are respectively located on the inner and outer sides of the spline groove to form a seal for the end opening of the spline groove.

[0014] As a further improvement of the present invention, the spiral sand guiding grooves on both sides of the bearing converging groove rotate in opposite directions.

[0015] As a further improvement of the present invention, the spiral sand guide groove gradually decreases in depth from the end connected to the bearing converging groove to the end away from the bearing converging groove.

[0016] As a further improvement of the present invention, an annular pre-sand collection trough and an annular water inlet pressure equalization trough are respectively provided on the inner wall of the bearing body at the two open ends, and the annular water inlet pressure equalization trough is provided inside the annular pre-sand collection trough.

[0017] As a further improvement of the present invention, the spiral sand guide groove is not directly connected to the annular water inlet pressure equalization groove on the inner wall of the bearing body.

[0018] As a further improvement of the present invention, it also includes multiple bolts, one end of which is provided with a rotating shaft portion, and a bushing is provided on the rotating shaft portion, the bushing being fitted outside the rotating shaft portion; the end of the bolt with the bushing installed passes through the stator and is installed into the annular pre-sand collection tank or the annular water inlet equalization tank, and the bushing is fitted to the sidewalls of the annular pre-sand collection tank or the annular water inlet equalization tank on both sides of the stator axial direction; the ends of the bolts and bushings shall not contact the inner wall of the annular pre-sand collection tank or the annular water inlet equalization tank.

[0019] As a further improvement of the present invention, the rotor is also provided with a valve hole and a slag discharge groove. The two ends of the external discharge channel are respectively connected to the annular sand discharge chamber and one end of the valve hole. A one-way valve assembly is installed in the valve hole. The one-way valve assembly includes a valve seat, a valve core, an inertial block, and a support ring. The support ring and the valve seat are installed and fixed in the valve hole. The end face of the valve seat away from the external discharge channel is a convex valve seat spherical surface. The valve seat spherical surface is an arc-shaped spherical surface that convexes towards the slag discharge groove. The valve seat is provided with a through valve seat hole. The opening of the valve seat hole is located on the valve seat spherical surface. The valve core is provided with a concave valve core spherical surface that fits with the valve seat spherical surface. The valve core is also provided with a through valve core groove. The valve core groove is misaligned with the valve seat hole so that when the valve seat spherical surface and the valve core spherical surface are fitted together, the valve core groove and the valve seat hole are not connected. The valve core is assembled with one end of the valve stem, and the other end of the valve stem is fitted with a spring, passes through the support ring, and is assembled with the inertial block; the two ends of the spring are respectively pressed against the valve core and the support ring to apply an elastic force to the valve core to press against the valve seat.

[0020] As a further improvement of the present invention, the other end of the valve hole is connected to the slag discharge groove, which is provided on the outer wall of the rotor.

[0021] The present invention also discloses a propulsion device that uses the aforementioned high wear-resistant plastic alloy composite water-lubricated bearing.

[0022] As a further improvement of the present invention, the propeller includes a first outer shell, a second outer shell, a third outer shell, and a housing. The housing is fitted over the rotor, the third outer shell is fitted over the housing, and the first outer shell and the second outer shell are respectively installed at both ends of the third outer shell. A blade cavity is provided inside the housing, and blades are installed inside the blade cavity. The first housing is provided with an input horn and an input connection section, and the input horn is connected to the stator flow channel inside the stator through the input connection section; the second housing is provided with an output connection section and an output horn, one end of the blade cavity is connected to the stator flow channel, and the other end of the blade cavity is connected to the output horn through the output connection section. The input horn, input connecting section, stator flow channel, blade cavity, output connecting section, and output horn are sequentially connected along the water flow direction to form a continuous variable cross-section water flow channel, and the maximum opening of the output horn is greater than the maximum opening of the input horn; the opening of the blade cavity is greater than the opening of the stator flow channel.

[0023] As a further improvement of the present invention, the propeller also includes a sand discharge ring, which is disposed on one side near the blade cavity. The sand discharge ring is fixed or limited to the stator and forms a relatively circumferentially rotatable fit with the bearing body and the rotor. The sand discharge ring is provided with a drainage groove corresponding to the water lubrication gap, and the shell is also provided with a slag discharge ring groove, which is connected to the slag discharge long groove on the rotor; the stator is provided with a stator through hole, which is connected to the water pressure chamber, which is connected to the water lubrication gap, and the water pressure chamber is surrounded by the first shell, the stator and the corresponding end cover or limiting structure.

[0024] As a further improvement of the present invention, the sand discharge ring is provided with a conical surface portion, a short check ring and a long check ring. A first check cavity is formed between the conical surface portion and the adjacent short check ring, and a second check cavity is formed between the short check ring and the long check ring. The short check ring and the long check ring are arranged sequentially along the reflux path from the slag discharge ring groove to the long slag discharge groove.

[0025] The beneficial effects of this invention are: In this invention, a water-lubricated gap is formed between the outer wall of the stator and the inner wall of the bearing body. The working water can form a lubricating water film between the relatively rotating support surfaces, thereby reducing the friction and wear between the bearing body and the stator and improving the stability of the external rotor or annular rotor underwater rotating equipment in a sandy water environment.

[0026] This invention incorporates an annular pre-sand collection groove, an annular water inlet equalization groove, a spiral sand guiding groove, and a bearing converging groove on the inner wall of the bearing body. After sand-laden water enters the bearing end, it is first slowed, expanded, and pre-separated in the annular pre-sand collection groove, and then evenly distributed circumferentially through the annular water inlet equalization groove, which helps improve the stability of the water film within the water lubrication gap. The silt entering the water lubrication gap can enter the spiral sand guiding groove and flow along it into the bearing converging groove, thereby reducing the long-term retention of silt in the water lubrication gap and reducing abrasive wear.

[0027] The spiral sand-guiding groove of this invention is designed with a deeper end near the bearing converging groove and a shallower end away from the bearing converging groove. This design not only preserves a larger bearing area near the water inlet to ensure water film support, but also improves sand holding and guiding capacity near the bearing converging groove. The spiral sand-guiding grooves on both sides of the bearing converging groove rotate in opposite directions, so that when the bearing body rotates in one direction relative to the stator, impurities entering from both sides can be guided to the bearing converging groove, achieving concentrated sand guiding from both sides.

[0028] This invention forms a continuous sand discharge path through radial sand discharge holes, annular sand discharge chambers, external discharge channels, valve holes, and long slag discharge grooves. This allows the silt in the bearing collection groove to be discharged from the inside of the bearing body to the outside of the rotor, preventing silt from entering the assembly gap between the rotor and the bearing body. Breaking with tradition, this invention interchanges the traditional stator and rotor design (traditionally the rotor is inside and the stator is outside), allowing the installation of a one-way valve assembly. The one-way valve assembly uses the centrifugal force generated by the inertial block when the rotor rotates to open the valve core, allowing sand-laden water to flow out. When the machine is stopped or at low speed, a spring pushes the valve core to reset and close the valve seat hole, thereby reducing the risk of external silt, weeds, debris, or sand-laden water entering the bearing from the back.

