CN101169159A - Large damp magnetic suspension high speed rotating system device - Google Patents
Large damp magnetic suspension high speed rotating system device Download PDFInfo
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- CN101169159A CN101169159A CNA2007101309135A CN200710130913A CN101169159A CN 101169159 A CN101169159 A CN 101169159A CN A2007101309135 A CNA2007101309135 A CN A2007101309135A CN 200710130913 A CN200710130913 A CN 200710130913A CN 101169159 A CN101169159 A CN 101169159A
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- 239000000725 suspension Substances 0.000 title claims abstract description 55
- 238000013016 damping Methods 0.000 claims abstract description 36
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- 230000000694 effects Effects 0.000 abstract description 5
- 238000011161 development Methods 0.000 abstract description 4
- 238000005316 response function Methods 0.000 description 17
- 238000012360 testing method Methods 0.000 description 17
- 238000005516 engineering process Methods 0.000 description 7
- 239000003985 ceramic capacitor Substances 0.000 description 5
- 230000005764 inhibitory process Effects 0.000 description 5
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- 230000001360 synchronised effect Effects 0.000 description 5
- 239000003990 capacitor Substances 0.000 description 4
- 238000013461 design Methods 0.000 description 4
- 238000011160 research Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- BQCADISMDOOEFD-UHFFFAOYSA-N Silver Chemical compound [Ag] BQCADISMDOOEFD-UHFFFAOYSA-N 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 229910052734 helium Inorganic materials 0.000 description 1
- 239000001307 helium Substances 0.000 description 1
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 1
- 238000005339 levitation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910052709 silver Inorganic materials 0.000 description 1
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Abstract
A large-damping magnetic-suspension high-speed rotating system device belongs to the technical field of magnetic suspension and comprises a rotator assembly, two radial magnetic-suspension baring assemblies, a thrust bearing assembly and a driving motor. The invention is characterized in that the device also comprises an assistant magnetic-suspension bearing assembly which has bearing damping but no bearing rigidity to the rotator assembly. The assistant magnetic-suspension bearing assembly of the invention does not provide bearing rigidity and only provides controllable additional damping, and therefore can avoid production of hyperstatic constraints on rigid-body modal vibration of rotators under low rotation speed; meanwhile, the bearing damping can be conveniently changed by adjusting an adjustable potentiometer to satisfy dynamic performance requirements of the system. The technical proposal is simple and easy to apply and has good effect. High-speed, heavy-bearing, and long and thin development requirements of rotating mechanical rotators increasingly highlight the dynamic problems of the machinery. The study results of the invention can provide guidance and reference for solving related practical problems.
Description
Technical field
Large damp magnetic suspension high speed rotating system device of the present invention belongs to the magnetic levitation technology field.
Background technique
Compare with traditional bearing, magnetic suspension bearing and rotor are contactless, and the supporting power consumption is little, long service life; Do not need lubricated and sealing, can be used for particular surroundingss such as high low temperature for a long time; Maintenance cost is low, be convenient to ACTIVE CONTROL or the like, thereby is considered to the revolution of supporting technology, is present unique practical active bearing device that drops into.Magnetic suspension bearing is mainly used in the stiffness rotor system, since the requirement of rotary machine rotor high speed, heavy duty, elongated development, the existing flexible rotor system that just progressively expands to.
But the correlative study result shows both at home and abroad, magnetic suspension bearing is applied to flexible rotor system exist bigger difficulty.Main cause is the equivalent stiffness of magnetic suspension bearing and the restriction in the controlled parameter stability of equivalent damping zone, generally than little 2～3 orders of magnitude of hydrodynamic sliding bearing.System near or when crossing crooked critical rotary speed, too small because of damping, the rotor amplitude is excessive, causes system destruction easily.Therefore, the research at flexible rotor system is the focus and the difficult point of this technical field always.In order to reduce the vibration of rotor system of magnetic suspension bearing, domestic and international many documents are studied from two aspects.The one, take synchronous vibration inhibition technology, the 2nd, utilization modern control theory or robust control theory design controlling schemes are to improve the supporting damping.
