High-efficiency shielded submersible pump

Abstract

The application belongs to the technical field of canned pumps, and specifically relates to a high-efficiency canned down pump, which comprises an impeller, wherein the impeller is externally provided with a main body mechanism, a concentric structure is coaxially arranged on one side of the impeller, and a mass center correction mechanism is arranged on one side of the concentric structure. The application forcibly ensures that the gravity center of the hexagon coincides with the axis under different rotating speeds of the motor shaft through the relative constraint of the hexagonal toothed belt wheel, and locks the initial centering accuracy of the shafting in structure. When the impeller appears radial runout due to factors such as wear, cavitation or deformation, the toothed belt queue re-establishes the hexagonal shape through toothed belt traction, real-time tracks the eccentric rotating inertia, avoids the further enlargement of the eccentricity degree caused by the radial runout, and cuts off the vicious cycle transmission path from the source.

Description

Technical Field

[0001] This invention belongs to the field of shielded pump technology, specifically relating to a high-efficiency shielded submersible pump. Background Technology

[0002] Canned motor pump: A seal-free centrifugal pump that integrates the motor and pump body on the same axis. Through a shielding sleeve made of non-magnetic metal and corrosion-resistant material, the stator and windings of the motor are completely physically isolated from the medium being transported in the pump chamber. It eliminates the mechanical seal or packing seal of traditional centrifugal pumps and relies solely on static seals to achieve the fluid machinery for transporting the medium.

[0003] Since the impeller and motor shaft of the canned motor pump are designed as a coaxial integrated unit, the essence of the impeller's center of mass deviating from the motor shaft center is that the impeller's mass distribution is uneven. Subsequently, during rotation, the uneven mass will generate additional centrifugal force acting on the shaft system, causing radial runout. Over a long period of time, this will continuously amplify the degree of eccentricity, further expand the mass unevenness, and form a more serious vicious cycle.

[0004] In practice, the following factors contribute to the uneven mass of the impeller:

[0005] 1. The erosion and wear of the impeller by impurity particles in the medium (e.g., sand, metal shavings, or crystalline particles) is the core cause of uneven mass distribution; and the wear on the impeller surface is a synergistic effect of impact wear and cutting wear.

[0006] Impact wear: When particles flow through the impeller channel with the medium, as the impeller rotates at high speed, the particles gain radial velocity and impact the impeller blade surface, gradually forming plastic deformation pits at the impact point. After repeated impacts, the pits expand and the material peels off, forming pits or corrosion pits.

[0007] Cutting wear: When particles slide along the blade surface at a small impact angle, the edge of the particle is equivalent to a cutting tool, which then produces micro-cutting on the blade surface, scraping out grooves parallel to the flow direction. Long-term accumulation leads to local thinning of the blade thickness.

[0008] In addition, the impellers of canned pumps are mostly closed impellers (including front and rear cover plates), with curved and narrow flow channels. Particles are prone to secondary impacts in the flow channels (after hitting the blades, they bounce back and then hit the cover plate or another blade), resulting in localized wear concentration and forming single-point excessive wear.

[0009] 2. Cavitation damage: Insufficient pump suction pressure causes bubbles to form at the impeller inlet. When the bubbles burst, they generate instantaneous high pressure, which impacts the impeller surface, leading to cavitation wear and subsequently honeycomb-like pits on the impeller surface.

[0010] 3. Sudden change in medium properties: Sudden change in medium viscosity leads to uneven force on the impeller. Under long-term action, the blades undergo elastic deformation, which in turn leads to an imbalance in mass distribution. Summary of the Invention

[0011] To solve the above problems, the present invention adopts the following technical solution: a high-efficiency shielded submersible pump, including an impeller, a main body mechanism is provided outside the impeller, a concentric mechanism is coaxially provided on one side of the impeller, and a centroid correction mechanism is provided on one side of the concentric mechanism.

[0012] The centroid correction mechanism includes:

[0013] The driving bevel gear is located on the outer edge of one side of the impeller;

[0014] An angle bracket is positioned opposite to the drive bevel gear on the side closest to the impeller axis.

[0015] Angle tube, with a plug-in snap-fit ​​installation in the middle of the horizontal section of the angle bracket;

[0016] Driven bevel gear, rotatably fitted on the end face of the angle tube near the impeller;

[0017] The gear ring is snapped onto the inner wall of the driven bevel gear;

[0018] Angle shaft, coaxially positioned inside the angle tube;

[0019] Angle sleeve is snapped onto the outer wall of the angle shaft near the impeller end;

[0020] Ear plates are symmetrically snapped onto the outer wall of the corner sleeve;

[0021] The connecting rod is rotatably fitted between the ear plates.

[0022] Preferably, a pawl that engages with the toothed ring is snapped onto the outer wall of the connecting rod. A torsion spring sleeved on the outer wall of the connecting rod is snapped onto the pawl and the ear plate. An angled device that is snapped onto the outer wall of the angled sleeve is arranged opposite to the pawl on one side. An angled post is snapped onto the end of the angled shaft away from the impeller. A spiral groove is formed on the outer wall of the angled post, and a groove is formed on the outer wall of the angled post that connects the beginning and end of the spiral groove.

[0023] Preferably, a face ring is coaxially arranged inside the corner tube. Angle blocks that slide and engage with the inner wall of the corner tube are symmetrically snapped onto the outer wall of the face ring. A ball rod is snapped onto the middle position of the inner wall of the face ring. A support column is arranged circumferentially on the end face of the face ring away from the impeller. Spring columns that slide and engage with the face ring are evenly arranged circumferentially on the inner wall of the corner tube near the impeller. A pressure plate that slides and engages with the inner wall of the corner tube is snapped onto the end of the support column away from the face ring. An angle valve is inserted into the outer wall of the corner tube away from the impeller. The angle valve is a one-way valve. A return valve is inserted into the outer wall of the corner tube away from the impeller. The return valve is distributed opposite to the angle valve. A replacement plate is snapped onto the outer wall of the corner tube away from the impeller.

