CN111946656A - Combined permanent magnetic suspension bearing for pump - Google Patents
Combined permanent magnetic suspension bearing for pump Download PDFInfo
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- CN111946656A CN111946656A CN202010894834.7A CN202010894834A CN111946656A CN 111946656 A CN111946656 A CN 111946656A CN 202010894834 A CN202010894834 A CN 202010894834A CN 111946656 A CN111946656 A CN 111946656A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/048—Bearings magnetic; electromagnetic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a combined permanent magnetic suspension bearing for a pump, which is arranged in a magnetic transmission pump and comprises two groups of axial permanent magnetic suspension bearings and one group of radial permanent magnetic suspension bearings; the axial permanent magnetic suspensions comprise axial static magnetic rings fixed on the pump cover and axial moving magnetic rings fixed on the pump shaft, the magnetic rings are axially magnetized, the magnetic rings close to the impeller side have opposite polarities, and the magnetic rings far away from the impeller side have the same polarity; the radial permanent magnetic suspension bearing comprises a static magnetic component fixed with the pump cover and a moving magnetic component fixed on the pump shaft, wherein the static magnetic component comprises a plurality of annular static magnetic coils arranged and installed along the axial direction, and the moving magnetic component comprises a plurality of annular moving magnetic coils arranged and installed along the axial direction; the annular static magnetic ring and the annular moving magnetic ring are both magnetized in the radial direction, and the polarities of the adjacent annular static magnetic ring and the adjacent annular moving magnetic ring are opposite. The invention can eliminate the defect of low magnetic energy action efficiency of the traditional permanent magnet thrust bearing caused by the opposite magnetic force of the movable magnetic disks at the two sides.
Description
Technical Field
The invention belongs to the technical field of magnetic transmission pumps, and particularly relates to a combined permanent magnetic suspension bearing for a pump.
Background
The magnetic transmission pump is widely used in industrial devices, is mainly used for petrochemical industry to convey flammable, explosive, toxic and high-temperature media, and is also used in nuclear industry. The magnetic pump has the following advantages:
(1) reliable sealing
The magnetic pump adopts static seal of the isolation sleeve, and cancels quick-wear parts on the conventional centrifugal pump, namely mechanical seal, so that the running reliability of the unit is greatly improved, and the fault-free running time is prolonged. The particles in the medium have good passing performance, and the sealing damage accident caused by the collision of the stator and the rotor is not easy to happen.
(2) Convenient maintenance
The magnetic pump is simple in structure and convenient to disassemble and assemble, and the motor is a conventional motor and is convenient to overhaul.
(3) Overload protection
The magnetic driver belongs to a non-contact driver, and when the pump is overloaded accidentally, the magnetic driver can cause the internal and external magnets to slip off due to overload. After the slipping, the magnetic driver does not transmit power any more, and the motor is in an idle state at the moment, so that the motor is prevented from being damaged due to overload.
(4) Vibration and noise reduction
The power transmission of the magnetic transmission pump is in a non-contact mode, namely the pump shaft is in non-contact with the motor shaft, so that the rigidity and the vibration resistance of a shaft system are improved, the non-centering vibration is reduced, meanwhile, the hydraulic excitation and the axial force applied to the pump shaft cannot be directly applied to the motor shaft by the pump shaft, and the vibration reduction of the motor is facilitated.
The principle of the magnetic transmission pump is that the non-contact power transmission between a conventional motor and the pump is carried out through the magnetic coupling of the inner permanent magnet and the outer permanent magnet of the magnetic transmission device. The isolating sleeve seals the medium in the pump cavity and isolates the medium from the outside, and the isolating sleeve and the shell are statically sealed by a sealing gasket to realize zero leakage; the device is suitable for conveying corrosive, dangerous, toxic, radioactive or high-pressure and high-temperature media. Compared with the conventional mechanical seal pump, the magnetic pump can greatly reduce or eliminate the disastrous accidents and hazards caused by leakage, prolong the service life of the product and is particularly suitable for working under specific harsh working conditions. In a typical direct-coupled magnetic transmission pump, an outer magnetic rotor is directly connected with a motor shaft head to form a rotating magnetic field to drag an inner magnetic rotor during operation, the whole pump rotor part is supported by a sliding bearing, and the axial direction is restricted by displacement through a thrust disc.
