An energy-saving permanent magnet synchronous motor

Abstract

This invention discloses an energy-saving permanent magnet synchronous motor, relating to the field of permanent magnet motor technology. It includes a body, a stator housed within the body, and a permanent magnet rotor rotatably housed within the stator. It also includes a fixed sleeve coaxially fitted inside the permanent magnet rotor, with an output shaft mounted therein. The body includes a rear end cover and a front end cover mounted on the rear end cover, with both ends of the permanent magnet rotor forming oil-sealed cavities with the two end covers respectively. The permanent magnet rotor and the opposite sides of the conical portion form an annular cavity. This energy-saving permanent magnet synchronous motor, through the cooperation of the conical portion and the annular cavity, reduces the rotational speed of the oil film with the maximum thickness within the annular cavity, preventing excessive centrifugal force and oil film oscillation caused by a thicker oil film at high speeds. Furthermore, the design of the rotating blades allows the blades to automatically tilt and decelerate the oil flow at high speeds, further preventing oscillation.

Description

Technical Field

[0001] This invention relates to the field of permanent magnet motor technology, and more specifically to an energy-saving permanent magnet synchronous motor. Background Technology

[0002] Energy-saving permanent magnet synchronous motors achieve ultra-high efficiency through efficient electromagnetic design (such as high-performance permanent magnets and optimized magnetic circuits) and low-loss materials (such as thin silicon steel sheets and flat copper wires). Their key innovation lies in the oil seals used at the bearings, which reduce frictional heat and mechanical energy during rotor rotation while isolating external contaminants. Lubrication further reduces bearing frictional losses, further saving energy and extending service life, making them suitable for harsh industrial environments.

[0003] Combined with publication number CN114079346B, an electric motor is disclosed, which has a housing in which a stator and a rotatable rotor are arranged. The stator is formed as a hollow column and disposed within a stator chamber of the housing, and the rotor is disposed within a rotor chamber through a columnar opening in the stator. An air gap is provided between the rotor and the stator, allowing the rotor to rotate relative to the stator. The stator chamber is defined radially inward by means of a columnar wall portion, which is sealed relative to the housing by means of at least one sealing element. The housing has at least one axially extending protrusion forming an axial end face and a radially outwardly pointing circumferential shoulder that carries the sealing element. This allows the seal to be positioned without radial stretching and elongation, thereby ensuring the long-term durability of the sealing element and preventing damage from widening during installation in certain situations.

[0004] However, in the aforementioned patent, the protrusion forms an axial end face and a radially outward-pointing surrounding shoulder, with the bearing element positioned on the surrounding shoulder to form a continuous annular segment. Since the seal itself is not radially stretched or elongated, the assembled shape of the seal matches the aforementioned annular segment and ultimately forms a continuous annular sealing structure. This annular sealing structure lacks any other radial or axial support structures for quick installation, thus the inner wall of the annular sealing structure is completely continuous. During rotor rotation, the rotor drives the seal to rotate synchronously. The lubricating oil within the seal forms directional vortices within the annular sealing structure. When the seal rotates at high speed, these directional vortices oscillate under centrifugal force, causing rotor eccentricity and significant swaying during torque output. This swaying increases with rotational speed, affecting rotor output efficiency and potentially leading to seal failure. Summary of the Invention

[0005] The purpose of this invention is to provide an energy-saving permanent magnet synchronous motor to solve the above-mentioned problems.

[0006] To achieve the above objectives, the present invention provides the following technical solution: an energy-saving permanent magnet synchronous motor, comprising a body and a stator disposed within the body, and a permanent magnet rotor rotatably disposed within the stator, and further comprising a fixed sleeve coaxially sleeved within the permanent magnet rotor, wherein an output shaft is assembled.

[0007] The body includes a rear end cover and a front end cover mounted on the rear end cover, and the two ends of the permanent magnet rotor are respectively enclosed by the two end covers to form an oil seal cavity;

[0008] The permanent magnet rotor has a tapered portion fixedly provided at its end, and the permanent magnet rotor and the opposite side of the tapered portion form an annular cavity.