[0029] In the propeller of this invention, the input flare, input connecting section, stator flow channel, blade cavity, output connecting section, and output flare are sequentially connected along the water flow direction, forming a continuous variable cross-section water flow channel with different front and rear openings. The input flare can converge and guide the water flow on the inlet side, the stator flow channel can rectify and guide the water flow before it enters the blade cavity, the blades can perform work on the rectified water flow within the blade cavity, and the output flare can form a large diffusion discharge area on the outlet side. Therefore, this propeller differs from ordinary duct structures with equal or symmetrical front and rear diameters, which helps reduce turbulence and flow deviation on the inlet side of the blades, minimizes local expansion losses on the outlet side, improves the stability and propulsion efficiency of the water flow through the blade cavity, and also accommodates reverse thrust output under blade reversing or reverse driving conditions.

[0030] This invention also utilizes a structure consisting of a sand-discharging ring, a drainage groove, a slag-discharging ring groove, a conical surface portion, a short check ring, a long check ring, and a check cavity to allow lubricating water and sand-laden water in the water-lubricating gap to be drawn out to the blade cavity and carried away by the main water flow within the blade cavity. The sand-discharging ring assists in forward sand discharge during propulsion and acts as a deflector, buffer, and blocker for reverse water flow and debris during reversing, reducing the probability of debris flowing back into the bearing through the slag-discharging long groove and valve orifice. Simultaneously, it provides a certain degree of reverse flushing to the water-lubricating gap, valve orifice, sand-discharging cavity, and bearing converging groove.

[0031] Furthermore, some embodiments employ an external mechanical power input structure, driving the housing and propeller blades to rotate via mechanical transmission components such as connecting pipes, external drive shafts, bevel gear sets, drive gears, and housing gear rings. This structure allows the power source to be located on the side of the hull or outside the connecting pipe, reducing the underwater portion of the propeller's reliance on motor sealing, waterproofing, insulation, and electrical heat dissipation. This helps reduce manufacturing costs and maintenance difficulty, and improves the propeller's durability and maintainability in waters with abundant silt and debris. Attached Figure Description

[0032] Figure 1 This is a schematic diagram of the structure of a high wear-resistant plastic alloy composite water-lubricated bearing; Figure 2The explosion was caused by a component of a high-wear-resistant plastic alloy composite water-lubricated bearing. Figure 1 ; Figure 3 The explosion was caused by a component of a high-wear-resistant plastic alloy composite water-lubricated bearing. Figure 2 ; Figure 4 This is an orthographic projection of a high wear-resistant plastic alloy composite water-lubricated bearing located on the axial direction of stator 130. Figure 5 yes Figure 4 Sectional view of AA; Figure 6 yes Figure 4 BB section view; Figure 7 yes Figure 6 Enlarged view at F1; Figure 8 yes Figure 6 CC section view; Figure 9 yes Figure 8 Enlarged view at F2 in the middle; Figure 10 This is a schematic diagram of the structure at 120 points on the bearing body. Figure 1 ; Figure 11 This is a schematic diagram of the structure at 120 points on the bearing body. Figure 2 ; Figure 12 This is a schematic diagram of the structure at 120 points on the bearing body. Figure 3 (Partially dissected); Figure 13 This is a schematic diagram of the one-way valve assembly. Figure 1 ; Figure 14 This is a schematic diagram of the one-way valve assembly. Figure 2 ; Figure 15 This is an exploded view of the parts at the check valve assembly; Figure 16 This is a schematic diagram of the thruster structure; Figure 17 This is a cross-sectional view of the thruster located at the center plane of the stator 130 axis; Figure 18 yes Figure 17 Enlarged view at F3; Figure 19 yes Figure 17 CC section view; Figure 20 yes Figure 17 DD section view; Figure 21 This is a schematic diagram of the thruster after the first outer shell 610 and the third outer shell 630 have been removed. Figure 22 This is a schematic diagram of the thruster after removing the first outer shell 610, the second outer shell 620, and the third outer shell 630. Figure 23 This is a schematic diagram of the structure located at the sand discharge ring 660 after the propeller separates from the rotor 110; Figure 24 This is a structural schematic diagram of stator 130, rotor 110, bearing body 120, and sand discharge ring 660. Figure 25 This is a schematic diagram of the structure at the 640th of the shell and the 910th of the blade. Detailed Implementation

[0033] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0034] See Figures 1-12 The high wear-resistant plastic alloy composite water-lubricated bearing of this embodiment includes a rotor 110, a bearing body 120, and a stator 130. A spline 115 is provided on the inner wall of the rotor 110, and a spline groove 126 is provided on the outer wall of the bearing body 120. The rotor 110 is fitted onto the bearing body 120, and the spline 115 is inserted into the spline groove 126, thereby preventing the rotor 110 and the bearing body 120 from rotating relative to each other. Preferably, the spline 115 and the spline groove 126 may be provided with widened or irregularly shaped positioning grooves and splines to prevent misassembly.

[0035] The rotor 110, as a follower rotating component, can rotate synchronously with the propeller, pump-jet propulsion device, or annular rotor assembly; the bearing body 120 rotates synchronously with the rotor 110, and the bearing body 120 is made of high wear-resistant plastic alloy composite material, including an engineering plastic matrix and dispersed wear-resistant components (such as glass fiber, carbon fiber, polytetrafluoroethylene, silicon carbide, etc.).

[0036] The stator 130 is installed inside the bearing body 120 and is rotatable but not axially movable relative to it. A water lubrication gap 101 is formed between the outer wall of the stator 130 and the inner wall of the bearing body 120. The water lubrication gap 101 is used to accommodate water to form a water film, thereby achieving radial support and rotational guidance.

[0037] Both ends of the bearing body 120 are respectively assembled and fixed to end caps 140. A first sealing gasket 210 and a second sealing gasket 220 are respectively installed on the end caps 140. The first sealing gasket 210 and the second sealing gasket 220 are located radially inside and outside the spline groove 126 (the diameter direction of the concentric circles of the bearing body is radial), forming a double seal for the end opening of the spline groove to prevent external impurities from entering the spline mating area. The second sealing gasket 220 can be pressed tightly against the end face of the rotor 110 for sealing (see...). Figure 5This seals the gap between the rotor 110 and the bearing body 120, thereby improving the sealing performance between the rotor 110 and the bearing body 120.

[0038] On the inner wall of the bearing body 120, at the two open ends, there are respectively an annular pre-sand collection groove 124 and an annular water inlet pressure equalization groove 125. The annular water inlet pressure equalization groove 125 is located inside the annular pre-sand collection groove 124 (the annular pre-sand collection groove 124 is close to the opening of the bearing body 120). Figure 5 (The middle part is located at both ends). The annular pre-sand collection tank 124 can slow down, expand, and pre-separate the sand-containing water flow, while the annular water inlet pressure equalization tank 125 provides circumferential pressure equalization for the water lubrication gap, improving the stability of the water film.

[0039] The bearing body 120 is provided with a spiral sand guide groove 121 and a bearing collection groove 122 on the inner wall between the two annular water inlet pressure equalizing grooves 125. The two sides of the bearing collection groove 122 are respectively connected to one end of the corresponding spiral sand guide groove 121. The other end of the spiral sand guide groove 121 extends spirally along the inner wall of the bearing body 120, and the spiral sand guide grooves 121 on both sides of the bearing collection groove 122 rotate in opposite directions. This design allows impurities entering the water lubrication gap 101 to enter the spiral sand guide groove 121 under the action of rotational force, and then enter the bearing collection groove 122 along the spiral sand guide groove 121 to collect, reducing interference and impact on the water lubrication gap 101, and thus reducing wear.