[0024] Preferably, one side of the impeller is provided with a counterweight chamber corresponding to the number of corner tubes, and the counterweight chambers and corner tubes are symmetrically distributed relative to the impeller axis. A base plate is symmetrically snapped onto the end face of the counterweight chamber near the impeller. An interface valve is plugged into and snapped onto the middle position of the end face of the counterweight chamber near the impeller axis. A diversion valve is plugged into and snapped onto the outer wall of the end of the counterweight chamber near the impeller axis. A plunger is slidably snapped onto the inner wall of the counterweight chamber. A counterweight ball is snapped onto the end of the plunger away from the impeller axis.

[0025] Preferably, a forked ring is rotatably installed at the middle position of the inner wall of the counterweight chamber, and a serrated groove is formed on the inner wall of the forked ring. A counterweight ring is snapped onto the outer wall of the plunger near the impeller axis. A push rod that cooperates with the serrated groove is snapped onto the inner wall of the counterweight ring. An angled wedge plate is circumferentially snapped onto the middle position of the inner wall of the counterweight chamber. A one-way rotating sheath plate is rotatably installed at the middle position of the outer wall of the forked ring through a rotating shaft and a torsion spring.

[0026] Preferably, the concentric mechanism includes:

[0027] The counterweight disc is coaxially snapped onto the outer wall of the impeller rear cover plate;

[0028] The annular guide rail is rotatably mounted inside the counterweight plate on the side opposite to the impeller; in addition, the outer wall of the annular guide rail is snapped into the other end of the filler plate.

[0029] The shaft disc is snapped onto the end face of the annular guide rail near the impeller, and the shaft disc and the counterweight disc are rotatably fitted together.

[0030] There are three fan blades, which are evenly snapped together on the outer wall of the shaft disk in a circumferential manner;

[0031] Angle plate is snap-fitted and installed at the middle position of the end face of the fan blade plate away from the impeller; in addition, the angle plate is snap-fitted and assembled with the angle bracket; at the same time, the end of the angle plate away from the shaft axis is rotatably assembled with the angle shaft.

[0032] The lead screw is rotatably mounted in the hollow area in the middle of the angle plate; in addition, the outer wall of the end of the lead screw away from the axis of the shaft is snapped together with the driving bevel gear.

[0033] The rod sleeve is snapped into place at one end of the lead screw near the impeller axis, and the rod sleeve is snapped into place with the angle plate.

[0034] The slide is movably sleeved on the outer wall of the lead screw. At the same time, the slide is slidably engaged with the lead groove on the outer wall of the lead screw through the limiting rod, and the slide is also slidably engaged with the angle plate; in addition, the slide is slidably engaged with the rod sleeve.

[0035] The return spring is snapped between the slide and the corner plate, and the return spring is sleeved on the outer wall of the rod sleeve.

[0036] Preferably, a slotted plate is provided between two adjacent fan blades, which is snapped onto the outer wall of the coaxial disk. An end plate is provided between two adjacent fan blades, which is snapped onto both the outer wall of the coaxial disk and the slotted plate. A toothed pulley is rotatably mounted between the middle position of the slide block and the end plate away from the axis of the shaft disk via a rotating shaft. A toothed belt is installed between the toothed pulleys. A pressure contact rod is snapped onto the end face of the slide block near the axis of the shaft disk. An electrode plate is symmetrically snapped onto the side of the corner plate near the axis, and there is a space allowance between adjacent electrode plates that does not affect the extension and retraction of the return spring. An electrode cap is snapped onto the end face of the electrode plate away from the axis of the shaft disk.

[0037] Preferably, the main body mechanism includes:

[0038] The pump casing is coaxially mounted outside the impeller.

[0039] The pump cover is snap-fitted onto one end of the pump casing;

[0040] The imported flange is snap-fitted onto the pump cover at the end furthest from the pump casing.

[0041] The outlet flange is installed on the outer wall of the pump cover by a plug-in snap-fit, and the outlet flange and the inlet flange are arranged in a vertical position.

[0042] The motor shaft is snapped onto the inner wall of the impeller shaft center.

[0043] The sliding bearings are symmetrically and slidingly mounted on both ends of the outer wall of the motor shaft.

[0044] The rotor assembly is snap-fitted onto the outer wall of the motor shaft at the end furthest from the pump cover.

[0045] The stator assembly is coaxially mounted outside the rotor assembly and snap-fitted to the pump casing.

[0046] The pump base is snap-fitted onto the other end of the pump casing and is positioned opposite to the pump cover.

[0047] The method for correcting the centroid of an impeller under arbitrary wear in a canned motor pump, using a high-efficiency canned submersible pump for cleaning, involves the following steps:

[0048] S1: First, by using the relative constraints between the regular hexagonal toothed belt pulleys, the overlap between the coaxial lines of the hexagonal centroids is ensured at different speeds of the motor shaft;

[0049] When radial runout occurs between the motor shaft and the impeller, the relative hexagonal arrangement changes, ultimately manifesting as the slide being at its maximum eccentric position, undergoing relative motion with the lead screw under centrifugal force (the slide moves outward from the motor shaft). That is, the three toothed pulleys in the fan blade area change their initial positions under the mutual traction of the toothed belt, and reconstruct a new hexagon with the three toothed pulleys in the end plate area. By utilizing the connection between the toothed belt and the toothed pulleys, real-time high-precision tracking is provided for the eccentric rotational inertia caused by arbitrary wear of the impeller.

