CN113883084B - Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application - Google Patents
Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application Download PDFInfo
- Publication number
- CN113883084B CN113883084B CN202111021011.4A CN202111021011A CN113883084B CN 113883084 B CN113883084 B CN 113883084B CN 202111021011 A CN202111021011 A CN 202111021011A CN 113883084 B CN113883084 B CN 113883084B
- Authority
- CN
- China
- Prior art keywords
- cavity
- impeller
- balance
- pump
- shell
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
- F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses an automatic axial force balancing device of a magnetic suspension centrifugal pump under a high-power working condition and application thereof. The pump cover is fixedly arranged on the pump cavity shell, the interior of the pump cavity shell is hollow and forms an installation cavity, an impeller assembly is arranged in the installation cavity of the pump cavity shell, and a plurality of circles of balance guide rings arranged at intervals are fixedly arranged on the circumferential side surface of the lower part of the impeller assembly; a first hydraulic suspension balance cavity is formed between the impeller assembly and the pump cover, a second hydraulic suspension balance cavity is formed between the impeller assembly and the pump cavity shell, a pump cavity is formed between the circumferential side surface of the upper portion of the impeller assembly, the pump cavity shell and the pump cover, and a pressure reduction balance cavity is formed between the circumferential side surface of the lower portion of the impeller assembly and the pump cavity shell. The invention reduces the axial hydraulic pressure on the impeller working under the high-power working condition, thereby balancing the axial hydraulic pressure of the impeller and the axial magnetic resistance formed between the stator and the rotor of the motor, and the balance of the hydraulic axial force of the impeller in different working point ranges under different working conditions can be realized by adjusting the size of the balance guide strips.
Description
Technical Field
The invention relates to an axial balancing device of a centrifugal pump, in particular to an automatic axial force balancing device of a magnetic suspension centrifugal pump under a high-power working condition (more than 4 KW) and application thereof.
Background
The magnetic suspension centrifugal pump is an electromagnetic induction driving fluid pump without bearing and mechanical component friction, has no friction in the rotation process of an impeller, has a series of advantages of high speed, no friction, no pollution, easy maintenance and the like, and is widely applied to the fields of medicine (artificial heart), semiconductor (pumping of ultrapure water), biotechnology (no leakage, seamless design), electroplating (sealing design) and the like.
In the magnetic suspension centrifugal pump, due to the structure of the centrifugal pump, the structure of the impeller assembly close to the center is communicated with the inlet and is used for suction pressure, and the pressure is lower; when the impeller rotates to generate centrifugal force, liquid in the flow channel is thrown to the periphery under the action of the blades under the action of the centrifugal force and flows into the pump shell, the kinetic energy of the liquid is converted into pressure energy, the liquid with the pressure energy is discharged through the discharge port, and the pressure at the edge of the impeller is higher. All in oneWhen the impeller is not in contact with the pump shell, high-pressure liquid flowing out of the edge of the impeller can enter the top and the bottom of the impeller through a non-contact flow passage gap between the impeller and the pump shell. As shown in FIG. 1, due to the up-and-down asymmetry between the inlet of the upper surface of the impeller itself and the bottom structure of the impeller, the axial force of the high-pressure liquid acting on the upper surface of the impeller is F 1 The size of which is the radius r of the central cavity 1 Is directed downwards; the axial force acting on the lower surface of the impeller is F 2 The radius r of the lower part of the pump cavity shell 2 Is directed upwards. Meanwhile, the liquid flow direction of the liquid to be conveyed is changed from the inlet to the outlet, and the liquid flow is deflected from the axial direction to the radial direction to generate a downward dynamic reaction force F on the impeller assembly 3 So that the resultant axial hydraulic force on the impeller is F 1 ，F 2 ，F 3 Vector sum of F h I.e. F h ＝ F 2 -F 1 -F 3 . Because the permanent magnet is arranged in the impeller and is a rotor of the motor, the rotor and the stator of the motor drive the impeller to rotate by generating a magnetic field, and the impeller can also receive axial passive magnetic resistance force F formed between the stator and the rotor of the motor z In a direction opposite to the direction of axial movement of the impeller. When axial passive magnetic resistance force F z Axial force F with respect to hydraulic pressure h Are equal, i.e. F z ＝F h The impeller is balanced in the axial direction. When the power of the motor is small (less than 200W), the axial passive magnetic resistance force can basically balance the axial hydraulic force of the impeller. However, as the motor power (more than 200W) increases, the axial passive detent force has been unable to balance the hydraulic axial force F h The hydraulic axial force F can be reduced by a certain damping structure h In centrifugal pumps, certain measures have been taken to balance the hydraulic axial forces.
It is known to use balancing holes or tubes, which are in flow communication between the front and the bottom of the rotor through a number of balancing holes extending axially in the central position of the bottom of the rotor, in order to relieve the pressure of the high-pressure liquid entering the bottom of the rotor, and thus to achieve axial balancing. The balance pipe is also used for communicating a high-pressure area to a low-pressure area so as to achieve axial force balance, but the balance pipe needs an external pipeline and is not suitable for a structure of a magnetic suspension pump.
The known measures are that a structure for installing a balance drum or a balance disc is adopted, the pressure difference at two ends of a balance drum device is realized by communicating one end of the balance drum device with a low-pressure end of an inlet, the leakage flow is determined by the radial clearance between the balance drum and a balance sleeve and the friction resistance of a disc, and the balance drum or the balance disc is fixed on a shaft by a key or a thread. The balance disc works by generating pressure difference according to the change of leakage amount, can move back and forth according to the change of the operation working condition of the device, and automatically adjusts the size of the balance force. The two structures are applied to common centrifugal pumps with shafts, but the centrifugal pumps working according to the principle of bearingless motors are relatively complex in structure and limited in space.
The known measures are that under the working condition of large flow, a back blade is arranged at the bottom of the impeller to reduce the pressure at the bottom of the impeller so as to balance the axial force.
