CN212343550U - Flywheel rotor system supported by vertical permanent magnet bearing and fluid dynamic pressure bearing - Google Patents
Flywheel rotor system supported by vertical permanent magnet bearing and fluid dynamic pressure bearing Download PDFInfo
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- CN212343550U CN212343550U CN202021721641.3U CN202021721641U CN212343550U CN 212343550 U CN212343550 U CN 212343550U CN 202021721641 U CN202021721641 U CN 202021721641U CN 212343550 U CN212343550 U CN 212343550U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
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Abstract
The utility model discloses a flywheel rotor system supported by a vertical permanent magnet bearing and a fluid dynamic pressure bearing, which comprises a flywheel rotor, a flywheel upper shaft, a flywheel lower shaft, an upper support structure arranged on the flywheel upper shaft, and a motor mechanism and a lower support mechanism arranged on the flywheel lower shaft; the upper supporting structure comprises a radial permanent magnet bearing inner ring and an outer ring, an upper extrusion film damper and an axial permanent magnet bearing which are sequentially sleeved; the motor mechanism comprises motor rotor magnetic steel, a motor stator iron core and a coil which are sequentially sleeved, and a motor outer wall heat dissipation water cavity is arranged outside the motor stator iron core and the coil; the lower support mechanism comprises a fluid dynamic pressure bearing and a shaft socket connected with the fluid dynamic pressure bearing, and the shaft socket is connected with the lower squeeze film damper. The utility model discloses squeeze film damper has all been disposed to the lower part on the rotor, combines good rotor dynamics parameter matching design, no matter two vibration modes to the rotor are through critical speed or earthquake impulse response all realized efficient vibration suppression, and the acceleration operation is very steady.
Description
Technical Field
The utility model belongs to flywheel rotor system, concretely relates to flywheel rotor system that vertical permanent magnet bearing and fluid dynamic pressure bearing supported.
Background
The application of energy storage technology in the aspects of energy conservation, stability and power supply quality of a power supply system is more and more important, and an energy storage flywheel is regarded as an important energy storage technology and is valued by countries in the world. Especially, the research and development and application of the flywheel continuously provide policy and fund support in China, so that the flywheel energy storage technology is greatly improved.
The design of the bearing is an important technical factor in flywheel research and development, the bearing technology adopted by the flywheel manufacturers at home and abroad at present uses the electromagnetic bearing to assist the permanent magnetic bearing, the mechanical bearing assists the permanent magnetic bearing as much, the URENCO adopts a support system with the upper part being the permanent magnetic bearing and the lower part being the fluid dynamic pressure bearing, and compared with the two support modes, the support system is a support system with smaller standby abrasion at present.
The largest application market of the energy storage flywheel is in an electric power system, and the electric power system has higher requirements on energy and power of the energy storage flywheel, the energy storage of the single energy storage flywheel is 50 kWh-1 MWh, the power is hundreds of kW-MW, and the flywheel technology with large energy, high power and low abrasion is increasingly important.
In response to the increasing demand of flywheel energy storage market, the patent publication of energy storage flywheels has also been shown to be soaring.
In the eighth European superconductor application Conference of 2007 (EUCAS 2007), R Viznechako 1, A V Velichko, Z Hong and T A Coombs, Journal of Physics: Conference Series 97 (2008) 012120 published an "Advantage of superconducting bearing in a commercial flyweight system" paper disclosing the detailed structure and technical parameters of a URENCO energy storage flywheel. The rotor height is 90cm, the outer diameter is 33cm, the inner diameter is 17cm, the rotor mass is 110kg, and the polar moment of inertia is 1.82kgm2The spiral groove ball bearing friction torque is 0.053Nm (where the main loss is the hysteresis loss of the stator core). The upper part of the flywheel is supported by a permanent magnet bearing, the upper part of the flywheel is not provided with a damper, the lower part of the flywheel is supported by a fluid dynamic pressure bearing, and an extrusion film damper is configured, so that a rotor supporting system combining the permanent magnet bearing and the fluid dynamic pressure bearing is formed.