When the pump operates, the front cover plate and the rear cover plate of the impeller are asymmetrical; b. the structural influences of the pillow block, the shaft end and the like; c. dynamic reaction force; d. the rotor part can bear large axial force due to the factors of different disk surface areas of the impeller of the centrifugal pump and the like, so the problem of axial force balance must be considered during design. For the measures of axial force balance, the following measures are adopted at present:
1. the balance hole, but the method can affect the main flow state, possibly leading to the reduction of pump head and efficiency, and even increasing the vibration of the pump; 2. balancing the tube, but this approach affects pump head and efficiency; 3. double suction impellers, but some pumps are not suitable; 4. a back leaf; 5. a balance drum and a balance disc; 6. and pushing the bearing. As for the thrust bearing, there are currently:
a. the bearing solves the problem of abrasion of the thrust collar by means of an electromagnetic technology, but has a relatively complex structure, and the bearing needs to be connected with a circuit in a medium, so that when the medium is flammable and explosive, the danger is increased greatly, and the explosion-proof requirement is not met, so that the bearing is difficult to apply to flammable and explosive media and has low practicability; meanwhile, a position feedback sensor is required to be arranged in the medium pressure cavity, so that the process difficulty is increased, and the operation reliability is reduced; the electromagnetic suspension bearing needs electricity, and once the electricity is lost accidentally, the bearing is damaged due to direct friction of a rotor under stress;
b. the water lubrication thrust bearing is in a contact type, the bearing is abraded after long-time operation, and when the axial force fluctuation is large, the bearing can be damaged after being continuously impacted, such as the SIC bearing is cracked;
c. the bearing is composed of a moving magnetic disk mounted on a rotor and a static magnetic disk mounted on a base body, and as the rotor needs bidirectional thrust, two pairs of back-to-back or face-to-face moving magnetic disks and static magnetic disks are needed. The magnetic force directions that two moving disks received are opposite, and the total axial magnetic force that the rotor received is 0 when both sides disk interval equals, and the rotor was in the home position this moment, but when the rotor received the axial force, the rotor moved to one side direction, and this side magnetic pole interval diminishes, and the magnetic force that the moving disk received grow, and the magnetic force that the opposite side received a pair of magnetic pole interval grow, and the magnetic force that the moving disk received diminishes, and total magnetic force is opposite with the atress direction, up to a stable position. However, because the directions of the magnetic forces applied to the two moving magnetic disks are opposite, a part of the magnetic force applied to the moving magnetic disk on one side is offset by the magnetic force of the moving magnetic disk on the other side, so that the magnetic energy action efficiency is low, and the magnetic energy utilization rate is low.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a combined type permanent magnetic suspension bearing for a pump, which not only solves the problem that a contact type bearing is axially worn, but also overcomes the defects that the traditional permanent magnetic thrust bearing has lower magnetic energy action efficiency due to opposite magnetic forces of moving disks at two sides, and an electromagnetic force bearing has power loss, complicated mechanism and the like.