But synchronous vibration inhibition technology is difficult to solve the unbalance vibration problem of compliance rotor-support-foundation system.This is that the caused vibration of unbalance mass, is relevant with the rotor bow deformation state because rotor will produce bending deflection in subcritical and supercritical state, and more than the stiffness rotor system complex, thereby synchronous vibration inhibition technology is primarily aimed at the stiffness rotor system at present.
Some results of study show both at home and abroad, adopt the suitable controlling schemes of modern control theory or robust control theory design can improve the dynamic performance of system, but still can not accomplish the supporting damping of the system that increases substantially when subcritical and overcritical operation at present, and research object mostly is experimental system, and practical application is few.Bearing in 2000 is made the researcher Hirochika Ueyama of famous enterprise Japan " silver dollar Co., Ltd. " research and development centre and is sent the documents in the 7th the magnetic suspension bearing international conference that Switzerland holds and think, although " some open source literatures show, adopt modern control theory (LQG, H
∞, μ theory etc.) can address this problem, but this remains a challenging problem.For fear of this problem, relevant practical application project adopts the stiffness rotor structure " (Hirochika Ueyama, Helium Cold Compressor with Active Magnetic Bearings, Proc.of the 7
ThInt.Symp.on Magnetic Bearings, Zurich, Switzerland, August 2000,1～6).
Summary of the invention
Purpose of the present invention is magnetic suspension bearing is applied to flexible rotor system, and the large damp magnetic suspension high speed rotating system device that a kind of Oscillation Amplitude is little, stability is strong promptly is provided.
This large damp magnetic suspension high speed rotating system device, comprise rotor assembly, two radial magnetic bearing assemblies, thrust bearing assembly and drive motor, it is characterized in that: also comprise the auxiliary magnetic suspension bearing assembly that only rotor assembly is had the supporting damping and do not have support stiffness.
General rotor system of magnetic suspension bearing mainly is made up of rotor assembly, two radial magnetic bearing assemblies, thrust bearing assembly and drive motor.Under suitable Control Parameter effect, magnetic bearing produces support stiffness and supporting damping to rotor, has determined the dynamic performance of whole system.Because the Control Parameter region of stability is limited, the selection of supporting damping is restricted.
Apparatus of the present invention have increased auxiliary magnetic suspension bearing assembly on the basis of general rotor system of magnetic suspension bearing.By increasing this assembly, improve the supporting damping of system, reduce the amplitude of rotor, improve the stability of system.Different with general radial magnetic bearing assembly is, auxiliary magnetic suspension bearing assembly does not provide support stiffness to rotor, controlled additional damping only is provided,, has designed the corresponding controller circuit for this reason to avoid that the rigid body mode vibration of slow-speed of revolution lower rotor part is produced indeterminate constraint.
In rotor-support-foundation system, have some practical applications to adopt the multi-point support mode, but the each point supporting all produce support stiffness and supporting damping to rotor by traditional bearing (rolling bearing, sliding bearing) supporting.Improve machining accuracy or adjust the bearing centre height and realize in order to reduce an indeterminate constraint of honouring rotor, to adopt usually.Traditional bearing contacts with rotor, and surface friction drag is big; This in addition method of avoiding multi-point support to produce indeterminate constraint makes complicated in mechanical structure, and it is undesirable to adjust effect, influences the working life and the systematic function of bearing.
In aforementioned, mention, both at home and abroad for the magnetic suspension flexible rotor system, the one, take synchronous vibration inhibition technology, the 2nd, utilization modern control theory or robust control theory design controlling schemes are to improve the supporting damping.Because rotor will produce bending deflection in subcritical and supercritical state, the caused vibration of unbalance mass, is relevant with the rotor bow deformation state, and more than the stiffness rotor system complex, thereby synchronous vibration inhibition technology is primarily aimed at the stiffness rotor system at present.Utilization modern control theory or the suitable controlling schemes of robust control theory design can be improved the dynamic performance of system, but, still can not accomplish the supporting damping of the system that increases substantially when subcritical and overcritical operation at present because the Control Parameter region of stability is still limited.