[0050] S2: Then, through the relative movement between the slide block and the lead screw, the lead screw is synchronously controlled to drive the active bevel gear to rotate a predetermined angle (in specific implementation, the slide block and the lead screw are slidably engaged by a limit rod). After that, the driven bevel gear synchronously controls the gear ring and the pawl to produce a one-way meshing, thereby promoting the relative movement between the corner column and the ball rod, and then realizing the synchronous lifting of the support column on the pressure plate.

[0051] In this process, the accuracy of sensing and expressing the small eccentric displacement of the slide is improved by the dual extension expression between the dust guide groove on the outer wall of the lead screw and the spiral groove on the outer wall of the corner column. At the same time, the smooth and continuous assembly between the lead screw and the slide enables the slide to express the small eccentricity in real time without damage.

[0052] S3: Finally, the space between the same angle tube is compressed by the pressure plate, which causes the gas in the aforementioned space to flow into the interface valve through the one-way guide valve angle valve. After that, the gas fills the space between the plunger and the counterweight chamber, causing the plunger to drive the counterweight ball to move a predetermined distance away from the impeller axis, thereby gradually balancing the eccentric inertia.

[0053] During this process, the rotation of the shaft disk can be controlled by the ring guide rail, thereby adjusting the relative angle between the fan blade and the impeller until all the toothed pulleys return to the regular hexagonal state at a predetermined speed.

[0054] The present invention has the following beneficial effects:

[0055] 1. This invention uses the relative constraint of regular hexagonal toothed pulleys to forcibly ensure that the hexagonal center of gravity coincides with the axis at different speeds of the motor shaft, thus structurally locking the initial alignment accuracy of the shaft system; and when the impeller experiences radial runout due to wear, cavitation, or deformation, the toothed pulley array reconstructs the hexagonal shape through toothed belt traction, tracks the eccentric rotational inertia in real time, and prevents the radial runout from further amplifying the degree of eccentricity, thus cutting off the vicious cycle transmission path at the source.

[0056] 2. The present invention forms a full circumferential constraint through the six toothed pulleys of the fan blade plate and the end plate. That is, regardless of whether the impeller is locally thinned or pitted, or damaged by cavitation, its eccentric inertia is always directly converted into the position offset of the toothed pulley through the shaft runout. In addition, the rigid meshing transmission between the toothed belts can ensure the relative distortion-free transmission of the eccentricity, and realize high-precision tracking of mass unevenness at any position and in any form.

[0057] 3. In this invention, the slide block and the lead screw are slidably engaged by a limiting rod. The radial movement of the slide block caused by eccentricity is directly converted into the rotational power of the lead screw, eliminating the need for external drive components such as additional motors and sensors. Furthermore, the unidirectional meshing design of the main and driven bevel gears, gear ring, and pawl ensures the irreversibility of power transmission. That is, once the compensation action is triggered, it will not be canceled out by the reverse force. This invention is highly suitable for the high reliability requirements of canned pumps without external power, while also reducing the risk of corrosion from contact between electrical control components and the medium.

[0058] 4. This invention uses a dual-range extension method, consisting of a dust guide groove on the outer wall of the lead screw and a spiral groove on the outer wall of the corner column, to amplify the minute eccentric displacement of the slide into a measurable rotation angle of the lead screw (the range extension ratio is determined by the spiral groove lead design and can achieve a 10 to 20-fold amplification), thus solving the problem of the difficulty in accurately sensing minute eccentricities. At the same time, the smooth and continuous assembly of the slide and the lead screw (without gaps or jamming) ensures the real-time lossless transmission of eccentric displacement and avoids compensation lag caused by mechanical transmission errors.

[0059] 5. This invention uses a pressure plate to compress gas and drive a plunger to move a counterweight ball away from the impeller axis. The centrifugal force of the counterweight ball is opposite to the eccentric centrifugal force of the impeller, and the movement distance of the counterweight ball is matched with the eccentricity in real time (the larger the eccentricity, the greater the displacement of the sliding seat, and the farther the counterweight ball moves), thus achieving dynamic cancellation of the eccentric inertia. When the eccentric inertia is completely balanced, the impeller's center of mass re-coincides with the motor shaft center, and the radial runout is significantly reduced. Attached Figure Description

[0060] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0061] Figure 2 This is an appendix to the present invention. Figure 1 Internal structure diagram of the central structure.

[0062] Figure 3 This is a three-dimensional view of the impeller and its partial structure in this invention.

[0063] Figure 4 This is an appendix to the present invention. Figure 3 A cross-sectional view of the internal structure.

[0064] Figure 5 This is a three-dimensional schematic diagram of the internal structure of the counterweight disc of the present invention.

[0065] Figure 6 This is an appendix to the present invention. Figure 5 Front view of the structure.

[0066] Figure 7 This is a plan view of the concentric mechanism and the center of mass correction mechanism of the present invention.

[0067] Figure 8 This is an appendix to the present invention. Figure 7 Right view of the middle structure.

[0068] Figure 9 This is a plan view of the internal structure of the corner tube of the present invention.

[0069] Figure 10 This is a three-dimensional view of the corner shaft, corner sleeve, and corner tube of the present invention, as well as some of their partial structures.

[0070] Figure 11 This is a three-dimensional view of the counterweight chamber and its partial structure of the present invention.

[0071] Figure 12 This is a plan view of the internal structure of the counterweight chamber of this invention.

[0072] The diagram is labeled as follows: 1. Impeller; 2. Main mechanism; 3. Concentric mechanism; 4. Center of mass correction mechanism.