These measures can balance the axial force to a certain extent under low power working conditions (less than or equal to 4 KW), but the force required for balancing depends on the working point, in particular the flow and pressure generated by the pump, and at some working points it is still difficult, the working range for balancing the axial force is narrow, and the impeller axial force of a magnetic suspension centrifugal pump working under the principle of bearingless motor cannot be automatically balanced.
The problem of impeller axial force imbalance is also particularly acute in magnetic pumps, especially when the axial support is done entirely magnetically without mechanical bearings. In order to balance the rotor of such bearingless machines, the forces can only be compensated for by hydrodynamic compensation, in addition to a certain compensation by passive magnetic reluctance.
Disclosure of Invention
The invention aims to provide an automatic axial force balancing device of a magnetic suspension centrifugal pump under a high-power working condition (more than 4 KW) and application thereof, wherein the axial force balancing device has a wider working range and can overcome the problems in the prior art. The invention should also be particularly applicable to centrifugal pumps having magnetically supported rotors.
The invention adopts the following technical scheme:
1. axial force automatic balancing device of magnetic suspension centrifugal pump under high-power working condition
The axial force automatic balancing device comprises a pump cover, a pump cavity shell, an impeller assembly and a balancing guide ring;
the pump cover is fixedly arranged on the pump cavity shell, the interior of the pump cavity shell is hollow and forms an installation cavity, an impeller assembly is arranged in the installation cavity of the pump cavity shell, and a plurality of circles of balance guide rings arranged at intervals are fixedly arranged on the circumferential side surface of the lower part of the impeller assembly; a pump cover convex ring is arranged in the middle of the lower surface of the pump cover, and a gap is formed between the lower surface of the pump cover convex ring and the upper surface of the impeller assembly; a pump cavity shell convex ring is arranged in the middle of the lower bottom surface of the inner wall of the pump cavity shell, a gap is formed between the upper surface of the pump cavity shell convex ring and the lower surface of the impeller assembly, and an impeller bottom cavity is formed between the radial inner side of the pump cavity shell convex ring and the middle of the lower bottom surface of the inner wall of the pump cavity shell and the lower bottom surface of the impeller assembly; a first hydraulic suspension balance cavity is formed between the upper surface of the impeller assembly and the lower surface of the pump cover convex ring, a second hydraulic suspension balance cavity is formed between the lower surface of the impeller assembly and the upper surface of the pump cavity shell convex ring, a pump cavity is formed between the circumferential side surface of the upper part of the impeller assembly, the inner wall of the pump cavity shell and the lower surface of the pump cover, and a pressure reduction balance cavity is formed between the circumferential side surface of the lower part of the impeller assembly and the balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell; the inlet pipeline has been seted up at the middle part of pump cover, has seted up the outlet pipeline on the circumference side on pump chamber shell upper portion, and inlet pipeline and outlet pipeline all communicate the installation cavity, and liquid flows in from the inlet pipeline, flows out from the outlet pipeline after impeller subassembly pressure boost.
The impeller assembly comprises a permanent magnet shell, a flow baffle, impeller blades and a permanent magnet;
the permanent magnet shell is internally and fixedly provided with an annular permanent magnet, the middle part of the permanent magnet shell is provided with a plurality of balance holes which are axially arranged at equal intervals along the circumference, and the circumferential side surface of the permanent magnet shell is fixedly provided with a plurality of circles of balance guide rings which are arranged at intervals; the upper surface of the permanent magnet shell is fixedly provided with impeller blades, the impeller blades are provided with central holes, a plurality of spiral flow channels which are uniformly distributed at intervals along the circumference are arranged in the impeller blades, all the spiral flow channels are arranged along the spiral direction of the same plane, and each spiral flow channel radially communicates the central holes of the impeller blades with the peripheral pump cavity on the periphery; the center hole of the impeller blade is internally provided with a flow baffle which is radially arranged, the flow baffle is hermetically embedded in the center hole of the impeller blade, the middle part of the flow baffle extends downwards and then is fixedly connected with the middle part of the permanent magnet shell, the flow baffle divides the center hole into two parts, the center hole on the upper surface of the flow baffle is marked as the center cavity on the upper part of the impeller, and the center hole on the lower surface of the flow baffle is communicated with the balance hole;
the upper surface of the impeller blade is used as the upper surface of the impeller assembly and forms a first hydraulic suspension balance cavity with the lower surface of the pump cover convex ring, the lower surface of the permanent magnet shell is used as the lower surface of the impeller assembly and forms a second hydraulic suspension balance cavity with the upper surface of the pump cavity shell convex ring, and pressure reduction balance cavities are formed between the circumferential side surface of the permanent magnet shell and the balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell;
the liquid flows into the central cavity of the upper part of the impeller from the inlet pipeline, the liquid in the central cavity of the upper part of the impeller flows into the impeller assembly in the axial direction, then flows into the pump cavity from a plurality of internal spiral flow channels of the impeller blades after being blocked and guided by the flow baffle plate, a large part of the liquid in the pump cavity flows out of the pump cavity from the outlet pipeline, the other part of the liquid in the pump cavity leaks upwards and downwards respectively, the liquid leaking upwards flows into the central cavity of the upper part of the impeller again through the first hydraulic suspension balance cavity, and the liquid leaking downwards flows into the central cavity of the upper part of the impeller again after sequentially passing through the pressure reduction balance cavity, the second hydraulic suspension balance cavity, the cavity of the bottom of the impeller, the balance hole and the central hole on the lower surface of the flow baffle plate.
The balance guide rings are identical in structure, each balance guide ring is mainly formed by arranging a plurality of balance guide strips on the circumferential side surface of the lower part of the impeller assembly at equal intervals along the same circumference, axial guide grooves are formed at intervals between adjacent balance guide strips of the same balance guide ring, and the axial guide grooves of the adjacent balance guide rings are arranged in a staggered mode; the interval between the adjacent balance guide rings forms a tangential guide groove, and a plurality of tangential guide grooves are arranged in parallel.
