CN104896007A - A transmission system torsional vibration reducing method and application thereof - Google Patents

A transmission system torsional vibration reducing method and application thereof Download PDF

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Publication number
CN104896007A
CN104896007A CN201510155620.7A CN201510155620A CN104896007A CN 104896007 A CN104896007 A CN 104896007A CN 201510155620 A CN201510155620 A CN 201510155620A CN 104896007 A CN104896007 A CN 104896007A
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damper
vibration
transmission system
torshional
vibration damper
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CN104896007B (en
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彭超
李明辉
张莹博
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Guoneng United Power Technology (Baoding) Co.,Ltd.
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Guodian United Power Technology Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1204—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/26—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using tide energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/30—Flywheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00—Nature of movement
    • F16F2232/02—Rotary
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Oceanography (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Wind Motors (AREA)

Abstract

The invention provides a transmission system torsional vibration reducing method and application thereof. The method is characterized in that a torsional vibration damper, which is a tuned rotary inertia damper, is added on a transmission shaft in a parallel connection manner, and the torsional rotation movement around the transmission shaft is used for reducing the vibration level of a certain first order torsional mode frequency. The method is flexible, can effectively reduce vibration without damage to the original structure of the transmission system, and can be used for later repair of the transmission system. The method can be applied to wind energy/tidal current energy generator sets; the torsional vibration damper is installed on a shaft, connected with a generator, of a high speed shaft coupler to greatly reduce a first-order mode component in the torsional vibration, so that a transmission system can operate more stably, the reliability of the structure can be improved and the service life can be prolonged.

