CN1132323A - Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance - Google Patents
Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance Download PDFInfo
- Publication number
- CN1132323A CN1132323A CN 95102823 CN95102823A CN1132323A CN 1132323 A CN1132323 A CN 1132323A CN 95102823 CN95102823 CN 95102823 CN 95102823 A CN95102823 A CN 95102823A CN 1132323 A CN1132323 A CN 1132323A
- Authority
- CN
- China
- Prior art keywords
- bearing
- vibration
- dynamic
- rigidity coefficient
- supports
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Testing Of Balance (AREA)
Abstract
A dynamic rigidity method and its appts. for the dynamic balance of rotary machine, esp. the rotary machine set with rotor whose distributed mass is continuous and multiple supporters feature that based on the equivalent dynamic rigidity coefficient Kd in vibration array equation: Kd]{Xs}={R'} of equivalent bearing mechanical model is a constant under a certain work condition, a special computer is used to calculate Kd or by slecting approximate Kd to preferably calculate optimal balancing weights and predetermine residual vibration according to measured Xs and R'. Its advantages are high balance precision and shorter balancing period.
Description
The invention provides dynamically balanced dynamic rigidity coefficient method of a kind of rotating machinery and device thereof, belong to the rotating machinery dynamic balancing technique of mechanical field.
Modern age, the rotating machinery dynamic balance method mainly contained two kinds, and a kind of is method of modal balancing, and another kind is an influence coefficient method; at present; improved dynamic balance method is called associating balancing method (UBA method), is that above-mentioned two kinds of methods are combined; vibration shape influence coefficient method and vibration shape circule method are arranged; though wherein vibration shape circule method can be found out ' high point ' and ' emphasis ' quickly on polar coordinates, it is comparatively reliable that examination is for the first time increased the weight of, in the multi-support system; still need examination several times to increase the weight of, open several times, shut down.The patent that have people such as nineteen eighty-three HIT Sato Kazuo deliver more approaching: introduced in " method of rotating machinery balance and device thereof " ' obtaining theoretical method and the application thereof that influence coefficient carries out balance ' by the impedance matrix of bearing spider with the present invention; Tang of Tsing-Hua University tin in 1985 is wide at " (ASME " (85-DET-120,7P) introduced the method for ' calculate the dynamic effects coefficient, and then calculating counterweight ' in " determining rotatory mechanical system bottom bracket equiva lent impedance and influence coefficient " that magazine is delivered with stiffness coefficient and the damping constant measured by calculating with test; They are at common feature: measured vibrational state amount is shaft vibration amount and bearing dynamic anti-force, and all on axle, two measuring points that are mutually the right angle will be put to measuring point at least in each bearing place.Their common shortcoming is in the dynamic balancing of multi-support rotation unit: all need repeatedly to try to increase the weight of, balance quality is low, opens, shuts down often.
The purpose of this invention is to provide dynamically balanced dynamic rigidity coefficient method of a kind of rotating machinery and device thereof, improve the precision of EQUILIBRIUM CALCULATION FOR PROCESS, make rotating machinery (unit) open, stop number of times and reduce to effectively 1～2 time.
The basis of ' the dynamically balanced dynamic rigidity coefficient method of rotating machinery ' provided by the invention its measurements and calculations is set up a Fig. 1 and is illustrated, the continuous rotor multispan of reflection distributed mass is bearing in the Equivalent Elasticity damping supporting seat model on several same orientation, it is rotor-supporting system dynamic model, rotor-supporting system is divided into two subtense angles, be rotor-support-foundation system and support system, its separating surface is taken on rotor journal and the bearing bearing shell oil film surface of contact, two subtense angles are set up the motion equation of oneself respectively, therebetween by a pair of bonding force: bearing dynamic anti-force R and bearing dynamic force R's '
{ R}=-{R ' }------(1) relation interrelates, with the vibration matrix equation of equivalent bearing mechanical model shown in Figure 2:
[K
d] { X
s}={ R ' }---(2) calculate bearing dynamic force R ', the accurate equivalent dynamic rigidity coefficient K of bearing
dAnd bearing residual oscillation amount X
s, be characterized in: with this Equivalent Elasticity damping support model, replaced four stiffness coefficients of anisotropy bearing and the bearing model of four damping constants, it only needs a stiffness coefficient and a damping constant, therefore, and each vibration of supports amount X
sMeasuring point only need one, the measuring point of bearing dynamic force R ' also only needs one, these two measuring points must be placed on same the radial line of supporting point; Measuring point on each bearing all will be placed on the plane of same axis excessively, and promptly its azimythal angle is ; Equivalence dynamic rigidity coefficient K
dIn [1] corresponding to V
cPlant under the operating load situation, [2] are at selected ω
kUnder the rotating speed, [3] have under the situation of definite selected correcting plane position and number m is a constant.