The staggered circle center angle of the staggered arrangement of the axial guide grooves between the adjacent balance guide rings is more than or equal to 30 degrees, and the width of each axial guide groove is less than or equal to 1/3 of the height of each balance guide strip;
the number of the tangential diversion grooves is at least 5, the height of the balance diversion strips is greater than or equal to that of the tangential diversion grooves, and the thickness of the balance diversion strips is less than or equal to that of the tangential diversion grooves;
the interval between the balance guide strip and the inner wall of the pump cavity shell is not more than 2mm.
The upper surface and the lower surface of the impeller assembly are the same in shape, and the upper surface and the lower surface of the impeller assembly are conical surfaces, so that the first hydraulic suspension balance cavity and the second hydraulic suspension balance cavity are both wedge-shaped circular rings.
The impeller assembly in the axial force automatic balancing device serves as a motor rotor, the axial force automatic balancing device is installed in a motor stator, after the motor stator is electrified, a magnetic field formed between the motor stator and the motor rotor drives the motor rotor, so that the impeller assembly is suspended in the installation cavity after overcoming gravity and liquid impact force, and the impeller assembly rotates in the circumferential direction, and the axial force automatic balancing of liquid is achieved.
2. Application of axial force automatic balancing device
The application field of the axial force automatic balancing device is a magnetic suspension pump or a magnetic pump which works under the principle of a bearingless motor.
The working principle of the invention is as follows:
the centrifugal pump works by driving an impeller wrapped by a permanent magnet to rotate at a high speed by a magnetic field generated by a motor, the impeller rotates at a high speed to generate centrifugal force, when liquid enters a central cavity at the upper part of the impeller from a pipeline, the liquid is converted from axial motion to radial motion under the action of a flow baffle plate, the liquid moves radially from the central cavity at the upper part of the impeller to the periphery under the action of inertial centrifugal force of an impeller assembly, and the liquid can obtain energy in the motion process of flowing through blades of the impeller, so that the static pressure energy is increased, and the flow rate is increased. When the liquid leaves the impeller blade and enters the pump cavity, the space of the pump cavity has a wider flow passageThe kinetic energy is converted into static pressure energy, and most of the liquid finally flows into the outlet pipeline along the tangential direction. Since the centrifugal pump impeller does not directly contact the inner wall of the pump chamber housing, the high-pressure liquid flowing to the pump chamber may partially leak. The invention relates to a method for reducing the pressure F of the leakage liquid at the bottom of an impeller by a pressure reducing balance cavity 2 The axial hydraulic resultant force F borne by the impeller is reduced and matched with the action of the balance hole h The axial magnetic resistance F of the magnetic suspension centrifugal pump under the high-power working condition is reduced z Axial hydraulic force F with impeller h Balance, and simultaneously, the hydraulic axial force can be automatically adjusted, so that an impeller in the magnetic suspension pump can stably run.
When part of leaked high-pressure liquid flows downwards through the pressure reducing balance cavity, a flow stream contraction effect exists, a plurality of balance guide strips and the inner wall of the pump cavity shell form a plurality of damping circular rings in the flowing direction, when the liquid flows through the damping circular rings, partial pressure energy of the liquid is converted into kinetic energy, the flowing speed of the liquid is increased, the pressure of the liquid is reduced, meanwhile, when the liquid with the increased kinetic energy of the damping circular rings enters the tangential guide grooves, the flowing area is suddenly increased, the flowing speed is reduced, a certain vortex is formed in the tangential guide grooves due to the viscosity of the liquid, partial energy is dissipated into heat energy, when the liquid enters the damping circular rings formed by the next stage of balance guide strips and the inner wall of the pump cavity shell again, the kinetic energy of the liquid cannot be restored into the initial pressure energy, and when the liquid passes through the balance guide rings formed by the multistage balance guide strips of the pressure reducing balance cavity, the pressure of the leaked liquid can be continuously reduced. Meanwhile, due to the viscous action of the liquid, when the liquid flows through the damping ring, friction force is generated in the process of contacting with the wall surface, and certain pressure loss is generated in the liquid. Because the axial guiding gutters are distributed in a staggered manner at different heights, the plurality of axial guiding gutters are equivalent to a plurality of damping gaps, a small part of liquid flowing into the tangential guiding gutters can generate transverse turbulence in the tangential guiding gutters, when the liquid flows to the axial guiding gutters formed between the next-stage balance guiding strips, the liquid can generate partial pressure loss, meanwhile, part of leaked liquid increases friction loss in the transverse turbulence process, simultaneously, the eddy dissipation of part of liquid is prolonged, and the pressure of the leaked liquid is further reduced.When part of leaked high-pressure liquid passes through the pressure reduction balance cavity, the liquid pressure entering the cavity at the bottom of the impeller is smaller than the pressure of the pump cavity, primary pressure reduction is realized, meanwhile, the liquid entering the cavity at the bottom of the impeller is communicated to the low-pressure area at the inlet of the impeller through a plurality of balance holes, secondary pressure reduction is realized, and axial hydraulic resultant force F borne by the impeller assembly is enabled to be F h The axial magnetic resistance F of the magnetic suspension centrifugal pump under the high-power working condition is reduced z Axial hydraulic force F with impeller h And (4) balancing. Meanwhile, the height and the thickness of the balance guide strips, the height of the tangential guide grooves and the height and the width of the axial guide grooves can be adjusted according to different working points under different working conditions, so that the balance of the hydraulic axial force of the impeller assembly has a wider working range.
