CN1632495A - Flexible rotor dynamic balance determination apparatus based on transfer function - Google Patents
Flexible rotor dynamic balance determination apparatus based on transfer function Download PDFInfo
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- CN1632495A CN1632495A CN 200410093866 CN200410093866A CN1632495A CN 1632495 A CN1632495 A CN 1632495A CN 200410093866 CN200410093866 CN 200410093866 CN 200410093866 A CN200410093866 A CN 200410093866A CN 1632495 A CN1632495 A CN 1632495A
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- transport function
- dynamic balance
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Abstract
It is a flexible rotor dynamic balance test device based on transfer function, which comprises the force hammer, charge amplifier, vortex sensor, vortex vibration detector, vibration detector, signal-collecting device and signal analysis device. The hammer with the force sensor strikes the static rotor correction plane to send the excitation signals measured by the force sensor to the charge amplifier and to the signal collector. The vortex sensor measures the multi-plane part displacement vibration signals, which are amplified by the vortex vibration device and sent to the signal-collecting device. It gets the influential coefficients of the rotor correction part according to relationship of the transfer function and influential coefficients. It gets the non-balance value of the correction plane through influential coefficients.
Description
Technical field
The invention belongs to vibration mechanics, be specifically related to a kind of device of flexible rotor dynamic balance.
Technical background
Flexible rotor dynamic balance method commonly used has two kinds: method of model balancing and influence coefficient method.The advantage of method of model balancing is that the good rotor of correction all has good counterbalance effect under various rotating speeds under each critical rotary speed.To general rotor, consider that preceding 3 first order modes of balance get final product, so start-stop time is less.The shortcoming of method of model balancing is that balancing rotor is the critical rotary speed of rotor, causes the permanent strain of rotor easily, and the phase measurement instability.The advantage of influence coefficient method is, do not carry out balance under critical rotary speed, the permanent strain of having avoided resonance to cause, and can pass through computer programing.Its shortcoming is that start-stop time is many, and is very high to the spot dynamic balance equalization charges.But both comprehensively compare, and influence coefficient method is used comparatively extensive.In influence coefficient method, the acquisition of influence coefficient all is to rely on the balance position to apply test mass, obtains by measuring the rotor response.The problem that exists is how can obtain the influence coefficient of rotor-support-foundation system by a kind of simple method fast at present, thereby carries out transient equilibrium at low cost, is problem to be solved by this invention.
Summary of the invention
The object of the present invention is to provide a kind of flex rotor influence coefficient and then low cost of obtaining simply, fast to carry out dynamic balance method, promptly based on the flexible rotor dynamic balance determination apparatus of transport function.
The present invention reaches computing method by the following technical programs and realizes.Based on the flexible rotor dynamic balance determination apparatus of transport function, mainly form (as accompanying drawing) by power hammer 1, charge amplifier 2, eddy current sensor 3, eddy current vialog 4, photoelectric velocity measurement meter 5, vibration measurement instrument 6, signal picker 7, signal analyzer 8.Power hammer 1 by the band force transducer knocks static rotor correcting plane position, and the pumping signal that force transducer records is sent into charge amplifier 2, sends into signal picker 7 after amplifying.The displacement response signal that is recorded a plurality of correcting planes of rotor position by current vortex sensor 3 is sent into signal picker 7 after current vortex vialog 4 amplifies.The response signal that pumping signal that force transducer records and eddy current sensor 3 record is sent into signal analyzer 8 simultaneously, can get rotor and respectively proofread and correct transport function between the position.Power by the band force transducer is hammered the transport function that 1 hammering measures rotor into shape, according to concerning α (Ω)=Ω between transport function and the influence coefficient
2H (Ω) obtains the influence coefficient that the rotor rotor is proofreaied and correct the position.Under balancing speed, record the vibratory response that rotor is proofreaied and correct the position by current vortex sensor 3, current vortex vialog 4, signal picker 7 and signal analyzer 8.By photoelectric velocity measurement meter 5, digital vibration measurement instrument 6, signal picker 7 and signal analyzer 8 record its balancing speed simultaneously.