[0040] The spiral sand guiding groove 121 is not directly connected to the annular water inlet equalizing groove 125 on the inner wall of the bearing body 120. The spiral sand guiding groove 121 gradually decreases in depth from the end connected to the bearing gathering groove 122 to the end away from the bearing gathering groove 122 (the depth is the change in displacement of the vertical distance from the axis of the bearing body), thus forming a spiral, sloping structure on the inner wall of the spiral sand guiding groove 121 along the axis of the bearing body 120. This design makes the depth of the spiral sand guiding groove 121 near the water inlet end (the end of the annular water inlet equalizing groove 125) shallower, which can take into account both the bearing area and the stability of the water film; the part near the bearing gathering groove 122 can increase the sand holding space and the guiding capacity, thereby reducing the retention of mud and sand near the lubrication bearing area. In particular, the spiral sand guiding grooves 121 on both sides of the bearing gathering groove 122 rotate in opposite directions, which allows the impurities of the spiral sand guiding grooves 121 on both sides to enter the bearing gathering groove 122 when the bearing body 120 and the stator 130 rotate in one direction.

[0041] After entering the bearing end, the sand-laden water first undergoes deceleration, expansion, and pre-separation through the annular pre-sand collection trough 124. Then, it is evenly distributed circumferentially into the water lubrication gap 101 through the annular water inlet equalization trough 125. Finally, impurities enter the spiral sand guiding trough 121. This reduces the direct entry of larger sand particles into the lubrication bearing area and improves the water supply uniformity of the spiral sand guiding trough, thereby enhancing operational stability and reducing wear.

[0042] The bearing converging groove 122 is also connected to one end of the radial sand discharge hole 123. The other end of the radial sand discharge hole 123 passes through the bearing body 120 and connects to the annular sand discharge cavity 114. The annular sand discharge cavity 114 is located inside the rotor 110. The rotor 110 is also provided with an external discharge channel 113, a valve hole 112, and a slag discharge long groove 111. The two ends of the external discharge channel 113 are connected to one end of the annular sand discharge cavity 114 and one end of the valve hole 112, respectively. The other end of the valve hole 112 is connected to the slag discharge long groove 111, which is located on the outer wall of the rotor 110. In use, the rotor 110 is installed inside the propeller, and the slag discharge long groove 111 forms a slag discharge channel, thereby ensuring that the corresponding impurities can be discharged.

[0043] Preferably, the assembly also includes multiple bolts 510, one end of which is provided with a rotating shaft portion 511. A bushing 520 is provided on the rotating shaft portion 511. The bushing 520 is rotatably fitted onto the rotating shaft portion 511 but cannot move axially. One end of some bolts 510 with the bushing 520 is inserted into the annular pre-collecting sand groove 124 after passing through the stator 130. The bushing 520 and the annular pre-collecting sand groove 124 are fitted together with the side walls on both sides of the axial direction of the stator 130, thereby restricting the stator 130 from sliding axially relative to the bearing body 120.

[0044] The ends of the bolt 510 and bushing 520 must not contact the inner wall of the annular pre-collecting sand groove 124. The annular pre-collecting sand groove 124 is an annular groove. The inner wall here refers to the inner wall on one side coaxial with the stator, not the two side walls of the bushing 520. Figure 5 (Both upper and lower sides). Meanwhile, the bushing 520 does not contact the stator 130. This design ensures that the bolts 510 and bushing 520 will not interfere with the rotation between the stator 130 and the bearing body 120 during use, guaranteeing stability.

[0045] Preferably, one end of a bolt 510 with a bushing 520 passes through the stator 130 and is inserted into the annular water inlet equalizing groove 125. The bushing 520 and the annular water inlet equalizing groove 125 are fitted against the side walls on both axial sides of the stator 130, thereby restricting the axial sliding of the stator 130 relative to the bearing body 120. The ends of the bolts 510 and bushings 520 must not contact the inner wall of the annular water inlet equalizing groove 125. The annular water inlet equalizing groove 125 is an annular groove; the inner wall here refers to the inner wall on one side coaxial with the stator, not the side walls on both sides of the bushing 520. Figure 5 (Both upper and lower sides). Meanwhile, the bushing 520 does not contact the stator 130. This design ensures that the bolts 510 and bushing 520 will not interfere with the rotation between the stator 130 and the bearing body 120 during use, guaranteeing stability.

[0046] In use, the bushing 520 can rotate circumferentially with the annular water inlet equalizing groove 125 and the annular pre-sand collecting groove 124 during rotation, and slightly rotates in contact with the side walls of the annular water inlet equalizing groove 125 and the annular pre-sand collecting groove 124, reducing friction and wear, and assisting in the equalization of water flow and sand removal in the annular water inlet equalizing groove 125 and the annular pre-sand collecting groove 124. In this embodiment, the bushing 520 and bolt 510 can be omitted, and the existing structure can be used to achieve the assembly between the stator 130 and the bearing body 120 that allows circumferential rotation but not axial movement. In other embodiments, bearing retaining rings, snap rings, thrust washers, or other axial limiting structures can be used to replace the bolt 510 and bushing 520 to achieve the assembly relationship between the stator 130 and the bearing body 120 that allows relative circumferential rotation but not relative axial movement. The bolt 510 can be fixed to the stator by threaded engagement, and the bolt and bushing 520 need to be treated with anti-corrosion measures, such as using high-strength corrosion-resistant metal materials.

[0047] See Figures 6-15 A one-way valve assembly is installed in the valve hole 112. The one-way valve assembly is used to control the fluid in the discharge channel 113 to enter the slag discharge trough 111 for discharge, while the impurities in the valve hole 112 are difficult to enter the discharge channel 113 in the reverse direction.

[0048] The one-way valve assembly includes a valve seat 310, a valve core 320, an inertial block 330, and a support ring 340. The support ring 340 and the valve seat 310 are installed and fixed in the valve hole 112. The end face of the valve seat 310 away from the external discharge channel 113 is a convex valve seat spherical surface 312. The valve seat spherical surface 312 is an arc-shaped spherical surface that convexes towards the slag discharge trough 111. The valve seat 310 is provided with a through valve seat hole 311. The opening of the valve seat hole 311 is located on the valve seat spherical surface 312; the valve core 320 is provided with a concave valve core spherical surface 322 that fits against the valve seat spherical surface 312, and the valve core 320 is also provided with a through valve core groove 321. The valve core groove 321 is misaligned with the valve seat hole 311 so that when the valve seat spherical surface 312 and the valve core spherical surface 322 are fitted together, the valve core groove 321 is not connected to the valve seat hole 311, that is... Figure 7 State. The valve seat hole 311 is located at the middle position of the valve seat spherical surface 312, that is... Figure 7 The part near the valve stem 323 is designed so that when debris remains between the valve seat 310 and the valve core 320, the impurities will settle to a lower position on the valve seat spherical surface 312, avoiding clogging of the valve seat hole 311. At the same time, when the impurities are discharged from the valve seat hole 311, they can also be carried out with the water flow to the slag discharge trough 111 for discharge.

[0049] The valve core 320 is assembled with one end of the valve stem 323. The other end of the valve stem 323 is fitted with a spring 350, passes through the support ring 340, and is assembled with the inertial block 330. The valve stem 323 and the support ring 340 are axially slidably assembled. The two ends of the spring 350 are respectively pressed against the valve core 320 and the support ring 340 to apply a spring force to the valve core 320 to press against the valve seat 310, so as to maintain the valve core 320 in the initial state of sealing the valve seat hole 311 and prevent external foreign objects from passing through the valve seat hole 311 and entering the external discharge channel 113.