A combined permanent magnetic suspension bearing for a pump is arranged in a magnetic transmission pump, the magnetic transmission pump comprises a pressure-bearing shell consisting of a pump body, a pump cover and an isolation sleeve, the pump shaft is arranged in the pressure-bearing shell, two groups of water lubrication bearings for supporting the pump shaft are arranged in the pump cover, two ends of the pump shaft are respectively connected with an impeller and an inner magnetic rotor, an outer magnetic rotor corresponding to the inner magnetic rotor is connected with one end of a transmission shaft, the other end of the transmission shaft is in transmission connection with a matched motor, and the isolation sleeve is arranged between the inner magnetic rotor and the outer magnetic rotor; the method is characterized in that: the combined permanent magnetic suspension bearing for the pump comprises two groups of axial permanent magnetic suspension bearings and a group of radial permanent magnetic suspension bearings;
the two groups of axial permanent magnetic suspension bearings are respectively arranged at the outer end sides of the two groups of water lubrication bearings, each group of axial permanent magnetic suspension bearings comprises an axial static magnetic ring and an axial moving magnetic ring which are opposite, wherein the axial static magnetic ring is fixed on the pump cover, and the axial moving magnetic ring is fixed on the pump shaft; the magnetic rings of the axial permanent magnetic suspension bearing are axially magnetized, the two magnetic rings close to the impeller side have opposite polarities, and the two magnetic rings far away from the impeller side have the same polarity;
the radial permanent magnetic suspension bearing is arranged between the two groups of water lubrication bearings and comprises a static magnetic component fixed with the pump cover and a movable magnetic component fixed on the pump shaft, the static magnetic component and the movable magnetic component are both cylindrical, the static magnetic component comprises a plurality of annular static magnetic rings arranged and installed along the axial direction, and the movable magnetic component comprises a plurality of annular movable magnetic rings arranged and installed along the axial direction; the axial width of each annular static magnetic ring is equal to that of each annular dynamic magnetic ring; the annular static magnetic ring and the annular moving magnetic ring are both magnetized in the radial direction, and the polarities of the adjacent annular static magnetic ring and the adjacent annular moving magnetic ring are opposite; the annular static magnetic coils and the annular dynamic magnetic coils are the same in number, and the polarities of the annular static magnetic coils and the annular dynamic magnetic coils which are opposite to each other are opposite when the annular static magnetic coils and the annular dynamic magnetic coils are in a free state without being influenced by external force.
In the use process, the bearing adopts the traditional water lubrication bearing to carry out displacement restraint in the radial direction, adopts two groups of axial permanent magnetic suspension bearings at two sides of the water lubrication bearing to carry out axial restraint in the axial direction, and the magnetic force directions of the two groups of axial permanent magnetic suspension bearings are the same and cannot be offset, so that the magnetic energy action efficiency is improved; when the pump does not operate, the sum of the magnetic force of the axial permanent magnet suspension bearing can be offset by the radial permanent magnet suspension bearing, and the rotor part cannot be attached to the static part, so that the pump cannot be started to operate.
Preferably, in the radial permanent magnet suspension bearing, the annular static magnetic ring and the annular moving magnetic ring are both adhered to the magnetic seat through AB glue, the surfaces of the annular static magnetic ring and the annular moving magnetic ring are respectively coated by a bushing and a shaft sleeve made of thin-wall metal materials, the end parts of the bushing and the shaft sleeve are sealed with the magnetic ring mounting seat through welding, and the annular static magnetic ring and the annular moving magnetic ring are respectively fixed with the pump cover and the pump shaft through the magnetic ring mounting seat.
Preferably, in the radial permanent magnetic suspension bearing, the number of the annular static magnetic rings and the number of the annular dynamic magnetic rings are at least 3.
Preferably, each annular static magnetic ring and each annular moving magnetic ring are respectively formed by assembling a plurality of fan-shaped permanent magnets in the same radial magnetizing direction, and the radial thickness of each permanent magnet is the same, so that the magnetizing and the manufacturing are convenient.
Further, the permanent magnet is made of rubidium, iron, boron or samarium cobalt.
Preferably, the initial design clearance between the static magnetic part and the moving magnetic part of the axial permanent magnetic suspension bearing and the axial permanent magnetic suspension bearing is larger than half of the axial length of a single permanent magnet on the radial permanent magnetic suspension bearing (composed of an annular moving magnetic coil and an annular static magnetic coil).
Further, the initial design gap between the static magnetic component and the moving magnetic component is 1-3 mm.
The maximum axial magnetic balance force of the radial permanent magnetic suspension bearing is larger than the sum of the maximum axial magnetic balance forces of the two sets of axial permanent magnetic suspension bearings.
Compared with the prior art, the invention has the following beneficial effects:
1. the invention adopts the axial permanent magnetic suspension bearing which is axially arranged to replace the conventional mechanical thrust bearing which is easy to wear and easy to damage when in starting impact, bears the axial force generated by the waterpower of the impeller and the self weight of the rotor and the like through the non-contact coupling of the magnetic force, and improves the operation reliability of the centrifugal pump.
2. The invention can make the traditional centrifugal pump cancel the structures of the balance hole of the impeller, the balance pipe and the like, improve the lift and the efficiency of the pump, and cancel the balance hole to be beneficial to the vibration reduction and the noise reduction of the pump.