Description

A kind of Torsional Vibration of Shafts oscillation damping method and application thereof
Technical field
The present invention relates to mechanical antivibration area, particularly relate to a kind of Torsional Vibration of Shafts oscillation damping method and application thereof.
Background technique
For with the wind power generating set of gearbox drive and marine tidal-current energy generator group, its transmission system torsional vibration is based on single order model frequency.Significantly reduce single order modal components in torsional vibration, transmission system will be made to run more steady, the torsional fatigue load of each component is less, is conducive to improving reliability of structure and life-span.
At present in wind power generating set and marine tidal-current energy generator group, the form vibration damping adopting gear box vibration damping to support more.The technological scheme of reduction transmission system torsional vibration common in automobile industry has driven disc type and double Mass Flywheel Type Torsional Vibration Damper.Driven disc type and double Mass Flywheel Type Torsional Vibration Damper are equivalent to mechanical low-pass filter, can effectively reduce dither.These two kinds of modes are all add spring-damper damper unit with cascade on load transfer path, but driven disc type and double Mass Flywheel Type Torsional Vibration Damper need "off" transmission system and add vibration damper with cascade, this just changes the structural type of original transmission system, therefore, these two kinds of technological schemes cannot be implemented in the transmission system run.
Therefore, it is strong how to found a kind of flexibility, can on the basis not destroying transmission system original structure the new Torsional Vibration of Shafts oscillation damping method of effective vibration damping, the target that real genus current industry pole need be improved.
Summary of the invention
The object of this invention is to provide a kind of Torsional Vibration of Shafts oscillation damping method, make that its flexibility is strong, good damping result, can on the basis not destroying transmission system original structure remarkable vibration damping, thus overcome the deficiency of existing vibration damping structure inconvenience later stage reparation.
Another object of the present invention is to provide the application of application said system in the transmission system of wind-force/marine tidal-current energy generator group.
For achieving the above object, the present invention adopts following technological scheme:
A kind of Torsional Vibration of Shafts oscillation damping method, with parallel form, torshional vibration damper is installed on transmission shaft, described torshional vibration damper is tuning rotary inertia damper, and by reducing the level of vibration of certain single order Torsion mode frequency in transmission system around the twist motion of transmission shaft.
Further, described torshional vibration damper is arranged on the maximal phase of certain single order torsion mode vibration shape of described transmission system to corner.
Further, the parameters of described torshional vibration damper obtains in accordance with the following methods: A. calculates the model frequency of former transmission system, determines certain the single order Torsion mode frequency ω needing vibration damping r; B. set μ as the rotary inertia of torshional vibration damper and described certain single order Torsion mode frequency ω rthe ratio of modal mass, selected μ value, and according to calculate the natural frequency of vibration of torshional vibration damper and compare f with the optimum frequency of certain single order Torsion mode frequency opt; According to calculate the optimal damping rate ζ of torshional vibration damper dopt; C. according to I d=μ I modecalculate the rotary inertia I of torshional vibration damper d, wherein I modefor the modal mass of target modalities to be damped; According to ω d=f optω rcalculate the natural frequency of vibration ω of torshional vibration damper d; According to K damper=I dω d 2calculate the torsional stiffness K of torshional vibration damper damper; According to calculate the torsion damping C of torshional vibration damper damper.
Further, in described step B, μ value is 0.01 ~ 0.05.
Further, described torshional vibration damper, for being arranged on rotating loop configuration on described transmission shaft, comprises the flywheel of outer ring portion and the spring-damper structure of annular inner portion, described flywheel and spring-damper anatomical connectivity; When described flywheel and transmission shaft relatively rotate, described spring-damper structure produces the power of circumferencial direction.
Further, described spring-damper structure comprises inner ring and spring-damper unit, described inner ring is radially provided with multiple evagination, the inner edge of described flywheel is radially inwardly provided with multiple convex, described evagination and the mutual intercross arrangement of convex and be uniformly distributed, described spring-damper unit is connected between adjacent evagination and convex.
Further, described spring-damper unit is arranged by single-row or multiple row, and often row distribute along the even circumferential being the center of circle with the ring heart.
Further, described torshional vibration damper comprises the installing sleeve for being fixed on described transmission shaft, and described inner ring is fixedly connected with installing sleeve.
Further, the two ends of described installing sleeve are separately installed with bearing, and the bearing support of described bearing is fixedly connected with the flywheel of described outer ring portion.
The application of described Torsional Vibration of Shafts oscillation damping method is that the axle that is connected with generator at the high speed shaft coupling of wind-force/marine tidal-current energy generator group installs described torshional vibration damper, to reduce the level of vibration of transmission system single order Torsion mode frequency.
Owing to adopting technique scheme, the present invention at least has the following advantages:
(1) driven disc type and double Mass Flywheel Type Torsional Vibration Damper are equivalent to mechanical low-pass filter, can effectively reduce dither; The present invention increases a torshional vibration damper with parallel form on transmission shaft, is equivalent to mechanical trapper, can effectively reduce the level of vibration of a certain modality-specific frequency of torsional direction in transmission system.