In order to calculate bearing dynamic force R ' and vibration of supports amount X
s, on considering rotor-support-foundation system, the given excitation force that always increases the weight of to be produced, also need take into account the caused additional uneven excitation force of rotor-support-foundation system unbalance response.For this reason, rotor-support-foundation system is reduced to lump quality rotator model shown in Figure 3.With rotor-supporting system dynamical balancing condition and condition of compatible deformation:
∑ M
x=0, ∑ M
y=0; [δ
Ij] { R
i}+{ S
Ip}={ X
Si---(3) and the transfer matrix that calculates the rotor-support-foundation system unbalance response:
{ Z}
i={ T}
I-1[T]
I-2..., [T]
1[P] { Z}
1---bearing dynamic force and vibration of supports amount are calculated in------(4), in the formula:
--the aequum of j correcting plane
The inertial force that is produced and since the rotor dynamic deformation cause
Additional uneven excitation force;
-the i indeterminate or static determinacy bearing dynamic anti-force;
All external force of-rotor and couple are respectively in the moment on ozy plane and ozx plane;
-each bearing exists
Vibratory output under the effect;
Flexibility under the unit load of each relevant point of-rotor can be calculated by Mohr integration or transfer matrix method;
S
Ip-rotor unbalance inertial force also can be calculated by Mohr integration or transfer matrix method at the deformation values of each relevant point;
ω
k-the k balancing speed.
---the initial state vector
---I cross section state vector [T]
i=[B]
i[D]
i------disk and shaft part composition element transfer matrix [B]
i---------no quality shaft part field battle array [D]
i---------making an inventory in the garden,---------initial matrix is used balance target equation peace treaty Shu Fangcheng to battle array [P] again: max{| ε
Si(ω
k, V
c, m, ) | → min ε
Si(ω
k, V
c, m, )=X
Si(ω
k, V
c, m, )+X
Oi(ω
k, V
c, m, ) [K
d] { x
s}={ R ' }------(5)
Come computation optimization the best on selected correcting plane to become set of weights U, in the formula: X
OiThe original vibration of supports amount of------i bearing measuring point record;
X
SiVibration of supports amount behind the increasing the weight of of------i bearing measuring point record;
ε
SiThe remaining vibration of supports amount of------i bearing measuring point record;
I=1,2 ...., n,---bearing measuring point number;
K=1, ... ..,, K+1, K+2, K combined critical speed;
Rated speed under K+1------is unloaded;
Rotating speed during K+2------full load;
C=1,2 ...., the c operating conditions, refer generally under the various loads and operating mode at full capacity steady in a long-term under;
The correcting plane number that m------is selected;
G
r------rotor quality;
The azimythal angle of ------supporting place measuring point;
U
j=m
jr
j---the aequum (mass-redius product) of correcting plane;
[G
r] the quality battle array of------rotor-support-foundation system;
[C
r] the damping battle array of------rotor-support-foundation system;
[K
r] Stiffness Matrix of------rotor-support-foundation system;
{ R}------bearing dynamic anti-force array; The external force array of { F}------rotor-support-foundation system;
The relevant matrix of flywheel moment of [J]------rotor-support-foundation system, J is an antisymmetric matrix, each element is a polar moment of inertia;
X},
The vibratory output array of-rotor-support-foundation system; Wherein x} is a rotor vibration displacement response battle array,
Be rotor oscillation speed responsive battle array,
It is rotor oscillation acceleration responsive battle array;
The method of computation optimization is:
With known support system equivalence dynamic rigidity coefficient [K
d], just can adopt coordinate to rotate the direction search method by formula (5), constantly change F
j, { R} can obtain at { R ' } the vibration of supports amount that produced under the effect (watt shake) { X again by formula (2) to utilize aforementioned (3), (4) formula can obtain bearing dynamic anti-force
s, warp and the former { X that shakes
0Superposition, can calculate residual oscillation amount { ε
Si, if be tending towards reducing, then continue this direction optimization, otherwise change F
jAnother coordinate direction respectively supports residual oscillation amount { ε until obtaining to make
SiThe optimum balance amount U that is all hour
j, each correcting plane is searched for down successively, until under the operating mode of selected plane, obtains the best set of weights value { U of one-tenth
j.