3. When the pump does not operate, the radial permanent magnet suspension bearings arranged in the radial direction are adopted, the sum of the magnetic forces of the axial permanent magnet suspension bearings can be offset, and the rotor part cannot be attached to the static part, so that the pump cannot be started to operate; and when the pump runs, the magnetic force directions of the axial permanent magnetic suspension bearings are the same and cannot be offset, so that the magnetic energy action efficiency is improved.
4. The combined bearing has strong axial bearing capacity and high magnetic energy action efficiency, and when the rotor part is subjected to hydraulic axial force, the rotor can be stabilized at a proper position by generating less axial displacement, so that the hydraulic performance is prevented from being influenced by overlarge axial displacement of the rotor.
5. The radial permanent magnetic suspension bearing can expand the proper number of the magnetic rings along the axial direction according to the magnitude of the axial force borne by the rotor component, and the mounting seats of the magnetic rings are processed in the shaft sleeve and the lining (the strength of the shaft sleeve and the lining needs to be ensured to be enough), so that the size of the shaft sleeve is not increased, and the additional friction loss of the disc is not increased.
6. The combined bearing of the invention has simple structure and easy arrangement, and does not increase the extra size of the pump.
Drawings
Fig. 1 is a schematic view illustrating an installation of a combined permanent magnetic suspension bearing for a pump according to the present invention.
FIG. 2 is an enlarged view of a portion of area A of FIG. 1;
FIG. 3 is a schematic view of a magnetic ring of the radial permanent magnetic suspension bearing of the present invention;
FIG. 4 is a load-bearing schematic diagram of the radial permanent magnetic suspension bearing of the present invention;
FIG. 5 is a graph showing the relationship between the magnetic bearing force and the displacement during the simulation test according to the embodiment of the present invention.
Detailed Description
The invention will be described in further detail below with reference to the drawings and examples, which are intended to facilitate the understanding of the invention without limiting it in any way.
The utility model provides a combination formula permanent magnetism suspension bearing for pump, install in magnetic drive pump, as shown in fig. 1 ~ 2, magnetic drive pump includes the pump body 1, the pressure-bearing casing that pump cover 3 and spacer sleeve are constituteed, pump shaft 5 sets up in the pressure-bearing casing, be equipped with two sets of water lubrication bearing 8 that support the pump shaft in the pump cover 3, impeller 2 and interior magnet rotor are connected respectively to the both ends of pump shaft 5, the one end of transmission shaft is connected with the outer magnet rotor that corresponds with interior magnet rotor, the other end of transmission shaft is connected with supporting motor 4 transmission, be equipped with the spacer sleeve between interior magnet rotor and the outer magnet rotor.
The combined permanent magnetic suspension bearing for the pump comprises two groups of axial permanent magnetic suspension bearings and a group of radial permanent magnetic suspension bearings.
As shown in fig. 2, the axial permanent magnetic suspension bearing 6 and the axial permanent magnetic suspension bearing 7 are respectively arranged at the outer end sides of the two groups of water lubricated bearings 8, each group of axial permanent magnetic suspension bearing comprises an axial static magnetic ring and an axial dynamic magnetic ring which are opposite, wherein the axial static magnetic ring is fixed on the pump cover, and the axial dynamic magnetic ring is fixed on the pump shaft; the magnetic rings of the axial permanent magnetic suspension bearing are axially magnetized, the two magnetic rings of the axial permanent magnetic suspension bearing 6 close to the impeller side are opposite in polarity, and the two magnetic rings of the axial permanent magnetic suspension bearing 7 far away from the impeller side are identical in polarity. Because the magnetic force directions of the two groups of axial permanent magnetic suspension bearings are the same, the two groups of axial permanent magnetic suspension bearings cannot be offset, and the magnetic energy action efficiency is improved.