[0009] The conical end face is radially provided with multiple main flow blades for forming oil flow channels and branch flow blades for separating the tail end of the oil flow channels.

[0010] The rotating blades, which are set in the annular cavity, change with the rotational speed of the permanent magnet rotor to switch between two positions: parallel and inclined oil flow within the annular cavity.

[0011] Preferably, the device also includes a movable ring rotatably mounted on the permanent magnet rotor and coupled to the permanent magnet rotor at a rated speed, which is used to drive the rotating blades.

[0012] Preferably, it also includes a fixed rail fixedly mounted on the movable ring, with rolling balls inside for striking the rotating blade.

[0013] Preferably, it also includes an inner flow channel formed on the fixed sleeve, and the side of the annular cavity is an arc-shaped guide surface facing the inner flow channel.

[0014] Preferably, the rotating blade is divided into an arc-shaped portion that abuts against the annular cavity and a trapezoidal portion for guiding the oil flow, with the rotating shaft as the boundary.

[0015] Preferably, the fixed sleeve has a pressure chamber inside, and a spring for engaging the output shaft is movably mounted on the fixed sleeve.

[0016] Preferably, the pressure chamber is connected to the oil seal chamber to dynamically distribute oil pressure when the output shaft is axially displaced.

[0017] Preferably, the permanent magnet rotor has a drainage channel for connecting the two ends of the permanent magnet rotor.

[0018] Preferably, the permanent magnet rotor is provided with a first spring and a second spring at both ends.

[0019] Preferably, the front end cover and the fixing sleeve are respectively provided with an oil inlet channel and an oil outlet channel for oil inlet and outlet.

[0020] In the above technical solution, the energy-saving permanent magnet synchronous motor provided by the present invention has the following beneficial effects: through the cooperation of the cone and the annular cavity, the rotation speed of the oil film with the maximum thickness in the annular cavity is reduced, avoiding the oil film oscillation caused by excessive centrifugal force at high speed due to the thicker oil film. In addition, combined with the design of the rotating blade, the rotating blade can automatically tilt and decelerate the oil flow at high speed, further playing the role of preventing oscillation. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this invention. For those skilled in the art, other drawings can be obtained based on these drawings.

[0022] Figure 1 This is an overall three-dimensional schematic diagram provided for an embodiment of the present invention;

[0023] Figure 2 This is a schematic diagram of the overall exploded structure provided in an embodiment of the present invention;

[0024] Figure 3 This is a cross-sectional schematic diagram of the permanent magnet rotor and conical structure provided in an embodiment of the present invention;

[0025] Figure 4 This is a side view schematic diagram provided for an embodiment of the present invention;

[0026] Figure 5 Provided for embodiments of the present invention Figure 4 A schematic diagram of the enlarged structure of A in the middle;

[0027] Figure 6 This is a schematic diagram of the cross-sectional structure of the permanent magnet rotor and the fixing sleeve provided in an embodiment of the present invention;

[0028] Figure 7 This is a schematic diagram of the permanent magnet rotor and movable ring structure provided in an embodiment of the present invention;

[0029] Figure 8 This is a schematic diagram of the moving ring and toothed portion in their moving state according to an embodiment of the present invention;

[0030] Figure 9 This is a schematic diagram of the rotating blade, movable ring, and toothed portion structure provided in an embodiment of the present invention;

[0031] Figure 10 This is a schematic diagram of the rotating blade, movable ring, and toothed portion provided in an embodiment of the present invention;

[0032] Figure 11 A front view of the front end of the permanent magnet rotor provided in an embodiment of the present invention;

[0033] Figure 12 This is a schematic diagram of the rotating blade, movable ring, and toothed portion structure provided in an embodiment of the present invention;

[0034] Figure 13 Provided for embodiments of the present invention Figure 12 Schematic diagram of the enlarged inner B structure.