The hydraulic suspension balance cavities which are symmetrical up and down are used for automatically adjusting the axial stability of the impeller, when part of high-pressure leakage liquid flows upwards from the pump cavity into the first hydraulic suspension balance cavity and downwards flows through the pressure reduction balance cavity to enter the second hydraulic suspension balance cavity, the first hydraulic suspension balance cavity and the second hydraulic suspension balance cavity are both wedge-shaped circular rings, the leakage liquid has certain viscosity, the liquid flows from a large opening to a small opening, and hydraulic suspension is formed in the first hydraulic suspension balance cavity and the second hydraulic suspension balance cavity due to certain pressure of the leakage liquid, so that the impeller assembly is in a suspension state in the axial direction. When the impeller assembly works at a certain working point and the impeller assembly is moved upwards by an axial force, the wedge-shaped small opening of the first hydraulic suspension balance cavity is reduced, the liquid pressure in the first hydraulic suspension balance cavity on the upper surface of the impeller assembly is increased, the wedge-shaped small opening of the second hydraulic suspension balance cavity is increased, and the liquid pressure in the second hydraulic suspension balance cavity is reduced, so that the impeller assembly is pushed back to the original position by the suspension force generated in the first hydraulic suspension balance cavity. Similarly, when the impeller subassembly was at certain operating point during operation, when the impeller subassembly received axial force to move down, the wedge osculum in the balanced chamber of second hydraulic suspension reduced, the hydraulic pressure in the balanced chamber of impeller subassembly upper surface second hydraulic suspension risees, the wedge osculum in the balanced chamber of first hydraulic suspension increases, the hydraulic pressure in the balanced chamber of first hydraulic suspension reduces, thereby the suspension power that produces in the balanced chamber of second hydraulic suspension pushes the impeller subassembly back original position, thereby realize the automatically regulated of impeller subassembly axial force, make the impeller steady operation in high-power magnetic suspension pump.
The invention has the beneficial effects that:
the invention relates to an automatic axial force balancing device of a magnetic suspension centrifugal pump under a high-power working condition, wherein a permanent magnet is arranged in an impeller of the centrifugal pump, and the impeller is driven to rotate through a magnetic field. The multistage balance guide strips on the circumferential cylindrical surface of the centrifugal pump impeller component are distributed to form a pressure reduction balance cavity with the inner wall of the pump cavity shell, high-pressure liquid is leaked to realize one-stage pressure reduction through the pressure reduction balance cavity, the pressure of the liquid is reduced by one part, and secondary pressure reduction is realized through the balance holes, so that the hydraulic axial force of the centrifugal pump impeller working under the high-power working condition is reduced, and the balance between the axial hydraulic force and the axial magnetic resistance force of the magnetic suspension centrifugal pump impeller is realized.
Meanwhile, the axial hydraulic pressure of the impeller in different working point ranges under different working conditions can be balanced by adjusting the size of the balance guide strips. The hydraulic suspension wedge-shaped balance cavities which are symmetrical up and down of the impeller can realize the automatic adjustment of the axial force of the impeller assembly, so that the impeller can stably run in the axial direction of the high-power magnetic suspension pump.
Drawings
FIG. 1 is a schematic view of the axial hydraulic force experienced by an impeller.
Fig. 2 is a cross-sectional schematic view of a magnetic suspension centrifugal pump according to an embodiment of the invention.
Fig. 3 is a schematic view of the inlet and outlet of the magnetic suspension centrifugal pump in the embodiment of the invention.
Fig. 4 is a schematic diagram of the flow direction of liquid in the magnetic suspension centrifugal pump according to the embodiment of the invention.
Fig. 5 is a schematic view of an impeller assembly according to an embodiment of the present invention.
Fig. 6 is a dimensional schematic diagram of an impeller assembly according to an embodiment of the present invention.
In the figure: 1 pump cover, 1-1 pump cover convex ring, 2 sealing ring, 3 pump cavity shell, 3-1 pump cavity shell convex ring, 4 permanent magnet shell, 5 baffle plate, 6 impeller blade, 7 impeller bladeBalance guide strips, 8 permanent magnets, 9 balance holes, 10 tangential guide grooves, 11 axial guide grooves, an inlet pipeline A, an outlet pipeline B, an upper central cavity of an impeller D, a pump cavity E, a bottom cavity of the impeller F, a first hydraulic suspension balance cavity, c a second hydraulic suspension balance cavity, B pressure reduction balance cavity, h 1 Height of the balance guide strip h 2 Height of tangential guide grooves, h 3 The thickness of the balance guide strip and the width of the w axial guide groove are adjusted.
Detailed Description
The technical scheme of the invention is further explained by combining the attached drawings.
As shown in fig. 1, 2, 3 and 4, the present invention includes a pump cover 1, a pump chamber housing 3, an impeller assembly and a balancing guide ring;
the pump cover 1 is fixedly arranged on a pump cavity shell 3 through a sealing ring 2 and a bolt, the interior of the pump cavity shell 3 is hollow and forms an installation cavity, an impeller assembly is arranged in the installation cavity of the pump cavity shell 3, the impeller assembly and the pump cavity shell 3 are arranged at intervals, a pump cover convex ring 1-1 is arranged in the middle of the lower surface of the pump cover 1, a gap is formed between the lower surface of the pump cover convex ring 1-1 and the upper surface of the impeller assembly, a pump cavity shell convex ring 3-1 is arranged in the middle of the lower bottom surface of the inner wall of the pump cavity shell 3, a gap is formed between the upper surface of the pump cavity shell convex ring 3-1 and the lower surface of the impeller assembly, and an impeller bottom cavity F is formed between the radial inner side of the pump cavity shell convex ring 3-1, the middle of the lower bottom surface of the inner wall of the pump cavity shell and the lower bottom surface of the impeller assembly; a plurality of circles of balance guide rings which are arranged at equal intervals are fixedly arranged on the circumferential side surface of the lower part of the impeller component; a first hydraulic suspension balance cavity a is formed between the upper surface of the impeller assembly and the lower surface of the pump cover convex ring 1-1, a second hydraulic suspension balance cavity c is formed between the lower surface of the impeller assembly and the upper surface of the pump cavity shell convex ring 3-1, a pump cavity E is formed between the circumferential side surface of the upper part of the impeller assembly, the inner wall of the pump cavity shell 3 and the lower surface of the pump cover 1, and a pressure reduction balance cavity b is formed between the circumferential side surface of the lower part of the impeller assembly and the balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell 3; an inlet pipeline A is arranged in the middle of the pump cover 1, an outlet pipeline B is arranged on one circumferential side face of the pump cavity shell 3, the inlet pipeline A and the outlet pipeline B are both communicated with the mounting cavity, liquid flows into the mounting cavity inside the axial force automatic balancing device from the inlet pipeline A, and flows out of the outlet pipeline B after being pressurized by the impeller assembly.