[0050] The spring 350 is fitted with a protective sleeve 360. The two ends of the protective sleeve 360 ​​are respectively assembled, fixed, and sealed to the support ring 340 and the valve core 320 to enclose the spring 350, ensuring the spring 350 is in a sealed state and preventing contamination. The protective sleeve 360 ​​has elasticity, allowing it to flexibly adapt to the movement of the valve core 320.

[0051] When the rotor 110 rotates, it drives the bearing body 120 to rotate, forming a rotating flow or an inertial sand-discharging flow within the water-lubricated gap 101. The silt and water flow are collected by the spiral sand-guiding groove 121 to the central bearing converging groove 122, then enter the annular sand-discharging chamber 114 through the radial sand-discharging hole 123, and finally reach the valve seat 310 through the external discharge channel 113. The rotation of the rotor 110 causes the inertial block 330 to generate centrifugal force. Once the centrifugal force exceeds the elastic force exerted by the spring 350 on the valve core 320 to push it towards the valve seat 310, the valve core 320 moves towards the support ring 340 and opens. The sand-laden water flows through the valve seat hole 311, the valve core groove 321, and the support ring channel 341 of the support ring 340, and is discharged into the slag discharge trough 111.

[0052] When the equipment stops and the centrifugal force of the inertial block 330 is insufficient to overcome the spring force, the valve core 320 remains closed to the valve seat hole 311 under the action of the spring 350. Figure 7 This reduces the probability that external mud, weeds, debris, or sand-laden water will enter the annular sand discharge chamber 114, the radial sand discharge hole 123, and the interior of the bearing body 120 via the external discharge channel 113.

[0053] Preferably, during use, the inertial block 330 cannot protrude through the valve hole 112, thus preventing it from colliding or rubbing against external devices after protruding through the valve hole 112, thereby reducing the risk of collision, entanglement, or jamming with external devices. This can be achieved by limiting the maximum displacement of the inertial block 330 in the axial direction of the valve stem 323, such as by controlling the length of the valve stem or the maximum compression of the spring.

[0054] Preferably, the number of spiral sand guiding grooves 121 can be adjusted according to bearing specifications, rotational speed, sand content, and operating conditions. For example, each side of the spiral sand guiding groove 121 can be set to three to sixteen grooves; the radial sand discharge holes 123 can be set to two to twelve holes; and the through spline grooves 126 at both ends can be set to four to twelve holes.

[0055] More preferably, each side has 8 spiral sand guide grooves 121, 6 radial sand discharge holes 123, and 8 through spline grooves 126 at both ends. Of course, the above-mentioned quantity range is only a preferred range for ease of implementation and does not limit the protection scope of the present invention.

[0056] Preferably, see Figures 23-24 To ensure the stability of the rotor 110 during rotation, the slag discharge trough 111, valve hole 112, external discharge channel 113, and one-way valve group are preferably evenly distributed along the circumference of the rotor 110. That is, at least two sets of the above structure are provided and arranged at equal angular intervals along the circumference of the rotor 110. This makes the rotor 110 rotate more balanced and stable.

[0057] See Figures 6-7The operation process of this embodiment is roughly as follows: During assembly, the bearing body 120 is fitted inside the rotor 110, and the spline 115 on the inner wall of the rotor 110 is inserted into the spline groove 126 on the outer wall of the bearing body 120, so that the rotor 110 and the bearing body 120 form a non-rotational assembly relationship. The stator 130 is installed inside the bearing body 120, and a water-lubricated gap 101 is formed between the outer wall of the stator 130 and the inner wall of the bearing body 120. End caps 140 are respectively installed at both ends of the bearing body 120, and the first sealing gasket 210 and the second sealing gasket 220 on the end caps 140 are located on the radial inner and outer sides of the spline groove 126, respectively, to seal the end opening of the spline groove 126.

[0058] Bolt 510 passes radially through stator 130 and is threaded into stator 130. A bushing 520 is rotatably fitted onto the rotating shaft portion 511 at the end of bolt 510. The bushings 520 on different bolts 510 extend into the annular pre-sand collection groove 124 or the annular water inlet equalization groove 125, respectively, and form a rotatable limiting fit with the sidewalls of the corresponding annular grooves located on both axial sides of stator 130. The outer circumferential surface of the bushing 520 is flush with the bottom of the corresponding annular groove. Figure 6 The bushing 520 maintains a gap between the inner wall of the stator 130 and the inner wall of the bearing body 120, and the end of the bolt 510 does not abut against the bottom of the corresponding annular groove, and the bushing 520 does not contact the stator 130. Thus, the bushing 520 can restrict the axial relative sliding between the stator 130 and the bearing body 120, while not hindering the circumferential relative rotation between the stator 130 and the bearing body 120.

[0059] In use, the rotor 110 rotates synchronously with the propeller, pump-jet propulsion device, or annular rotor assembly, and drives the bearing body 120 to rotate synchronously. The stator 130 remains relatively fixed. The water lubrication gap 101 between the inner wall of the bearing body 120 and the outer wall of the stator 130 contains working water and forms a lubricating water film, thereby providing radial support and rotational guidance for the rotor 110 and the bearing body 120, and reducing friction and wear between the bearing body 120 and the stator 130.

[0060] After entering from the end of the bearing body 120, the sand-laden water first enters the annular pre-sand collection tank 124. The annular pre-sand collection tank 124 decelerates, expands, and pre-separates the sand-laden water flow, reducing the velocity of larger sand particles. The water then enters the annular inlet equalization tank 125, which evenly distributes the water flow along the circumference of the bearing body 120 before entering the water lubrication gap 101. The bushing 520 can rotate slightly within the corresponding annular groove, reducing friction with the groove sidewalls and agitating the water within the groove, thus aiding in water flow equalization and reducing sand deposition in the annular pre-sand collection tank 124 and the annular inlet equalization tank 125.

[0061] Mud, sand, or other impurities entering the water lubrication gap 101 are drawn into the spiral sand guide groove 121 by the relative rotation between the bearing body 120 and the stator 130 and by the water flow. Since the spiral sand guide grooves 121 on both sides of the bearing collection groove 122 rotate in opposite directions, impurities located on both sides of the bearing body 120 can move along the corresponding spiral sand guide grooves 121 towards the center of the bearing body 120 and eventually enter the bearing collection groove 122. The spiral sand guide groove 121 is shallower at the end near the annular inlet pressure equalization groove 125, which helps retain the bearing area and water film stability of the inner wall of the bearing body 120; the spiral sand guide groove 121 is deeper at the end near the bearing collection groove 122, which helps enhance the sand holding space and drainage capacity.

[0062] After impurities enter the bearing collecting groove 122, they enter the annular sand discharge chamber 114 inside the rotor 110 through the radial sand discharge hole 123 that communicates with the bearing collecting groove 122. The annular sand discharge chamber 114 collects the sand-laden water flow from different radial sand discharge holes 123, and then the sand-laden water flow enters the external discharge channel 113, and then enters the one-way valve group in the valve hole 112 through the external discharge channel 113.