[0035] Explanation of reference numerals in the attached figures:

[0036] 1. Front cover; 11. Rear cover; 12. Stator; 13. Oil inlet channel; 14. Front oil seal cavity; 15. Rear oil seal cavity; 2. Permanent magnet rotor; 21. Front sealing ring; 22. Rear sealing ring; 23. First spring; 24. Second spring; 25. Cone; 251. Main flow vane; 252. Flow divider vane; 26. Rotating vane; 261. Rotating component; 262. Rotating rod; 27. Inner flow channel; 271. Annular cavity; 28. Lead-in Flow channel; 29. ​​Toothed part; 291. Stop block; 292. Slot; 3. Output shaft; 31. Limiting groove; 4. Fixing sleeve; 41. Pressure chamber; 42. Oil outlet; 43. Sealing block; 431. Third spring; 44. Spring leaf; 45. Oil outlet channel; 46. Filter screen; 5. Moving ring; 51. Clamping part; 511. Clip; 512. Fourth spring; 513. Inclined groove; 52. Rack; 53. Fixed rail; 531. Ball bearing. Detailed Implementation

[0037] To enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings.

[0038] like Figure 1-13 As shown, an energy-saving permanent magnet synchronous motor includes a housing and a stator 12 disposed within the housing, and a permanent magnet rotor 2 rotatably disposed within the stator 12. It also includes a fixed sleeve 4 coaxially sleeved within the permanent magnet rotor 2, and an output shaft 3 (such as...) is assembled therein. Figure 3 (as shown);

[0039] The machine body includes a rear end cover 11 and a front end cover 1 mounted on the rear end cover 11. The two ends of the permanent magnet rotor 2 are respectively enclosed by the two end covers to form oil seal cavities (including a front oil seal cavity 14 and a rear oil seal cavity 15, the two oil seal cavities being as follows...). Figure 4 (The area highlighted by the dashed line is shown).

[0040] A cone 25 is fixedly provided at the end of the permanent magnet rotor 2, and the opposite sides of the permanent magnet rotor 2 and the cone 25 form an annular cavity 271 (e.g., Figure 6 (as shown);

[0041] Multiple main flow vanes 251 for forming oil flow channels and branch flow vanes 252 for separating the tail ends of the oil flow channels are radially arranged on the end face of the cone 25 (e.g. Figure 11 (as shown);

[0042] The rotating blade 26, which is rotatably disposed within the annular cavity 271, switches between two positions relative to the oil flow within the annular cavity 271—parallel and inclined—as the rotational speed of the permanent magnet rotor 2 changes (e.g., ...). Figure 11 (As shown).

[0043] Specifically, the end of the permanent magnet rotor 2 closest to the front end cover 1 is designated as the front end, and the opposite end is designated as the rear end. The front end cover 1 has an oil inlet channel 13. A front sealing ring 21 and a rear sealing ring 22 are fixedly installed at both ends of the permanent magnet rotor 2, respectively. The front sealing ring 21 and the rear sealing ring 22, together with the front end cover 1 and the rear end cover 11, respectively, form a front oil seal cavity 14 and a rear oil seal cavity 15. The front end of the permanent magnet rotor 2, together with the front end cover 1 and the front sealing ring 21, forms the front oil seal cavity 14, while the rear end, together with the rear end cover 11 and the rear sealing ring 22, forms the rear oil seal cavity 15 (e.g., ...). Figure 4 (As shown in the dotted line box), the oil injection channel 13 is connected to the front oil seal cavity 14 and is filled with oil.

[0044] Furthermore, after the stator 12 is energized, it drives the permanent magnet rotor 2 to rotate. At this time, the permanent magnet rotor 2 and the cone 25 rotate at high speed and drive the oil in the front oil seal cavity 14 to rotate through shear force. The oil forms an oil film with a certain thickness. This oil film keeps a predetermined distance between the cone 25 and the front oil seal cavity 14 to reduce sliding friction. During rotation, the main flow vane 251 pushes the lubricating oil to flow along the conical surface of the cone 25. The oil flow direction is from the smallest diameter end of the cone 25 to the largest diameter end. At the tail end of the oil flow channel, it is separated by the diverting vane 252. The oil flow is divided into two paths and then merges into the annular cavity 271. Since the inner diameter of the annular cavity 271 is relatively large compared with the oil flow channel, the flow velocity of the oil in the oil flow channel automatically decreases when entering the annular cavity 271. This causes the flow velocity of the oil in the annular cavity 271 to decrease, that is, the rotation speed of the oil film with the maximum thickness in the annular cavity 271 decreases, avoiding excessive centrifugal force caused by the thicker oil film at high speed, which would cause oil film oscillation.