The auxiliary magnetic suspension bearing assembly that adopts in apparatus of the present invention, support stiffness is not provided, controlled additional damping only is provided, can avoid the rigid body mode vibration of slow-speed of revolution lower rotor part is produced indeterminate constraint, change the supporting damping flexibly to satisfy the requirement of dynamic performance by adjusting adjustable potentiometer simultaneously.This technological scheme is simple, and is effective.The requirement of rotary machine rotor high speed, heavy duty, elongated development becomes increasingly conspicuous the dynamics problem of machinery, and result of study of the present invention can provide thinking and reference for solving relevant practical problem.
Description of drawings
Fig. 1 is the mechanical structure general assembly drawing of device.Label title among Fig. 1: 1,6 is the radial magnetic bearing assembly, 2. rotor assembly, 3. thrust bearing assembly, 4. high-frequency electric machines assembly; 5. auxiliary magnetic suspension bearing assembly, 7. pedestal, 8. thrust force protection bearing; 9. radially protect bearing, 10. radial transducer, 11. axial sensor.
Fig. 2 is the controller circuitry figure of auxiliary magnetic suspension bearing assembly.
Fig. 3 is a test modal analysis exciting position view.Arrange 11 exciting points and 1 pick-up point on rotor, wherein the 5th is exciting point and pick-up point simultaneously.
Fig. 4 is not for having under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Fig. 5 is not for there being under the auxiliary magnetic suspension bearing condition mode software analysis result of the multiple vibration shape of each rank natural frequency correspondence and damping value.
Fig. 6 is for having under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Fig. 7 is for there being under the auxiliary magnetic suspension bearing condition mode software analysis result of the multiple vibration shape of each rank natural frequency correspondence and damping value.
Fig. 8 is the 1st group of Control Parameter, do not have under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Fig. 9 is the 1st group of Control Parameter, has under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Figure 10 is the 2nd group of Control Parameter, do not have under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Figure 11 is the 2nd group of Control Parameter, has under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Figure 12 is the 3rd group of Control Parameter, do not have under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Figure 13 is the 3rd group of Control Parameter, has under the auxiliary magnetic suspension bearing condition, strides a frequency response function between the 9th pick-up point and exciting point.
Embodiment
In conjunction with shown in Figure 1, apparatus of the present invention comprise radial magnetic bearing assembly 1,6, rotor assembly 2, and thrust bearing assembly 3, high-frequency drive electric machine assembly 4, pedestal 7, thrust force protection bearing 8 is radially protected bearing 9, radial transducer 10, axial sensor 11.Magnetic bearing provides supporting role to rotor on 5 degrees of freedom, for each degrees of freedom, form closed-loop system by sensor, controller, power amplifier, magnetic bearing, rotor etc.Under suitable Control Parameter effect, magnetic bearing produces support stiffness and supporting damping to rotor, has determined the dynamic performance of whole system.Because the Control Parameter region of stability is limited, the selection of supporting damping is restricted.
Apparatus of the present invention have increased auxiliary magnetic suspension bearing assembly 5 on the basis of general rotor system of magnetic suspension bearing, this assembly is identical with general radial magnetic bearing assembly on mechanical structure.Different with general radial magnetic bearing assembly is that this assembly does not provide support stiffness, and controlled additional damping only is provided, and can avoid the rigid body mode vibration of slow-speed of revolution lower rotor part is produced indeterminate constraint.In order to reach this purpose, the structure and parameter of controller is selected different with normal controller.Controller circuitry figure such as Fig. 2, each type of device, numbering and nominal value see Table 1 explanation in the circuit.
Each type of device, numbering and label in table 1. circuit diagram
| Type | Numbering | Nominal value | Type | Numbering | Nominal value |
| Electrochemical capacitor | C1 | 22u/35V | Resistance | R8 | 20k |
| Electrochemical capacitor | C2 | 22u/35V | Resistance | R9 | 3.9k |
| Electrochemical capacitor | C3 | 22u/35V | Resistance | R10 | 3.9k |
| Electrochemical capacitor | C4 | 22u/35V | Resistance | R11 | 5.1 |
| Leaded multilayer ceramic capacitor | C5 | 0.1uF | Resistance | R12 | 10k |
| Leaded multilayer ceramic capacitor | C6 | 0.1uF | Resistance | R13 | 0.43k |
| Leaded multilayer ceramic capacitor | C7 | 0.1uF | Resistance | R14 | 300k |
| Leaded multilayer ceramic capacitor | C8 | 0.1uF | Resistance | R15 | 5.1k |
| Leaded multilayer ceramic capacitor | C9 | 2.2uF | Resistance | R16 | 20k |
| Resistance | R3 | 7.9k | Diode | D1 | 1N4148 |
| Resistance | R4 | 2.1k | Diode | D2 | 1N4148 |
| Resistance | R5 | 20k | Adjustable potentiometer | W1 | 25K |
| Resistance | R6 | 20k | Intergrated circuit | U1 | TL084 |
| Resistance | R7 | 20k |
This circuit structure is simple, only is made up of resistance, electric capacity, diode, adjustable potentiometer and 1 intergrated circuit.Wherein by U1A and resistance capacitance proportion of composing operational amplifier on every side; Form differentiator by U1B with resistance capacitance on every side; It by U1C and the proportional coefficient of resistor group on every side 1 operational amplifier; Form follower circuit by U1D with resistance on every side.
This circuit is exported a certain size scaling signal and differential signal.When adopting this circuit as controller, the export ratio signal makes aiding support produce suitable control electric current, forms the positive rigidity to rotor.This positive rigidity and aiding support itself intrinsic displacement negative stiffness offset, auxiliary like this magnetic suspension bearing is zero to rotor bearing rigidity.And, can change the size of controller output differential signal, thereby change of the supporting damping of auxiliary magnetic suspension bearing to rotor by adjusting adjustable potentiometer W1.
Further specify effect of the present invention below by system test modal analysis and system high-speed rotation test.
The system test modal analysis
Before the real system operation, by the stable suspersion rotor system is carried out test modal analysis, can obtain the dynamic performance parameter of the systems such as natural frequency, damping and the vibration shape of system, the operation conditions of precognition system.
Position distribution is as shown in Figure 3 arranged 11 exciting points and 1 pick-up point on rotor, wherein the 5th is exciting point and pick-up point simultaneously.Adopt pulse hammer that exciting point is implemented to knock, the response of adopting acceleration transducer to record pick-up point, analysis software " intelligent data acquisition and the Signal Analysis System " (version number: DAST2006) carry out modal analysis that adopts " Beijing Orient vibration and noise technique research institute " development.