[0063] When the rotor 110 reaches a predetermined speed, the inertial block 330 rotates synchronously with the rotor 110 and generates centrifugal force. The predetermined speed can be determined by the mass of the inertial block 330, the distance from the inertial block 330 to the rotation axis of the rotor 110, the elastic coefficient of the spring 350, and the preload, so that the centrifugal force generated by the inertial block 330 when the rotor 110 reaches the predetermined speed can overcome the clamping force exerted by the spring 350 on the valve core 320. When the centrifugal force on the inertial block 330 is greater than the clamping force exerted by the spring 350 on the valve core 320, the inertial block 330 drives the valve core 320 to move towards the support ring 340 through the valve stem 323, causing the valve core 320 to move away from the valve seat 310. At this time, a gap is formed between the valve seat 310 and the valve core 320, and the valve seat hole 311 communicates with the valve core groove 321. The sand-laden water flows sequentially through the valve seat hole 311, the gap between the valve seat 310 and the valve core 320, the valve core groove 321, and the support ring channel 341 of the support ring 340 into the slag discharge trough 111. The slag discharge trough 111 is set on the outer wall of the rotor 110 and extends along the axial direction of the rotor 110, thus enabling the impurities to be discharged axially and from the rotor 110 mounting area.

[0064] When the equipment stops or the rotor 110 rotates at a low speed, the centrifugal force on the inertial block 330 is insufficient to overcome the elastic force of the spring 350. The spring 350 pushes the valve core 320 to press against the valve seat 310, so that the spherical surface 322 of the valve core fits against the spherical surface 312 of the valve seat. At this time, the valve core groove 321 is misaligned with the valve seat hole 311, and the valve seat hole 311 is closed by the valve core 320. External mud, weeds, debris, or sandy water cannot easily enter the annular sand discharge chamber 114, the radial sand discharge hole 123, and the interior of the bearing body 120 through the slag discharge trough 111, the valve hole 112, and the external discharge channel 113.

[0065] Through the above operation process, this embodiment can form a stable water film in the water lubrication gap 101 while discharging the mud and sand that enters the bearing through the annular pre-collecting sand tank 124, the annular water inlet pressure equalization tank 125, the spiral sand guiding tank 121, the bearing gathering tank 122, the radial sand discharge hole 123, the annular sand discharge cavity 114, the external discharge channel 113, the valve hole 112, and the slag discharge long tank 111. This achieves the synergistic effect of multi-stage pre-collecting sand, pressure equalization water supply, spiral sand guiding, centralized sand collection, centrifugal opening sand discharge, and shutdown backflow prevention.

[0066] In some embodiments, to reduce the frictional resistance of the rotor 110 relative to the stator 130 during startup, low speed, or load fluctuations, an auxiliary rolling support can be provided between the stator 130 and the bearing body 120. The auxiliary rolling support may include balls, rollers, ceramic rolling elements, wear-resistant polymer rolling elements, or a group of rolling elements limited by a cage. Preferably, a rolling element receiving groove adjacent to the annular water inlet equalizing groove 125 can be provided on the bearing body 120 or the stator 130. The rolling element receiving groove and the annular water inlet equalizing groove 125 are connected through a water passage gap, water passage holes, or spaced water guiding channels, allowing the annular water inlet equalizing groove 125 to still supply water to the water lubrication gap 101 and maintain pressure equalization. The rolling elements are disposed within the rolling element receiving groove and their axial and radial positions are limited by raceways, cages, or limiting flanges, thereby providing auxiliary rolling support for the relative movement between the stator 130 and the bearing body 120 without blocking the annular water inlet equalizing groove 125. This part is existing technology, and the relevant design of existing bearings can be directly adopted.

[0067] In another embodiment, the rolling element can also be disposed in a partially widened area of ​​the annular water inlet equalizing groove 125. A water passage gap is reserved in the partially widened area to allow water to flow through, so that the rolling element is used only as an auxiliary support component and does not block the water supply, pressure equalization and sand removal functions of the annular water inlet equalizing groove 125 to the water lubrication gap 101.

[0068] See Figures 16-25The propeller in this embodiment includes a first outer shell 610, a second outer shell 620, a third outer shell 630, and a housing 640. The housing 640 internally contains a blade cavity 643, a slag discharge ring groove 641, and a housing spline 642. A blade 910 is installed within the blade cavity 643. The blade root 911 of the blade 910 is fixedly fitted to the inner wall of the blade cavity 643, and the blade tip 912 of the blade 910 is located near the axis of the blade cavity 643. In operation, the housing 640 rotates, causing the blade 910 to rotate, thereby obtaining forward or backward propulsion. The blade 910 extends from the inner wall of the blade cavity 643 towards the axis of the blade cavity 643, and a flow clearance is maintained between the blade tip 912 of the blade 910 and the axial region of the blade cavity 643. In operation, the housing 640 rotates, causing the blade 910 to rotate, thereby propelling the water flow and obtaining forward or backward propulsion.

[0069] The housing spline 642 engages with the rotor spline groove 116, which is located on the rotor 110, thus preventing the housing 640 and rotor 110 from rotating relative to each other. The housing 640 is rotatably mounted within a third outer shell 630. The two ends of the third outer shell 630 are respectively fixed to the first outer shell 610 and the second outer shell 620. The first outer shell 610 has an input flare 611 and an input connecting section 612. The input flare 611 communicates with the stator flow channel 131 inside the stator 130 via the input connecting section 612. The cross-sectional area or opening of the input flare 611 gradually increases from the end connected to the input connecting section 612 towards the end away from the input connecting section 612. The cross-sectional area is... Figure 20 The sectional view direction in the middle.

[0070] The second outer casing 620 is installed on the side of the casing 640 where the blade 910 is mounted. The second outer casing 620 contains an output connection section 622 and an output horn opening 621. The two ends of the output connection section 622 are connected to one end of the blade cavity 643 and one end of the output horn opening 621, respectively. The other end of the blade cavity 643 is connected to the stator flow channel 131. The cross-sectional area or opening of the output horn opening 621 gradually increases from the end connected to the blade cavity 643 towards the end away from the blade cavity 643. The cross-sectional area is... Figure 20 The sectional view direction in the middle.

[0071] In one embodiment, the input horn 611, input connecting section 612, stator flow channel 131, blade cavity 643, output connecting section 622 and output horn 621 are connected sequentially along the water flow direction (from the first outer shell 610 to the second outer shell 620), and together form a variable cross-section water flow channel with different front and rear openings.

[0072] The input flare 611 has a large end away from the input connection section 612 and a small end close to the input connection section 612. The flow cross-sectional area of ​​the input flare 611 gradually decreases from the large end to the small end, so that the water flow entering the first housing 610 is gradually constricted and guided into the input connection section 612. The input connection section 612 and the stator flow channel 131 are preferably connected by a smooth transition structure to reduce the local turbulence and impact loss generated when the water flow enters the stator flow channel 131 from the input connection section 612.

[0073] The output flare 621 has a small end near the output connection section 622 and a large end away from the output connection section 622. The flow cross-sectional area of ​​the output flare 621 gradually increases from the small end to the large end, so that the water flow driven by the blade 910 can diffuse outward through the output connection section 622.

[0074] Preferably, the large opening of the output horn 621 is greater than the large opening of the input horn 611, and the stator flow channel 131 is located between the input horn 611 and the blade cavity 643. With this structure, the input horn 611 can converge and guide the water flow on the inlet side, the stator flow channel 131 can rectify and guide the water flow before it enters the blade cavity 643, the blade 910 can perform work on the rectified water flow within the blade cavity 643, and the output horn 621 can form a large diffusion and discharge area on the outlet side, allowing the water flow propelled by the blade 910 to gradually diffuse and discharge. Thus, this embodiment forms a continuous variable cross-section guiding structure of "inlet water convergence - mid-section rectification - blade work - outlet water diffusion", which is different from the ordinary duct structure with equal diameter at the front and rear or symmetrical front and rear. It is beneficial to reduce the turbulence and deflection of the water flow before entering the blade 910, and to reduce the local sudden expansion loss on the outlet side of the blade 910, thereby improving the stability and propulsion efficiency of the water flow when passing through the blade cavity 643.