Chinese utility model patent (CN 209730966U) "uses two stator brushless dc motor's flywheel energy storage device" rotor upper portion has used permanent magnet bearing, and the lower part has used fluid dynamic pressure bearing. However, the most important drawback of the utility model is that the upper part has no damper, corresponding to two modes of the rigid vibration of the rotor, namely, the first mode of translation (inverted pendulum) and the second mode of conical pendulum, and the squeeze film damper connected with the fluid dynamic pressure bearing seat at the lower part can only take the second conical pendulum mode with larger vibration energy into consideration, and no damping measure is taken for the first mode of translation. The first critical rotating speed of undamped forced vibration inevitably occurs in the speed increasing process, the rotor with large mass is slow in speed increasing, strong collision phenomena can occur, and the rotor can be damaged in serious cases. Meanwhile, according to typical seismic spectrum analysis, the flywheel rotor adopting the magnetic bearing has no obvious response to the seismic spectrum above 10Hz, and if the first-order modal frequency of the flywheel rotor falls within 10Hz, when the earthquake occurs, the radial vibration amplitude of the flywheel is large, and the possibility of rotor damage also becomes large. The disclosure of URENCO shows that the first modal frequency of the flywheel rotor is 10Hz and the second modal frequency is 25Hz, substantially avoiding the effects of earthquakes. The first-order modal frequency of the heavy rotor mainly depends on the radial rigidity of the upper permanent magnet bearing, and the first-order modal frequency of the rotor is improved to be above 10Hz, so that the possibility is almost eliminated, and the serious damage caused by an earthquake cannot be avoided.
SUMMERY OF THE UTILITY MODEL
The utility model provides a overcome the shortcoming that exists among the prior art and propose, its purpose provides the flywheel rotor system that vertical permanent magnet bearing and fluid dynamic pressure bearing supported.
The utility model discloses a realize through following technical scheme:
a flywheel rotor system supported by a vertical permanent magnet bearing and a fluid dynamic pressure bearing comprises a flywheel rotor, a flywheel upper shaft and a flywheel lower shaft, an upper supporting structure, a motor mechanism and a lower supporting mechanism, wherein the flywheel upper shaft and the flywheel lower shaft are respectively arranged at two ends of the flywheel rotor; the upper supporting structure comprises a radial permanent magnet bearing inner ring, a radial permanent magnet bearing outer ring, an upper extrusion film damper and an axial permanent magnet bearing which are sequentially sleeved from inside to outside; the motor mechanism comprises motor rotor magnetic steel, a motor stator iron core and a coil which are sequentially sleeved from inside to outside, and a motor outer wall heat dissipation water cavity is arranged outside the motor stator iron core and the coil; the lower support mechanism comprises a fluid dynamic pressure bearing arranged at the bottom end of the lower shaft of the flywheel and a shaft socket connected with the fluid dynamic pressure bearing, and the shaft socket is connected with the lower squeeze film damper.
In the above technical solution, the flywheel rotor is a columnar or disc-shaped structure without a through hole.
In the technical scheme, when the flywheel rotor is columnar, the ratio of the diameter moment of inertia to the pole moment of inertia of the flywheel rotor is greater than 1.4; when the flywheel rotor is in a disc shape, the ratio of the polar moment of inertia to the diametric moment of inertia of the rotor is greater than 1.4.
In the technical scheme, an upper mechanical protection bearing is arranged at one end of the flywheel upper shaft, which is far away from the flywheel rotor; and the middle part of the lower shaft of the flywheel is provided with a lower bidirectional mechanical protection bearing.
In the above technical solution, the lower bidirectional mechanical protection bearing is disposed between the motor mechanism and the lower support mechanism.
In the technical scheme, the motor rotor magnetic steel is in a HALBACH array form.
In the above technical scheme, when the horizontal positions of the magnetic centers of the motor rotor magnetic steel and the stator core are offset in the axial direction, the motor rotor magnetic steel is offset downwards.
In the above technical solution, the horizontal position of the upper end surface of the inner ring of the radial permanent magnet bearing is higher than the horizontal position of the upper end surface of the outer ring of the radial permanent magnet bearing.