(2) driven disc type and double Mass Flywheel Type Torsional Vibration Damper need "off" transmission system and add vibration damper with cascade, and this just changes the structural type of original transmission system, and the transmission system run cannot be implemented.The present invention adds torshional vibration damper with parallel form, does not destroy the form of original transmission system, can be used in the transmission system run, reduces vibration or repairs abnormal vibrations.
(3) method of the present invention can be applied on blower fan but to be not limited to blower fan, also can be applied to marine tidal-current energy generator group or car transmissions etc.To be applied to generator set, the axle that can be connected with generator at high speed shaft coupling is installed the torshional vibration damper of described form, by reducing single order modal components in torsional vibration, transmission system will be made to run more steady, the torsional fatigue load of each component is less, is conducive to improving reliability of structure and life-span.
Accompanying drawing explanation
Above-mentioned is only the general introduction of technical solution of the present invention, and in order to better understand technological means of the present invention, below in conjunction with accompanying drawing and embodiment, the present invention is described in further detail.
Figure 1A is torsional vibration damper schematic diagram.
Figure 1B be in Figure 1A AA to sectional view.
Fig. 2 is former transmission system schematic diagram.
Fig. 3 is the transmission system schematic diagram of band torshional vibration damper.
Fig. 4 is comparison diagram before and after transmission system frequency response curve.
Embodiment
The invention provides a kind of Torsional Vibration of Shafts oscillation damping method, be mainly and add torshional vibration damper with parallel form in transmission system, vibration damping is carried out for modality-specific frequency a certain on torsional direction, Be very effective, and parallel form does not change original drive system structure form, can be used for repairing abnormal vibrations afterwards.
The mechanics principle of this technological scheme is tuning rotary inertia vibration damping, namely tuning rotary inertia damper (comprising rotary inertia block, spring and damping unit) is connected in transmission system, by the control vibration shape resonance of rotary inertia block and transmission system, the torsional vibration energy in transmission system is transferred on tuning rotary inertia damper, thus suppress the torsional vibration of transmission system.
Based on above-mentioned principle, the structure of torshional vibration damper can be designed to following form: one is had flywheel compared with large rotating inertia by spring-damper anatomical connectivity on former transmission shaft, when flywheel and transmission shaft relatively rotate, spring-damper structure produces the power of circumferencial direction.
Below for double-feedback aerogenerator group, introduce embodiments of the present invention and working principle.
As shown in Figure 1A, Figure 1B, torshional vibration damper is arranged on the axle that wind power generating set high speed shaft coupling is connected with generator, the structural type of torshional vibration damper is set to be arranged on rotating loop configuration on transmission shaft 1, comprise the flywheel 7 of outer ring portion and the spring-damper structure of annular inner portion, described flywheel 7 and spring-damper anatomical connectivity; When described torshional vibration damper and transmission shaft 1 relatively rotate, described spring-damper structure produces the power of circumferencial direction.
Installing sleeve 2 is fixedly connected with by interference fit with transmission shaft 1, and the spring-damper structure of torshional vibration damper annular inner portion has inner ring 6, and inner ring 6 is fixed on installing sleeve 2.The two ends of installing sleeve 2 are provided with bearing, are respectively right bearing 3, left bearing 10, corresponding, described right bearing 3 is arranged on right bearing seat 5, and right bearing lid 4 is equipped with in outside; Left bearing 10 is arranged on left shaft holder 8, and left bearing lid 9 is equipped with in outside.Locking nut 11 is threaded connection on installing sleeve 2, for fixing left bearing 10.Left bearing lid 9, right bearing lid 4 are separately fixed on left and right bearing 8,3 by bolt 12; Left shaft holder 8, right bearing seat 5 are fixedly connected with described flywheel 7 by bolt and pad 13.
As shown in Figure 1B, described spring-damper structure comprises multiple spring-damper unit 14, the inner edge of described flywheel 7 is radially inwardly provided with multiple convex, described inner ring 6 is radially provided with multiple evagination, described evagination and convex cross one another and arrange and be uniformly distributed, adjacent evagination be connected described spring-damper unit 14 between convex.
Described multiple spring-damper unit 14 is by axially single-row or multiple row setting, and often row distribute along the even circumferential being the center of circle with the ring heart.Spring-damper unit 14 in Figure 1A, Figure 1B is the form of dually arrayed, and often row circumference uniform distribution 8, is only example, can adopt the form that any number of, any columns of circumference uniform distribution is arranged.Spring in spring-damper unit 14 is including, but not limited to extension spring, Compress Spring, torsion spring etc., and damper includes but not limited to cylinder damper, hydraulic damper etc.
In addition, based on above-mentioned design basic thought, the structure of torshional vibration damper can have following variants:
For being fixedly connected with between transmission shaft 1 with installing sleeve 2, between installing sleeve 2 with torshional vibration damper inner ring 6, the various Connecting format such as the connection of interference fit, key, spline joint, pin connection, expansion set connection, profile connection, astrolabe connection can be adopted.
Bearing 3,10 is rolling bearing, includes but not limited to all kinds of rolling bearing such as deep groove ball bearing, tapered roller bearing.Right side bearing 3 is by right side bearing cap 4, right-hand axis bearing 5 support flying wheel 7, and left side bearing 10 is by left side bearing cap 9, Left hand bearing block 8 support flying wheel 7.Bearing 3,10 makes flywheel 7 can make circular-rotation around transmission shaft 1.
Based on above-mentioned form of implementation, the brief introduction of work principle of oscillation damping method of the present invention is as follows.
When not installing torshional vibration damper, as shown in Figure 2, transmission system can be reduced to two quality spring oscillators, and namely wind wheel is connected with torsion spring-damping unit with generator amature.
Note: in Fig. 2, the rotary inertia of wind wheel and generator amature, transmission system rigidity, damping constant are the numerical value of equivalence to high speed shaft side, all like this below.