As shown in fig. 5 and 6, the impeller assembly includes a permanent magnet housing 4, a baffle plate 5, impeller blades 6, and permanent magnets 8; in specific implementation, the impeller assembly is integrally manufactured by adopting a 3D printing technology or a casting mode.
An annular permanent magnet 8 is fixedly installed in the permanent magnet shell 4, a plurality of balance holes 9 which are axially arranged at equal intervals along the circumference are formed in the middle of the permanent magnet shell 4, and a plurality of circles of balance guide rings which are arranged at intervals are fixedly installed on the circumferential side surface of the permanent magnet shell 4; the upper surface of the permanent magnet shell 4 is fixedly provided with an impeller blade 6, the impeller blade 6 is provided with a central hole, a plurality of spiral flow channels which are uniformly distributed at intervals along the circumference are arranged in the impeller blade 6, all the spiral flow channels are arranged along the spiral direction of the same plane, and each spiral flow channel radially communicates the central hole of the impeller blade 6 with the peripheral pump cavity E on the periphery; a flow baffle plate 5 which is radially arranged is arranged in a central hole of the impeller blade 6, the flow baffle plate 5 is hermetically embedded in the central hole of the impeller blade 6, the middle part of the lower surface of the flow baffle plate 5 extends downwards and then is fixedly connected with the middle part of the permanent magnet shell 4, the central hole is divided into two parts by the flow baffle plate 5, the central hole in the upper surface of the flow baffle plate 5 is marked as an upper central cavity D of the impeller, and the central hole in the lower surface of the flow baffle plate 5 is communicated with a balance hole 9;
the upper surface and the lower surface of the impeller assembly are the same in shape, and the upper surface and the lower surface of the impeller assembly are conical surfaces, so that the first hydraulic suspension balance cavity a and the second hydraulic suspension balance cavity c are both in a wedge-shaped circular ring shape, and the first hydraulic suspension balance cavity a and the second hydraulic suspension balance cavity c are used for automatically adjusting the axial hydraulic pressure of the impeller assembly to be stable, and the impeller assembly can stably run in a high-power magnetic suspension pump.
The upper surfaces of the impeller blades 6 serve as the upper surfaces of the impeller assembly and form a first hydraulic suspension balance cavity a with the lower surface of the pump cover convex ring 1-1, the lower surface of the permanent magnet shell 4 serves as the lower surface of the impeller assembly and forms a second hydraulic suspension balance cavity c with the upper surface of the pump cavity shell convex ring 3-1, and the circumferential side surface of the permanent magnet shell 4 and a pressure reduction balance cavity b between the balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell 3;
the liquid flows into the central cavity D at the upper part of the impeller from the inlet pipeline A, the liquid in the central cavity D at the upper part of the impeller flows into the impeller assembly in the axial direction, then flows into the pump cavity E from a plurality of internal spiral flow channels of the impeller blades 6 after being blocked and guided by the flow baffle plate 5, most of the liquid in the pump cavity E flows out of the pump cavity E through the outlet pipeline B, the other part of the liquid in the pump cavity E leaks upwards and downwards respectively, the liquid leaking upwards flows into the central cavity D at the upper part of the impeller again through the first hydraulic suspension balance cavity a, and the liquid leaking downwards flows into the central cavity D at the upper part of the impeller again after sequentially passing through the pressure reduction balance cavity B, the second hydraulic suspension balance cavity c, the cavity F at the bottom of the impeller, the balance hole 9 and the central hole at the lower surface of the flow baffle plate 5.
The liquid leaked downwards enters the cavity F at the bottom of the impeller after passing through the pressure reduction balance cavity b and the second hydraulic suspension balance cavity c, the liquid pressure entering the cavity F at the bottom of the impeller is smaller than that of the pump cavity E, primary pressure reduction is realized, meanwhile, the liquid entering the cavity F at the bottom of the impeller is communicated to the central hole at the lower surface of the flow baffle plate 5 through the balance holes 9, and the central hole at the lower surface of the flow baffle plate 5 is an impeller inlet low-pressure area, so that secondary pressure reduction is realized.
The structures of the plurality of balance guide rings are the same, each balance guide ring is mainly formed by arranging a plurality of balance guide strips 7 at the circumferential side surface of the lower part of the impeller component at equal intervals along the same circumference, the plurality of balance guide strips 7 of the same balance guide ring are arranged on the same circumferential surface, axial guide grooves 11 are formed at intervals between the adjacent balance guide strips 7 of the same balance guide ring, and the arrangement of the axial guide grooves 11 of the adjacent balance guide rings is staggered along the circumferential direction; the interval between adjacent balance guide rings forms a tangential guide groove 10, and a plurality of tangential guide grooves 10 are arranged in parallel and at intervals.
The staggered circle center angle of the axial guide grooves 11 between the adjacent balance guide rings in staggered arrangement is more than or equal to 30 degrees, and the width w (w =0.6 mm) of the axial guide grooves 11 is less than or equal to 1/3 of the height h of the balance guide strips 7 1 (h 1 ＝2mm)；
The tangential channels 10 are at least 5To balance the height h of the guide strips 7 1 Greater than or equal to the height h of the tangential diversion trench 10 2 (h 2 =2 mm), the thickness h of the balancing guide strip 7 3 (h 3 =1 mm) is not more than the height h of the tangential guide groove 10 2 The height h1 and the thickness h3 of the balance guide strip 7, the height h2 of the tangential guide groove 10 and the width w of the axial guide groove 11 are adjusted according to different working points under different working conditions, so that the balance of the hydraulic axial force of the impeller has a wider working range.