As shown in fig. 2, the radial permanent magnetic suspension bearing is arranged between two groups of water lubricated bearings 8, and includes a static magnetic component fixed with the pump cover and a moving magnetic component fixed on the pump shaft 5, the static magnetic component and the moving magnetic component are both cylindrical, the static magnetic component includes a plurality of annular static magnetic coils 9 arranged and installed along the axial direction, and the moving magnetic component includes a plurality of annular moving magnetic coils 10 arranged and installed along the axial direction; the axial width of each annular static magnetic ring 9 is equal to that of each annular dynamic magnetic ring 10; the annular static magnetic ring 9 and the annular moving magnetic ring 10 are both magnetized in the radial direction, and the polarities of the adjacent annular static magnetic ring 9 and the adjacent annular moving magnetic ring 10 are opposite; the annular static magnetic coils and the annular dynamic magnetic coils are the same in number, and the polarities of the annular static magnetic coils and the annular dynamic magnetic coils which are opposite to each other are opposite when the annular static magnetic coils and the annular dynamic magnetic coils are in a free state without being influenced by external force.
As shown in fig. 3, each of the annular static magnetic ring 9 and the annular moving magnetic ring 10 is assembled by a plurality of fan-shaped permanent magnets 20 in the same radial magnetizing direction, and the radial thickness of each permanent magnet 20 is the same. The permanent magnet 20 may be made of rare earth materials such as rubidium, iron, boron or samarium, cobalt.
As shown in fig. 4, in the radial permanent magnetic suspension bearing, the annular static magnetic ring 9 and the annular moving magnetic ring 10 are both adhered to the magnetic base by an AB adhesive, and the surfaces of the two are respectively covered by a bush 13 and a shaft sleeve 14 made of thin-wall metal materials.
The end part of the bush 13 is sealed with the magnetic ring mounting seat 11 through welding, the end part of the shaft sleeve 14 is sealed with the magnetic ring mounting seat 12 through welding, and the annular static magnetic ring 9 and the annular movable magnetic ring 10 are respectively fixed with the pump cover and the pump shaft through the magnetic ring mounting seats.
For the radial permanent magnetic suspension bearing, when the rotor is axially moved by an axial force, the moving magnetic part is also axially moved together, for the radial permanent magnetic suspension bearing, at this time, the annular moving magnetic ring 10 is axially displaced relative to the annular static magnetic ring 9 to cause magnetic pole dislocation, at this time, the magnetic pole of each annular moving magnetic ring 10 is attracted by the opposite magnetic pole of the original annular static magnetic ring 9, and is simultaneously subjected to the repulsive force of the same magnetic pole adjacent to the magnetic pole in the moving direction, the magnetic force applied to each magnetic ring can reach 2 times of the force applied to a single magnetic ring, the magnetic force is increased along with the increase of the dislocation amount, when the dislocation position reaches half of the axial length of the permanent magnet, the axial magnetic force is the maximum, and the principle is shown in fig. 4. For an axially disposed axial permanent magnetic suspension bearing, the left bearing presents suction to the rotor component and the right bearing presents repulsion to the rotor component, which will also assist in maintaining the axial force balance of the rotor components.
On the axial permanent magnetic suspension bearing 6 and the axial permanent magnetic suspension bearing 7, the initial designed gap between the static magnetic component and the moving magnetic component is larger than half of the axial length of a single permanent magnet on the radial permanent magnetic suspension bearing (composed of an annular moving magnetic ring 10 and an annular static magnetic ring 9). Through the arrangement, when the rotor component moves, the moving amount of the rotor component can reach half of the axial length of a single permanent magnet, and the magnetic pull force of the thrust bearing is the maximum and reaches the maximum design value.
As shown in FIG. 5, for a designed thrust bearing test, the transmission radius is 64mm, the total magnetic length of the radial permanent magnet suspension bearing is 70mm, 10 annular static magnetic rings and 10 annular dynamic magnetic rings are provided, the thickness of each magnetic ring is 7mm, the magnetic gap is 2mm, and N40H is obtained. From the test results, if the axial length of the single magnetic steel is 7mm, the bearing axial bearing capacity reaches the maximum design value when the dislocation is 3.5 mm. The pump unit is provided with a rotor component, a rotor component and a pump set, wherein the rotor component is provided with a thrust disc; when the pump set normally operates, the thrust disc and the thrust bearing do not collide and rub, the vibration characteristic is good, and the situation that the axial thrust capability of the thrust disc is reduced due to abrasion after long-term operation, so that the operation of the pump is unstable and even the thrust disc is cracked can be avoided.