The undamped model frequency of former transmission system is:
ω n = K drivetrain ( I r + I g ) I r I g
Wherein:
I r---wind wheel rotary inertia
I g---generator amature rotary inertia
K drivetrain---the transmission system torsional stiffness of equivalence
Damping ratio is:
ζ = C drivetrain 2 K drivetrain · I r I g I r + I g
Wherein:
C drivetrain---the transmission system of equivalence reverses damping
Damping model frequency is had to be:
ω r = ω n 1 - ζ 2
The model frequency ω herein calculated rfor transmission system fundamental frequency.The torsional vibration of the component in wind power generating set transmission system, based on this frequency content, therefore, specifies the single order model frequency reducing wind power generating set transmission system herein.
After the axle that high speed shaft coupling is connected with generator installs torshional vibration damper, the dynamic model of transmission system as shown in Figure 3:
Wherein:
I d---the rotary inertia of torshional vibration damper
K damper---the torsional stiffness of torshional vibration damper
C damper---the torsion damping of torshional vibration damper
For convenience of discussing, created symbol:
The ratio of μ---torshional vibration damper and the rotary inertia of former transmission system,
ω d---the natural frequency of vibration of torshional vibration damper,
ζ d---the damping ratio of torshional vibration damper,
The natural frequency of vibration of f---torshional vibration damper and the ratio of former transmission system frequency,
When frequency than f close to 1 time, torshional vibration damper and former driveline resonance, by the vibrational energy transfer in former transmission system on torshional vibration damper, thus suppress the torsional vibration of former transmission system.
According to the vibration attenuation mechanism of tuning rotary inertia damper, the optimal parameter of torshional vibration damper is:
f opt = 1 1 + μ
ζ d opt = 3 μ 8 ( 1 + μ )
For with the wind power generating set of gearbox drive and marine tidal-current energy generator group, its transmission system torsional vibration is based on single order model frequency.Utilize method provided by the invention significantly to reduce single order modal components in torsional vibration, transmission system will be made to run more steady, the torsional fatigue load of each component is less, is conducive to improving reliability of structure and life-span.As shown in Figure 4, after installing torsional vibration damper, the torsion vibration response amplitude of transmission system significantly reduces.
Oscillation damping method of the present invention, when practical application, is not limited to and installs described form torshional vibration damper in wind power generating set transmission system, can be applicable in the transmission system of any products, as marine tidal-current energy generator set or car transmissions.And, significantly can reduce the torsional vibration of former transmission system near setting model frequency, setting model frequency can be the model frequency of specifying arbitrarily order, such as the 2nd rank or the 5th rank etc., but vibration damping can only be carried out for certain single order, the level of vibration of two rank modal components can not be reduced simultaneously.
For different transmission systems, the design cycle of torshional vibration damper can be undertaken by following process:
First calculate the model frequency of former transmission system, and determine the frequencies omega of certain the single order mode needing vibration damping rwith Mode Shape maximal phase to corner.Mode Shape maximal phase is the mounting point of torshional vibration damper to corner, is arranged on the place that in Mode Shape, relative rotation is large as much as possible, can improve effectiveness in vibration suppression.
Determine the ratio of inertias μ of torshional vibration damper, calculate the rotary inertia I of torshional vibration damper d.μ is larger, and effectiveness in vibration suppression is better, but cost is higher.According to engineering practical experience, generally, μ gets 0.01 ~ 0.05.
For fan transmission system, I d=μ (I r+ I g).
For other transmission systems, I d=μ I mode.Wherein I modefor the modal mass of target modalities to be damped.
According to selected ratio of inertias μ, calculate optimum frequency ratio
Then the natural frequency of vibration of torshional vibration damper is:
ω d＝f optω r
The torsional stiffness of torshional vibration damper is:
K damper＝I dω d 2
According to selected ratio of inertias μ, calculate the optimal damping rate of torshional vibration damper
Then the torsion damping of torshional vibration damper is:
C damper = 2 ζ d opt K damper I d = 2 ζ d opt ω d I d
According to the rotary inertia I of the torshional vibration damper calculated d, torsional stiffness K damper, reverse damping C damper, in conjunction with the structural limitations of former transmission system, carry out the detail design of torshional vibration damper with reference to Figure 1A, Figure 1B, comprise the rotary inertia etc. of structural type, specification, spring-damper element number, the rigidity of spring-damper unit and damping constant, flywheel.
Specifically, the outer ring of flywheel 7, left shaft holder 8, right bearing seat 5, left bearing lid 9, right bearing lid 4, left bearing 10, the outer ring of right bearing 3 and between total rotary inertia of connecting bolt be the rotary inertia I calculated d, the equivalent torsional stiffness of spring-damper unit 14 is the K calculated damper, equivalence is reversed damping and is the C calculated damper.
For the structure in Figure 1A, Figure 1B, spring-damper unit 14 is dually arrayed, often row circumference uniform distribution 8, amounts to 16.For pressure-bearing spring, pressure-bearing damping, when flywheel 7 relatively transmission shaft 1 clockwise or when rotating counterclockwise, often arrange and circumferentially have 4 spring-damper unit 14 to produce relatively rotating of restoring force opposing flywheel 7 and transmission shaft 1, biserial amounts to 8 spring-damper unit 14 and produces restoring force.If the rigidity of each spring-damper unit 14 is K 1, damping is C 1; The spring-damper unit 14 be uniformly distributed along the circumference is R (diameter of the circumference that spring-damper unit 14 is formed is 2R) with the shaft axis distance of transmission shaft 1.Then have:
K damper＝8K 1R 2
C damper＝8C 1R 2
So the rigidity of spring-damper unit 14 is: damping is:
The above; it is only preferred embodiment of the present invention; not do any pro forma restriction to the present invention, those skilled in the art utilize the technology contents of above-mentioned announcement to make a little simple modification, equivalent variations or modification, all drop in protection scope of the present invention.