The interval between the balance guide strip 7 and the inner wall of the pump cavity shell 3 is not more than 2mm.
The impeller assembly in the axial force automatic balancing device serves as a motor rotor, the axial force automatic balancing device is installed in a motor stator, and after the motor stator is electrified, a magnetic field formed between the motor stator and the motor rotor drives the motor rotor, so that the impeller assembly is suspended in the installation cavity after overcoming gravity and liquid impact force, and the impeller assembly rotates in the circumferential direction, and the axial force automatic balancing of liquid is achieved.
The application field of the axial force automatic balancing device is a magnetic suspension pump or a magnetic pump which works under the principle of a bearingless motor.
In the embodiment, the pressure of the leakage liquid at the bottom of the impeller is reduced through the pressure reduction balance cavity b, and the axial hydraulic resultant force F borne by the impeller is enabled to be matched with the action of the balance hole 9 h Reducing the axial magnetic resistance F of the magnetic suspension centrifugal pump under the high-power working condition z Axial hydraulic pressure F with impeller h Balance, and simultaneously, the hydraulic axial force can be automatically adjusted, so that an impeller in the magnetic suspension pump can stably run.
When the partially leaked high-pressure liquid flows downwards through the pressure reducing balance cavity b, the flow beam contraction effect exists, a plurality of damping circular rings are formed by the balance flow guide strips 7 and the inner wall of the pump cavity shell 3 in the flowing direction, when the liquid flows through the damping circular rings, partial pressure energy of the liquid is converted into kinetic energy, the flowing speed of the liquid is increased, the pressure of the liquid is reduced, meanwhile, when the liquid which is increased by the kinetic energy of the damping circular rings enters the tangential flow guide groove 10, the flowing area is suddenly increased, the flowing speed is reduced, and due to the viscous effect of the liquid, a certain vortex is formed in the tangential flow guide groove 10And partial energy is dissipated into heat energy, when the liquid enters the damping circular ring formed by the next-stage balance guide strip 7 and the inner wall of the pump cavity shell 3 again, the kinetic energy of the liquid cannot be restored into the original pressure energy again, so that when the liquid passes through the multistage balance guide strips 7 of the decompression balance cavity b, the pressure of the leaked liquid can be continuously reduced. Meanwhile, due to the viscous action of the liquid, when the liquid flows through the damping ring, friction force is generated in the process of contacting with the wall surface, and certain pressure loss is generated in the liquid. Because the axial diversion trenches 11 are distributed in a staggered manner at different heights, the plurality of axial diversion trenches 11 are equivalent to a plurality of damping gaps, a small part of liquid flowing into the tangential diversion trenches 10 can be transversely turbulent in the tangential diversion trenches 10, when the liquid flows into the axial diversion trenches 11 formed between the next-stage balance diversion strips 7, the liquid can also generate partial pressure loss, meanwhile, partial leakage liquid is in the transverse turbulent flow process, the friction loss is increased, meanwhile, the eddy dissipation of partial liquid is prolonged, and the pressure of the leakage liquid is further reduced. When part of leaked high-pressure liquid passes through the pressure reduction balance cavity b, the pressure of the liquid entering the cavity F at the bottom of the impeller is lower than that of the pump cavity E, primary pressure reduction is realized, meanwhile, the liquid entering the cavity F at the bottom of the impeller is communicated to a low-pressure area at the inlet of the impeller through a plurality of balance holes 9, secondary pressure reduction is realized, and axial hydraulic resultant force F borne by an impeller assembly is enabled to be reduced h The axial magnetic resistance Fz of the magnetic suspension centrifugal pump and the axial hydraulic pressure F of the impeller assembly under the working condition of high power (more than 4 KW) are reduced h And (4) balancing.
First hydraulic suspension balance chamber a and second hydraulic suspension balance chamber c in this embodiment are used for automatically regulated impeller subassembly's axial stability, leak liquid from pump chamber E upwards flows into first hydraulic suspension balance chamber a when partial high pressure, also downward flow through decompression balance chamber b simultaneously, when getting into second hydraulic suspension balance chamber c, because first hydraulic suspension balance chamber a and second hydraulic suspension balance chamber c are wedge ring, it has certain viscosity to leak liquid simultaneously, the liquid flow direction is by the osculum of big-end-up flow, because it has certain pressure to leak liquid itself again, so first, form hydraulic suspension in second hydraulic suspension balance chamber a, c, make impeller subassembly be the suspended state in the axial direction. When the impeller component works at a certain working point, when the impeller component is moved upwards by an axial force, the wedge-shaped small opening of the first hydraulic suspension balance cavity a is reduced, the liquid pressure in the first hydraulic suspension balance cavity a on the upper surface of the impeller component is increased, the wedge-shaped small opening in the second hydraulic suspension balance cavity c is increased, and the liquid pressure in the second hydraulic suspension balance cavity c is reduced, so that the impeller component is pushed back to the original position by the suspension force generated in the first hydraulic suspension balance cavity a. Similarly, when the impeller assembly works at a certain working point and is moved downwards by the axial force, the wedge-shaped small opening of the hydraulic suspension balance cavity c is reduced, the liquid pressure in the hydraulic suspension balance cavity c on the upper surface of the impeller assembly is increased, the wedge-shaped small opening in the first hydraulic suspension balance cavity a is increased, and the liquid pressure in the first hydraulic suspension balance cavity a is reduced, so that the impeller assembly is pushed back to the original position by the suspension force generated in the second suspension balance cavity c, the automatic adjustment of the axial force of the impeller assembly is realized, and the impeller can stably run in the high-power magnetic suspension pump.