[0073] 21. Pump casing; 22. Pump cover; 23. Inlet flange; 24. Outlet flange; 25. Motor shaft; 26. Sliding bearing; 27. Rotor assembly; 28. Stator assembly; 29. ​​Pump base;

[0074] 31. Counterweight plate; 32. Circular guide rail; 33. Shaft plate; 34. Fan blade plate; 35. Angle plate; 36. Lead screw; 37. Rod sleeve; 38. Slide block; 39. Return spring;

[0075] 311. End plate; 312. End plate; 313. Toothed pulley; 314. Toothed belt; 315. Pressure contact rod; 316. Electrode plate; 317. Electrode cap;

[0076] 41. Driving bevel gear; 42. Angle bracket; 43. Angle tube; 44. Driven bevel gear; 45. Gear ring; 46. Angle shaft; 47. Angle sleeve; 48. Ear plate; 49. Connecting rod;

[0077] 411. Pawl; 412. Torsion spring; 413. Angle positioner; 414. Angle post; 415. Spiral groove; 416. Wire groove;

[0078] 421. Face ring; 422. Corner block; 423. Cue stick; 424. Support; 425. Spring post; 426. Pressure plate; 427. Angle valve; 428. Return valve; 429. Filler plate;

[0079] 431. Counterweight chamber; 432. Base plate; 433. Interface valve; 434. Drain valve; 435. Plunger; 436. Counterweight ball;

[0080] 441. I-shaped ring; 442. Snake groove; 443. Counterweight ring; 444. Top rod; 445. Angle wedge plate; 446. One-way sheath plate. Detailed Implementation

[0081] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0082] It should be noted that the terms "vertical," "horizontal," "left," "right," and similar expressions used in this article are for illustrative purposes only and do not represent the only possible implementation.

[0083] The specific implementation of the present invention will be described in detail below with reference to specific embodiments.

[0084] Reference Figure 2 , Figure 3 and Figure 4 and Figure 6 It is known that a high-efficiency shielded submersible pump includes an impeller 1, a main body mechanism 2 is provided on the outside of the impeller 1, a concentric mechanism 3 is provided on one side of the impeller 1, and a center of mass correction mechanism 4 is provided on one side of the concentric mechanism 3.

[0085] Reference Figure 1 and Figure 2 It can be seen that the main body 2 includes: a pump casing 21, coaxially disposed outside the impeller 1; a pump cover 22, snap-fitted onto one end of the pump casing 21; an inlet flange 23, snap-fitted onto the end of the pump cover 22 away from the pump casing 21; an outlet flange 24, plug-in snap-fitted onto the outer wall of the pump cover 22, and the outlet flange 24 and the inlet flange 23 are vertically distributed; a motor shaft 25, snap-fitted onto the inner wall at the shaft center of the impeller 1; sliding bearings 26, symmetrically snap-fitted onto both ends of the outer wall of the motor shaft 25; a rotor assembly 27, snap-fitted onto the outer wall of the end of the motor shaft 25 away from the pump cover 22; a stator assembly 28, coaxially disposed outside the rotor assembly 27, and snap-fitted onto the pump casing 21; and a pump base 29, snap-fitted onto the other end of the pump casing 21, and directly opposite the pump cover 22.

[0086] Simplified working process of a canned motor pump:

[0087] First, after the stator assembly 28 is energized, it generates a rotating magnetic field. Under the action of the magnetic field and electromagnetic force, the rotor assembly 27 drives the motor shaft 25 to rotate synchronously (the motor shaft 25, rotor assembly 27, and impeller 1 are coaxial integrated structures). The stator assembly 28 and rotor assembly 27 are completely physically isolated from the pump chamber medium by the shielding sleeve (not shown in the figure), which prevents the medium from corroding the motor windings. At the same time, the sliding bearing 26 is equipped with a built-in lubrication channel (existing mature technology) to achieve self-lubrication using the medium inside the pump, ensuring the smoothness of the motor shaft 25 when it rotates at high speed.

[0088] Next, the conveying medium enters the suction chamber inside the pump casing 21 through the inlet flange 23 (not shown in the figure, the area inside the pump casing 21 that matches the impeller 1), at which time the medium is in a low-pressure state;

[0089] Subsequently, the impeller 1 rotates at high speed with the motor shaft 25, the medium is drawn into the impeller 1 flow channel, and under the action of centrifugal force, the medium is thrown from the center of the impeller 1 (low pressure zone) to the outer edge of the impeller 1 (high pressure zone), and the speed and pressure increase synchronously.

[0090] Finally, the high-pressure medium is transported to the downstream pipeline through the outlet flange 24.

[0091] Reference Figure 4 , Figure 6 , Figure 7 and Figure 8 It is known that the concentric mechanism 3 includes: a counterweight disk 31, which is coaxially snapped onto the outer wall of the rear cover plate of the impeller 1; an annular guide rail 32, which is rotatably fitted onto the end face of the counterweight disk 31 facing away from the impeller 1; in addition, the outer wall of the annular guide rail 32 is snapped onto the other end of the supplementary plate 429; a shaft disk 33, which is snapped onto the end face of the annular guide rail 32 near the impeller 1, and the shaft disk 33 is rotatably fitted onto the counterweight disk 31; three fan blades 34, which are circumferentially snapped onto the outer wall of the shaft disk 33; and a corner plate 35, which is snapped onto the middle position of the end face of the fan blade 34 away from the impeller 1; in addition, the corner plate 35 is snapped onto the corner bracket 42; at the same time, the end of the corner plate 35 away from the axis of the shaft disk 33 is rotatably fitted onto the corner shaft 46.