[0075] Meanwhile, the input horn port 611, stator flow channel 131, blade cavity 643, output connecting section 622, and output horn port 621 maintain continuous communication, and both the input horn port 611 and the output horn port 621 have gradually changing flow guiding openings. Therefore, when the blade 910 rotates in the reverse direction, the water flow can still form a reverse flow channel through the output horn port 621, output connecting section 622, blade cavity 643, stator flow channel 131, and input horn port 611, thereby optimizing the forward propulsion guiding effect while also taking into account the reverse thrust output under the reverse or reverse operation conditions of the blade 910.

[0076] In this embodiment, the flow cross-sectional area is the cross-sectional area perpendicular to the water flow direction; when the corresponding flow channel is a circular cross-section, the opening can be characterized by the maximum inner diameter; when the corresponding flow channel is annular, arc-shaped or non-circular cross-section, the opening can be characterized by the equivalent flow cross-sectional area or the equivalent flow diameter.

[0077] exist Figures 16 to 25 In the illustrated embodiment, bolts 510 penetrating the stator 130 and end cap 140 may not be required. Instead, the first housing 610 and the sand-removing ring 660 jointly restrict the axial displacement of the stator 130. Specifically, one end of the stator 130 is fixed or limited to the first housing 610, and the end of the stator 130 away from the first housing 610 is assembled and fixed to the limiting ring 664 of the sand-removing ring 660. The sand-removing ring 660 is located on the side near the blade cavity 643 and can replace part of the axial limiting function of the end cap 140 on that side. The sand-removing ring 660 forms a relatively circumferentially rotatable fit with the bearing body 120 and the rotor 110, so that the stator 130 and the sand-removing ring 660 remain fixed, while the rotor 110 and the housing 640 can rotate relative to them.

[0078] The sand discharge ring 660 is provided with a drainage groove 667 corresponding to the water lubrication gap 101. The drainage groove 667 is used to lead the lubricating water or impurity-containing water in the water lubrication gap 101 to the blade cavity 643. The slag discharge ring groove 641 provided in the housing 640 is connected to the slag discharge long groove 111 on the rotor 110, so that the impurities in the slag discharge long groove 111 can enter the slag discharge ring groove 641 and be further discharged with the water flow in the blade cavity 643.

[0079] The sand discharge ring 660 is provided with a conical surface portion 661, a short check ring 662, and a long check ring 663. The outer diameter of the conical surface portion 661 gradually decreases along the axial direction of the stator 130 from the end closer to the slag discharge long channel 111 to the end farther away from the slag discharge long channel 111, so that the outer wall of the conical surface portion 661 forms a conical surface that guides the flow towards the slag discharge ring groove 641. As a result, the debris discharged from the slag discharge long channel 111 can smoothly enter the slag discharge ring groove 641 along the conical surface portion 661, while the debris in the slag discharge ring groove 641 is less likely to flow back into the slag discharge long channel 111, thereby reducing the risk of backflow or blockage at the valve orifice 112.

[0080] The tapered portion 661 and the adjacent short check ring 662 form a first check cavity 665. The short check ring 662 and the long check ring 663 are arranged sequentially along the diameter direction of the slag discharge ring groove 641, and a second check cavity 666 is formed between adjacent short check rings 662 and long check rings 663. The short check ring 662 and the long check ring 663 can be axially ( Figure 18The varying lengths (from left to right), radial extension heights, or a combination of both, create multiple stepped, undulating, or labyrinthine checkpoint spaces around the outer periphery of the sand discharge ring 660. When the blade 910 reverses direction, the reverse water flow entering the slag discharge ring groove 641 must sequentially pass through the second checkpoint chamber 666, the short checkpoint ring 662, the long checkpoint ring 663, and the first checkpoint chamber 665. These multiple checkpoint spaces buffer, deflect, and block the reverse water flow, reducing the probability of water directly entering the long slag discharge groove 111 and the valve hole 112, and lowering the risk of debris clogging.

[0081] To ensure sufficient lubricating water in the water lubrication gap 101, a stator through-hole 132 is provided near the first housing 610, extending radially through the stator 130. One end of the stator through-hole 132 communicates with the stator flow channel 131, and the other end communicates with the water pressure chamber 601. The water pressure chamber 601 is formed by the first housing 610, the stator 130, and the corresponding end cap 140 or limiting structure, and communicates with the water lubrication gap 101. Thus, pressurized water in the stator flow channel 131 can enter the water pressure chamber 601 through the stator through-hole 132, and then enter the water lubrication gap 101 to lubricate the relatively rotating parts between the stator 130 and the bearing body 120.

[0082] In propulsion mode, the blade 910 rotates forward, and water flows from the input bell mouth 611 through the input connecting section 612, stator flow channel 131, blade cavity 643, output connecting section 622, and output bell mouth 621. At this time, the water pressure at the stator flow channel 131 can be introduced into the water pressure chamber 601 through the stator through hole 132, then enter the water lubrication gap 101, and then be discharged through the slag discharge long groove 111, drainage groove, and slag discharge ring groove 641. This structure ensures that the water lubrication gap 101 has sufficient lubricating water, and also uses water pressure to push debris from the slag discharge long groove 111 to the slag discharge ring groove 641.

[0083] In reverse mode, the blade 910 rotates in the opposite direction, allowing some water to flow through the output horn 621, output connection section 622, and blade cavity 643 into the drainage trough, replenishing water or backwashing the water lubrication gap 101. Simultaneously, the short check ring 662, long check ring 663, and check cavity structure on the sand discharge ring 660 reduce the risk of debris in the slag discharge ring groove 641 directly flowing back into the slag discharge long groove 111 and valve hole 112. Therefore, in both forward and reverse driving conditions, it is beneficial to maintain the lubricating water volume and sand discharge capacity of the water lubrication gap 101.

[0084] Preferably, in some embodiments, a connecting pipe 650 is installed on the third outer shell 630, and a shell gear ring 840 is fitted on the shell 640 corresponding to the connecting pipe 650. The shell gear ring 840 is provided with shell teeth 841, which mesh with a drive gear 831. The drive gear 831 is fitted on a drive gear shaft 830, and the drive gear shaft 830 is rotatably mounted on a gear seat 670. The gear seat 670 is mounted on the third outer shell 630. A second bevel gear 832 is non-rotatably fitted on the drive gear shaft 830, and the second bevel gear 832 meshes with a first bevel gear 822. The first bevel gear 822 is mounted on an outer drive shaft 820, and the outer drive shaft 820 is rotatably mounted on a partition 652 that cannot be moved axially. The partition 652 is installed in the connecting cavity 651 of the connecting pipe 650. The end of the external drive shaft 820 away from the housing 640 passes through the partition 652 and is provided with an external drive gear portion 821. In use, the external drive gear portion 821 meshes with the power gear 811, which is mounted on the power shaft 810. The power shaft 810 can be driven by an electric motor, gearbox, drive shaft, or other power output device on the hull. Through the above transmission structure, external power is transmitted sequentially through the power shaft 810, power gear 811, external drive gear portion 821, external drive shaft 820, first bevel gear 822, second bevel gear 832, drive gear shaft 830, drive gear 831, housing tooth portion 841, and housing tooth ring 840 to the housing 640, causing the housing 640 to drive the propeller blade 910 to rotate.