Claims (6)
1. An automatic axial force balancing device of a magnetic suspension centrifugal pump under a high-power working condition is characterized by comprising a pump cover (1), a pump cavity shell (3), an impeller assembly and a balancing guide ring;
the pump cover (1) is fixedly arranged on the pump cavity shell (3), the interior of the pump cavity shell (3) is hollow and forms an installation cavity, an impeller assembly is arranged in the installation cavity of the pump cavity shell (3), and a plurality of circles of balance guide rings arranged at intervals are fixedly arranged on the circumferential side surface of the lower part of the impeller assembly; a pump cover convex ring (1-1) is arranged in the middle of the lower surface of the pump cover (1), and a gap is formed between the lower surface of the pump cover convex ring (1-1) and the upper surface of the impeller assembly; a pump cavity shell convex ring (3-1) is arranged in the middle of the lower bottom surface of the inner wall of the pump cavity shell (3), a gap is formed between the upper surface of the pump cavity shell convex ring (3-1) and the lower surface of the impeller assembly, and an impeller bottom cavity (F) is formed between the radial inner side of the pump cavity shell convex ring (3-1), the middle of the lower bottom surface of the inner wall of the pump cavity shell and the lower bottom surface of the impeller assembly; a first hydraulic suspension balance cavity (a) is formed between the upper surface of the impeller assembly and the lower surface of the pump cover convex ring (1-1), a second hydraulic suspension balance cavity (c) is formed between the lower surface of the impeller assembly and the upper surface of the pump cavity shell convex ring (3-1), a pump cavity (E) is formed between the circumferential side surface of the upper part of the impeller assembly, the inner wall of the pump cavity shell (3) and the lower surface of the pump cover (1), and a pressure reduction balance cavity (b) is formed between the circumferential side surface of the lower part of the impeller assembly, the balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell (3); an inlet pipeline (A) is formed in the middle of the pump cover (1), an outlet pipeline (B) is formed in one circumferential side face of the upper portion of the pump cavity shell (3), the inlet pipeline (A) and the outlet pipeline (B) are communicated with the mounting cavity, liquid flows in from the inlet pipeline (A), and flows out from the outlet pipeline (B) after being pressurized by the impeller assembly;
the multi-circle balance guide rings are identical in structure, each balance guide ring is mainly formed by arranging a plurality of balance guide strips (7) at equal intervals along the same circumference on the circumferential side surface of the lower part of the impeller assembly, axial guide grooves (11) are formed at intervals between adjacent balance guide strips (7) of the same balance guide ring, and the axial guide grooves (11) of the adjacent balance guide rings are arranged in a staggered mode; the interval between the adjacent balance guide rings forms a tangential guide groove (10), and a plurality of tangential guide grooves (10) are arranged in parallel.
2. The axial force automatic balancing device of the magnetic suspension centrifugal pump under the high-power working condition of claim 1, characterized in that the impeller assembly comprises a permanent magnet shell (4), a flow baffle plate (5), impeller blades (6) and permanent magnets (8);
an annular permanent magnet (8) is fixedly installed in the permanent magnet shell (4), a plurality of balance holes (9) which are axially arranged at equal intervals along the circumference are formed in the middle of the permanent magnet shell (4), and a plurality of circles of balance guide rings which are arranged at intervals are fixedly installed on the circumferential side surface of the permanent magnet shell (4); the upper surface of the permanent magnet shell (4) is fixedly provided with impeller blades (6), the impeller blades (6) are provided with center holes, a plurality of spiral flow channels which are uniformly distributed at intervals along the circumference are arranged in the impeller blades (6), all the spiral flow channels are arranged along the spiral direction of the same plane, and each spiral flow channel radially communicates the center holes of the impeller blades (6) with a peripheral pump cavity (E) on the periphery; a flow baffle plate (5) which is radially arranged is arranged in a central hole of the impeller blade (6), the flow baffle plate (5) is embedded in the central hole of the impeller blade (6) in a sealing manner, the middle part of the flow baffle plate (5) extends downwards and then is fixedly connected with the middle part of the permanent magnet shell (4), the central hole is divided into two parts by the flow baffle plate (5), the central hole in the upper surface of the flow baffle plate (5) is marked as an impeller upper central cavity (D), and the central hole in the lower surface of the flow baffle plate (5) is communicated with a balance hole (9);
the upper surface of an impeller blade (6) is used as the upper surface of an impeller assembly and forms a first hydraulic suspension balance cavity (a) with the lower surface of a pump cover convex ring (1-1), the lower surface of a permanent magnet shell (4) is used as the lower surface of the impeller assembly and forms a second hydraulic suspension balance cavity (c) with the upper surface of a pump cavity shell convex ring (3-1), and a pressure reduction balance cavity (b) is formed among the circumferential side surface of the permanent magnet shell (4), a balance guide ring on the circumferential side surface and the inner wall of the pump cavity shell (3);
liquid flows into an impeller upper central cavity (D) from an inlet pipeline (A), liquid in the impeller upper central cavity (D) flows into an impeller assembly in the axial direction and then flows into a pump cavity (E) from a plurality of internal spiral flow channels of impeller blades (6) after being blocked and guided by a flow blocking plate (5), most of liquid in the pump cavity (E) flows out of the pump cavity (E) through an outlet pipeline (B), the other part of liquid in the pump cavity (E) leaks upwards and downwards respectively, the liquid leaked upwards flows into the impeller upper central cavity (D) again through a first hydraulic suspension balance cavity (a), and the liquid leaked downwards flows into the impeller upper central cavity (D) again after sequentially passing through a pressure reduction balance cavity (B), a second hydraulic suspension balance cavity (c), an impeller bottom cavity (F), a balance hole (9) and a central hole in the lower surface of the flow blocking plate (5).
3. The axial force automatic balancing device of the magnetic suspension centrifugal pump under the high-power working condition as claimed in claim 1, characterized in that:
axial flow guidance between adjacent balancing flow guiding ringsThe staggered circle center angle of the staggered arrangement of the grooves (11) is more than or equal to 30 degrees, the width (w) of the axial diversion groove (11) is less than or equal to 1/3 of the height (h) of the balance diversion strip (7) 1 ）；
The number of the tangential diversion grooves (10) is at least 5, and the height (h) of the diversion strips (7) is balanced 1 ) Greater than or equal to the height (h) of the tangential diversion trench (10) 2 ) Balancing the thickness (h) of the guide strip (7) 3 ) Less than or equal to the height (h) of the tangential diversion trench (10) 2 ）；
The interval between the balance guide strips (7) and the inner wall of the pump cavity shell (3) is not larger than 2mm.