[0092] A lead screw 36 is rotatably mounted in the hollow area of ​​the center of the angle plate 35; furthermore, the outer wall of the end of the lead screw 36 away from the axis of the shaft disk 33 is snapped into the drive bevel gear 41; a rod sleeve 37 is snapped into the end of the lead screw 36 near the axis of the impeller 1, and the rod sleeve 37 is snapped into the angle plate 35; a slide block 38 is movably sleeved on the outer wall of the lead screw 36, and the slide block 38 is slidably snapped into the lead groove on the outer wall of the lead screw 36 through a limiting rod, and the slide block 38 is slidably snapped into the angle plate 35; furthermore, the slide block 38 is slidably assembled with the rod sleeve 37; a return spring 39 is snapped into the slide block 38 and the angle plate 35, and the return spring 39 is sleeved on the outer wall of the rod sleeve 37;

[0093] Reference Figure 5 and Figure 8 It is known that a slotted plate 311 is installed between two adjacent fan blades 34, which is snapped onto the outer wall of the coaxial disk 33. An end plate 312 is installed between two adjacent fan blades 34, which is snapped onto both the outer wall of the coaxial disk 33 and the slotted plate 311. A toothed pulley 313 is installed in the middle of the slide block 38 via a rotating shaft. The end of the slotted plate 311 away from the axis of the shaft disk 33 and the end plate 312 are rotatably fitted together via a rotating shaft. A toothed belt 314 is installed between the toothed pulleys 313. A pressure contact rod 315 is snapped onto the end face of the slide block 38 near the axis of the shaft disk 33. An electrode plate 316 is symmetrically snapped onto the side of the corner plate 35 near the axis. There is a space allowance between adjacent electrode plates 316 that does not affect the extension and retraction of the return spring 39. An electrode cap 317 is snapped onto the end face of the electrode plate 316 away from the axis of the shaft disk 33.

[0094] Real-time monitoring process of impeller 1 eccentric displacement (eccentric rotation caused by uneven mass after wear):

[0095] It should be noted that in the initial state, the six toothed pulleys 313 (three fixed positions and three movable positions) together form a regular hexagon, thereby locking the initial alignment accuracy of the relative shaft system.

[0096] Prerequisite: Localized wear occurs on one side of impeller 1 (and corresponds exactly to a certain area of ​​the fan blade 34), resulting in uneven overall mass of the counterweight disk 31 of impeller 1;

[0097] First, during the rotation of the impeller 1 with uneven mass, due to the relative shift of the center of mass, the impeller 1 will no longer rotate around its own center of mass, but will instead make eccentric circular motion around the center of rotation. The eccentric motion generates unbalanced centrifugal force, and the direction of the centrifugal force changes periodically with the rotation, forming a periodic radial load.

[0098] Next, under the aforementioned centrifugal force, the slide 38 generates relative motion with the lead screw 36 (taking the motion of the slide 38 at the maximum eccentricity point as an example). At this time, the return spring 39 in the current area is relatively stretched, and the return springs 39 in other areas synchronously undergo corresponding extension and contraction movements (global synchronous constraint is achieved through the toothed belt 314). The pressure contact rod 315 and the electrode cap 317 have relative contact to relative separation (indicating that at this time, the slide 38 is located on one side of the impeller 1's center of mass; conversely, the slide 38 is located on the opposite side of the impeller 1's center of mass, and at this time, the relative contact pressure between the pressure contact rod 315 and the electrode cap 317 increases. The annular guide rail 32 controls the shaft disk 33 to drive the fan blade plate 34 to move at a predetermined angle until the pressure contact rod 315 and the electrode cap 317 are relatively separated).

[0099] Finally, during the operation of the centroid correction mechanism 4, the relative contact status between the pressure contact rod 315 and the electrode cap 317 in all areas is monitored in real time through an external display device to determine whether the current centroid coincides with the axis of the motor shaft 25 (the toothed belt 314 returns to a regular hexagon and the relative contact pressure between the pressure contact rod 315 and the electrode cap 317 is zero).

[0100] Reference Figure 7 , Figure 8 , Figure 9 and Figure 10 It can be seen that the center of gravity correction mechanism 4 includes: an active bevel gear 41, which is disposed on the outer edge of one side of the impeller 1; an angle bracket 42, which is disposed opposite to the active bevel gear 41 on the side near the axis of the impeller 1; an angle tube 43, which is plugged into and snapped into the middle position of the horizontal section of the angle bracket 42; a driven bevel gear 44, which is rotatably fitted onto the end face of the angle tube 43 near the impeller 1; a gear ring 45, which is snapped into the inner wall of the driven bevel gear 44; an angle shaft 46, which is coaxially disposed inside the angle tube 43; an angle sleeve 47, which is snapped into the outer wall of the angle shaft 46 near the impeller 1; ear plates 48, which are symmetrically snapped into the outer wall of the angle sleeve 47; and a connecting rod 49, which is rotatably fitted between the ear plates 48.

[0101] Reference Figure 9 and Figure 10 It can be seen that a pawl 411 that cooperates with the toothed ring 45 is snapped onto the outer wall of the connecting rod 49. A torsion spring 412 sleeved on the outer wall of the connecting rod 49 is snapped onto the pawl 411 together with the ear plate 48. An angle positioner 413 that is snapped onto the outer wall of the angle sleeve 47 is set opposite to one side of the pawl 411. An angle column 414 is snapped onto the end of the angle shaft 46 away from the impeller 1. A spiral groove 415 is opened on the outer wall of the angle column 414, and a wire groove 416 that connects the beginning and end of the spiral groove 415 is opened on the outer wall of the angle column 414.