[0085] Compared to designs that directly house the brushless motor within the underwater hull of the thruster, this design places the power source on the side of the hull or outside the connecting pipe 650, transmitting power to the hull 640 via mechanical transmission. This reduces the requirements for motor sealing, waterproofing, insulation, and electrical heat dissipation in the underwater thruster, thus lowering manufacturing and maintenance costs. Since the underwater rotating part mainly consists of gears, shafts, a hull, and a support structure, its structure is relatively simple, easy to maintain, and exhibits good durability in waters with abundant silt and debris. In embodiments using external mechanical power, the rotor 110 can be understood as a ring-shaped rotating component rotating relative to the stator 130, and the stator 130 can be understood as a fixed support and guide component; it is not required that the rotor 110 and stator 130 necessarily constitute an electromagnetic drive motor.

[0086] Preferably, the axis of the drive shaft 810 or the drive gear 811 coincides with or substantially coincides with the axis of the connecting pipe 651, so that the connecting pipe 650 can serve as a composite connector for power input and propeller installation. This structure helps to simplify the installation relationship between the propeller and the hull and helps to ensure the stability of the meshing position between the drive gear 811 and the external drive gear part 821.

[0087] Compared to designs that directly house the brushless motor within the underwater thruster casing, this embodiment places the power source on the hull side or outside the connecting pipe 650, transmitting power to the casing 640 via mechanical transmission. This reduces the requirements for motor sealing, waterproofing, insulation, and electrical heat dissipation in the underwater thruster section, thus lowering manufacturing and maintenance costs. Since the underwater rotating part mainly consists of gears, shafts, casing, and support structures, its structure is relatively simple, easy to maintain, and exhibits good durability even in waters with abundant silt and debris.

[0088] Through the above design, the housing 640 and rotor 110 rotate synchronously via a spline connection. The blade 910 is fixed within the blade cavity 643 inside the housing 640, forming an inwardly extending blade structure that extends from the outer periphery to the center. This facilitates water flow propulsion even without a central drive shaft passing through the blade cavity 643. The input bell mouth 611, stator flow channel 131, blade cavity 643, and output bell mouth 621 form an asymmetric continuous variable cross-section guiding structure, which is beneficial for water intake convergence, flow channel rectification, blade work, and water outlet diffusion during forward propulsion. The stator through hole 132, water pressure cavity 601, water lubrication gap 101, slag discharge groove 111, sand discharge ring 660, and slag discharge ring groove 641 form a water lubrication and sand discharge path, which helps maintain the water replenishment, lubrication, and sand discharge capabilities of the water lubrication gap 101 during propulsion and reversing operations. The conical surface 661, short check ring 662, long check ring 663, first check chamber 665, and second check chamber 666 on the sand discharge ring 660 form an anti-backflow structure, which helps reduce the probability of debris flowing back into the slag discharge trough 111 and valve hole 112 when reversing or experiencing reverse water flow impact. The external mechanical power input structure moves the power source from inside the underwater hull of the propeller to the side of the hull or outside the connecting pipe 650, which helps reduce the difficulty of sealing and maintaining the underwater motor and improves structural durability.

[0089] Preferably, sealing rings 230 are also installed on both sides of the housing toothed ring 840 (axially upward) of the housing 640. The sealing rings 230 are pressed against the inner wall of the third outer shell 630, can rotate circumferentially, and provide a seal. This design is mainly to form a seal at the housing toothed ring 840 and reduce the probability of foreign objects entering and causing jamming or corrosion.

[0090] See Figure 17 In one embodiment, the thruster of this embodiment can replenish water, lubricate and remove sand from the water lubrication gap 101 in both the propulsion state and the reversing state.

[0091] In propulsion mode, the housing 640 drives the blade 910 to rotate forward. Water flows from one side of the first housing 610 into the input horn 611, through the input connecting section 612 into the stator flow channel 131, and then through the blade cavity 643, the output connecting section 622, and the output horn 621 to exit from one side of the second housing 620. During this process, a relatively high water pressure is formed in the stator flow channel 131 near the stator through hole 132. Part of the water flows through the stator through hole 132 into the water pressure chamber 601, and then into the water lubrication gap 101, thereby continuously replenishing water and lubricating the relatively rotating parts between the bearing body 120 and the stator 130.

[0092] The water flowing into the water lubrication gap 101 can be partially discharged into the blade cavity 643 via the drainage channel 667, while the other part can carry the mud or debris in the water lubrication gap 101 into the slag discharge trough 111 and then into the blade cavity 643 via the slag discharge ring groove 641. In the propulsion state, the main water flow in the blade cavity 643 flows from the stator flow channel 131 side to the output bell mouth 621 side. The outlet sides of the drainage channel 667 and the slag discharge trough 111 are located in the carry-off zone of this main water flow, which reduces the discharge back pressure at the outlet sides of the drainage channel 667 and the slag discharge trough 111 and facilitates the continuous renewal of the water flow in the water lubrication gap 101. Therefore, on the one hand, it ensures a continuous supply of lubricating water in the water lubrication gap 101, reducing wear between the bearing body 120 and the stator 130; on the other hand, it promptly removes mud or debris from the slag discharge trough 111, reducing the probability of mud and sand stagnation and accumulation in the water lubrication gap 101 and the slag discharge trough 111.

[0093] In reverse, the housing 640 drives the blade 910 to rotate in the opposite direction. Water flows in from one side of the second housing 620 through the output horn 621, and then through the output connection section 622, the blade cavity 643, and the stator flow channel 131 before being discharged from one side of the first housing 610. During this process, a reverse flow pressure is formed near the drainage groove 667 and the slag discharge ring groove 641 in the blade cavity 643. Some water can enter the water lubrication gap 101 through the drainage groove 667 to replenish water and perform reverse flushing on the water lubrication gap 101. Some water can also enter the slag discharge ring groove 641, and under the action of the conical surface portion 661 of the sand discharge ring 660, the short check ring 662, the long check ring 663, the first check chamber 665, and the second check chamber 666, a flow deflection and buffer are formed.

[0094] The conical surface 661 of the sand discharge ring 660 can guide and block the water flow and debris flowing back from the slag discharge ring groove 641 to the slag discharge long groove 111. The short check ring 662, the long check ring 663, and the adjacent check chamber can form a labyrinthine check channel, causing the reverse water flow to undergo multiple deflections and energy attenuation before entering the slag discharge long groove 111. Therefore, when the blade 910 rotates in the reverse direction, most of the debris is blocked on the side of the slag discharge ring groove 641 or the blade cavity 643, making it difficult for it to directly enter the slag discharge long groove 111 in the reverse direction.

[0095] Furthermore, in the reverse state, the pressure or reverse flow direction on the side of the slag discharge trough 111 acts on the closing direction of the one-way valve assembly, causing the one-way valve assembly to tend to remain closed, thereby reducing the probability that debris in the slag discharge trough 111 will enter the sand discharge chamber 114 or the bearing collection groove 122 through the valve hole 112. Even under high speed, pressure difference fluctuations, or local particle impact, if the one-way valve assembly opens briefly, the reverse water flow can still form a short-term backwashing effect on the valve hole 112, the sand discharge chamber 114, and the bearing collection groove 122 to disperse any mud or debris that may be attached near the valve hole 112; in the subsequent propulsion state, this mud or debris can be discharged with the water flow through the slag discharge trough 111, the slag discharge ring groove 641, and the blade chamber 643. Thus, this embodiment can achieve water replenishment lubrication and forward sand discharge in the propulsion state, and simultaneously achieve reverse flushing of the water lubrication gap 101 and anti-backflow prevention of the one-way valve assembly in the reverse state.