Claims (10)

1. a Torsional Vibration of Shafts oscillation damping method, it is characterized in that, be install torshional vibration damper with parallel form on transmission shaft, described torshional vibration damper is tuning rotary inertia damper, and by reducing the level of vibration of certain single order Torsion mode frequency in transmission system around the twist motion of transmission shaft.
2. Torsional Vibration of Shafts oscillation damping method according to claim 1, is characterized in that, described torshional vibration damper is arranged on the maximal phase of certain single order torsion mode vibration shape of described transmission system to corner.
3. Torsional Vibration of Shafts oscillation damping method according to claim 1, is characterized in that, the parameters of described torshional vibration damper obtains in accordance with the following methods:
A. calculate the model frequency of former transmission system, determine certain the single order Torsion mode frequency ω needing vibration damping r;
B. set μ as the rotary inertia of torshional vibration damper and described certain single order Torsion mode frequency ω rthe ratio of modal mass, selected μ value, and according to calculate the natural frequency of vibration of torshional vibration damper and compare f with the optimum frequency of certain single order Torsion mode frequency opt; According to calculate the optimal damping rate ζ of torshional vibration damper dopt;
C. according to I d=μ I modecalculate the rotary inertia I of torshional vibration damper d, wherein I modefor the modal mass of target modalities to be damped;
According to ω d=f optω rcalculate the natural frequency of vibration ω of torshional vibration damper d;
According to K damper=I dω d 2calculate the torsional stiffness K of torshional vibration damper damper;
According to calculate the torsion damping C of torshional vibration damper damper.
4. Torsional Vibration of Shafts oscillation damping method according to claim 3, is characterized in that, in described step B, μ value is 0.01 ~ 0.05.
5. Torsional Vibration of Shafts oscillation damping method according to claim 1, it is characterized in that, described torshional vibration damper, for being arranged on rotating loop configuration on described transmission shaft, comprises the flywheel of outer ring portion and the spring-damper structure of annular inner portion, described flywheel and spring-damper anatomical connectivity; When described flywheel and transmission shaft relatively rotate, described spring-damper structure produces the power of circumferencial direction.
6. Torsional Vibration of Shafts oscillation damping method according to claim 5, it is characterized in that, described spring-damper structure comprises inner ring and spring-damper unit, described inner ring is radially provided with multiple evagination, the inner edge of described flywheel is radially inwardly provided with multiple convex, described evagination and the mutual intercross arrangement of convex and be uniformly distributed, described spring-damper unit is connected between adjacent evagination and convex.
7. Torsional Vibration of Shafts oscillation damping method according to claim 6, is characterized in that, described spring-damper unit is arranged by single-row or multiple row, and often row distribute along the even circumferential being the center of circle with the ring heart.
8. Torsional Vibration of Shafts oscillation damping method according to claim 6, is characterized in that, described torshional vibration damper comprises the installing sleeve for being fixed on described transmission shaft, and described inner ring is fixedly connected with installing sleeve.
9. Torsional Vibration of Shafts oscillation damping method according to claim 7, is characterized in that, the two ends of described installing sleeve are separately installed with bearing, and the bearing support of described bearing is fixedly connected with the flywheel of described outer ring portion.
10. the application of the Torsional Vibration of Shafts oscillation damping method described in any one of claim 1-9, it is characterized in that, that the axle that is connected with generator at the high speed shaft coupling of wind-force/marine tidal-current energy generator group installs described torshional vibration damper, to reduce the level of vibration of transmission system single order Torsion mode frequency.
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WO2017070915A1 (en) * 2015-10-30 2017-05-04 林高合 Flywheel device
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CN109899448A (en) * 2019-03-11 2019-06-18 汉腾汽车有限公司 A kind of automobile twisting vibration wideband vibration and noise reducing device
CN110103972A (en) * 2019-05-23 2019-08-09 衢州职业技术学院 Vehicle multi power source coupled drive system torsional resonance control method
CN111288149A (en) * 2020-02-12 2020-06-16 常州工学院 Portable high damping is gyration power vibration attenuation gear drive for axle
CN112560216A (en) * 2019-09-24 2021-03-26 上海汽车集团股份有限公司 Parameter configuration method and device and vehicle
CN115030986A (en) * 2022-05-13 2022-09-09 安徽工程大学 Piezoelectric active flywheel for suppressing torsional vibration of vehicle transmission shaft and control method