[0045] Furthermore, when the rotational speed does not exceed the limit, the rotating blade 26 is in a state of parallel oil flow (e.g. Figure 11(As shown by the black dashed line), at this time, the rotating blade 26 follows the flow direction of the oil, dividing the annular cavity 271 into two concentric annular channels. Solid impurities in the lubricating oil (such as sludge or coking caused by high temperature) are thrown from the inner annular channel to the outer annular channel under the action of centrifugal force. At this time, the inner annular channel forms a stable laminar flow to prevent the outer annular channel from flowing back radially. Subsequently, the solid impurities adhere to the inner wall of the annular cavity 271 rather than the inner wall of the front sealing ring 21. The front sealing ring 21 acts as a barrier between the outside world and the front oil seal cavity 14. Once the inner wall is adhered to by lubricating oil impurities, it is very likely to damage the sealing interface. For example, sludge forms a hard deposit layer on the inner wall of the oil seal, causing the rubber lip and the journal to not fit tightly, resulting in an increase in the dynamic sealing gap.

[0046] When the rotational speed exceeds the limit, the rotating blade 26 deflects (see below for details on the specific transmission method). At this time, the multiple rotating blades 26 are tilted relative to the oil flow (e.g., Figure 11 (As shown by the solid black line in the middle), at this time, a semi-closed area is formed between the two adjacent rotating blades 26. The rotating blades 26 will block the oil flow and slow down the oil flow to prevent the oil flow from oscillating under the centrifugal force.

[0047] In the above technology, the cooperation between the cone 25 and the annular cavity 271 reduces the rotational speed of the oil film with the maximum thickness in the annular cavity 271, avoiding excessive centrifugal force caused by the thicker oil film at high speed, which would cause oil film oscillation. In addition, the design of the rotating blade 26 allows the rotating blade 26 to automatically tilt and decelerate the oil flow at high speed, further preventing oscillation.

[0048] As a further embodiment of the present invention, it also includes a movable ring 5 rotatably disposed on the permanent magnet rotor 2 and coupled to the permanent magnet rotor 2 at a rated speed, which is used to drive the rotating blade 26.

[0049] Specifically, the front end circumferential array of the permanent magnet rotor 2 is provided with multiple tooth-like portions 29 (e.g., Figure 7 As shown), multiple clamping parts 51 are fixedly provided on the movable ring 5, and inclined grooves 513 are opened in the clamping parts 51 (as shown). Figure 13 As shown), the inclined slot 513 has relatively high and low positions (as shown). Figure 13 (The direction shown is for reference), and a retainer 511 is rolled inside the inclined groove 513. A fourth spring 512 is provided on the inclined groove 513 to keep the retainer 511 in a low position.

[0050] The first end of the toothed portion 29 has a slot 292 for engaging the clip 511 (e.g., Figure 8 As shown in the figure below), and the first end of the toothed portion 29 is provided with an inclined arc groove (such as...). Figure 9 and Figure 10As shown), a stop 291 is fixedly provided at the second end of the toothed portion 29. In the default state, the locking piece 511 is in a low position due to the push of the fourth spring 512, and the locking piece 511 is engaged in the slot 292. At this time, the clamping part 51 engages the toothed portion 29 from both sides. At this time, the permanent magnet rotor 2 rotates clockwise, and the toothed portion 29 drives the movable ring 5 to rotate synchronously through the friction between the clamping part 51 and the locking piece 511 (as shown). Figure 8 (As shown in the image above).