In the technical scheme, the upper extrusion film damper is connected with the inner wall of the vacuum protection shell; the upper end face of the axial permanent magnet bearing is connected with a transition flange of the vacuum protection shell, and the lower end face of the axial permanent magnet bearing directly acts on the upper end face of the flywheel rotor.
In the above technical scheme, the heat dissipation water cavity on the outer wall of the motor is connected with the external cooling device through a pipeline.
The utility model has the advantages that:
the utility model provides a flywheel rotor system that tens ~ hundreds of kWh's vertical permanent magnet bearing and fluid dynamic pressure bearing supported has all disposed the squeeze film attenuator in the lower part on the rotor, combines good rotor dynamics parameter matching design, no matter has all realized efficient vibration suppression through critical speed or earthquake impulse response to two vibration modes of rotor, and the speed-raising operation is very steady.
Drawings
Fig. 1 is a schematic structural diagram of the flywheel energy storage device of the present invention.
Wherein:
1 upper mechanical protection bearing 2 axial permanent magnet bearing
3 upper extrusion film damper 4 radial permanent magnet bearing inner ring
5 radial permanent magnet bearing outer ring 6 flywheel rotor
7 motor rotor magnetic steel 8 motor stator core and coil
9 bidirectional mechanical protection bearing at lower part of outer wall heat dissipation water cavity 10 of motor
11 fluid dynamic pressure bearing 12 lower part squeeze film damper
13 flywheel upper shaft 14 flywheel lower shaft
15 axle sockets.
For a person skilled in the art, other relevant figures can be obtained from the above figures without inventive effort.
Detailed Description
In order to make those skilled in the art better understand the technical solution of the present invention, the following description is provided with the accompanying drawings and the detailed description of the technical solution of the flywheel rotor system supported by the vertical permanent magnet bearing and the fluid dynamic pressure bearing.
As shown in fig. 1, a flywheel rotor system supported by a vertical permanent magnet bearing and a fluid dynamic pressure bearing comprises a flywheel rotor 6, a flywheel upper shaft 13 and a flywheel lower shaft 14 which are respectively arranged at two ends of the flywheel rotor 6, an upper support structure arranged on the flywheel upper shaft 13, and a motor mechanism and a lower support mechanism arranged on the flywheel lower shaft 14; the upper supporting structure and the lower supporting mechanism are combined to form a flywheel rotor supporting system.
The upper supporting structure comprises a radial permanent magnet bearing inner ring 4, a radial permanent magnet bearing outer ring 5, an upper extrusion film damper 3 and an axial permanent magnet bearing 2 which are sequentially sleeved from inside to outside; the upper squeeze film damper 3 is connected with the inner wall of a vacuum protection shell (not shown); the upper end face of the axial permanent magnet bearing 2 is connected with a transition flange of the vacuum protection shell, and the lower end face of the axial permanent magnet bearing directly acts with the upper end face of the flywheel rotor 6 to form part of axial unloading force. The radial permanent magnet bearing inner ring 4 and the radial permanent magnet bearing outer ring 5 are two independent magnetic bearings and respectively complete the axial and radial supporting functions of the upper part of the rotor. The radial permanent magnet bearing inner ring 4 is adjusted and displaced delta mm on the horizontal position of the upper end face of the radial permanent magnet bearing outer ring 5 to form upward axial thrust, and partial axial unloading force is formed.
The motor mechanism comprises a motor rotor magnetic steel 7, a motor stator iron core and a coil 8 which are sequentially sleeved from inside to outside, and the motor rotor magnetic steel 7, the motor stator iron core and the coil 8 form a permanent magnet synchronous motor/generator. The horizontal position of the magnetic centers of the rotor magnetic steel 7 and the stator iron core 8 of the motor can generate axial force when the magnetic centers are axially deviated, and the preferential installation position is that the rotor magnetic steel is deviated downwards, so that partial axial supporting force of the rotor can be provided. The motor mechanism is arranged close to the flywheel rotor 6.
The motor stator core and the coil 8 are externally provided with a motor outer wall heat dissipation water cavity 9, and the motor outer wall heat dissipation water cavity 9 is connected with an external cooling device through a pipeline to form a complete cooling circulation system.