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Cited By (11)

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Publication number Priority date Publication date Assignee Title
WO2017070915A1 (en) * 2015-10-30 2017-05-04 林高合 Flywheel device
CN109654162A (en) * 2019-02-01 2019-04-19 青岛理工大学 Actively compound variable damping control device for pivoting
CN109654162B (en) * 2019-02-01 2024-04-12 青岛理工大学 Active composite damping-variable rotation control device
CN109899448A (en) * 2019-03-11 2019-06-18 汉腾汽车有限公司 A kind of automobile twisting vibration wideband vibration and noise reducing device
CN110103972A (en) * 2019-05-23 2019-08-09 衢州职业技术学院 Vehicle multi power source coupled drive system torsional resonance control method
CN110103972B (en) * 2019-05-23 2020-09-01 衢州职业技术学院 Torsional resonance control method for vehicle multi-power-source coupling transmission system
CN112560216A (en) * 2019-09-24 2021-03-26 上海汽车集团股份有限公司 Parameter configuration method and device and vehicle
CN111288149A (en) * 2020-02-12 2020-06-16 常州工学院 Portable high damping is gyration power vibration attenuation gear drive for axle
CN111288149B (en) * 2020-02-12 2021-09-28 常州工学院 Portable high damping is gyration power vibration attenuation gear drive for axle
CN115030986A (en) * 2022-05-13 2022-09-09 安徽工程大学 Piezoelectric active flywheel for suppressing torsional vibration of vehicle transmission shaft and control method
CN115030986B (en) * 2022-05-13 2023-04-18 安徽工程大学 Piezoelectric active flywheel for suppressing torsional vibration of vehicle transmission shaft and control method

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