When the bearing is designed and installed, the maximum axial magnetic balance force of the radial permanent magnetic suspension bearing is larger than the sum of the maximum axial magnetic balance forces of the two sets of axial permanent magnetic suspension bearings.
The method comprises the following steps of 1, theoretical design: calculating the maximum bearing capacity of the radial permanent magnetic suspension bearing and the axial permanent magnetic suspension bearing through the magnetic energy product of the magnetic steel, the gap between the annular movable magnetic ring and the annular static magnetic ring, the arc length of each magnetic steel, the total length of the magnetic steel, the thickness of the magnetic steel and the like; 2. and (3) finite element analysis and verification: design and check are carried out on the theoretical calculation result through an electromagnetic field finite element method, and the design is verified to meet the use requirement; 3. after the combined type suspension bearing is manufactured, processed and installed, an operation test is carried out for 100 hours in a factory, a pump is disassembled after the test, and the parts are checked to be free of friction and the like.
When the pump does not operate, the radial permanent magnet suspension bearings arranged in the radial direction are adopted, the sum of the magnetic forces of the axial permanent magnet suspension bearings can be offset, and the rotor part cannot be attached to the static part, so that the pump cannot be started to operate; and when the pump runs, the magnetic force directions of the axial permanent magnetic suspension bearings are the same and cannot be offset, so that the magnetic energy action efficiency is improved.
The embodiments described above are intended to illustrate the technical solutions and advantages of the present invention, and it should be understood that the above-mentioned embodiments are only specific embodiments of the present invention, and are not intended to limit the present invention, and any modifications, additions and equivalents made within the scope of the principles of the present invention should be included in the scope of the present invention.
Claims (8)
1. A combined permanent magnetic suspension bearing for a pump is arranged in a magnetic transmission pump, the magnetic transmission pump comprises a pressure-bearing shell consisting of a pump body, a pump cover and an isolation sleeve, the pump shaft is arranged in the pressure-bearing shell, two groups of water lubrication bearings for supporting the pump shaft are arranged in the pump cover, two ends of the pump shaft are respectively connected with an impeller and an inner magnetic rotor, an outer magnetic rotor corresponding to the inner magnetic rotor is connected with one end of a transmission shaft, the other end of the transmission shaft is in transmission connection with a matched motor, and the isolation sleeve is arranged between the inner magnetic rotor and the outer magnetic rotor; the method is characterized in that: the combined permanent magnetic suspension bearing for the pump comprises two groups of axial permanent magnetic suspension bearings and a group of radial permanent magnetic suspension bearings;
the two groups of axial permanent magnetic suspension bearings are respectively arranged at the outer end sides of the two groups of water lubrication bearings, each group of axial permanent magnetic suspension bearings comprises an axial static magnetic ring and an axial moving magnetic ring which are opposite, wherein the axial static magnetic ring is fixed on the pump cover, and the axial moving magnetic ring is fixed on the pump shaft; the magnetic rings of the axial permanent magnetic suspension bearing are axially magnetized, the two magnetic rings close to the impeller side have opposite polarities, and the two magnetic rings far away from the impeller side have the same polarity;
the radial permanent magnetic suspension bearing is arranged between the two groups of water lubrication bearings and comprises a static magnetic component fixed with the pump cover and a movable magnetic component fixed on the pump shaft, the static magnetic component and the movable magnetic component are both cylindrical, the static magnetic component comprises a plurality of annular static magnetic rings arranged and installed along the axial direction, and the movable magnetic component comprises a plurality of annular movable magnetic rings arranged and installed along the axial direction; the axial width of each annular static magnetic ring is equal to that of each annular dynamic magnetic ring; the annular static magnetic ring and the annular moving magnetic ring are both magnetized in the radial direction, and the polarities of the adjacent annular static magnetic ring and the adjacent annular moving magnetic ring are opposite; the annular static magnetic coils and the annular dynamic magnetic coils are the same in number, and the polarities of the annular static magnetic coils and the annular dynamic magnetic coils which are opposite to each other are opposite when the annular static magnetic coils and the annular dynamic magnetic coils are in a free state without being influenced by external force.