Can obtain the amount of unbalance of correcting plane according to the influence coefficient of trying to achieve.
The pass that the present invention proposes flex rotor influence coefficient and transport function is:
α(Ω)＝Ω
2H(Ω)?????????????????(a)
Ω is a rotating speed in the formula, and α (Ω) is an influence coefficient matrix, and H (Ω) is a transfer function matrix.
The application of force hammering method, try to achieve the transfer function matrix of rotor easily:
X(Ω)＝H(Ω)F(Ω)????????????????(b)
X in the formula (Ω) is a transient response amplitude spectrum array, and F (Ω) is a pulse excitation amplitude spectrum array.
Under balancing speed, the displacement response A (Ω) on measurement update plane, can be tried to achieve the amount of unbalance U (Ω) of rotor by following formula:
A(Ω)＝α(Ω)U(Ω)???????????????(c)
Beneficial effect of the present invention and advantage are: the apparatus and method that provided a kind of flexible rotor dynamic balance determination, by measuring the transport function of rotor, obtain the influence coefficient of rotor simply, apace, and then the amount of unbalance on definite rotor correcting plane, carry out flexible rotor dynamic balance at low cost.Key of the present invention has been to provide the relation of rotor influential coefficient and transport function, thereby can not obtain the influence coefficient of rotor by the heavy method of adding an examination of.This method only needs a start and stop rotor-support-foundation system, have method simple, fast, low cost and other advantages, be applicable to the dynamic balance determination that relates to all kinds of rotating machinery products and on-the-spot single span and multi-bearing rotor.
Description of drawings
Accompanying drawing is the test block diagram based on the flexible rotor dynamic balance determination apparatus of transport function.
Wherein: the power hammer-1 of band force transducer; Charge amplifier-2; Current vortex sensor-3; Current vortex vialog-4; Photoelectric velocity measurement meter-5; Digital vibration measurement instrument-6; Signal picker-7; Signal analyzer-8; Rotating shaft-9; Rotor discs-10; Bearing-11; Spring coupling-12; Dc speed-regulating motor-13.
Embodiment
Below in conjunction with accompanying drawing principle of the present invention and device are described further.Implementation process is carried out (the frame of broken lines part in the accompanying drawing) by a rotor experiment table.Flex rotor is made up of rotating shaft 9 and two disks 10 and is supported by two bearings 11.Rotor is driven by dc speed-regulating motor 13 by shaft coupling 12.For present embodiment, Structural Parameters of its Rotor is: the mass M of disk 10
1=M
2=0.991kg; Dish is apart from l
1=l
2=l
3=0.183m; Rotating shaft 9 length (span) L=l
1+ l
2+ l
3=0.55m; Rotating shaft 9 diameter d=0.012m; Disk 10 is reserved eccentric arm: r
e=0.0415m.Weighing apparatus rotation speed n=1600rpm (Ω=167.55rad/s) makes even.
Power hammer 1 by the band force transducer knocks static rotor correcting plane disk 10-1 along vertical direction, and the pumping signal that force transducer records is sent into charge amplifier 2, sends into signal picker 7 after amplifying.Record the vertical displacement response signal at rotor discs 10-1 and 10-2 position by current vortex sensor 3, after current vortex vialog 4 amplifies, send into signal picker 7.The response signal that pumping signal that force transducer records and eddy current sensor 3 record is sent into signal analyzer 8 simultaneously, and the transport function by formula X (Ω)=H (Ω) F (Ω) can get two disk 10-1 of rotor and 10-2 sees Table 1.According to concerning α (Ω)=Ω between transport function and the influence coefficient
2H (Ω) obtains rotor rotor discs 10-1 and the influence coefficient of 10-2 under balancing speed Ω, sees Table 2.Under balancing speed, record level and the response of vertical vibration displacement that rotor is proofreaied and correct the position by current vortex sensor 3, current vortex vialog 4, signal picker 7 and signal analyzer 8.By photoelectric velocity measurement meter 5, digital vibration measurement instrument 6, signal picker 7 and signal analyzer 8 record its balancing speed simultaneously.(its anti-phase quality promptly intends being added on balance mass on the disk 10-2 (4.9126e+00,7.1000e+01) (g, °) for 4.9126e+00 ,-1.0900e+02) (g, °) can to obtain the unbalance mass, of correcting plane disk 10-2 according to the influence coefficient of trying to achieve.Displacement response before and after the disk 10-2 balance sees Table 3, and it is original 12.67% that displacement response drops to, and counterbalance effect is good.