For this reason, all formula also need measure the position number of distance between each measuring point, each selected rectifying plane and increase the weight of radius, axle is the axial dimension of each section and the inside and outside footpath size of rotating shaft.
Then ' the dynamically balanced dynamic rigidity coefficient method of rotating machinery ' of the present invention's proposition finished by following three steps at least:
The first step ties up to corresponding to V unbalanced rotor and axle
cPlant under the operating load situation, at selected ω
kUnder the rotating speed, selected under the situation of the position of correcting plane and number m, measured the original vibration of supports quantity of state of each bearing, said vibration of supports quantity of state comprises vibration of supports amount X
sWith bearing dynamic force R '; And original vibration of supports quantity of state is meant original vibration of supports amount X
0With the dynamic R of original bearing
0'; And be confirmed to be mass unbalance with conventional means;
Second step: according to each the original vibration of supports amount X that measures
0With each the original bearing dynamic force R that measures
0' substitution formula (2) calculates the accurate equivalent dynamic rigidity coefficient K of each bearing
d, the best of being obtained on the selected correcting plane by formula (3), (4), (5) becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing again
Si
The 3rd step: after selected plane adds the best set of weights U of one-tenth, measure the remaining vibration of supports amount ε of each bearing
SiLess than permitted value, balance finishes.
If the vibrational state amount of each measured bearing is only measured original vibration of supports amount X in the first step
0, then second step just needed the original vibration of supports amount X according to each bearing of measuring
0With a selected Approximate Equivalent dynamic rigidity coefficient Kd, calculate and on selected correcting plane, be approximated to set of weights U
x, the 3rd step added at selected correcting plane and is approximated to set of weights U
1After (as just increasing the weight of), measure the first vibration of supports amount X that increases the weight of of each bearing
1, if X
1Value is less than permitted value, and then balance finishes, if X
1Value just need be carried out for the 4th step, according to each the original vibration of supports amount X that measures still greater than permitted value
0With each the first vibration of supports amount X that increases the weight of that measures
1Between variable quantity X
sCalculate the accurate equivalent dynamic rigidity coefficient Kd of each bearing, thereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing
SiThe 5th step added the best set of weights U of one-tenth at selected correcting plane, measured the remaining vibration of supports amount ε of each bearing
SiLess than permitted value, balance finishes.
Approximate Equivalent dynamic rigidity coefficient Kd chooses, optional one of the two kinds of situations of stating of taking off: the unit that [1] was crossed for former lack of equilibrium is to take the numerical value that has same model unit in the database, unit of the same type once used accurate equivalent dynamic rigidity coefficient Kd on its balance history, as the Approximate Equivalent dynamic rigidity coefficient, can obtain the scene with it and be balanced the rotation unit and on selected correcting plane, be approximated to set of weights U
1, as just increasing the weight of.[2] for the unit of crossing with forward horizontal stand, (has a correcting plane position at least with its balance record, a balancing speed and two measuring point vibratory output change records), be balanced with formula (2), (3), (4), (5) scene of calculating and be approximated to set of weights U on the Approximate Equivalent dynamic rigidity coefficient of rotation unit relevant bearing and the selected correcting plane
1, as just increasing the weight of.