System only by the magnetic suspension bearing supporting, chooses controller scaling factor k
Pr=4.16, integral coefficient K
Ir=22.21, differential coefficient k
Dr=7.2 * 10
-3, derivative time coefficient T
Dr=1.12 * 10
-5S.By test modal analysis, can get each initial point and stride a frequency response function.With the 9th pick-up point is example, and it strides a frequency response function such as Fig. 4, the multiple vibration shape of each rank natural frequency correspondence and damping such as Fig. 5.Each rank natural frequency of system is as follows:
N
1＝1169rpm，N
2＝3549rpm，N
3＝12817rpm，N
4＝28682rpm
Show among Fig. 5 that corresponding damping ratio is:
ζ
1＝0.02，ζ
2＝0.05，ζ
3＝0.07，ζ
4＝0.03
On the basis of the above, increase auxiliary magnetic suspension bearing, its equivalent damping d
Eqr=5.5 5 * 10
4Ns/m.By test modal analysis, can get each initial point and stride a frequency response function.Be example still, stride a frequency response function such as Fig. 6, the multiple vibration shape of each rank natural frequency correspondence and damping such as Fig. 7 with the 9th pick-up point.Each rank natural frequency of system is as follows:
N
1＝1128rpm，N
2＝5912rpm，N
3＝13072rpm，N
4＝28765rpm
Show among Fig. 7 that corresponding damping ratio is:
ζ
1＝0.02，ζ
2＝0.32，ζ
3＝0.18，ζ
4＝0.04
By the exciting experiment test result of Fig. 4, Fig. 6 and damping ratio as can be seen, after increasing auxiliary magnetic suspension bearing, the following corresponding damping ratio of each rank natural mode of vibration (comprising the crooked natural mode of vibration in the 1st, 2 rank) of 400Hz is greatly improved, and system's frequency response amplitude then has reduction largely.This explanation increases the crooked natural mode of vibration vibration in the 1st, 2 rank that auxiliary magnetic suspension bearing can effectively suppress rotor, helps rotor and crosses crooked critical rotary speed.
Similar to the above, provide the system test modal analysis result under other three groups of different magnetic suspension bearing Control Parameter below.Three groups of magnetic bearings control parameter such as tables 2 that test is corresponding.
The magnetic bearings control parameter of table 2.3 group test modal analysis correspondence
| Scaling factor | Integral coefficient | Differential coefficient | Coefficient derivative time (s) | |
| The 1st group | 3.29 | 17.54 | 5.7×10 -3 | 1.12×10 -5 |
| The 2nd group | 3.46 | 18.48 | 6.0×10 -3 | 1.12×10 -5 |
| The 3rd group | 3.81 | 20.34 | 6.6×10 -3 | 1.12×10 -5 |
When each group test, system only by the magnetic bearing supporting, can get each initial point and stride a frequency response function earlier; Increase auxiliary magnetic suspension bearing then, its equivalent damping d
Eqr=5.55 * 10
4Ns/m can get under the combined support each initial point and stride a frequency response function.
Be example with the 9th pick-up point still, Fig. 8, Figure 10 and Figure 12 represent that respectively each test group of not having auxiliary magnetic suspension bearing strides a frequency response function, and Fig. 9, Figure 11 and Figure 13 represent that respectively each test group that increases auxiliary magnetic suspension bearing strides a frequency response function.By the frequency response function figure of each group test as can be seen, under the different magnetic suspension bearing Control Parameter, after increasing auxiliary magnetic suspension bearing, the following corresponding damping ratio of each rank natural mode of vibration (comprising the crooked natural mode of vibration in the 1st, 2 rank) of 400Hz all is greatly improved, and system's frequency response amplitude then has reduction largely.This explanation under the different magnetic suspension bearing Control Parameter, increases the crooked natural mode of vibration vibration in the 1st, 2 rank that auxiliary magnetic suspension bearing all can effectively suppress rotor, helps rotor and crosses crooked critical rotary speed.
The system high-speed rotation test
In the high-speed test (HST), choose magnetically suspended bearing scaling factor k
Pr=4.16, integral coefficient k
Ir=22.21, differential coefficient k
Dr=7.2 * 10
-3, derivative time coefficient T
Dr=1.12 * 10
-5S, auxiliary magnetic suspension bearing equivalent damping d
Eqr=5.55 * 10
4Ns/m suspends rotor stability, and by built-in high-frequency electric machines drive rotor by 0rpm stable operation to 16000rpm.In the operation process, the rotor actual speed is measured by photoelectric sensor, the analysis software " intelligent data acquisition and Signal Analysis System " that adopts " Beijing Orient vibration and noise technique research institute " to develop (version number: DAST2006) analyze to eddy current displacement sensor, and the three-dimensional that can get rotor oscillation is composed shake figure such as Figure 14 by output.
As seen from Figure 14, stable single order crooked critical rotary speed about 5900rpm and the second order crooked critical rotary speed about 13000rpm crossed of system.
Claims (1)
1. large damp magnetic suspension high speed rotating system device, comprise rotor assembly, two radial magnetic bearing assemblies, thrust bearing assembly and drive motor, it is characterized in that: also comprise the auxiliary magnetic suspension bearing assembly that only rotor assembly is had the supporting damping and do not have support stiffness.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101309135A CN101169159B (en) | 2007-08-23 | 2007-08-23 | Large damp magnetic suspension high speed rotating system device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101309135A CN101169159B (en) | 2007-08-23 | 2007-08-23 | Large damp magnetic suspension high speed rotating system device |
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| Publication Number | Publication Date |
|---|---|
| CN101169159A true CN101169159A (en) | 2008-04-30 |
| CN101169159B CN101169159B (en) | 2010-07-21 |
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ID=39389877
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|---|---|---|---|
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072251A (en) * | 2011-01-21 | 2011-05-25 | 南京航空航天大学 | Control device and control method for variable bias current of flexible rotors of magnetic suspension bearings |
| CN102611360A (en) * | 2012-03-08 | 2012-07-25 | 南京航空航天大学 | Five-freedom-degree magnetic suspension motor with brake function and control method thereof |
| CN103307103A (en) * | 2013-05-08 | 2013-09-18 | 南京航空航天大学 | Combined support device of magnetic bearing rotor system |
| CN105257699A (en) * | 2015-10-16 | 2016-01-20 | 浙江工业大学 | Mixed three-phase magnetic bearing |
| CN108869541A (en) * | 2018-01-12 | 2018-11-23 | 至玥腾风科技投资集团有限公司 | A kind of control method of transverse bearing, rotor-support-foundation system and transverse bearing |
| 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 |
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Family Cites Families (2)
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| JPS5881217A (en) * | 1981-11-11 | 1983-05-16 | Seiko Instr & Electronics Ltd | Five dimentional freedom control type magnetic bearing device |
| CN1945940A (en) * | 2006-07-18 | 2007-04-11 | 沈阳工业大学 | Integrated permanent magnet rotor magnetic suspension high speed motor |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072251A (en) * | 2011-01-21 | 2011-05-25 | 南京航空航天大学 | Control device and control method for variable bias current of flexible rotors of magnetic suspension bearings |
| CN102072251B (en) * | 2011-01-21 | 2012-11-28 | 南京航空航天大学 | Control device and control method for variable bias current of flexible rotors of magnetic suspension bearings |
| CN102611360A (en) * | 2012-03-08 | 2012-07-25 | 南京航空航天大学 | Five-freedom-degree magnetic suspension motor with brake function and control method thereof |
| CN103307103A (en) * | 2013-05-08 | 2013-09-18 | 南京航空航天大学 | Combined support device of magnetic bearing rotor system |
| CN105257699A (en) * | 2015-10-16 | 2016-01-20 | 浙江工业大学 | Mixed three-phase magnetic bearing |
| CN105257699B (en) * | 2015-10-16 | 2018-01-09 | 浙江工业大学 | Mix three-phase magnetic bearing |
| CN108869541A (en) * | 2018-01-12 | 2018-11-23 | 至玥腾风科技投资集团有限公司 | A kind of control method of transverse bearing, rotor-support-foundation system and transverse bearing |
| CN108869541B (en) * | 2018-01-12 | 2024-04-02 | 刘慕华 | Radial bearing, rotor system and control method of radial bearing |
| 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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| CN101169159B (en) | 2010-07-21 |
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Effective date of registration: 20160922 Address after: 214000, room 1, building 311, No. 1512-2, Yan Xin Road, Huishan Economic Development Zone, Jiangsu, Wuxi Patentee after: Wuxi Source Power Technology Co., Ltd. Address before: Yudaojie Nanjing 210016 Jiangsu province No. 29 Patentee before: Nanjing University of Aeronautics and Astronautics |
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