The transport function that table 1 present embodiment is tried to achieve
| ??n＝1600rpm | Transfer function H/m/N, ° | |
| ??H 12(H 21) | ??H 22(H 11) | |
| ??0.237e-04，-6.00 + | ??0.244e-04，-6.00 | |
| ??0.433e-04，-14.0 | ??0.425e-04，-13.0 | |
+Annotate: because excitation orientation is-2x, the phasing degree is a measured value-180 ° in the table.
The influence coefficient that table 2 present embodiment is tried to achieve
| ????n＝1600rpm | Influence coefficient α/1/Kg, ° | |
| ??α 12(α 21) | ??α 22(α 11) | |
| Transfer function method | ??6.740e-01，-6.000 | ??6.939e-01，-6.000 |
The displacement response of disk 10-2 before and after table 3 balance
| Displacement A/mm, ° | |
| ????n＝1600rpm | ????2x |
| Before the balance | ????0.15，-115.0 |
| After the balance | ????0.019，-135.0 |
Claims (4)
1. based on the flexible rotor dynamic balance determination apparatus of transport function, mainly by power hammer (1), charge amplifier (2), eddy current sensor (3), eddy current vialog (4), photoelectric velocity measurement meter (5), vibration measurement instrument (6), signal picker (7), signal analyzer (8) is formed, it is characterized in that knocking static rotor correcting plane position by the power hammer (1) of band force transducer, the pumping signal that force transducer records is sent into charge amplifier (2), after amplifying, send into signal picker (7), the displacement response signal that is recorded a plurality of correcting planes of rotor position by current vortex sensor (3) is sent into signal picker (7) after current vortex vialog (4) amplifies, the response signal that pumping signal that the while force transducer records and current vortex sensor (3) record is sent into signal analyzer (8).
2. according to the described flexible rotor dynamic balance determination apparatus of claim 1 based on transport function, it is characterized in that described current vortex sensor (3), current vortex vialog (4), signal picker (7) and signal analyzer (8) record the vibratory response that rotor is proofreaied and correct the position, record balancing speed by photoelectric velocity measurement meter (5), digital vibration measurement instrument (6), signal picker (7) and signal analyzer (8) simultaneously.
3. according to claim 1 or 2 described flexible rotor dynamic balance determination apparatus based on transport function, it is characterized in that measuring by power hammer (1) hammering of described band force transducer the transport function of rotor, the pass of flex rotor influence coefficient and transport function is: by α (Ω)=Ω
2H (Ω).