4. The axial force automatic balancing device of the magnetic suspension centrifugal pump under the high-power working condition of claim 1, which is characterized in that: the upper surface and the lower surface of the impeller component are the same in shape, and the upper surface and the lower surface of the impeller component are conical surfaces, so that the first hydraulic suspension balance cavity (a) and the second hydraulic suspension balance cavity (c) are both wedge-shaped circular rings.
5. The axial force automatic balancing device of the magnetic suspension centrifugal pump under the high-power working condition of claim 1, which is characterized in that: the impeller assembly in the axial force automatic balancing device is used as a motor rotor, the axial force automatic balancing device is installed in a motor stator, after the motor stator is electrified, a magnetic field formed between the motor stator and the motor rotor drives the motor rotor, so that the impeller assembly is suspended in the installation cavity after overcoming gravity and liquid impact force, and the impeller assembly rotates in the circumferential direction, and the axial force automatic balancing of liquid is realized.
6. The axial force automatic balancing device of the magnetic suspension centrifugal pump under the high-power working condition of claim 1, which is characterized in that: the application field of the axial force automatic balancing device is a magnetic suspension pump or a magnetic pump which works under the principle of a bearingless motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111021011.4A CN113883084B (en) | 2021-09-01 | 2021-09-01 | Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111021011.4A CN113883084B (en) | 2021-09-01 | 2021-09-01 | Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113883084A CN113883084A (en) | 2022-01-04 |
| CN113883084B true CN113883084B (en) | 2022-12-06 |
Family
ID=79011634
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111021011.4A Active CN113883084B (en) | 2021-09-01 | 2021-09-01 | Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113883084B (en) |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0240674B1 (en) * | 1986-04-08 | 1992-08-05 | Ebara Corporation | Pump |
| JP2003205030A (en) * | 2002-01-15 | 2003-07-22 | Mitsubishi Heavy Ind Ltd | Artificial cardiac pump |
| CN2869405Y (en) * | 2005-11-07 | 2007-02-14 | 上海东方泵业(集团)有限公司 | Axial force balance device for pump |
| EP2273124B1 (en) * | 2009-07-06 | 2015-02-25 | Levitronix GmbH | Centrifugal pump and method for compensating for the axial impulse in a centrifugal pump |
| CN101732769B (en) * | 2010-01-26 | 2011-10-05 | 浙江大学 | Implantable blood pump adopting driven suspension bearing |
| CN201705714U (en) * | 2010-07-06 | 2011-01-12 | 合肥皖化电机技术开发有限责任公司 | Motor for boiler water pump with load of thrust bearing thereof being reduced |
| CN105343950B (en) * | 2015-09-25 | 2017-09-22 | 济南大学 | A kind of artificial blood pump of use Hydrodynamic suspension bearing |
| CN205207206U (en) * | 2015-12-02 | 2016-05-04 | 湖南师范大学 | Miniature pump integral type magnetic drive pump based on axial motor drive |
| CN108223242B (en) * | 2017-12-05 | 2019-12-13 | 中海石油气电集团有限责任公司 | Axial force balance mechanism of FLNG hydraulic turbine and calculation method |
| CN209458197U (en) * | 2018-12-29 | 2019-10-01 | 米顿罗工业设备（上海）有限公司 | A kind of axial force balance structure of single-stage magnetic centrifugal pump |
| CN112963379A (en) * | 2020-12-11 | 2021-06-15 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Composite structure of inducer and centrifugal impeller |
-
2021
- 2021-09-01 CN CN202111021011.4A patent/CN113883084B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN113883084A (en) | 2022-01-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6129507A (en) | Method and device for reducing axial thrust in rotary machines and a centrifugal pump using same | |
| US6280157B1 (en) | Sealless integral-motor pump with regenerative impeller disk | |
| US5158440A (en) | Integrated centrifugal pump and motor | |
| US8221070B2 (en) | Centrifugal impeller with controlled force balance | |
| US7731476B2 (en) | Method and device for reducing axial thrust and radial oscillations and rotary machines using same | |
| CN105102823B (en) | Fluid machine and flow guide element for a fluid machine | |
| CN201265547Y (en) | Balancing type single-suction horizontal multiple-stage centrifugal pump | |
| CN108869379B (en) | Centrifugal pump sealing ring with axial guide vanes | |
| CN113137373B (en) | Magnetic suspension pump based on hydraulic balance principle | |
| CN113883084B (en) | Automatic axial force balancing device of magnetic suspension centrifugal pump under high-power working condition and application | |
| CN102434215B (en) | Outer-rotor fluid power machine | |
| CN108869384B (en) | Radial sealing ring of centrifugal pump with cylindrical guide vanes | |
| CN114001036B (en) | Miniature hydraulic suspension mechanical pump and assembly method thereof | |
| CN214533584U (en) | Sealing structure for centrifugal pump | |
| CN216306246U (en) | Centrifugal pump | |
| CN214577901U (en) | Water throwing groove sealing structure for centrifugal pump | |
| CN214499541U (en) | Dynamic sealing structure for centrifugal pump | |
| CN211900990U (en) | Impeller for multistage centrifugal pump and multistage centrifugal pump | |
| AU8907591A (en) | Integrated centrifugal pump and motor | |
| CN217462582U (en) | Electromechanical integrated guide vane type centrifugal pump with floating rotor | |
| CN110685922A (en) | Centrifugal liquid metal magnetic drive pump of no rotor | |
| CN214577915U (en) | Connecting cavity for centrifugal pump | |
| CN114060286B (en) | Two-stage centrifugal pump | |
| RU2238442C2 (en) | Method of and device for decreasing axial forces in rotary machines | |
| CN116857222B (en) | Impeller, pump head and impeller design method for magnetic suspension pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |