CN102758874A - Self-adaptive variable-damping variable-stiffness shock absorber for multi-frequency component vibration of rotary machine rotator - Google Patents

Self-adaptive variable-damping variable-stiffness shock absorber for multi-frequency component vibration of rotary machine rotator Download PDF

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Publication number
CN102758874A
CN102758874A CN2012102477158A CN201210247715A CN102758874A CN 102758874 A CN102758874 A CN 102758874A CN 2012102477158 A CN2012102477158 A CN 2012102477158A CN 201210247715 A CN201210247715 A CN 201210247715A CN 102758874 A CN102758874 A CN 102758874A
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China
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vibration
damper
rotor
signal
control
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CN2012102477158A
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Chinese (zh)
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CN102758874B (en
Inventor
何立东
张震坤
常健
刘每
高金吉
郝伟
陈果
刘明
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北京化工大学
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Abstract

The invention discloses a self-adaptive variable-damping variable-stiffness shock absorber for multi-frequency component vibration of a rotary machine rotator, belonging to the technical field of vibration control. The shock absorber comprises a rotator vibration transmission ring, a connecting rod, a composite damper and a control system, wherein the rotator vibration transmission ring is sleeved on the rotary shaft of the rotary machine rotator; the connecting rod is sleeved on the rotator vibration transmission ring; the connecting rod is simultaneously connected to pistons of a magnetorheogical fluid damper and a viscous damper; the pistons are pushed to reciprocate in the magnetorheogical fluid damper and the viscous damper, so as to absorb and dissipate vibration energy. The rotator vibration transmission ring comprises an additional bearing, wherein the additional bearing is connected with the rotary shaft of the rotary machine rotator and sleeved on the rotary shaft, but does not serve as a support. The shock absorber uses a compound damper, so as to not only restrain vibration when the rotator exceeds critical speed of rotation, but also restrain the vibration under a non-critical status of a rotator system, thereby restraining the vibration under each rotation speed of the rotator; besides, the shock absorber is flexible in installation manner.

Description

Rotary machine rotor multi-frequency composition vibration self-adaptive damping variable variable rigidity shock absorption device
Technical field
The present invention is a kind of vibration damper that in rotating machinery, uses, and is a kind of damping device, is mainly used in the vibration problem of the rotor of rotating machineries such as control blower fan, compressor, steam turbine, belongs to the vibration control technology field.
Technical background
In recent years, rotating machineries such as compressor, steam turbine, gas turbine develop towards high rotating speed, high load, high efficiency direction, and the vibration problem of thereupon bringing becomes a very outstanding and stubborn problem.Because the magnitude of vibrations of rotor-support-foundation system is the key factor of decision rotating machinery product performance reliability; Thereby how to reduce the vibration of rotor-support-foundation system; Improve rotor life, guarantee that the machinery safe and reliable operation becomes the important step that needs to be resolved hurrily in the research of rotating machinery.
The vibrative reason of rotating machinery has a lot, mainly is because rotor and component thereof exist amount of unbalance to cause rotor in rotary course, to produce vibration, the vibration that rotor produces owing to distortion when also comprising critical speed of rotation.In addition, cause the vibration of rotating machinery to also have some other aspect: like the coupling die misalignment, bearing arrangement fault, a variety of causes such as fluid dynamic exciting and extraneous vibration source interference.Often according to vibrative a variety of causes, take the means of " suiting the remedy to the case " to reduce amplitude in the engineering reality, the control vibration.Yet; The character of various vibrations is different with type, and the reason of generation is different with mechanism, and solution and means and the measure taked targetedly also is not quite similar; But each method is generally all only effective to a certain type of vibration problem; Maybe can only reduce the vibration of a certain frequency content, the vibration when for example squeeze film damper can reduce rotor and crosses critical speed of rotation, but can not reduce the vibration that rotor misalignment produces; And often there is multiple vibration cause in the actual vibration problem, takes place simultaneously etc. like the rotor unbalance of a frequency multiplication and the problem that misaligns of two frequencys multiplication.Thereby hope to find a kind of Applicable scope method more widely, promptly can effectively play the effect of vibration damping to certain single vibration problem and multiple simultaneous vibration problem.
Additional external damping is a kind of highly effective means in the practical applications with the purpose that reaches vibration damping.Damper is a kind of device that resistance to motion, dissipation kinergety are provided, and is widely used in energy-obsorbing and damping at numerous areas such as Aero-Space, military project, shipping vehicle, building construction, road and bridge, petrochemical equipments.The damper that is used for rotating machinery at present mainly comprises squeeze film damper (SFD), electric current (magnetic current) liquescent damper etc.
Chinese scholars has been carried out a large amount of experimental researcies to squeeze film damper; Liu Fangjie has been introduced the achievement that structure, working principle and the squeeze film damping of squeeze film damper obtained (machine-building 1989 the 12nd phase the 13rd~16 page) in " squeeze film damper damping technology "; Xia Nan etc. sum up and the research course of having looked back squeeze film damper in " to squeeze film damper bearing and selection mechanical rotor---the reviews and prospects of squeeze film damping bearing system dynamic characteristic research "; The problem and the future studies direction (mechanical strength was rolled up the 216th~224 page of the 2nd phase in 2002 the 24th) of existence have been proposed; These researchs show that squeeze film damper can effectively reduce the vibration of high speed rotor; Amplitude when reducing critical speed of rotation especially greatly; And the critical speed of rotation of reduction rotor; Be to use maximum damping devices in the present rotating machinery, be widely used in various rotating machineries such as compressor, gas turbine, become a kind of modular design of aeroengine.Simultaneously squeeze film damper has obvious defects: the first, design improper or the uneven deterioration of rotor-support-foundation system will increase considerably the non-linear of oil-film force, and cause bistable state to be jumped, the phenomenon generation that locked and non-coordination precession etc. are extremely harmful; The second, can cause squeeze film damper to lose efficacy during burst large unbalance amount (like the turbomachine leaf destruction, fall blade), not only can't vibration damping, also can aggravate the vibration of rotor; The 3rd, when rotor was in non-critical rotating speed district, squeeze film damper was not obvious to the reduction of amplitude, and its effectiveness in vibration suppression is unsatisfactory.
Electric current (magnetic current) liquescent damper utilize the controllability change ER fluid in extra electric field or magnetic field or the viscosity of magnetic flow liquid, thereby the damping of change damper and rigidity is to reach the controlled purpose of vibration damping.People such as Wang Jianxiao, Meng Guang proposes the rigidity that magnetic pull can reduce elastic support in " dynamics of extruding type magnetic rheological liquid damper---rotor-support-foundation system and control "; The critical speed of rotation of reduction system and critical amplitudes; Can make damper have best effectiveness in vibration suppression (the mechanical engineering journal was rolled up the 76th~83 page of the 3rd phase in 2004 the 40th) through switch control, and the application patent of invention: magnetic flow change liquid damper for control of rotary machinery rotor vibration.Its advantage is that compare the damping force of generation with current liquescent damper bigger, the vibration amplitude of rotor when obviously reducing the critical speed of rotation district, and can improve the critical speed of rotation of rotor-support-foundation system; Shortcoming is that damper can only be installed in the bearings place, and only vibration damping is effective under critical speed of rotation, and non-critical rotating speed effectiveness in vibration suppression is undesirable, and the fundamental vibration that only imbalance is caused is effective, and is bad to the vibration effectiveness in vibration suppression of other frequency contents.Wish that the long-living magnetic control squeeze film damper dynamic property that in " magnetic control squeeze film damper rotor-support-foundation system experimental research on dynamic properties ", shows is easy to control; And under the good situation of design; Can reduce the vibration (the vibration engineering journal was rolled up the 107th~111 page of the 2nd phase in 2007 the 20th) in each resonance critical speed of rotation district, rank of rotor-support-foundation system significantly; Its defective is that the magnetic control squeeze film damper also can only be installed in the bearings place, and effectiveness in vibration suppression is bad under non-critical rotating speed.Keun-Joo Kim in " Optimal positioning and control of a MR-squeeze film damper for reducing unbalanced vibrations in a rotor system with multiple masses ", also show the unbalance response of rotor-support-foundation system under critical speed of rotation since the damping function of magnetic rheological liquid damper obviously weak (2009 the 131st volumes of Journal of Vibration and Acoustics the 4th phase 0410061-0410069); Its advantage is to have provided damper to be installed in epitrochanterian optimum position; And effectiveness in vibration suppression is remarkable under the critical speed of rotation of former rank; Deficiency is that effectiveness in vibration suppression is bad under non-critical rotating speed; Rely on magnetic rheological liquid damper regulation and control damping and rigidity fully, can not form the real-time continuous self adaptive control.Although magnetic rheological liquid damper can be realized the active or half ACTIVE CONTROL of rotor oscillation; But still there are some problems: first; Produce the favorable damping effect when only crossing critical speed of rotation to rotor, the vibration of rotor under non-critical speed range, effectiveness in vibration suppression is undesirable; The second, the vibration that causes for other reasons, as misalign, vibration problem such as oil whip, sealing flow-induced vibration can't play the better damping effect; The 3rd, all be installed in the bearings position of rotor-support-foundation system generally speaking, can not adjust flexibly; The 4th, mostly present control device is switch control or segmentation control, can not form the self adaptive control of real-time continuous according to the vibration situation.
Control for the rotor oscillation problem at present has some damping vibration attenuation measures; But generally speaking means are single relatively; Hope to design and can both play damping effect, damping shock absorber that applicability is stronger to the vibration of polytype vibration, multiple frequency content, the present invention proposes under such background.
The summary of the invention summary
The problem that the present invention will solve is: to the defective and the problem of damping shock absorber in the present rotating machinery, designing a kind ofly can provide enough big variable damping force according to actual needs; The mounting point is versatile and flexible; Realization level, the control of vertical and axial three-dimensional vibrating; Vibration and rotor to the multiple frequency content of rotor all guarantees good effectiveness in vibration suppression, realizes the novel change damping variable rigidity shock absorption device of closed-loop adaptation control under various rotating speeds.Advantages such as this vibration damper has stable performance, adaptability is strong, practicability good, reliability is high, long service life.
For realizing above purpose, the present invention takes following technological scheme:
A kind of rotary machine rotor multi-frequency composition vibration self-adaptive damping variable variable rigidity shock absorption device, this vibration damper comprises rotor oscillation transmission ring, connecting rod, composite buffer, control system.The outside in the rotating shaft of rotary machine rotor is with the rotor oscillation transmission ring; The outside at the rotor oscillation transmission ring is socketed with connecting rod; Connecting rod is connected on the piston of magnetic rheological liquid damper and viscous damper simultaneously; Promote piston and move reciprocatingly, absorb and the dissipates vibration energy at magnetic rheological liquid damper and in viscous damper.Described viscous damper and MR damper constitute composite buffer.Described rotor oscillation transmission ring includes additional bearing, and additional bearing links to each other with the rotating shaft of rotary machine rotor, and is socketed in the rotating shaft, but not as supporting; Described additional bearing is a rolling bearing, or is other forms of bearings such as sliding bearing, reaches the effect of transfer of vibration with this.
Described viscous damper and MR damper constitute composite buffer.
Live signal check and analysis system comprises eddy current displacement sensor, tenminal block, signal condition module, data collecting card and computer; Wherein eddy current displacement sensor is fixed on the axial direction of rotating shaft of rotary machine rotor; The vibration displacement signal of rotating shaft is converted into the vibration electrical signal, inserts the signal condition module through tenminal block, the signal condition module is carried out rectification, filtering and amplification with mixed and disorderly signal; Extract for analyzing the useful signal of vibration; Signal is through getting into data collecting card after rectification, filtering, the amplification, number is adopted card and converted analog electric signal to digital electric signal, and signal is sent in the control analysis system in the computer; The control analysis system passes through the analysis of vibration electrical signal; Confirm the size of vibration, and combine the parameter of composite buffer to provide best control voltage or electric current, controlled signal; Executive system comprises voltage regulator, circuit and magnetic rheological liquid damper composition; The control signal that the input analytical system provides passes to voltage regulator through circuit; Control voltage regulator output voltage produces electric current in the coil of assurance magnetic rheological liquid damper, thereby can produce damping and rigidity that magnetic intensity is controlled composite buffer; Reach effectiveness in vibration suppression, form the control loop of real-time continuous closed loop.
The present invention has following characteristics:
(1) the rotor oscillation transmission ring is represented the coupled relation of rotor master vibrating system and vibration damping equipment subtense angle; Its function is that the vibrational energy that produces in the rotor rotation process is passed to the vibration damping equipment subtense angle; Can not influence simultaneously the proper functioning of rotor again, this also is a difficult point of rotating machinery vibrating energy transfer.This device has adopted an additional bearing to reach this purpose, and this additional bearing can be a rolling bearing, also can be other forms of bearings such as sliding bearing; Additional bearing links to each other with the rotor of rotating machinery, but not as supporting, the vibrational energy that produces during working rotor is delivered to bearing inner race; And connecting rod is passed in vibration through bearing; Its characteristics are exactly not as supporting, and do not disturb the normal rotation of rotor, can be good at playing the effect of transfer of vibration simultaneously.
(2) connecting rod has certain rigidity, connects rotor oscillation transmission ring and damper, and the rotor oscillation transmission ring is transmitted the vibration of getting off passes to damper with outer power transmission.The actual conditions of number, position and rotor-support-foundation system that the shape of connecting rod can be installed according to damper change flexibly, to reach better transfer of vibration effect.Connecting rod also can be designed to different rigidity to adapt to the vibration of the multiple frequency content of rotor-support-foundation system.
(3) composite buffer comprises a viscous damper and a magnetic rheological liquid damper, the two combination use in pairs.Only rely on magnetic rheological liquid damper can't realize the inhibition of various frequency content vibrations and vibration under each rotating speed of rotor is also needed viscous damper.Viscous damper is fixed on the basis; Inside can be placed the different macromolecule damp liquid of damping capacity as required, after vibration is got off through rotor oscillation transmission ring, connecting rod transmission, drives the damper piston with certain mass and stirs damp liquid; Make damp liquid and damper piston produce relative movement; Rub, vibrational energy is converted into heat energy by mechanical energy also finally consumes in the damping material, play the effect of damping vibration attenuation.The major function of viscous damper just provides basic damping, and the absorbed oscillation energy plays inhibitory action to the vibration and the vibration under each rotating speed of rotor of the multiple frequency content of rotor.
Magnetic rheological liquid damper replenishes as viscous damper, plays power-assisted, and inside is marked with magnetic flow liquid; The housing internal fixation has coil; And link to each other with control system, through changing the size of external voltage or electric current, can change the size of electric current in the coil; Thereby the magnetic field that regulating winding produces, the viscosity of regulating magnetic flow liquid within the specific limits.The major function of magnetic rheological liquid damper is: first; Rotor-support-foundation system only uses viscous damper control vibration, a certain moment under a certain specific occasion generally speaking; When crossing the very large damping force of critical speed of rotation district generation resonance needs like rotor; Magnetic rheological liquid damper is launched in energising, unites and uses two kinds of dampers to reduce bigger vibration, crosses the vibration decline back outage of critical speed of rotation district and closes magnetic rheological liquid damper.The second, the occasion that some vibration is violent especially just need be used magnetic rheological liquid damper always, and this device can be exported optimum damping force thereby control magnetic rheological liquid damper according to vibration situation real-time regulated magnetic field size simultaneously.The 3rd, magnetic rheological liquid damper has the function that becomes rigidity, such as certain many rotor-support-foundation system; Rotor A boosting velocity procedure medium speed can make rotor B that violent coupled vibrations takes place during near the critical speed of rotation of rotor B; At this moment we just can apply magnetic rheological liquid damper at rotor B, and energising increases the rigidity of magnetic rheological liquid damper, thereby the critical speed of rotation of rotor B is increased; Cross the critical speed of rotation district of rotor B when the rotor A rotating speed after; Outage is restored the critical speed of rotation of rotor B again, so just avoids resonance through becoming rigidity, steadily tides over the critical speed of rotation resonance region.
(4) control system mainly is to be used with magnetic rheological liquid damper, and its function is: the first, and without magnetic rheological liquid damper, sensor was just opened use when vibration aggravates, after vibration reduces, close automatically again when rotor-support-foundation system ran well; The second, when vibration especially acutely need be used magnetic rheological liquid damper always, can realize regulating automatically the damping and the rigidity of magnetic rheological liquid damper according to the vibration situation, provide variable damping force to realize self adaptive control.This apparatus control system comprises live signal check and analysis system and executive system.Live signal check and analysis system is made up of eddy current displacement sensor, tenminal block, signal condition module, data collecting card and computer.Wherein eddy current displacement sensor converts the displacement signal of rotor oscillation into electrical signal; Electrical signal is through tenminal block entering signal conditioning module; Signal after the conditioning inserts in the data acquisition card, converts the discernible digital signal of computer into, and the control system that compiling in advance is good in the computer is carried out analytical calculation to the oscillating signal of gathering; Confirm magnitude of vibrations; In conjunction with the parameter of composite buffer, calculate the size of needed magnetic force size of vibration control and corresponding external voltage, then control signal is passed to executive system.Executive system is made up of voltage regulator, magnetic rheological liquid damper and related circuit; The suitable voltage of control signal control voltage regulator output that the input analytical system provides; Guarantee that electric current can produce damping and the rigidity that suitable magnetic intensity is controlled composite buffer in the coil; Reach optimum effectiveness in vibration suppression, form the control loop of real-time continuous closed loop.
Vibration damping basic principle of the present invention is: rotating machinery produces the vibration of various different frequencies at work for various reasons; Correct position (need not and fix on the bearings place) at rotor is installed the compostie damp vibration damping equipment; Wherein be contained in epitrochanterian rotor oscillation transmission ring the vibrational energy that rotor produces is passed to connecting rod; Connecting rod passes to damper piston with vibrational energy, and damper piston is stirred damp liquid, makes damp liquid and damper piston produce relative movement; Rub, vibrational energy is converted into heat energy by mechanical energy also finally consumes in the damping material.The effect of viscous damper provides basic damping, the absorbed oscillation energy.The magnetic rheological liquid damper effect is: certain needs the moment of very big damping force to open magnetic rheological liquid damper, and vibration is closed after reducing again; The violent especially operating mode of vibration continues to open magnetic rheological liquid damper, and forms the control loop of real-time continuous closed loop, output variable damping force according to the vibration situation; Regulate the damping and the rigidity of composite buffer within the specific limits, change rotor critical speed, thereby avoid the resonance region of adjacent rotor.
The present invention compares with damper with existing oscillation damping method has following advantage:
One. can suppress the vibration of multiple frequency content simultaneously.Vibration to multiple reason causes can both be played the favorable damping effect, can suppress the vibration of multiple frequency content in the rotor-support-foundation system simultaneously, the vibration that reason such as for example can reduce imbalance, oil whirl simultaneously, misalign causes.This is an innovative point of the present invention.
Two. adopt composite buffer.Both can when rotor is crossed critical speed of rotation, suppress vibration, and can under the non-critical situation of rotor-support-foundation system, suppress vibration again, but promptly under each rotating speed of rotor, can both play the usefulness of bestirring oneself; To vibration control is three-dimensional, promptly can both play inhibitory action to rotor level, vibration vertical and axial three directions; Some resonance occasion can also provide enough big variable damping force to reduce vibration; Can also adopt the method that becomes rigidity to change rotor critical speed for many rotor-support-foundation systems and avoid the adjacent rotor resonance region.
Three. installation quantity and position are flexible.Can at epitrochanterian correct position the compostie damp vibration damping equipment be installed, to realize various purposes according to actual conditions and needs.Reach the purpose of protecting bearing like hope, so the compostie damp vibration damping equipment can be installed near bearing; Reduce coupling or the vibration of impeller place like hope, can the compostie damp vibration damping equipment be installed in corresponding position so.The installation quantity of damper can be a cover, two covers or even many covers according to actual conditions; The mounting point not only can be near bearing, impeller; As long as the space allows, can be installed in along the arbitrary position of rotor total length according to actual conditions, this is an advantage of the present invention.
Four. form the control of real-time closed-loop continuous adaptive optimization according to the vibration situation.The control of tradition magnetic rheological liquid damper is generally switch control or segmentation control, and voltage or change in current are steps, and the damping force that promptly provides is discontinuous.Control system of the present invention can make voltage or electric current on-line continuous regulate; Computer calculates the voltage or the size of current of required the best automatically according to oscillating signal; So just can adjust voltage or electric current in real time according to the vibration situation; Form only damping and rigidity, better control the vibration situation of rotor.
Five. do not rely on lubricant oil.The damper that is used for rotor-support-foundation system at present all relies on lubricant oil, because lubricating oil viscosity is limited, so the damping force that provides is limited.Compostie damp vibration damping equipment of the present invention has particular structure; Adopt macromolecule viscous damping liquid; Have very high viscosity, can break away from the not enough constraint of lubricating oil viscosity, have very strong stability and very high reliability; Even under the working condition of certain adverse, also can normally use, has longer working life.This device need not change the original mechanical structure simultaneously; Can accomplish the transformation of some large-scale old equipment; Especially in the present petroleum chemical enterprise some because the machinery of the excessive compelled shut-down of vibration amplitude; Can play the favorable damping effect, ensure the safe operation of machinery, resume production rapidly.
In a word, damping device structure of the present invention is unique, strong robustness, and reliability is high, stable performance; No wearout parts, therefore maintenance is less, the life-span is long; It is flexible that damper applies the position, do not rely on lubricant oil, and adaptability is good; Control system is good, is convenient to realize the self adaption ACTIVE CONTROL.
Accompanying drawing and brief description of drawings:
Accompanying drawing 1 is the structure diagram of the present invention in rotor-support-foundation system
Accompanying drawing 2 is the structural representation of compostie damp device viscous damper of the present invention
Accompanying drawing 3 is the structural representation of compostie damp device magnetic rheological liquid damper of the present invention
Accompanying drawing 4 is closed loop control system block diagram of the present invention
Accompanying drawing 5 is magnetic rheological liquid damper control system block diagram of the present invention
Accompanying drawing 6 is embodiment 1 a schematic representation
Accompanying drawing 7 is embodiment 2 a schematic representation
Accompanying drawing 8 is embodiment 3 a schematic representation
Accompanying drawing 9 is embodiment 4 a schematic representation
Accompanying drawing 10 is embodiment 5 a schematic representation
Accompanying drawing 11 is embodiment 6 a schematic representation
Accompanying drawing 12 is embodiment 7 a schematic representation
Accompanying drawing 13 is embodiment 8 a schematic representation
Accompanying drawing 14 is embodiment 9 a schematic representation
Marginal data
1, rotating shaft
2, rotor oscillation transmission ring
3, connecting rod
4, piston
5, viscous damper
6, magnetic rheological liquid damper
7, rotor-support-foundation system supports
8, coupling
9, motor
10, coil
11, eddy current displacement sensor
12, oscillating signal
13, tenminal block
14, signal condition module
15, capture card
16, computer
17, control signal
18, voltage regulator
19, magnetic rheological liquid damper control circuit
Embodiment
Specify rotating machinery rotor multifrequency vibration damping vibration damping equipment of the present invention below in conjunction with accompanying drawing.
In the accompanying drawing 1, motor 9 provides power, makes rotating shaft 1 rotation through coupling 8, and this is a structure the most basic in the rotating machinery.Rotor-support-foundation system supports 7 and generally comes supporting revolving shaft 1 through bearing, bearing support.Apply the compostie damp vibration damping equipment in certain position, it mainly comprises rotor oscillation transmission ring 2, connecting rod 3, piston 4, viscous damper 5 and magnetic rheological liquid damper 6.Accompanying drawing 2 and accompanying drawing 3 have provided the structural representation of viscous damper 5 and magnetic rheological liquid damper 6 in the compostie damp vibration damping equipment respectively, the two in pairs combination use.Concrete working procedure is: during the rotating machinery running; Rotating shaft 1 is because a variety of causes will produce vibration; Rotor oscillation transmission ring 2 is installed in the rotating shaft 1, can play the effect of transmitting vibrations, can not influence the normal operation of rotating shaft 1 simultaneously again; Connecting rod 3 connects rotor oscillation transmission ring 2 and piston 4; And the compostie damp vibration damping equipment is passed in the vibration that rotor oscillation transmission ring 2 transmits with piston 4, and piston 4 is immersed in the middle of the inner damp liquid of compostie damp vibration damping equipment, and the vibrational energy that transmits makes piston 4 move reciprocatingly in compostie damp vibration damping equipment inside.Piston 4 stirs damp liquid and vibrational energy is passed to damp liquid, and damp liquid produces damping force and the vibrational energy absorption is dissipated, and finally reaches the purpose of vibration damping.
Accompanying drawing 5 is a magnetic rheological liquid damper control system block diagram, and live signal check and analysis system comprises eddy current displacement sensor 11, tenminal block 13, signal condition module 14, data collecting card 15 and computer 16 among the figure.Wherein eddy current displacement sensor 11 is converted into vibration electrical signal 12 with the vibration displacement signal of rotating shaft 1; Insert signal condition module 14 through tenminal block 13; Signal condition module 14 is carried out rectification, filtering and amplification with mixed and disorderly signal; Extract for analyzing and vibrate useful signal, and it is adjusted to suitable scope.Signal is through getting into data collecting card 15 after rectification, filtering, the amplification; Number is adopted card 15 and is converted analog electric signal to digital electric signal; And signal sent in the control analysis system in the computer 16, the control analysis system confirms the size of vibration through vibration electrical signal 12 is analyzed; And combine the parameter of composite buffer to provide best control voltage or electric current, controlled signal 17.Executive system comprises voltage regulator 18, circuit 19 and magnetic rheological liquid damper 6 compositions; The control signal 17 that the input analytical system provides passes to voltage regulator 18 through circuit 19; The suitable voltage of control voltage regulator 18 outputs produces suitable current in the coil of assurance magnetic rheological liquid damper 6, thereby can produce damping and rigidity that suitable magnetic intensity is controlled composite buffer; Reach optimum effectiveness in vibration suppression, form the control loop of real-time continuous closed loop.
Embodiment 1
Referring to accompanying drawing 6; Present embodiment shaft 1 substantially horizontal has enough spaces, and the compostie damp device can be installed, and can on the substantially horizontal of rotating shaft 1 a certain correct position, apply the compostie damp device so; Right-hand is viscous damper 5, and left is a magnetic rheological liquid damper 6.
Embodiment 2
Referring to accompanying drawing 7, to compare with embodiment 1, present embodiment shaft 1 vertical direction has enough spaces; The compostie damp device can be installed; On the vertical direction of rotating shaft 1 a certain correct position, apply the compostie damp device so, the top is a viscous damper 5, and the below is a magnetic rheological liquid damper 6.
Embodiment 3
Referring to accompanying drawing 8; Compare with embodiment 1,2; Present embodiment shaft 1 can't symmetry apply the compostie damp device; The substantially horizontal and the vertical direction of not limited a certain correct position apply the compostie damp device in rotating shaft 1 space so, and right-hand is viscous damper 5, and the below is a magnetic rheological liquid damper 6.
Embodiment 4
Referring to accompanying drawing 9, some vibrates violent occasion, need reduce the effectiveness in vibration suppression of rotating shaft as much as possible.Compare with embodiment 1,2,3, present embodiment is that a kind of even more ideal damper applies mode, and under the identical situation of other conditions, present embodiment can provide bigger damping force, fully reduces the vibration of all directions.
Embodiment 5
Referring to accompanying drawing 10, some occasion rotor-support-foundation system that needs protection supports the bearing at 7 places, avoids bearing damage to occur and destroys, so just need be near supporting 7 position installation damper.Give full play to that damping device applies the flexile advantage in position among the present invention; Two diverse locations in rotating shaft 1, promptly at the installed inside compostie damp device that supports 7, bearing place in left side is a viscous damper 5; Bearing place, right side is a magnetic rheological liquid damper 6; Reduce the amplitude that supports 7 places so as far as possible, reduce vibration, reach the purpose of protection bearing.
Embodiment 6
Referring to accompanying drawing 11; Compare with embodiment 5; Do not have enough spaces to apply damping device between 1 liang of support 7 of some rotating shaft, will reach the purpose of protection bearing equally, can be chosen in two yet and support 7 outer fix installation compostie damp device; Bearing place, left side is a viscous damper 5, and bearing place in right side is a magnetic rheological liquid damper 6.Although the mode that the applies difference of damping device can serve the same role, thereby can as the case may be and need in the practical engineering application, select the mode that applies of damping device flexibly.
Embodiment 7
Referring to accompanying drawing 12, for the supercritical rotor of used load symmetry, two support its amount of deflection maximum of midpoint between 7; Thereby the amount of unbalance here is also relatively large, and when rotating shaft was rotated, the vibration here also can be bigger; In order to reduce the vibration here, damper can be installed herein.Generally have transmitted load at the two ends of rotating shaft 1 in addition,, also damper need be installed in order to protect rotating shaft 1.So the form that applies of compostie damp device is shown in accompanying drawing 12, the rotor neutral position is a viscous damper 5, and rotating shaft 1 right-hand member is a magnetic rheological liquid damper 6.
Embodiment 8
Referring to accompanying drawing 13; For two rotor-support-foundation systems or many rotor-support-foundation systems; Coupling 8 both sides rotating shaft A and rotating shaft B causes problems such as axle system misaligns to cause owing to reason absolute altitudes such as heat rises are different vibration can promptly apply damper in the both sides of coupling 8 on two different rotating shaft A and rotating shaft B; Because rotating shaft A and rotating shaft B misalign the vibration that brings, protect coupling 8 and two rotating shaft stable operations to reduce.So the form that applies of compostie damp device is shown in accompanying drawing 13, the left side rotating shaft A of coupling 8 goes up viscous damper 5 is installed, and the right side rotating shaft B of coupling 8 goes up magnetic rheological liquid damper 6 is installed.
Embodiment 9
Referring to accompanying drawing 14, magnetic rheological liquid damper 6 has the function that becomes rigidity, certain many rotor-support-foundation system, and motor 9 drives rotating shaft A rotation through coupling 8, and rotating shaft A drives rotating shaft B rotation through the engagement of gear A and gear B.When rotating shaft A boosting velocity procedure medium speed can make rotating shaft B that violent coupled vibrations takes place during near the critical speed of rotation of rotating shaft B; At this moment we just can apply magnetic rheological liquid damper 6 on rotating shaft B, and energising increases the rigidity of magnetic rheological liquid damper, thereby the critical speed of rotation of rotating shaft B is increased; Cross the critical speed of rotation district of rotating shaft B when rotating shaft A rotating speed after; Outage is restored the critical speed of rotation of rotating shaft B again, so just avoids resonance through becoming rigidity, steadily tides over the critical speed of rotation resonance region.So the form that applies of damping device shown in accompanying drawing 14, is installed magnetic rheological liquid damper 6 on rotating shaft B, to regulate the critical speed of rotation of rotating shaft B.

Claims (3)

1. a rotary machine rotor multi-frequency composition vibrates self-adaptive damping variable variable rigidity shock absorption device, and it is characterized in that: it comprises rotor oscillation transmission ring, connecting rod, composite buffer, control system; The outside in the rotating shaft of rotary machine rotor is with the rotor oscillation transmission ring; The outside at the rotor oscillation transmission ring is socketed with connecting rod; Connecting rod is connected on the piston of magnetic rheological liquid damper and viscous damper simultaneously; Promote piston and move reciprocatingly, absorb and the dissipates vibration energy at magnetic rheological liquid damper and in viscous damper; Described viscous damper and MR damper constitute composite buffer; Described rotor oscillation transmission ring includes additional bearing, and additional bearing links to each other with the rotating shaft of rotary machine rotor, and is socketed in the rotating shaft, but not as supporting.
2. a kind of rotary machine rotor multi-frequency composition vibration self-adaptive damping variable variable rigidity shock absorption device according to claim 1; It is characterized in that: described additional bearing is a rolling bearing; Or be other forms of bearings such as sliding bearing, reach the effect of transfer of vibration with this.
3. a kind of rotary machine rotor multi-frequency composition vibration self-adaptive damping variable variable rigidity shock absorption device according to claim 1 is characterized in that: said live signal check and analysis system comprises eddy current displacement sensor, tenminal block, signal condition module, data collecting card and computer; Wherein eddy current displacement sensor is fixed on the axial direction of rotating shaft of rotary machine rotor; The vibration displacement signal of rotating shaft is converted into the vibration electrical signal, inserts the signal condition module through tenminal block, the signal condition module is carried out rectification, filtering and amplification with mixed and disorderly signal; Extract for analyzing the useful signal of vibration; Signal is through getting into data collecting card after rectification, filtering, the amplification, number is adopted card and converted analog electric signal to digital electric signal, and signal is sent in the control analysis system in the computer; The control analysis system passes through the analysis of vibration electrical signal; Confirm the size of vibration, and combine the parameter of composite buffer to provide best control voltage or electric current, controlled signal; Executive system comprises voltage regulator, circuit and magnetic rheological liquid damper composition; The control signal that the input analytical system provides passes to voltage regulator through circuit; Control voltage regulator output voltage produces electric current in the coil of assurance magnetic rheological liquid damper, thereby can produce damping and rigidity that magnetic intensity is controlled composite buffer; Reach effectiveness in vibration suppression, form the control loop of real-time continuous closed loop.
CN201210247715.8A 2012-07-17 2012-07-17 Self-adaptive variable-damping variable-stiffness shock absorber for multi-frequency component vibration of rotary machine rotator CN102758874B (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103267085A (en) * 2013-05-07 2013-08-28 北京化工大学 Hydraulic multifrequency dynamic vibration absorber for rotary mechanical rotor
CN103423365A (en) * 2013-08-12 2013-12-04 重庆材料研究院有限公司 Membrane type magneto-rheological damper and system
CN103821875A (en) * 2014-03-03 2014-05-28 北京化工大学 Vibration targeting control device for multi-span rotor shaft of rotary machine
CN105443857A (en) * 2015-12-13 2016-03-30 北京化工大学 Variable-damping vibration attenuation and noise reduction device for valve
CN105604944A (en) * 2015-12-18 2016-05-25 成都成发科能动力工程有限公司 Compressor capable of changing critical speed of rotation of rotor and adjusting device thereof
CN105952831A (en) * 2016-04-28 2016-09-21 北京化工大学 Eccentricity adjusting and vibration damping device for non-contact sealing
CN105987119A (en) * 2015-03-17 2016-10-05 现代自动车株式会社 Roll mount using magnetorheological fluid
CN108361319A (en) * 2018-01-23 2018-08-03 西南交通大学 A kind of rubber shock absorber control system
CN109764080A (en) * 2019-03-12 2019-05-17 上海理工大学 A kind of oscillation of rotary machine rotor control system using shear thickening fluid damper

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6129185A (en) * 1997-12-30 2000-10-10 Honeywell International Inc. Magnetically destiffened viscous fluid damper
CN2472006Y (en) * 2001-02-28 2002-01-16 汪建晓 Magnet rheological fluid damper for rotor system oscilation control
EP1255935A1 (en) * 2000-01-31 2002-11-13 Delphi Technologies, Inc. Tuneable steering damper using magneto-rheological fluid
CN1670399A (en) * 2005-04-22 2005-09-21 清华大学 Rigidity and damp adjustable air spring vibration isolator
JP2009058081A (en) * 2007-08-31 2009-03-19 Hitachi Ltd Magnetic fluid damper
CN102278408A (en) * 2011-05-05 2011-12-14 江苏大学 Coaxial integrated air spring absorber with linkage and controllable rigidity and damping
CN102470716A (en) * 2009-07-10 2012-05-23 萱场工业株式会社 Suspension device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6129185A (en) * 1997-12-30 2000-10-10 Honeywell International Inc. Magnetically destiffened viscous fluid damper
EP1255935A1 (en) * 2000-01-31 2002-11-13 Delphi Technologies, Inc. Tuneable steering damper using magneto-rheological fluid
CN2472006Y (en) * 2001-02-28 2002-01-16 汪建晓 Magnet rheological fluid damper for rotor system oscilation control
CN1670399A (en) * 2005-04-22 2005-09-21 清华大学 Rigidity and damp adjustable air spring vibration isolator
JP2009058081A (en) * 2007-08-31 2009-03-19 Hitachi Ltd Magnetic fluid damper
CN102470716A (en) * 2009-07-10 2012-05-23 萱场工业株式会社 Suspension device
CN102278408A (en) * 2011-05-05 2011-12-14 江苏大学 Coaxial integrated air spring absorber with linkage and controllable rigidity and damping

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103267085A (en) * 2013-05-07 2013-08-28 北京化工大学 Hydraulic multifrequency dynamic vibration absorber for rotary mechanical rotor
CN103267085B (en) * 2013-05-07 2015-12-23 北京化工大学 Hydraulic multifrequency dynamic vibration absorber for rotary mechanical rotor
CN103423365A (en) * 2013-08-12 2013-12-04 重庆材料研究院有限公司 Membrane type magneto-rheological damper and system
CN103423365B (en) * 2013-08-12 2016-01-20 重庆材料研究院有限公司 Membrane type magneto-rheological damper and system
CN103821875B (en) * 2014-03-03 2016-03-30 北京化工大学 Rotating machinery multi-bearing rotor shafting vibration target control gear
CN103821875A (en) * 2014-03-03 2014-05-28 北京化工大学 Vibration targeting control device for multi-span rotor shaft of rotary machine
CN105987119A (en) * 2015-03-17 2016-10-05 现代自动车株式会社 Roll mount using magnetorheological fluid
CN105987119B (en) * 2015-03-17 2019-12-06 现代自动车株式会社 Rolling suspension using magnetorheological fluid
CN105443857A (en) * 2015-12-13 2016-03-30 北京化工大学 Variable-damping vibration attenuation and noise reduction device for valve
CN105443857B (en) * 2015-12-13 2018-06-29 北京化工大学 A kind of variable damping vibration and noise reducing device for valve
CN105604944A (en) * 2015-12-18 2016-05-25 成都成发科能动力工程有限公司 Compressor capable of changing critical speed of rotation of rotor and adjusting device thereof
CN105952831A (en) * 2016-04-28 2016-09-21 北京化工大学 Eccentricity adjusting and vibration damping device for non-contact sealing
CN105952831B (en) * 2016-04-28 2018-01-23 北京化工大学 A kind of eccentric adjusting vibration absorber for non-contact seals
CN108361319A (en) * 2018-01-23 2018-08-03 西南交通大学 A kind of rubber shock absorber control system
CN108361319B (en) * 2018-01-23 2020-02-04 西南交通大学 Rubber shock absorber control system
CN109764080A (en) * 2019-03-12 2019-05-17 上海理工大学 A kind of oscillation of rotary machine rotor control system using shear thickening fluid damper

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