CN112615471A - Flywheel rotor assembly for energy storage flywheel - Google Patents
Flywheel rotor assembly for energy storage flywheel Download PDFInfo
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- CN112615471A CN112615471A CN202011516522.9A CN202011516522A CN112615471A CN 112615471 A CN112615471 A CN 112615471A CN 202011516522 A CN202011516522 A CN 202011516522A CN 112615471 A CN112615471 A CN 112615471A
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/02—Additional mass for increasing inertia, e.g. flywheels
- H02K7/025—Additional mass for increasing inertia, e.g. flywheels for power storage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
- F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
- F16F15/3156—Arrangement of the bearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/08—Structural association with bearings
- H02K7/09—Structural association with bearings with magnetic bearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
- H02K2213/03—Machines characterised by numerical values, ranges, mathematical expressions or similar information
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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
Abstract
A flywheel rotor component for an energy storage flywheel relates to the technical field of energy storage flywheels, the invention designs an energy storage disc (1) and a main shaft (6) into a single disc bias structure in an integrated manner, a right-end radial magnetic bearing rotor (2) and a left-end radial magnetic bearing rotor (5) which are composed of silicon steel sheets at two ends of the main shaft form a supporting part, under the working state, the flywheel rotor component leans against the right end radial magnetic bearing rotor and the left end radial magnetic bearing rotor at the two ends to elastically support and do vertical rotary motion, the flywheel rotor is reasonably simplified into a rotating structure consisting of the mass-free elastic shaft and the rigid thin disc according to the structural characteristics of the flywheel rotor, reference basis is provided for structural design of other parts of the energy storage flywheel, assistance is provided for industrialization and productization of the energy storage flywheel, and the flywheel rotor has the characteristics of simple structure, convenience in manufacturing and the like, and is suitable for large-scale popularization and application.
Description
Technical Field
The invention relates to the technical field of energy storage flywheels, in particular to a flywheel rotor assembly for an energy storage flywheel.
Background
As is known, the flywheel energy storage technology has been applied to the fields of power grid frequency modulation, peak clipping and valley filling, wind power and photovoltaic power generation grid connection, light rail braking kinetic energy regeneration, Uninterruptible Power Supply (UPS), high power pulse power supply, satellite energy storage/attitude control, and the like of a power system, and developed countries such as the united states, germany, japan, and the like have many developments and applications of the flywheel energy storage technology. The frequency conversion speed regulation flywheel energy storage power generation system with the maximum capacity in the world is manufactured in Japan (the capacity is 26.5MVA, the voltage is 1100V, the rotating speed is 510690r/min, and the rotating inertia is 710 t.m 2). The university of maryland, usa, has also developed a 24kwh electromagnetically levitated flywheel system for electrical peak shaving. The flywheel weighs 172.8kg, the working rotating speed range is 11,610-46,345 rpm, the destruction rotating speed is 48,784rpm, the system output constant voltage is 110V and 240V, and the whole process efficiency is 81%. Economic analysis showed that operating for 3 years can recover the full cost. Flywheel energy storage technology has matured in the united states and they have produced a device with energy losses of up to 0.1% per hour at idle. The research on the flywheel energy storage system of the high-temperature superconducting magnetic suspension bearing is being developed by the French national research center in Europe, the German institute of physical high technology, and the Italy SISE.
The research of China in the aspect of flywheel energy storage starts late, the technical difficulty of flywheel energy storage is mainly focused on the aspects of rotor materials, manufacturing, electromagnetic bearings and the like at present, except that colleges and universities such as Qinghua university and the like have some research and progress in the aspects of rotors and electromagnetic bearings, some enterprises have the capability of producing related products after purchasing foreign companies, and the technology is supported by foreign technology teams seriously, so that the weaknesses of the companies in the aspect of autonomous technology are caused, and some materials are also required to be imported seriously, hidden dangers are buried for later-period actual product operation, maintenance and the like.
Therefore, it is important to provide a flywheel energy storage technology with fully proprietary intellectual property rights, and in the flywheel energy storage technology, a flywheel rotor assembly is one of the key components, so that it has been a long-term technical appeal for those skilled in the art how to provide a flywheel rotor assembly for an energy storage flywheel.
Disclosure of Invention
In order to overcome the defects in the background art, the invention provides the flywheel rotor assembly for the energy storage flywheel, provides a reference basis for the structural design of other parts of the energy storage flywheel, provides help for industrialization and productization of the energy storage flywheel and the like.
In order to achieve the above purpose, the invention adopts the following technical scheme:
a flywheel rotor assembly for an energy storage flywheel comprises an energy storage disc and a spindle, wherein a left-end radial sensor detection ring is sleeved on the outer edge face of the left end of the spindle, a left-end radial magnetic bearing rotor is sleeved on the outer edge face of the spindle on the right side of the left-end radial sensor detection ring, a motor rotor is sleeved on the outer edge face of the spindle on the right side of the left-end radial magnetic bearing rotor, the energy storage disc is arranged on the outer edge face of the spindle on the right side of the motor rotor, a right-end radial magnetic bearing rotor is sleeved on the outer edge face of the spindle on the right side of the energy storage disc, and a right-end radial sensor detection ring is sleeved on the outer edge face of the spindle on the right side of the right-end radial magnetic bearing rotor to form the flywheel rotor assembly for the energy.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the diameter of the energy storage disc is 600mm, and the width of the energy storage disc is 172 mm.
A chamfer is arranged between the energy storage disc and the main shaft of the flywheel rotor assembly for the energy storage flywheel, and the size of the chamfer is R25 mm.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the diameter of the main shaft is phi 150mm, and the length of the main shaft is 1400 mm.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the right-end radial magnetic bearing rotor and the left-end radial magnetic bearing rotor are made of concentric circular silicon steel sheets, and the inner edge surfaces of the right-end radial magnetic bearing rotor and the left-end radial magnetic bearing rotor are sleeved with the outer edge surface of the main shaft in an interference mode.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the motor rotor is of a tile-shaped structure and is directly attached to the outer edge surface of the main shaft, and the outer surface of the motor rotor is wound by carbon fiber prestress.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the energy storage disc and the main shaft are made of HHE1000 or 35 CrMnSiA.
The flywheel rotor assembly for the energy storage flywheel is characterized in that the HHE1000 is made of 4340 high-strength steel serving as a base material, and a material obtained by adjusting the proportion of rare metal elements has high strength and certain toughness.
The flywheel rotor assembly for the energy storage flywheel has the density of 7700 kg x m of 35CrMnSiA3The elastic modulus is 210GPa, the Poisson ratio is 0.35, the yield strength is 900MPa, and the tensile strength is 1024 MPa.
By adopting the technical scheme, the invention has the following advantages:
the invention designs the energy storage disc and the main shaft into a single disc bias structure, the two ends of the main shaft form a supporting part by the right-end radial magnetic bearing rotor and the left-end radial magnetic bearing rotor which are composed of silicon steel sheets, under the working state, the flywheel rotor assembly is supported by the right-end radial magnetic bearing rotor and the left-end radial magnetic bearing rotor at the two ends to do vertical rotary motion by elastic support, the flywheel rotor is reasonably simplified into a rotary structure composed of a non-mass elastic shaft and a rigid thin disc according to the structural characteristics of the flywheel rotor, reference is provided for the structural design of other parts of the energy storage flywheel, and help is provided for industrialization and productization of the energy storage flywheel.
Drawings
FIG. 1 is a schematic perspective view of the present invention;
FIG. 2 is a grid division diagram of the present invention;
FIG. 3 is a first order natural mode in the present invention;
FIG. 4 is a second order natural mode in the present invention;
FIG. 5 is a third order natural mode in the present invention;
FIG. 6 is a fourth order natural mode in accordance with the present invention;
FIG. 7 is a flywheel rotor finite element model in accordance with the present invention;
FIG. 8 is a Campbell diagram according to the present invention;
FIG. 9 is a rotor translational modal shape of the present invention;
FIG. 10 is a rotor rocking mode shape of the present invention;
FIG. 11 is a first order bending mode shape (oxz plane) of the rotor according to the present invention;
FIG. 12 shows the first order bending mode of the rotor (oyz plane) in the present invention;
FIG. 13 is a graph of the displacement response of a rotor shaft under unbalanced force excitation in the present invention;
FIG. 14 is a diagram of the locus of the translational motion of the rotating shaft in the present invention;
FIG. 15 is a diagram showing the swing trajectory of the rotary shaft in the present invention;
FIG. 16 is a trace diagram of a first order bend in the spindle of the present invention;
in the figure: 1. an energy storage disk; 2. a right-hand radial magnetic bearing rotor; 3. a right-end radial sensor detection ring; 4. a left end radial sensor detection ring; 5. a left-end radial magnetic bearing rotor; 6. a main shaft; 7. a rotor of an electric machine.
Detailed Description
The present invention will be explained in more detail by the following examples, which are not intended to limit the invention;
it should be noted that the directions or positional relationships indicated by "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", etc., used in describing the structure of the present invention are based on the directions or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and thus, should not be construed as limiting the present invention.
The flywheel rotor assembly for an energy storing flywheel of the present invention as described with reference to figure 1,the energy storage disc comprises an energy storage disc 1 and a spindle 6, the diameter of the spindle 6 is phi 150mm, the length of the spindle 6 is 1400mm, a left-end radial sensor detection ring 4 is sleeved on the outer edge surface of the left end of the spindle 6, a left-end radial magnetic bearing rotor 5 is sleeved on the outer edge surface of the right spindle 6 of the left-end radial sensor detection ring 4, a motor rotor 7 is sleeved on the outer edge surface of the right spindle 6 of the left-end radial magnetic bearing rotor 5, the motor rotor 7 is of a tile-shaped structure and directly attached to the outer edge surface of the spindle 6, the outer surface of the motor rotor 7 is wound by carbon fiber prestress, the energy storage disc 1 is arranged on the outer edge surface of the right spindle 6 of the motor rotor 7, the energy storage disc 1 and the spindle 6 are made of HHE1000 or 35CrMnSiA, the HHE1000 is made of 4340 high-strength steel, and a material obtained by adjusting the proportion of rare metal elements has higher strength, the 35CrMnSiA has a certain toughness, and the density of the 35CrMnSiA is 7700 kg x m3The elastic modulus is 210GPa, the Poisson ratio is 0.35, the yield strength is 900MPa, and the tensile strength is 1024 MPa; the diameter of the energy storage disc 1 is phi 600mm, the width is 172mm, a chamfer is arranged between the energy storage disc 1 and the main shaft 6, the size of the chamfer is R25mm, the outer edge surface of the main shaft 6 on the right side of the energy storage disc 1 is sleeved with the right-end radial magnetic bearing rotor 2, in the implementation process, the right-end radial magnetic bearing rotor 2 and the left-end radial magnetic bearing rotor 5 adopt concentric circular silicon steel sheets, the inner edge surfaces of the right-end radial magnetic bearing rotor 2 and the left-end radial magnetic bearing rotor 5 are sleeved with the outer edge surface of the main shaft 6 in an interference mode, and the outer edge surface of the main shaft 6 on the right side of the right-end radial magnetic bearing rotor 2 is sleeved with the right-end radial sensor detection ring 3 to form the flywheel rotor assembly.
In practice, the simulation analysis of the present invention is as follows:
1. and (3) analyzing the stress of a wheel body formed by the energy storage disc 1 and the main shaft 6:
the material, the structure size and the structure strength of the wheel body are mainly considered in the structural design of the wheel body.
The wheel body material is 35CrMnSiA, and the corresponding parameters are as follows:
in the structural design of the wheel body, the inner rotor and the outer rotor of the motor, and the structural form and the size of each pressure ring are comprehensively considered.
2. Rotor assembly modal analysis:
the flywheel rotor portion is constructed as shown in figure 1 in accordance with the overall design, and as can be seen from figure 1, the rotor assembly is profiled in the form of a large central hub and elongate shafts at each end. The rotor belongs to the slender shaft class, and the flywheel rotor axial length is: 1400mm and a maximum outer diameter of 600 mm. In order to reduce the interference of the radial unbalance amount on the axial stability, the ratio of the polar moment of inertia to the equatorial moment of inertia is ensured to be less than 0.707.
The right-end radial magnetic bearing rotor 2 and the left-end radial magnetic bearing rotor 5 adopt concentric circular silicon steel sheets, and the inner diameter and the main shaft 6 are installed in a small interference mode. The magnetic steel of the motor rotor 7 is of a tile-shaped structure and is directly attached to the main shaft 6, and the outer surface of the magnetic steel is wound by carbon fiber prestress. And after the whole wheel body is processed, the whole wheel body is subjected to overall dynamic balance, and the dynamic balance grade is required to be superior to G0.4.
The wheel body material can also be HHE1000, and the material is obtained by using 4340 high-strength steel as a base material and adjusting the proportion of some rare metal elements in a steel mill, and has high strength and certain toughness. Flywheel rotor assembly weight: 290.5 kg. Polar moment of inertia: 3.78, equatorial moment of inertia: 19.55, and the polar red ratio is 0.193 (less than 0.707). The position of the mass center: on the central axis 540.6mm from the lower end. Maximum linear velocity at 10500 rpm: 427.3 m/s.
Because the 5-DOF magnetic bearing is adopted to support the flywheel rotor, and the magnetic bearing force constraint is flexible constraint, the flywheel rotor is calculated according to an unconstrained state when the rotor mode is calculated.
1) Modeling of the rotor assembly:
a three-dimensional model of the rotor assembly is shown in figure 1.
2) Grid division:
the established rotor assembly model is introduced into analysis software for meshing, tetrahedral and hexahedral units are adopted for partitioning, the result of meshing is shown in fig. 2, and the model is divided into 106110 nodes and 39701 units.
Through calculation, the natural frequency and the mode of the rotor assembly are obtained, and are shown in the following table:
natural frequency and mode of rotor assembly
As can be seen from the above table, the natural frequency of the rotor assembly can meet the design requirements.
The natural modes of the 1-4 order rotor assembly are shown in fig. 3, 4, 5 and 6, respectively.
Because the 5-freedom-degree magnetic suspension structure is adopted for supporting, the supporting force of the magnetic bearing is flexible support, and rigid constraint is not formed on the rotor, so that the supporting force of the magnetic bearing does not influence the vibration mode of the flywheel rotor. The flywheel rotor part and the flywheel rotor assembly are different in that the flywheel rotor part is provided with parts such as a magnetic bearing rotor, a motor rotor and the like, and the assembling interface between the parts is complex, so that finite element analysis is not facilitated. For this purpose, the modes of the flywheel rotor parts and the flywheel rotor assembly (the parts are connected by GLUE) are calculated separately.
The first 4-order vibration mode frequencies are respectively about 351.4Hz, 351.5Hz, 750.6Hz and 1370.2Hz, and the corresponding flywheel rotation speeds are 21084rpm, 21090rpm, 59400rpm and 81660 rpm. The 351.4Hz and 351.5Hz frequencies are of the first order bending matrix type. The 750.6Hz frequency is an axial rotation matrix. The 1370.2Hz frequency is a second order bending matrix type.
From the above analysis, the flywheel rotor assembly has no resonance frequency point between 8000 rpm-10500 rpm (corresponding to 133.3 Hz-175 Hz) of the charging and discharging normal working speed, so that the rotor is a rigid rotor in the working interval, and the control of the magnetic bearing is favorable.
3. Calculating the critical rotating speed of the rotor assembly:
the energy storage flywheel rotor is of a single disc offset structure, the length of a main shaft 6 is 1400mm, the diameter of an energy storage disc 1 is 600mm, the magnetic bearing supporting parts at two ends are composed of metal laminations, and the rated working rotating speed is 8000-10500 rpm. The finite element of the rotor is established by using ANSYS software, the rotor model adopts SOLID272 axisymmetric entity units, and the grid division is shown in FIG. 7.
The supporting positions of the magnetic bearings at the two ends of the flywheel rotor adopt an elastic supporting mode of a COMBIN14 spring unit equivalent magnetic bearing. And loading the rotor with a rotating speed of 0-20000 rpm. Opening the Coriolis Effect (Coriolis Effect), extracting the first 4-order modal frequency and mode shape by adopting a Reduced Damped method, solving the critical rotating speed of the rotor under different support stiffness through APDL programming, and calculating the following results:
calculation of the critical rotational speed
At a support stiffness of 5X 104 N/m to 5X 107Within the range of N/m, the influence of the rigidity of the magnetic bearing on the critical rotating speed increases along with the increase of the rigidity of the magnetic bearing, and the critical rotating speed of the rotor also increases. The stiffness of the magnetic bearing can be adjusted to tune the natural frequency of vibration of the rotor away from unwanted resonances.
As shown in FIG. 8, the support stiffness was 5X 105Campbell Diagram at N/m (Campbell Diagram). The intersection point of the vortex frequency curves (BW stable and FW stable) and the straight line (F =1 × spin) of the rotational frequency is the critical rotational speed of the rotor, and the first-order critical rotational speed, the second-order critical rotational speed and the third-order critical rotational speed (namely the first-order bending critical rotational speed) respectively correspond to the intersection point from low to high.
Through the vibration mode (figure 9) corresponding to the first-order critical rotating speed of the rotor, the rotor can be seen to do radial translation, and the radial displacement of the left end is smaller than that of the right end. The vibration mode (fig. 10) corresponding to the second-order critical rotation speed of the rotor is a radial swing generated by the swing mode of the rotor, and basically takes the disc as the center, and the deviation distance of the left end is greater than that of the right end. Fig. 11 and 12 correspond to the mode shapes of the third-order critical rotational speed, which respectively show the first-order bending modes of the rotor in two different planes, and in the campbell diagram 8, the reverse whirling and the forward whirling of the rotor caused by the first-order bending modes correspond to each other.
The first-order and second-order critical rotation speeds of the rotor can be seen as rigid vibration of the rotor through the vibration mode corresponding to the critical rotation speed, and the third-order critical rotation speed is flexible vibration of bending of the rotor. When the energy storage flywheel is designed, the working rotating speed range should avoid the first-order and second-order rigid critical rotating speeds and not exceed the third-order bending critical rotating speed. In practical design, the maximum working rotating speed of the rotor is less than the bending critical rotating speed, so that the rotor is ensured to be a rigid rotor and is prevented from being interfered by the critical rotating speed. The maximum working speed of the energy storage flywheel is 10500rpm which is less than the third-order bending critical speed 13238 rpm, so the setting of the speed of the flywheel is reasonable.
4. Calculation of imbalance response:
the rotor model adopts BEAM188 unit modeling, and the COMBIN214 unit is used for supporting the rotor, and the supporting rigidity is 1 x 106N/m. Applying 1.88X 10 at the center of the rotor-4N imbalance force. And carrying out harmonic response analysis on the rotor unbalance response by using a complete method. Setting the excitation of the unbalanced forces in synchronism with the rotor frequency rotation, assigning 500 substeps for the execution of the loading step, defining a frequency range for harmonic analysis of 0 to 500Hz, by command<CORIOLIS>The coriolis effect is turned on and then solved for. And drawing a displacement response diagram of three points (the upper radial magnetic bearing support position, the rotor center position and the lower radial magnetic bearing support position) on the rotating shaft under the excitation of unbalance in the frequency conversion of 0-500 Hz, as shown in FIG. 13.
As can be seen from fig. 13, three significant fluctuations of the rotating shaft occur under the excitation of the unbalanced force, which correspond to the translational motion, the swing motion and the first-order bending of the rotor, the frequencies are 10.4 Hz, 35.2 Hz and 280.0 Hz, respectively, and the locus diagrams corresponding to the rotating shaft are shown in fig. 14, 15 and 16, respectively. The fluctuation at 280.0 Hz is the critical rotational speed caused by the reverse vortex of the first order bending mode. Through the locus diagram of the rotating shaft, three times of vibration generated by the rotor under the excitation of unbalanced force corresponds to three times of critical rotating speed. When the supporting rigidity is 1 multiplied by 106N/m, the critical rotating speeds of the rotor are 534.60 rpm, 1788.95 rpm and 13263.92 rpm (namely 8.91 Hz, 29.8 Hz and 221.06 Hz) respectively, and the error of about 20 percent exists between the critical rotating speeds and the vibration frequency under the excitation of the unbalanced force, which is mainly caused by adopting a BEAM188 unit to obtain a rotating track simplified model.
Through carrying out unbalance response analysis on the rotor, the accuracy of solving the critical rotating speed is verified, and the fact that the critical rotating speed caused by a first-order bending mode can cause the vibration of the rotor within a certain range and reaches a peak value at the critical rotating speed can be obtained through analysis of fig. 13.
The invention utilizes finite element software to carry out simulation analysis on the intensity of the rotor, the mode of the rotor, the calculation of unbalance response and the motion track of the rotor. The analysis result can completely meet the design requirement of the rotor. The energy storage flywheel is a whole, and the rotor design is an important component of the energy storage flywheel design and is closely related to the structural design of other components. According to the invention, through the research on the design of the energy storage flywheel rotor, reference basis can be provided for the structural design of other parts of the energy storage flywheel, and help can be provided for the industrialization and productization of the energy storage flywheel.
The present invention is not described in detail in the prior art.
The embodiments selected for the purpose of disclosing the invention, are presently considered to be suitable, it being understood, however, that the invention is intended to cover all variations and modifications of the embodiments which fall within the spirit and scope of the invention.
Claims (9)
1. A flywheel rotor subassembly for energy storage flywheel, includes energy storage dish (1) and main shaft (6), characterized by: the flywheel rotor assembly is characterized in that a left-end radial sensor detection ring (4) is sleeved on the outer edge surface of the left end of the main shaft (6), a left-end radial magnetic bearing rotor (5) is sleeved on the outer edge surface of a right-side main shaft (6) of the left-end radial sensor detection ring (4), a motor rotor (7) is sleeved on the outer edge surface of the right-side main shaft (6) of the left-end radial magnetic bearing rotor (5), an energy storage disc (1) is arranged on the outer edge surface of the right-side main shaft (6) of the motor rotor (7), a right-end radial magnetic bearing rotor (2) is sleeved on the outer edge surface of the right-side main shaft (6) of the energy storage disc (1), and a right-end radial sensor detection ring (3) is sleeved on the outer edge surface of the right-side main shaft (6) of the right-end radial magnetic bearing rotor (2) to form the flywheel.
2. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: the diameter of the energy storage disc (1) is phi 600mm, and the width of the energy storage disc is 172 mm.
3. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: a chamfer is arranged between the energy storage disc (1) and the main shaft (6), and the size of the chamfer is R25 mm.
4. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: the diameter of the main shaft (6) is phi 150mm, and the length is 1400 mm.
5. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: the right-end radial magnetic bearing rotor (2) and the left-end radial magnetic bearing rotor (5) adopt concentric circular silicon steel sheets, and the inner edge surfaces of the right-end radial magnetic bearing rotor (2) and the left-end radial magnetic bearing rotor (5) are sleeved with the outer edge surface of the main shaft (6) in an interference mode.
6. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: the motor rotor (7) is of a tile-shaped structure and is directly attached to the outer edge surface of the main shaft (6), and the outer surface of the motor rotor (7) is wound by carbon fiber prestress.
7. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 1 wherein: the energy storage disc (1) and the main shaft (6) are made of HHE1000 or 35 CrMnSiA.
8. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 7 wherein: the HHE1000 is a material obtained by taking 4340 high-strength steel as a base material and adjusting the proportion of rare metal elements, and has high strength and certain toughness.
9. A flywheel rotor assembly for an energy storing flywheel as claimed in claim 7 wherein: the density of the 35CrMnSiA is 7700 kg m3The elastic modulus is 210GPa, the Poisson ratio is 0.35, the yield strength is 900MPa, and the tensile strength is 1024 MPa.
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| CN202011516522.9A CN112615471A (en) | 2020-12-21 | 2020-12-21 | Flywheel rotor assembly for energy storage flywheel |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117515033A (en) * | 2024-01-08 | 2024-02-06 | 山东天瑞重工有限公司 | Speed increasing method, control device and system for crossing critical rotation speed of rotor |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1759518A (en) * | 2003-01-21 | 2006-04-12 | 帕特里克·T·麦克马伦 | Energy storage flywheel with minimum power magnetic bearing and motor/generator |
| CN101777810A (en) * | 2010-03-31 | 2010-07-14 | 哈尔滨工业大学 | Automatic inner-cooling rotor of high speed permanent magnet synchronous motor |
| CN102082483A (en) * | 2011-02-16 | 2011-06-01 | 东南大学 | Flywheel energy storing device with permanent magnet bearing and thrust bearing |
| CN102437675A (en) * | 2011-10-13 | 2012-05-02 | 山东科技大学 | Energy storage device of magnetic suspension flywheel |
| CN202510551U (en) * | 2012-02-29 | 2012-10-31 | 上海大学 | Vertical superconducting magnetic levitation support system adopting UPS (uninterruptible power supply) flywheel to store energy |
| CN103368326A (en) * | 2013-08-01 | 2013-10-23 | 南京化工职业技术学院 | Low-power-consumption magnetic suspension flywheel energy storing device |
| CN104779722A (en) * | 2015-04-28 | 2015-07-15 | 哈尔滨工业大学 | Rotor structure of high-speed permanent magnet motor |
| CN105024479A (en) * | 2015-07-23 | 2015-11-04 | 江苏大学 | Flywheel energy storing device |
| CN109510382A (en) * | 2018-12-11 | 2019-03-22 | 上海航天控制技术研究所 | A kind of novel magnetically levitated accumulated energy flywheel rotor |
| CN208904827U (en) * | 2018-12-06 | 2019-05-24 | 哈尔滨电气股份有限公司 | The flywheel energy storage system of curved surface variable cross-section rotor mixing bearing |
| CN110460190A (en) * | 2019-07-26 | 2019-11-15 | 上海航天控制技术研究所 | A kind of high-power magnetic-suspension accumulated energy flywheel device |
| CN110571975A (en) * | 2013-01-31 | 2019-12-13 | Skf磁性机械技术公司 | High-speed flywheel on magnetic bearing |
-
2020
- 2020-12-21 CN CN202011516522.9A patent/CN112615471A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1759518A (en) * | 2003-01-21 | 2006-04-12 | 帕特里克·T·麦克马伦 | Energy storage flywheel with minimum power magnetic bearing and motor/generator |
| CN101777810A (en) * | 2010-03-31 | 2010-07-14 | 哈尔滨工业大学 | Automatic inner-cooling rotor of high speed permanent magnet synchronous motor |
| CN102082483A (en) * | 2011-02-16 | 2011-06-01 | 东南大学 | Flywheel energy storing device with permanent magnet bearing and thrust bearing |
| CN102437675A (en) * | 2011-10-13 | 2012-05-02 | 山东科技大学 | Energy storage device of magnetic suspension flywheel |
| CN202510551U (en) * | 2012-02-29 | 2012-10-31 | 上海大学 | Vertical superconducting magnetic levitation support system adopting UPS (uninterruptible power supply) flywheel to store energy |
| CN110571975A (en) * | 2013-01-31 | 2019-12-13 | Skf磁性机械技术公司 | High-speed flywheel on magnetic bearing |
| CN103368326A (en) * | 2013-08-01 | 2013-10-23 | 南京化工职业技术学院 | Low-power-consumption magnetic suspension flywheel energy storing device |
| CN104779722A (en) * | 2015-04-28 | 2015-07-15 | 哈尔滨工业大学 | Rotor structure of high-speed permanent magnet motor |
| CN105024479A (en) * | 2015-07-23 | 2015-11-04 | 江苏大学 | Flywheel energy storing device |
| CN208904827U (en) * | 2018-12-06 | 2019-05-24 | 哈尔滨电气股份有限公司 | The flywheel energy storage system of curved surface variable cross-section rotor mixing bearing |
| CN109510382A (en) * | 2018-12-11 | 2019-03-22 | 上海航天控制技术研究所 | A kind of novel magnetically levitated accumulated energy flywheel rotor |
| CN110460190A (en) * | 2019-07-26 | 2019-11-15 | 上海航天控制技术研究所 | A kind of high-power magnetic-suspension accumulated energy flywheel device |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117515033A (en) * | 2024-01-08 | 2024-02-06 | 山东天瑞重工有限公司 | Speed increasing method, control device and system for crossing critical rotation speed of rotor |
| CN117515033B (en) * | 2024-01-08 | 2024-03-29 | 山东天瑞重工有限公司 | Speed increasing method, control device and system for crossing critical rotation speed of rotor |
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