4. according to the described flexible rotor dynamic balance determination apparatus based on transport function of claim 3, what it is characterized in that described flex rotor influence coefficient and transport function concerns α (Ω)=Ω
2H (Ω), wherein said Ω are rotating speed, and described α (Ω) is an influence coefficient matrix, and described H (Ω) is a transfer function matrix.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410093866 CN1632495A (en) | 2004-12-08 | 2004-12-08 | Flexible rotor dynamic balance determination apparatus based on transfer function |
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|---|---|---|---|
| CN 200410093866 CN1632495A (en) | 2004-12-08 | 2004-12-08 | Flexible rotor dynamic balance determination apparatus based on transfer function |
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| CN1632495A true CN1632495A (en) | 2005-06-29 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101915640A (en) * | 2010-08-02 | 2010-12-15 | 浙江大学 | Biaxial adaptive dynamic balance executing method for centrifuge |
| CN102012259A (en) * | 2010-12-07 | 2011-04-13 | 沈阳远大机电装备有限公司 | Fast test device for natural frequency of motor rotor |
| CN102252836A (en) * | 2011-04-14 | 2011-11-23 | 唐德尧 | Testing method and apparatus for supporting state, dynamic balancing state and non-centering state of rotating machine |
| CN102297650A (en) * | 2011-05-20 | 2011-12-28 | 河南电力试验研究院 | Method suitable for rotation shaft bending and phase testing, and apparatus thereof |
| CN106289645A (en) * | 2016-11-07 | 2017-01-04 | 北京东方振动和噪声技术研究所 | Rotor dynamic balancing assay method based on steady stimulation method and device |
| CN108827536A (en) * | 2018-03-27 | 2018-11-16 | 江苏大学 | Online dynamic balance detection system and detection method are assembled by a kind of combination revolution system |
| CN110118632A (en) * | 2018-02-07 | 2019-08-13 | 申克罗泰克有限责任公司 | By the method for the degree of unbalancedness of displacement sensor axis elastic rotor |
| CN110579312A (en) * | 2019-10-17 | 2019-12-17 | 江苏方天电力技术有限公司 | dynamic balance fault detection method for multi-wheel-disc shafting of non-trial-weight rotating machinery |
| CN114112192A (en) * | 2021-11-26 | 2022-03-01 | 中国汽车工程研究院股份有限公司 | Fan residual unbalance testing and analyzing method based on transfer function |
-
2004
- 2004-12-08 CN CN 200410093866 patent/CN1632495A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101915640A (en) * | 2010-08-02 | 2010-12-15 | 浙江大学 | Biaxial adaptive dynamic balance executing method for centrifuge |
| CN102012259A (en) * | 2010-12-07 | 2011-04-13 | 沈阳远大机电装备有限公司 | Fast test device for natural frequency of motor rotor |
| CN102252836A (en) * | 2011-04-14 | 2011-11-23 | 唐德尧 | Testing method and apparatus for supporting state, dynamic balancing state and non-centering state of rotating machine |
| CN102252836B (en) * | 2011-04-14 | 2013-05-22 | 唐德尧 | Testing method and apparatus for supporting state, dynamic balancing state and non-centering state of rotating machine |
| CN102297650A (en) * | 2011-05-20 | 2011-12-28 | 河南电力试验研究院 | Method suitable for rotation shaft bending and phase testing, and apparatus thereof |
| CN106289645A (en) * | 2016-11-07 | 2017-01-04 | 北京东方振动和噪声技术研究所 | Rotor dynamic balancing assay method based on steady stimulation method and device |
| CN106289645B (en) * | 2016-11-07 | 2020-05-01 | 北京东方振动和噪声技术研究所 | Rotor dynamic balance measuring method and device based on steady state excitation method |
| CN110118632A (en) * | 2018-02-07 | 2019-08-13 | 申克罗泰克有限责任公司 | By the method for the degree of unbalancedness of displacement sensor axis elastic rotor |
| CN108827536A (en) * | 2018-03-27 | 2018-11-16 | 江苏大学 | Online dynamic balance detection system and detection method are assembled by a kind of combination revolution system |
| CN110579312A (en) * | 2019-10-17 | 2019-12-17 | 江苏方天电力技术有限公司 | dynamic balance fault detection method for multi-wheel-disc shafting of non-trial-weight rotating machinery |
| CN114112192A (en) * | 2021-11-26 | 2022-03-01 | 中国汽车工程研究院股份有限公司 | Fan residual unbalance testing and analyzing method based on transfer function |
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