[0051] When the rotational speed of the permanent magnet rotor 2 exceeds a certain limit, the clamp 511 will be thrown towards the circumference under the action of centrifugal force. At this time, the centrifugal force overcomes the elastic force of the fourth spring 512, causing the clamp 511 to slide towards the higher part of the inclined groove 513, such as... Figure 13 As shown, because the inclined groove 513 is inclined, the spherical surface of the clamping member 511 moves from extending a certain distance beyond the clamping part 51 to retracting into the clamping part 51, and the clamping member 511 is misaligned with the groove 292. At the same time, at low speed, the clamping part 51 is locked onto the toothed part 29 by static friction, but at high speed, the centrifugal force reduces the contact pressure, causing sliding friction to occur prematurely. That is, the clamping part 51 cannot keep up with the rapidly rotating toothed part 29, and the clamping part 51 and the movable ring 5 slide off along the arc. At this time, the clamping part 51 slides from being clamped on the toothed part 29 to being located between the two toothed parts 29 (as shown). Figure 8 As shown in the figure below), the clamping part 51 rotates counterclockwise relative to the toothed part 29 (as shown in the figure below). Figure 8 As shown by the dashed arrow in the figure below, the toothed part 29 continues to push the clamping part 51 to rotate through the second side stop 291. At this time, the clamping part 51 and the toothed part 29 are staggered to form a continuous ring structure, which blocks the outer ring channel of the annular cavity 271 and prevents the solid impurities originally attached to the inner wall from continuing to diffuse radially under the further increased centrifugal force, causing backflow.

[0052] Furthermore, one end of the rotating shaft of the rotating blade 26 is rotatably connected to the annular cavity 271, and the other end extends into a movable ring 5. A rotating component 261 is fixedly mounted on the extended portion. The rotating component 261 adopts a half-gear structure, and a rack 52 that meshes with the rotating component 261 is fixedly mounted on the movable ring 5 for transmission. In the default state, the rotating component 261 and the rack 52 maintain a certain position. Figure 8 In the meshing state shown in the diagram above, the rotating blade 26 is in a parallel state. When the rotational speed of the permanent magnet rotor 2 exceeds a certain limit, the clamping part 51 and the movable ring 5 will rotate counterclockwise relative to the toothed part 29, that is, the movable ring 5 will rotate counterclockwise relative to the shaft of the rotating blade 26. At this time, the rack 52 will drive the rotating blade 26 to deflect to an inclined state.

[0053] As another embodiment of the present invention, it also includes a fixed rail 53 fixedly disposed on the movable ring 5, wherein a ball bearing 531 for striking the rotating blade 26 is rolled inside the rail.

[0054] Specifically, during the high-speed rotation of the permanent magnet rotor 2, the stop block 291 continues to push the clamping part 51 to rotate until the permanent magnet rotor 2 decelerates. The movable ring 5 will maintain its original motion trend under the action of inertia. At this time, the speed of the permanent magnet rotor 2 decreases, and the movable ring 5 will rotate clockwise relative to the permanent magnet rotor 2 and the toothed part 29, so that the inner wall of the clamping part 51 slides relative to the two sides of the toothed part 29 again. The bottom surface of the arc groove is an inclined surface that guides to the bottom of the slot 292. After the rotation speed of the clamping part 51 decreases, the elastic force of the fourth spring 512 pushes the locking piece 511 back to the low position. At this time, the locking piece 511 squeezes the arc groove and automatically locks into the slot 292 along the guide of the arc groove, completing the reset.

[0055] During the above process, the ball 531 rolls within the fixed rail 53, and a rotating rod 262 is fixedly mounted on the rotating component 261. The fixed rail 53 has a groove for the rotating rod 262 to swing; the width of the groove is smaller than the radius of the ball 531 to prevent the ball 531 from rolling out. When the permanent magnet rotor 2 rotates at high speed, the ball 531 provides part of the centrifugal force, making the effect of the rotational speed on the movable ring 5 more pronounced. When the retaining element 511 returns to the retaining groove 292, it returns to the default state. At this time, the movable ring 5 rotates clockwise relative to the rotating component 261, and the rotating component 261 and the rotating rod 262 swing to... Figure 8 As shown in the figure above, the ball 531 continues to roll clockwise under inertia and impacts the rotating part 261.

[0056] As another embodiment of the present invention, it further includes an inner flow channel 27 formed on the fixed sleeve 4, and the side of the annular cavity 271 is an arc-shaped guide surface facing the inner flow channel 27 (e.g., Figure 6 (As shown).

[0057] Specifically, since the inner diameter of the annular cavity 271 is relatively large compared to the oil flow channel, the flow velocity of the oil in the oil flow channel automatically decreases when entering the annular cavity 271, which causes the flow velocity of the oil in the annular cavity 271 to decrease. Therefore, the oil pressure in the annular cavity 271 increases, which will spontaneously squeeze the lubricating oil into the inner flow channel 27, providing the necessary basis for subsequent operations.

[0058] Meanwhile, since the side of the annular cavity 271 is a circular arc guide surface, the oil flow is concentrated towards the axis along the circumferential direction, and the oil flowing in the annular cavity 271 is guided to the inner flow channel 27 through the circular arc guide surface.

[0059] As another embodiment of the present invention, the rotating blade 26 is divided into an arc-shaped portion that abuts against the annular cavity 271 and a trapezoidal portion for guiding the oil flow, with the rotating shaft as the boundary.

[0060] Specifically, during the process of switching from the parallel station to the inclined station, the arc-shaped part of the rotating part 261 abuts against and scrapes the arc-shaped guide surface, causing impurities on the arc-shaped guide surface to be scraped to the side of the rotating part 261 facing the inner flow channel 27. At this time, the impurities are carried by the oil flow and automatically enter the inner flow channel 27 along the trapezoidal part for collection. The rotating rod 262 is struck and vibrated by the ball 531, causing the impurities on the rotating blade 26 to fall off and enter the inner flow channel 27 with the liquid flow.

[0061] As another embodiment of the present invention, a pressure chamber 41 is provided inside the fixing sleeve 4 (e.g. Figure 6 As shown), and the fixed sleeve 4 is movably fitted with a spring 44 for engaging the output shaft 3.

[0062] Specifically, the spring 44 is the part of the pressure chamber 41 that extends out of the fixed sleeve 4. The output shaft 3 is provided with a limiting groove 31 corresponding to the position of the spring 44. When assembling the output shaft 3, it is only necessary to insert the output shaft 3 into the fixed sleeve 4 along the axial direction. The spring 44 is first squeezed and deformed by the end of the output shaft 3 until the position of the spring 44 and the limiting groove 31 are opposite. Then the spring 44 is released and locked in the limiting groove 31, so that the spring 44 and the limiting groove 31 are interference fit, thereby increasing the connection stability of the fixed sleeve 4 and the limiting groove 31.

[0063] As another embodiment of the present invention, the pressure chamber 41 is connected to the oil seal chamber (including the front oil seal chamber 14 and the rear oil seal chamber 15) to dynamically distribute oil pressure when the output shaft 3 is axially displaced.

[0064] Specifically, the permanent magnet rotor 2 has a flow channel 28 for connecting the two ends of the permanent magnet rotor 2. The flow channel 28 has a filter membrane at the port facing the front oil seal cavity 14, and the fixed sleeve 4 has an oil outlet channel 45 for oil discharge. The pressure chamber 41 is connected to the inner flow channel 27, and is connected to a suction pump through the oil outlet channel 45 to draw lubricating oil in the pressure chamber 41. This causes the lubricating oil to flow along the path of oil injection channel 13 - front oil seal cavity 14 - annular cavity 271 - inner flow channel 27 - pressure chamber 41 - oil outlet channel 45. The flow channel 28 is opened on the inner wall of the annular cavity 271, and the lubricating oil in the annular cavity 271 flows into the rear oil seal cavity 15 for lubrication through the flow channel 28.

[0065] The pressure chamber 41 has an oil outlet 42 for connecting to the rear oil seal chamber 15. A sealing block 43 is provided at the port of the oil outlet 42, and the sealing block 43 and the oil outlet 42 are connected by a third spring 431. When the output shaft 3 undergoes axial displacement, the output shaft 3 will squeeze the spring 44, which will reduce the volume of the pressure chamber 41 and increase the pressure accordingly. However, the opening of the inner flow channel 27 towards the pressure chamber 41 is small, which makes the resistance to the return flow from the pressure chamber 41 to the inner flow channel 27 relatively large, which is equivalent to a one-way valve.

[0066] The lubricating oil in the pressure chamber 41 will first push the sealing block 43 and overcome the elastic force of the third spring 431 to enter the rear oil seal chamber 15, which will increase the oil pressure in the rear oil seal chamber 15. Since the opening of the drainage channel 28 to the rear oil seal chamber 15 is relatively narrow, when the oil pressure in the rear oil seal chamber 15 increases, the pressure of the rear oil seal chamber 15 on the narrow end of the drainage channel 28 is relatively large, which will stop the lubricating oil in the drainage channel 28 from being transported to the rear oil seal chamber 15, thereby maintaining the lubricating oil pressure in the front oil seal chamber 14. At this time, there is a certain oil pressure in both the front oil seal chamber 14 and the rear oil seal chamber 15.

[0067] When the output shaft 3 moves axially, the spring 44 first dissipates part of the axial impact force, and then drives the fixed sleeve 4 and the permanent magnet rotor 2 to move axially. At this time, the oil at one end of the permanent magnet rotor 2 is squeezed, and the pressure in the corresponding oil seal cavity increases. The pressure is transmitted to the other end through the drainage channel 28, forming a reverse thrust. This design can automatically balance the axial force. Combined with the first spring 23 and the second spring 24 set at both ends of the permanent magnet rotor 2, it can play a good axial balance role and prevent sudden axial movement problems.

[0068] At the same time, a filter screen 46 is also installed inside the oil outlet 42 (such as...). Figure 5 As shown, the filter screen 46 intercepts impurities in the pressure chamber 41 inside the pressure chamber 41, while the spring 44 is detachably assembled in the fixed sleeve 4. When it is necessary to clean the impurities, the spring 44 can be opened and combined with the rinsing operation.

[0069] Working principle: In the default state, the locking piece 511 is in a low position due to the push of the fourth spring 512, and the locking piece 511 is engaged in the slot 292. At this time, the clamping part 51 engages with the toothed part 29 from both sides. At this time, the permanent magnet rotor 2 rotates clockwise, and the toothed part 29 drives the movable ring 5 to rotate synchronously through the friction between the clamping part 51 and the locking piece 511 (e.g., Figure 8 (As shown in the image above).

[0070] At this time, the rotating blade 26 follows the flow direction of the oil flow, so that the annular cavity 271 is divided into two concentric annular channels by the rotating blade 26. The solid impurities in the lubricating oil (such as sludge or coking generated under high temperature environment) are thrown from the inner annular channel to the outer annular channel under the action of centrifugal force. At this time, the inner annular channel forms a stable laminar flow to prevent the outer annular channel from flowing back radially.

[0071] When the rotational speed of the permanent magnet rotor 2 exceeds a certain limit, the clamp 511 will be thrown towards the circumference under the action of centrifugal force. At this time, the centrifugal force overcomes the elastic force of the fourth spring 512, causing the clamp 511 to slide towards the higher part of the inclined groove 513, such as... Figure 13As shown, because the inclined groove 513 is inclined, the spherical surface of the clamping member 511 moves from extending a certain distance beyond the clamping part 51 to retracting into the clamping part 51, and the clamping member 511 is misaligned with the groove 292. At the same time, at low speed, the clamping part 51 is locked onto the toothed part 29 by static friction, but at high speed, the centrifugal force reduces the contact pressure, causing sliding friction to occur prematurely. That is, the clamping part 51 cannot keep up with the rapidly rotating toothed part 29, and the clamping part 51 and the movable ring 5 slide off along the arc. At this time, the clamping part 51 slides from being clamped on the toothed part 29 to being located between the two toothed parts 29 (as shown). Figure 8 As shown in the figure below, the toothed portion 29 continues to push the clamping portion 51 to rotate via the stop 291 on the second side, while the clamping portion 51 rotates counterclockwise relative to the toothed portion 29 (as shown in the figure below). Figure 8 As shown by the dotted arrow in the figure below, the movable ring 5 rotates counterclockwise relative to the axis of the rotating blade 26. At this time, the rack 52 drives the rotating blade 26 to deflect to an inclined state.

[0072] At this time, the multiple rotating blades 26 are tilted relative to the oil flow (e.g. Figure 11 As shown by the solid black line, a semi-enclosed area is formed between two adjacent rotating blades 26. The rotating blades 26 will block the oil flow and slow down the oil flow to prevent the oil flow from oscillating under the influence of centrifugal force.

[0073] As the permanent magnet rotor 2 decelerates, the movable ring 5 will maintain its original motion trend under the action of inertia. At this time, the speed of the permanent magnet rotor 2 decreases, and the movable ring 5 will rotate clockwise relative to the permanent magnet rotor 2 and the toothed part 29, so that the inner wall of the clamping part 51 slides relative to the two sides of the toothed part 29 again. The bottom surface of the arc groove is an inclined surface that guides to the bottom of the slot 292. After the rotation speed of the clamping part 51 decreases, the elastic force of the fourth spring 512 pushes the locking piece 511 back to the low position. At this time, the locking piece 511 squeezes the arc groove and automatically locks into the slot 292 along the guide of the arc groove, completing the reset.

[0074] The foregoing has only described certain exemplary embodiments of the present invention by way of illustration. Undoubtedly, those skilled in the art can modify the described embodiments in various ways without departing from the spirit and scope of the present invention. Therefore, the foregoing drawings and descriptions are illustrative in nature and should not be construed as limiting the scope of protection of the claims of the present invention.

Claims

1. An energy-saving permanent magnet synchronous motor comprising a machine body and a stator (12) arranged in the machine body, and a permanent magnet rotor (2) rotatably arranged in the stator (12), characterized in that, A fixed sleeve (4) coaxially sleeved in the permanent magnet rotor (2) is further included, and an output shaft (3) is assembled in the fixed sleeve (4); The machine body comprises a rear end cover (11) and a front end cover (1) assembled on the rear end cover (11), and the two ends of the permanent magnet rotor (2) are enclosed with the two end covers to form an oil seal cavity; A taper portion (25) is fixedly arranged at the end of the permanent magnet rotor (2), and the permanent magnet rotor (2) and the taper portion (25) on the opposite side thereof enclose an annular cavity (271); A plurality of main flow vanes (251) for forming an oil flow channel and a flow separation vane (252) for separating the tail end of the oil flow channel are radially arranged on the end face of the taper portion (25); A rotating vane (26) is rotatably arranged in the annular cavity (271) and switches between parallel and inclined two working positions of the oil flow in the annular cavity (271) with the change of the rotating speed of the permanent magnet rotor (2); An activity ring (5) is further included, which is rotatably arranged on the permanent magnet rotor (2) and coupled with the permanent magnet rotor (2) at a rated rotating speed, and is used for driving the rotating vane (26); A fixed rail (53) is further included, which is fixedly arranged on the activity ring (5) and has a rolling ball (531) arranged therein for knocking the rotating vane (26); An inner flow channel (27) is further included, which is arranged on the fixed sleeve (4), and the side face of the annular cavity (271) is a circular arc guide surface facing the inner flow channel (27); The rotating vane (26) is divided into an arc-shaped portion abutting against the annular cavity (271) and a trapezoidal portion for guiding the oil flow by the rotating shaft.

2. An energy saving permanent magnet synchronous motor according to claim 1, characterized by The fixed sleeve (4) is provided with a pressure cavity (41), and a spring sheet (44) for clamping the output shaft (3) is movably assembled on the fixed sleeve (4).

3. An energy saving permanent magnet synchronous motor according to claim 2, characterized by The pressure cavity (41) is in communication with the oil seal cavity to dynamically distribute the oil pressure when the output shaft (3) axially displaces.

4. An energy saving permanent magnet synchronous motor as claimed in claim 1, characterized in that, The permanent magnet rotor (2) is provided with a drainage channel (28) for communicating the two ends of the permanent magnet rotor (2).

5. An energy saving permanent magnet synchronous motor as claimed in claim 1, characterized by, The permanent magnet rotor (2) is provided with a first spring (22) and a second spring (24) at the two ends thereof.

6. An energy efficient permanent magnet synchronous motor as claimed in claim 1, wherein, The front end cover (1) and the fixed sleeve (4) are respectively provided with an oil injection channel (13) and an oil outlet channel (45) for oil inlet and oil outlet.

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