[0096] It should be noted that, unless otherwise stated, the technical or scientific terms used in this application shall have the ordinary meaning as understood by one of ordinary skill in the art to which this application pertains.

[0097] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, 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, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0098] Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. In the description of this application, "a plurality of" means two or more, unless otherwise explicitly defined.

[0099] In this application, a circumferentially rotatable assembly is a connection assembly that can rotate relative to each other, such as an assembly using bearings; a circumferentially rotatable but axially movable assembly is one that can rotate relative to each other but cannot move axially, such as by installing shaft clips on both sides of the shaft and the mounting device to prevent the shaft from moving axially; a circumferentially rotatable and axially movable assembly is a movable assembly, such as an assembly where the shaft passes through a shaft hole; an assembly that cannot rotate circumferentially but can move axially can be an assembly using spline grooves or spline mating.

[0100] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0101] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0102] The above description is merely a preferred embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A high wear-resistant plastic alloy composite water-lubricated bearing, characterized in that, The system includes a rotor, a bearing body, and a stator. The rotor is mounted on the bearing body in a non-circular manner, while the bearing body is mounted on the stator in a circumferential manner. A water-lubricating gap is formed between the outer wall of the stator and the inner wall of the bearing body, and the water-lubricating gap is used to accommodate water to form a water film. The inner wall of the bearing body is also provided with a spiral sand guide groove and a bearing collection groove. The two sides of the bearing collection groove are respectively connected to one end of the corresponding spiral sand guide groove, and the other end of the spiral sand guide groove extends spirally along the inner wall of the bearing body. The bearing converging groove is also connected to one end of the radial sand discharge hole, and the other end of the radial sand discharge hole passes through the bearing body and is connected to the annular sand discharge cavity. The annular sand discharge cavity is set inside the rotor, and the rotor is also provided with an external discharge channel, which is directly or indirectly connected to the outside of the rotor to discharge impurities from the rotor.

2. The high wear-resistant plastic alloy composite water-lubricated bearing according to claim 1, characterized in that, The inner wall of the rotor is provided with splines, and the outer wall of the bearing body is provided with spline grooves. The rotor is fitted onto the bearing body and the splines are inserted into the spline grooves. The bearing body is also assembled and fixed to the end caps at both ends. The end caps are respectively equipped with a first sealing gasket and a second sealing gasket. The first sealing gasket and the second sealing gasket are located on the inner and outer sides of the spline groove to form a seal for the end opening of the spline groove.

3. The high wear-resistant plastic alloy composite water-lubricated bearing according to claim 1, characterized in that, The spiral sand guiding grooves on both sides of the bearing converging groove rotate in opposite directions; the depth of the spiral sand guiding groove gradually decreases from the end connected to the bearing converging groove to the end away from the bearing converging groove.

4. The high wear-resistant plastic alloy composite water-lubricated bearing according to claim 1, characterized in that, On the inner wall of the bearing body, at the two open ends, there are respectively an annular pre-sand collection trough and an annular water inlet pressure equalization trough, and the annular water inlet pressure equalization trough is located inside the annular pre-sand collection trough.

5. The high wear-resistant plastic alloy composite water-lubricated bearing according to claim 4, characterized in that, It also includes multiple bolts, one end of which is provided with a rotating shaft part, and a bushing is provided on the rotating shaft part, with the bushing fitted outside the rotating shaft part; the end of the bolt with the bushing installed passes through the stator and is installed into the annular pre-sand collection tank or the annular water inlet equalization tank, and the bushing is fitted to the side wall of the annular pre-sand collection tank or the annular water inlet equalization tank on both sides of the stator axial direction; the ends of the bolts and bushings must not contact the inner wall of the annular pre-sand collection tank or the annular water inlet equalization tank.

6. The high wear-resistant plastic alloy composite water-lubricated bearing according to any one of claims 1-5, characterized in that, The rotor is also provided with a valve hole and a long slag discharge groove. The two ends of the external discharge channel are respectively connected to the annular sand discharge chamber and one end of the valve hole. A one-way valve assembly is installed in the valve hole. The one-way valve assembly includes a valve seat, a valve core, an inertial block, and a support ring. The support ring and the valve seat are installed and fixed in the valve hole. The end face of the valve seat away from the external discharge channel is a convex valve seat spherical surface. The valve seat spherical surface is an arc-shaped spherical surface that convexes towards the slag discharge groove. The valve seat is provided with a through valve seat hole. The opening of the valve seat hole is located on the valve seat spherical surface. The valve core is provided with a concave valve core spherical surface that fits with the valve seat spherical surface. The valve core is also provided with a through valve core groove. The valve core groove is misaligned with the valve seat hole so that when the valve seat spherical surface and the valve core spherical surface are fitted together, the valve core groove and the valve seat hole are not connected. The valve core is assembled with one end of the valve stem, and the other end of the valve stem is fitted with a spring, passes through the support ring, and is assembled with the inertial block; the two ends of the spring are respectively pressed with the valve core and the support ring to apply an elastic force to the valve core to press against the valve seat; the other end of the valve hole is connected to the slag discharge groove, which is set on the outer wall of the rotor.

7. A thruster, characterized in that, The application is the high wear-resistant plastic alloy composite water-lubricated bearing as described in any one of claims 1-6.

8. The thruster according to claim 7, characterized in that, The propeller includes a first outer shell, a second outer shell, a third outer shell, and a housing. The housing is fitted over the rotor, and the third outer shell is fitted over the housing. The first and second outer shells are respectively installed at both ends of the third outer shell. A blade cavity is provided inside the housing, and blades are installed inside the blade cavity. The first housing is provided with an input horn and an input connection section, and the input horn is connected to the stator flow channel inside the stator through the input connection section; the second housing is provided with an output connection section and an output horn, one end of the blade cavity is connected to the stator flow channel, and the other end of the blade cavity is connected to the output horn through the output connection section. The input horn, input connecting section, stator flow channel, blade cavity, output connecting section and output horn are connected sequentially along the water flow direction to form a continuous variable cross-section water flow channel, and the maximum opening of the output horn is greater than the maximum opening of the input horn. The opening of the blade cavity is greater than the opening of the stator flow channel.

9. The thruster according to claim 8, characterized in that, The propeller also includes a sand discharge ring, which is located on one side near the blade cavity. The sand discharge ring is fixed or limited to the stator and forms a relatively circumferential rotatable fit with the bearing body and the rotor. The sand discharge ring is provided with a drainage groove corresponding to the water lubrication gap, and the shell is also provided with a slag discharge ring groove, which is connected to the slag discharge long groove on the rotor; the stator is provided with a stator through hole, which is connected to the water pressure chamber, which is connected to the water lubrication gap, and the water pressure chamber is surrounded by the first shell, the stator and the corresponding end cover or limiting structure.

10. The thruster according to claim 9, characterized in that, The sand discharge ring is provided with a conical surface portion, a short check ring, and a long check ring. The conical surface portion and the adjacent short check ring form a first check cavity, and the short check ring and the long check ring form a second check cavity. The short check ring and the long check ring are arranged sequentially along the reflux path from the slag discharge ring groove to the slag discharge long groove.

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