The lower support mechanism comprises a hydrodynamic bearing 11 arranged at the bottom end of a flywheel lower shaft 14 and a shaft socket 15 connected with the hydrodynamic bearing, and the hydrodynamic bearing and the shaft socket are combined to form a complete hydrodynamic bearing. The shaft pocket 15 is connected to the lower squeeze film damper 12. The fluid dynamic pressure bearing 11 comprises a connecting rod and a small ball connected with the bottom end of the connecting rod, and a spiral groove is arranged on the small ball. The shaft socket 15 is a smooth spherical surface.
The flywheel rotor 6 is a columnar or disc-shaped structure without a through hole, and is made of a ferromagnetic material or the surface of the ferromagnetic material is provided with a composite material coating. The flywheel rotor 6, the upper flywheel shaft 13 and the lower flywheel shaft 14 are coaxially arranged.
When the flywheel rotor 6 is columnar, the ratio of the diameter moment of inertia to the pole moment of inertia of the flywheel rotor 6 is greater than 1.4; when the flywheel rotor 6 is disk-shaped, the ratio of the polar moment of inertia to the diametric moment of inertia of the sub-rotor of the flywheel rotor 6 is greater than 1.4.
An upper mechanical protection bearing 1 is arranged at one end of the flywheel upper shaft 13 far away from the flywheel rotor 6; the middle part of the flywheel lower shaft 14 is provided with a lower bidirectional mechanical protection bearing 10, and the lower bidirectional mechanical protection bearing 10 is used for providing displacement protection of the flywheel rotor 6 in two directions, namely the axial direction and the radial direction.
The lower bidirectional mechanical protection bearing 10 is arranged between the motor mechanism and the lower support mechanism.
The motor rotor magnetic steel 7 adopts an HALBACH array form.
When the horizontal positions of the magnetic centers of the motor rotor magnetic steel 7 and the stator iron core 8 are deviated in the axial direction, the motor rotor magnetic steel 7 is deviated downwards.
The utility model discloses a theory of operation:
the utility model relates to a vertical axle flywheel rotor, upper portion adopt independent radial permanent magnet bearing, axial permanent magnet bearing as the upper portion axial and the radial support of flywheel rotor, and the lower part adopts fluid dynamic pressure bearing to support, the utility model discloses in energy storage flywheel rotor system arranges vacuum protection shell in, the flywheel rotor operation is under the vacuum condition, and upper portion permanent magnet bearing supports for contactless, does not basically have the friction. The lower fluid dynamic pressure bearing works in a liquid friction state, the friction torque is small, and the combination of the upper bearing and the lower bearing forms a low-abrasion flywheel rotor supporting system.
The radial permanent magnet bearing outer ring at the upper end of the flywheel rotor is connected with the upper extrusion die damper, and the fluid dynamic pressure bearing and the shaft socket at the lower end of the rotor are connected with the lower extrusion die damper, so that a damping system of the flywheel rotor is formed, and the stable operation of the flywheel rotor is ensured.
The utility model discloses a two strong points all have configured the squeeze film attenuator about the flywheel rotor, and the optimal design of rotor dynamics parameter can make the flywheel rotor through critical speed, or all can suppress the response amplitude effectively when meeting with the earthquake and strikeing, has guaranteed that the flywheel rotor has reliable high stability.
The utility model discloses an in the design of rotor dynamics stability, when adopting column flywheel rotor structure (be not limited to column, disc structure), the diameter inertia of requiring the flywheel rotor is greater than 1.4 with utmost point inertia's ratio, when adopting disc flywheel rotor structure, requires the utmost point inertia of flywheel rotor and diameter inertia's ratio to be greater than 1.4.
The utility model discloses a permanent magnet bearing on flywheel rotor upper portion has adopted independent axial magnetic bearing and independent radial magnetic bearing, according to three-dimensional finite element magnetic bearing simulation design result analysis, adopt a permanent magnet bearing who compromises axial and radial support in the rotor upper end, will consume the magnetic material more than one time than adopting independent radial magnetic bearing and axial magnetic bearing, manufacturing cost is very high, in order to satisfy radial rigidity and axial rigidity's demand simultaneously, structural design becomes complicated. The independent radial permanent magnet bearing and the independent axial permanent magnet bearing can be separately and independently designed to respectively meet the respective rigidity design requirements.