2. The combined permanent magnetic suspension bearing for the pump according to claim 1, wherein in the radial permanent magnetic suspension bearing, the annular static magnetic ring and the annular moving magnetic ring are both adhered to the magnetic base by AB glue, and the surfaces of the annular static magnetic ring and the annular moving magnetic ring are respectively coated by a bushing and a shaft sleeve made of thin-wall metal materials, the ends of the bushing and the shaft sleeve are sealed with the magnetic ring mounting base by welding, and the annular static magnetic ring and the annular moving magnetic ring are respectively fixed with the pump cover and the pump shaft by the magnetic ring mounting base.
3. The combined permanent magnetic suspension bearing for the pump according to claim 1, wherein the number of the annular static magnetic rings and the annular moving magnetic rings in the radial permanent magnetic suspension bearing is at least 3.
4. The combined permanent magnetic suspension bearing for the pump according to claim 1, wherein each of the annular static magnetic ring and the annular moving magnetic ring is assembled by a plurality of fan-shaped permanent magnets in the same radial magnetizing direction, and the radial thickness of each permanent magnet is the same.
5. The combined permanent magnetic suspension bearing for the pump according to claim 4, wherein the permanent magnet is made of rubidium, iron, boron or samarium cobalt.
6. The combined permanent magnetic suspension bearing for pump according to claim 4, wherein the initial design gap between the static magnetic component and the moving magnetic component is larger than half of the axial length of a single permanent magnet on the radial permanent magnetic suspension bearing.
7. The combined permanent magnetic suspension bearing for the pump according to claim 1, wherein an initial design gap between the static magnetic component and the moving magnetic component is 1-3 mm.
8. The combined permanent magnetic suspension bearing for pump according to claim 1, wherein the maximum axial magnetic balance force of the radial permanent magnetic suspension bearing is greater than the sum of the maximum axial magnetic balance forces of the two sets of axial permanent magnetic suspension bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010894834.7A CN111946656A (en) | 2020-08-31 | 2020-08-31 | Combined permanent magnetic suspension bearing for pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010894834.7A CN111946656A (en) | 2020-08-31 | 2020-08-31 | Combined permanent magnetic suspension bearing for pump |
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| CN111946656A true CN111946656A (en) | 2020-11-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010894834.7A Pending CN111946656A (en) | 2020-08-31 | 2020-08-31 | Combined permanent magnetic suspension bearing for pump |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113107892A (en) * | 2021-05-18 | 2021-07-13 | 浙江理工大学 | Magnetic force type balance disc for pump |
| CN113187758A (en) * | 2021-06-22 | 2021-07-30 | 晋江爱家制冷设备有限公司 | Impeller axial force counteracts and balancing unit |
| CN113931852A (en) * | 2021-10-21 | 2022-01-14 | 安徽银龙泵阀股份有限公司 | Corrosion-resistant magnetic pump |
| CN115247650A (en) * | 2022-07-28 | 2022-10-28 | 瑞希特(浙江)科技股份有限公司 | Full permanent magnetism suspension bearing magnetic drive pump |
| CN117997040A (en) * | 2024-04-07 | 2024-05-07 | 中国石油天然气股份有限公司 | Underground magnetic suspension power generation device |
-
2020
- 2020-08-31 CN CN202010894834.7A patent/CN111946656A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113107892A (en) * | 2021-05-18 | 2021-07-13 | 浙江理工大学 | Magnetic force type balance disc for pump |
| CN113187758A (en) * | 2021-06-22 | 2021-07-30 | 晋江爱家制冷设备有限公司 | Impeller axial force counteracts and balancing unit |
| CN113187758B (en) * | 2021-06-22 | 2022-06-07 | 晋江爱家制冷设备有限公司 | Impeller axial force counteracts and balancing unit |
| CN113931852A (en) * | 2021-10-21 | 2022-01-14 | 安徽银龙泵阀股份有限公司 | Corrosion-resistant magnetic pump |
| CN115247650A (en) * | 2022-07-28 | 2022-10-28 | 瑞希特(浙江)科技股份有限公司 | Full permanent magnetism suspension bearing magnetic drive pump |
| CN117997040A (en) * | 2024-04-07 | 2024-05-07 | 中国石油天然气股份有限公司 | Underground magnetic suspension power generation device |
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