[0102] Reference Figure 7 , Figure 8 and Figure 9 It can be seen that a face ring 421 is coaxially arranged inside the corner tube 43. A corner block 422, which slides and engages with the inner wall of the corner tube 43, is symmetrically fitted onto the outer wall of the face ring 421. A ball rod 423 is fitted onto the middle position of the inner wall of the face ring 421. A support column 424 is circumferentially arranged on the end face of the face ring 421 opposite to the impeller 1. Spring columns 425, which slide and engage with the face ring 421, are evenly arranged circumferentially on the inner wall of the corner tube 43 near the impeller 1. The support column 424 is connected to the pressure plate 426 that is slidably assembled on the inner wall of the corner tube 43 at the end away from the face ring 421. An angle valve 427 is plugged into the outer wall of the corner tube 43 away from the impeller 1, and the angle valve 427 is a one-way valve. A return valve 428 is plugged into the outer wall of the corner tube 43 away from the impeller 1, and the return valve 428 is directly opposite to the angle valve 427. A replacement plate 429 is snapped into the outer wall of the corner tube 43 away from the impeller 1.

[0103] Reference Figure 5 , Figure 11 and Figure 12 It can be seen that one side of the impeller 1 is provided with a counterweight chamber 431 corresponding to the number of corner tubes 43, and the counterweight chamber 431 and the corner tubes 43 are symmetrically distributed with respect to the axis of the impeller 1. The base plate 432 is symmetrically snapped on the end face of the counterweight chamber 431 near the impeller 1. The interface valve 433 is plugged and snapped on the middle position of the end face of the counterweight chamber 431 near the axis of the impeller 1. The drain valve 434 is plugged and snapped on the outer wall of the end of the counterweight chamber 431 near the axis of the impeller 1. The plunger 435 is slidably snapped on the inner wall of the counterweight chamber 431. The counterweight ball 436 is snapped on the end of the plunger 435 away from the axis of the impeller 1.

[0104] Reference Figure 11 and Figure 12 It is known that a fork ring 441 is rotatably installed in the middle of the inner wall of the counterweight chamber 431. A snake groove 442 is opened in the inner wall of the fork ring 441. A counterweight ring 443 is snapped onto the outer wall of the plunger 435 near the axis of the impeller 1. A push rod 444 that cooperates with the snake groove 442 is snapped onto the inner wall of the counterweight ring 443. An angle wedge plate 445 is circumferentially snapped onto the middle of the inner wall of the counterweight chamber 431. A one-way rotating sheath plate 446 is rotatably installed in the middle of the outer wall of the fork ring 441 through a rotating shaft and a torsion spring 412.

[0105] The process by which the counterweight ball 436 counteracts the eccentric inertia:

[0106] Prerequisite scenario: Impeller 1 is eccentric due to wear, cavitation, and other factors;

[0107] First, the radial runout of the shaft system between the motor shaft 25 and the impeller 1 is converted into rotational meshing between the driving bevel gear 41 and the driven bevel gear 44 via the relative linear displacement between the slide block 38 and the lead screw 36. The gear ring 45 synchronously engages with the pawl 411 in a one-way action (the torsion spring 412 provides elastic support to the pawl 411, while the angular positioner 413 ensures the one-way rotation of the pawl 411). Then, the rotational thrust of the gear ring 45 drives the angular shaft 46 to rotate synchronously under the support and guidance of the end plate 312, thereby converting the eccentric radial displacement of the impeller 1 into the angular rotation signal of the angular shaft 46, realizing the mechanical sensing of eccentricity.

[0108] Next, as the corner post 414 rotates, the engagement motion between the spiral groove 415 and the ball joint 423 on the inner wall of the face ring 421 converts the rotation of the corner post 414 into the axial sliding of the face ring 421. When the face ring 421 slides, it pushes the support column 424, which stretches the spring column 425. Under its support and guidance, the pressure plate 426 slides along the inner wall of the corner tube 43, continuously compressing the enclosed space inside the corner tube 43. (The spiral groove 415 here realizes the amplification of angular rotation and axial displacement. Together with the slide block 38 and the lead groove on the outer wall of the lead screw 36, it significantly improves the sensing accuracy of small eccentric signals.)

[0109] Finally, after the space inside the corner tube 43 is compressed by the pressure plate 426, the internal gas is injected into the counterweight chamber 431 through the angle valve 427 (in specific implementation, there is one-way flow, that is, only gas is allowed to flow into the counterweight chamber 431). (In specific implementation, the angle valve 427 and the interface valve 433 are connected by an external hose).

[0110] Subsequently, the reverse pressure of the gas (the locally increased equivalent gas) pushes the plunger 435, causing the plunger 435 to move the counterweight ball 436 away from the axis of the impeller 1. (During this process, the relative engagement between the one-way sheath plate 446 and the wedge plate 445 can be referred to as the one-way meshing between the pawl 411 and the gear ring 45. This ensures the relative stability of the position of the counterweight ball 436 after the relative movement between the push rod 444 and the snake groove 442, improves the relative consistency of the counterweight before and after, and avoids the instability caused by the local fluctuation of the counterweight ball 436 and the eccentric inertia cancellation.)

[0111] The centrifugal force generated by the movement of the counterweight ball 436 is opposite in direction to the centrifugal force generated by the eccentricity of the impeller 1. The inertia of the two cancel each other out, thereby correcting the center of mass shift of the impeller 1 (in specific implementation, when the degree of eccentricity changes, the sliding stroke of the pressure plate 426 is adjusted synchronously, and the displacement of the counterweight ball 436 also changes accordingly to achieve dynamic balance).

[0112] In practice, the diversion valve 434 and the return valve 428 can be connected by an external hose, and a gas delivery power source and a certain amount of equivalent gas storage can be added at a suitable position inside the counterweight plate 31 to achieve relative self-sufficiency and recycling of the aforementioned gas.

[0113] The present invention provides a high-efficiency shielded submersible pump with the following working principle: First step: First, by means of the relative constraint between the regular hexagonal toothed pulleys 313, the overlap between the coaxial lines of the hexagonal centroids is ensured at different speeds of the motor shaft 25;

[0114] When radial runout occurs between the motor shaft 25 and the impeller 1, the relative hexagonal arrangement changes. Ultimately, the slide 38 is at its maximum eccentric position and moves relative to the lead screw 36 under the action of centrifugal force (the slide 38 moves outward from the motor shaft 25). That is, the three toothed pulleys 313 in the fan blade plate 34 area change their initial positions under the mutual traction of the toothed belt 314 and reconstruct a new hexagon with the three toothed pulleys 313 in the end plate 312 area. By utilizing the linkage between the toothed belt 314 and the toothed pulleys 313, real-time high-precision tracking is provided for the eccentric rotational inertia caused by arbitrary wear of the impeller 1.

[0115] Step 2: Next, through the relative movement between the slide block 38 and the lead screw 36, the lead screw 36 is synchronously controlled to drive the active bevel gear 41 to rotate a predetermined angle (in specific implementation, the slide block 38 and the lead screw 36 are slidably engaged through a limit rod). Then, the driven bevel gear 44 synchronously controls the gear ring 45 to produce a one-way meshing with the pawl 411, thereby promoting the relative movement between the corner column 414 and the ball rod 423, and thus realizing the synchronous lifting of the support column 424 on the pressure plate 426.

[0116] In this process, the dual extension expression between the dust guide groove on the outer wall of the lead screw 36 and the spiral groove 415 on the outer wall of the corner column 414 improves the sensing accuracy of the small eccentric displacement of the slide block 38. At the same time, through the smooth and continuous assembly between the lead screw 36 and the slide block 38, the slide block 38 can express the small eccentricity in real time without damage.

[0117] Step 3: Finally, the space between the angle tube 43 is compressed by the pressure plate 426, causing the gas in the aforementioned space to flow into the interface valve 433 through the one-way guide valve angle valve 427. After that, the gas fills the space between the plunger 435 and the counterweight chamber 431, causing the plunger 435 to drive the counterweight ball 436 to move a predetermined distance away from the axis of the impeller 1, thereby gradually balancing the eccentric inertia.

[0118] During this process, the rotation of the shaft disk 33 can be controlled by the annular guide rail 32, thereby adjusting the relative angle between the fan blade plate 34 and the impeller 1 until all the toothed pulleys 313 return to the regular hexagonal state at the predetermined speed.

[0119] The circuits and controls involved in this invention are all existing technologies and will not be described in detail here.

[0120] The above are merely embodiments of the present invention and do not limit the scope of the patent. Any equivalent structural or procedural transformations made based on the description and drawings of the present invention, or direct or indirect applications in other related technical fields, are similarly included within the scope of patent protection of the present invention.

Claims

1. A high-efficiency canned motor pump comprising an impeller (1), characterized in that: The impeller (1) is provided with a main body mechanism (2) on the outside, and a concentric mechanism (3) is provided on one side of the impeller (1) along the same axis. A centroid correction mechanism (4) is provided on one side of the concentric mechanism (3). The centroid correction mechanism (4) includes: The driving bevel gear (41) is located on the outer edge of one side of the impeller (1); Angle bracket (42) is positioned opposite to the drive bevel gear (41) on the side near the impeller (1) axis; Angle tube (43) is installed in the middle of the horizontal section of the angle bracket (42) using a plug-in snap-fit ​​method; Driven bevel gear (44) is rotatably fitted on the end face of the angle tube (43) near the impeller (1); The gear ring (45) is snapped onto the inner wall of the driven bevel gear (44); Angle shaft (46) is coaxially located inside angle tube (43); Angle sleeve (47) is snapped onto the outer wall of the angle shaft (46) near the impeller (1); Ear plates (48) are symmetrically snapped onto the outer wall of the corner sleeve (47); The connecting rod (49) is rotatably fitted between the ear plates (48).

2. A high efficiency canned motor pump as claimed in claim 1, wherein: The connecting rod (49) is fitted with a pawl (411) that cooperates with the toothed ring (45) on its outer wall. The pawl (411) and the ear plate (48) are fitted together with a torsion spring (412) sleeved on the outer wall of the connecting rod (49). A corner positioner (413) is fitted with the outer wall of the corner sleeve (47) on one side of the pawl (411). A corner post (414) is fitted at the end of the corner shaft (46) away from the impeller (1). A spiral groove (415) is opened on the outer wall of the corner post (414), and a wire groove (416) is opened on the outer wall of the corner post (414) that connects the beginning and end of the spiral groove (415).

3. The high-efficiency shielded submersible pump according to claim 2, characterized in that: The corner tube (43) is coaxially provided with a face ring (421). The outer wall of the face ring (421) is symmetrically fitted with corner blocks (422) that slide and engage with the inner wall of the corner tube (43). A ball stick (423) is fitted with the middle position of the inner wall of the face ring (421). A support column (424) is circumferentially provided on the end face of the face ring (421) away from the impeller (1). The inner wall of the corner tube (43) near the impeller (1) is circumferentially provided with spring columns (425) that slide and engage with the face ring (421). The supports in the same group are... The column (424) is connected to the pressure plate (426) that slides on the inner wall of the corner tube (43) at the end away from the face ring (421). An angle valve (427) is installed on the outer wall of the corner tube (43) away from the impeller (1) by insertion. The angle valve (427) is a one-way valve. A return valve (428) is installed on the outer wall of the corner tube (43) away from the impeller (1). The return valve (428) is opposite to the angle valve (427). A replacement plate (429) is installed on the outer wall of the corner tube (43) away from the impeller (1).

4. The high-efficiency shielded submersible pump according to claim 3, characterized in that: The impeller (1) is provided with a counterweight chamber (431) on one side, which corresponds to the number of corner tubes (43). The counterweight chamber (431) and the corner tubes (43) are symmetrically distributed relative to the axis of the impeller (1). The counterweight chamber (431) is symmetrically fitted with a base plate (432) on the end face of the side of the counterweight chamber (431) near the axis of the impeller (1). The counterweight chamber (431) is fitted with an interface valve (433) in the middle position of the end face of the side of the counterweight chamber (431) near the axis of the impeller (1). The counterweight chamber (431) is fitted with a diversion valve (434) in the outer wall of the end of the counterweight chamber (431) near the axis of the impeller (1). The counterweight chamber (431) is fitted with a plunger (435) in the inner wall of the counterweight chamber (431). The counterweight ball (436) is fitted with the end of the plunger (435) away from the axis of the impeller (1).

5. The high-efficiency shielded submersible pump according to claim 4, characterized in that: A ferrule (441) is rotatably fitted at the middle position of the inner wall of the counterweight chamber (431). A serpentine groove (442) is opened on the inner wall of the ferrule (441). A counterweight ring (443) is snapped onto the outer wall of the plunger (435) near the axis of the impeller (1). A push rod (444) that cooperates with the serpentine groove (442) is snapped onto the inner wall of the counterweight ring (443). An angle wedge plate (445) is circumferentially snapped onto the middle position of the inner wall of the counterweight chamber (431). A one-way rotating sheath plate (446) is rotatably fitted onto the middle position of the outer wall of the ferrule (441) through a rotating shaft and a torsion spring (412).

6. The high-efficiency shielded submersible pump according to claim 3, characterized in that: The concentric mechanism (3) includes: The counterweight disc (31) is coaxially snapped onto the outer wall of the rear cover plate of the impeller (1); The annular guide rail (32) is rotatably mounted inside the counterweight plate (31) on the side opposite to the impeller (1); in addition, the outer wall of the annular guide rail (32) is snapped onto the other end of the supplementary plate (429); The shaft disc (33) is snapped onto the end face of the annular guide rail (32) near the impeller (1), and the shaft disc (33) and the counterweight disc (31) are rotatably fitted together. Three fan blades (34) are evenly snapped together on the outer wall of the shaft disk (33) in a circumferential manner; Angle plate (35) is snapped onto the middle position of the end face of the fan blade plate (34) away from the impeller (1); in addition, angle plate (35) is snapped onto the angle bracket (42); at the same time, the end of angle plate (35) away from the axis of the shaft disk (33) is rotated onto the angle shaft (46); The lead screw (36) is rotatably fitted in the hollow area in the middle of the angle plate (35); in addition, the outer wall of the end of the lead screw (36) away from the axis of the shaft disk (33) is snapped together with the driving bevel gear (41); The sleeve (37) is snapped onto one end of the lead screw (36) near the axis of the impeller (1), and the sleeve (37) is snapped onto the angle plate (35); The slide (38) is movably sleeved on the outer wall of the lead screw (36). At the same time, the slide (38) is slidably engaged with the lead groove on the outer wall of the lead screw (36) through the limiting rod, and the slide (38) is slidably engaged with the angle plate (35). In addition, the slide (38) is slidably engaged with the rod sleeve (37). The return spring (39) is snapped between the slide (38) and the corner plate (35), and the return spring (39) is sleeved on the outer wall of the rod sleeve (37).

7. A high-efficiency shielded submersible pump according to claim 6, characterized in that: A common joint between two adjacent fan blades (34) is a slotted plate (311) that is snapped onto the outer wall of a coaxial disk (33). An end plate (312) is also snapped onto the outer wall of the coaxial disk (33) and the slotted plate (311) between two adjacent fan blades (34). A toothed pulley (313) is rotatably fitted between the end plate (311) and the end plate (312) at the middle position of the slide (38) via a rotating shaft. A toothed belt (314) is installed between the toothed pulleys (313) and meshes with each other. A pressure contact rod (315) is snapped onto the end face of the slide (38) near the axis of the shaft disk (33). An electrode plate (316) is snapped onto the side of the angle plate (35) near the axis in a symmetrical manner. There is a space allowance between adjacent electrode plates (316) that does not affect the extension and retraction of the reset spring (39). An electrode cap (317) is snapped onto the end face of the electrode plate (316) away from the axis of the shaft disk (33).

8. The high-efficiency shielded submersible pump according to claim 1, characterized in that: The main body (2) includes: The pump casing (21) is coaxially arranged outside the impeller (1); The pump cover (22) is snapped onto one end of the pump casing (21); The imported flange (23) is snap-fitted onto the pump cover (22) at the end away from the pump casing (21); The outlet flange (24) is installed on the outer wall of the pump cover (22) by a plug-in snap-fit, and the outlet flange (24) and the inlet flange (23) are vertically distributed; The motor shaft (25) is snapped onto the inner wall of the impeller (1) shaft center; The sliding bearing (26) is symmetrically and slidingly connected to both ends of the outer wall of the motor shaft (25); The rotor assembly (27) is snapped onto the outer wall of the motor shaft (25) away from the pump cover (22); The stator assembly (28) is coaxially disposed outside the rotor assembly (27) and snap-fitted to the pump housing (21); The pump base (29) is snapped onto the other end of the pump casing (21) and is directly opposite to the pump cover (22).

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