The flywheel rotor is made of ferromagnetic material or has composite material coating on its surface, and the upper end face of the flywheel rotor and the axial permanent magnet bearing directly generate acting force. The flywheel rotor is made of forged steel, the appearance of the flywheel rotor is a simple shaft piece, the machining process is simple, the manufacturing cost is low, and the process expansion difficulty is low when a large-scale rotor is manufactured.
The utility model provides high flywheel rotor's energy density (Wh/kg), can realize tens ~ hundreds of kWh's energy storage flywheel design. Because the energy storage of the flywheel is in direct proportion to the shape coefficient, the shape coefficient of the rotor structure with the through hole is approximately 0.3, the rotor structure without the middle through hole has the shape coefficient of approximately 0.6, and the energy storage of the rotor without the through hole is twice that of the rotor with the through hole. The utility model discloses a no through-hole structure's flywheel rotor has improved the energy density of rotor.
The utility model discloses a flywheel rotor's flywheel has all set up mechanical protection bearing from top to bottom, and wherein the mechanical protection bearing of lower extreme has radial, axial bidirectional thrust protect function, and the radial thrust protect function of bearing is used for resisting the sudden impact vibration of rotor, and the axial thrust function of bearing plays very important effect when installation fluid dynamic pressure bearing, protection lower part attenuator and transportation locking rotor.
The utility model discloses omitted hardware such as all required electro-magnets of active control, sensor, controller, power amplifier, the flywheel rotor has constituted stable operation system with permanent magnetic bearing, fluid dynamic pressure bearing, extrusion film attenuator, and fluid dynamic pressure bearing is the maintenance-free operation for a long time. Compared with a system with active control, the system has the advantages of greatly reducing manufacturing cost and having high operation stability.
The motor rotor magnetic steel, the motor stator core and the coil form a permanent magnet synchronous motor/generator, and the motor rotor magnetic steel structure preferably adopts an HALBACH array form and can be designed into a high-power motor/generator. The horizontal position of the magnetic centers of the rotor magnetic steel and the stator core of the motor can generate axial force when the magnetic centers are axially deviated, and the preferential installation position is that the rotor magnetic steel is deviated downwards, so that partial axial supporting force of the rotor can be provided.
The utility model provides a flywheel rotor system that radial permanent magnet bearing, axial permanent magnet bearing and fluid dynamic pressure bearing combination supported, radial permanent magnet bearing, fluid dynamic pressure bearing all combine together with the squeeze film attenuator, and the flywheel rotor is epaxial distribution motor rotor magnet steel of dress down, constitutes PMSM with stator core, has constituted high stability, big energy, high-power, low wearing and tearing flywheel energy memory, the utility model discloses flywheel energy memory has very high stability, simple structure, low in manufacturing cost, and the operation of non-maintaining, market competition is very strong.
It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The applicant states that the above description is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto, and those skilled in the art should understand that any changes or substitutions easily conceivable by those skilled in the art within the technical scope of the present invention are within the protection scope and the disclosure scope of the present invention.
Claims (10)
1. The utility model provides a flywheel rotor system that vertical permanent magnet bearing and fluid dynamic pressure bearing supported, includes flywheel rotor (6) and sets up respectively in flywheel upper shaft (13) and flywheel lower shaft (14) at flywheel rotor (6) both ends, its characterized in that: the device also comprises a motor mechanism, an upper supporting structure arranged on the upper shaft (13) of the flywheel and a lower supporting mechanism arranged on the lower shaft (14) of the flywheel;
the upper supporting structure comprises a radial permanent magnet bearing inner ring (4), a radial permanent magnet bearing outer ring (5), an upper extrusion film damper (3) and an axial permanent magnet bearing (2) which are sequentially sleeved from inside to outside;
the motor mechanism comprises a motor rotor magnetic steel (7) and a motor stator core and coil (8) which are sequentially sleeved from inside to outside, and a motor outer wall heat dissipation water cavity (9) is arranged outside the motor stator core and the coil (8);
the lower support mechanism comprises a fluid dynamic pressure bearing (11) arranged at the bottom end of a flywheel lower shaft (14) and a shaft socket (15) connected with the fluid dynamic pressure bearing, and the shaft socket (15) is connected with the lower extrusion film damper (12).
2. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: the flywheel rotor (6) is of a columnar or disc-shaped structure without a through hole.
3. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 2, wherein: when the flywheel rotor (6) is columnar, the ratio of the diameter moment of inertia to the pole moment of inertia of the flywheel rotor (6) is greater than 1.4; when the flywheel rotor (6) is in a disc shape, the ratio of the polar moment of inertia to the diametric moment of inertia of the rotor (6) is greater than 1.4.
4. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: an upper mechanical protection bearing (1) is arranged at one end of the flywheel upper shaft (13) far away from the flywheel rotor (6); the middle part of the flywheel lower shaft (14) is provided with a lower bidirectional mechanical protection bearing (10), and the lower bidirectional mechanical protection bearing (10) is arranged adjacent to the lower support mechanism.
5. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: the motor mechanism is arranged between the upper supporting structure and the top surface of the flywheel rotor (6) or between the lower supporting mechanism and the bottom surface of the flywheel rotor (6).
6. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: the motor rotor magnetic steel (7) adopts an HALBACH array form.
7. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: when the horizontal position of the magnetic centers of the motor rotor magnetic steel (7) and the stator core deviates in the axial direction, the motor rotor magnetic steel (7) deviates downwards.
8. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: the horizontal position of the upper end face of the radial permanent magnet bearing inner ring (4) is higher than that of the upper end face of the radial permanent magnet bearing outer ring (5).
9. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: the upper extrusion film damper (3) is connected with the inner wall of the vacuum protection shell; the upper end face of the axial permanent magnet bearing (2) is connected with a transition flange of the vacuum protection shell, and the lower end face of the axial permanent magnet bearing directly acts on the upper end face of the flywheel rotor (6).
10. The vertical permanent magnet bearing and hydrodynamic bearing supported flywheel rotor system of claim 1, wherein: and the heat dissipation water cavity (9) on the outer wall of the motor is connected with an external cooling device through a pipeline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021721641.3U CN212343550U (en) | 2020-08-18 | 2020-08-18 | Flywheel rotor system supported by vertical permanent magnet bearing and fluid dynamic pressure bearing |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202021721641.3U CN212343550U (en) | 2020-08-18 | 2020-08-18 | Flywheel rotor system supported by vertical permanent magnet bearing and fluid dynamic pressure bearing |
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| CN212343550U true CN212343550U (en) | 2021-01-12 |
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| CN202021721641.3U Active CN212343550U (en) | 2020-08-18 | 2020-08-18 | Flywheel rotor system supported by vertical permanent magnet bearing and fluid dynamic pressure bearing |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114412963A (en) * | 2022-01-27 | 2022-04-29 | 中国长江三峡集团有限公司 | Radial vibration isolation device of high-temperature superconducting magnetic suspension flywheel |
| CN114448161A (en) * | 2022-01-27 | 2022-05-06 | 中国长江三峡集团有限公司 | High-temperature superconducting magnetic suspension flywheel with axial vibration isolation function |
-
2020
- 2020-08-18 CN CN202021721641.3U patent/CN212343550U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114412963A (en) * | 2022-01-27 | 2022-04-29 | 中国长江三峡集团有限公司 | Radial vibration isolation device of high-temperature superconducting magnetic suspension flywheel |
| CN114448161A (en) * | 2022-01-27 | 2022-05-06 | 中国长江三峡集团有限公司 | High-temperature superconducting magnetic suspension flywheel with axial vibration isolation function |
| CN114412963B (en) * | 2022-01-27 | 2023-07-14 | 中国长江三峡集团有限公司 | Radial vibration isolation device of high-temperature superconductive magnetic suspension flywheel |
| CN114448161B (en) * | 2022-01-27 | 2023-10-13 | 中国长江三峡集团有限公司 | High-temperature superconductive magnetic suspension flywheel with axial vibration isolation function |
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