The invention provides the dynamically balanced dynamic rigidity coefficient Equilibrator of a kind of rotating machinery, its functional-block diagram illustrates at Fig. 4, and it comprises conventional vibratory output sensor, vibration force sensor (404), eddy current head (405) and photoelectrical head measuring elements such as (406); Vibration measurement signal front processor (407)～(415) that the with dashed lines frame table shows; With a special-purpose host computer (416); Wherein, special-purpose host computer (416) has and vibration measurement signal front processor special purpose interface, display device or printer interface, and has a computer that comprises bearing dynamic force computing module (418), bearing equivalence dynamic rigidity coefficient computing module (419), becomes set of weights and remaining vibration of supports amount computing module (420) and exclusive data library management and maintenance program module four software modules such as (421), it can finish all calculating in the aforementioned equilibrium step according to program shown in Figure 5, and this computer is portable computer preferably.Its measurement signal front processor is made up of attenuator (407), amplifier (408), shaping amplifier (409), wave filter (410), phase-locked loop circuit (411), analog-digital converter (412), central data processing single chip (413), RAM storage chip (414) and EPROM chip (415), and their single line annexation is: the one tunnel is that (407) connect (409) and connect (411) and connect (412) and be connected to (413); Same (408) of two-way connect (410) and are connected to (413) in addition, and two feedback lines of (413) are connected to two (408) respectively; (411) the two other line is connected to respectively on two (410); (414), (415) have bidirectional cable to be connected with (413) respectively; The interface that vibration transducer (404) are arranged on two (408) has the interface of eddy current head (405) on (407), the interface of photoelectrical head is arranged on (409), and the interface that links to each other with private host calculation machine is arranged on (413).(417) be display device or the printer that is connected on the host computer, wherein, the computing module of bearing dynamic force R ' is the vibration of supports amount X that measures according to the vibratory output sensor that has according to formula (3), (4) establishment
sCalculate bearing dynamic force R ' and utilize bearing dynamic force R ' data computing software that the vibration force sensor directly measures therein module admittedly; Bearing equivalence dynamic rigidity coefficient computing module is the original vibration of supports amount Xo value measured according to the vibratory output sensor according to having of formula (2) establishment and the bearing dynamic force R ' value that is calculated by bearing dynamic force computing module or is solidificated in wherein module with the software for calculation that bearing dynamic force R ' value that the vibration force sensor is directly measured calculates the equivalent dynamic rigidity coefficient of bearing; Becoming set of weights and remaining vibration of supports amount computing module is that the original vibration of supports amount Xo value of measuring according to the vibratory output sensor according to having of formula (5) establishment, the numerical value of each bearing equivalence dynamic rigidity coefficient Kd, selected correcting plane position and number m and Vc kind operation conditions parameter come computation optimization to go out selecting the best that correcting plane need add to become the software for calculation of set of weights and remaining vibration of supports amount to be solidificated in wherein module; Exclusive data library management and maintenance program module are to have storage and call the structural parameter of various rotary machine rotor-supporting systems and the management of the accurate equivalent dynamic rigidity coefficient of each bearing of dynamic balancing history record and maintenance program are solidificated in wherein module.
Advantage of the present invention and beneficial effect are:
[1] balance quality height.Because the present invention has adopted the accurate equivalent dynamic rigidity coefficient and the optimized calculation method of bearing, has simplified measurements and calculations, improved the degree of accuracy that calculating optimum becomes set of weights.Only survey the vibratory output and the dynamic force of bearing common-azimuth, become set of weights and precompute remaining vibration of supports amount, can both reach the good criteria of vibration permitted value with the straightforward computation optimization the best of accurate equivalent dynamic rigidity coefficient.
[2] do not need examination to increase the weight of.Be to calculate with the Approximate Equivalent dynamic rigidity coefficient to be approximated to set of weights, just can calculate best one-tenth set of weights, do not need calculating influence coefficient as just increasing the weight of the back for the first time.
[3] reduce the on-the-spot number of starts that is balanced unit effectively, shortened the balance duration.This method only need add and restarts 1～2 time, and promptly only need open, shut down 1～2 time, behind the 3rd step or the 5th step starting up, be the balance success.
Suitable general enclosing extensively of the present invention, it both had been applicable to the dynamic balancing of stiffness rotor and axle system thereof, was applicable to the dynamic balancing that supercritical rotor and axle thereof are again; Can be used for hard bearing dynamic balancing machine, use in the dynamic balancing at the scene again, also can be used for the hot dynamic balancing of Turbo-generator Set.
Description of drawings: Fig. 1: the dynamic model figure of rotor-supporting system
Among the figure: G
S1, G
S2, G
SnRepresent the 1 2nd and the mass of vibration of n bearing respectively,
C
O1, C
O2, C
OnRepresent the 1 2nd and the equivalent oil-film damping coefficient of n bearing respectively,
C
S1, G
S2, C
SnRepresent the 1 2nd and the equivalent basic damping constant of n bearing respectively,
K
O1, K
O2, K
OnRepresent the 1 2nd and the equivalent oil film rigidity coefficient of n bearing respectively,
K
S1, K
S2, K
SnRepresent the 1 2nd and the equivalent soil rigidity coefficient of n bearing respectively,
ω
K------angular velocity of rotor during balance,
The azimuth view 2 on axis plane is crossed at ------measuring point place: the mechanical model figure of support system
Among the figure: K
d-bearing equivalence dynamic rigidity coefficient
X
sThe vibratory output of-bearing under R ' effect
Dynamic force Fig. 3 that R '-bearing bore: rotor-support-foundation system mechanical model figure
Among the figure:
--the inertial force that aequum Uj produced on j correcting plane
-the i indeterminate or static determinacy bearing dynamic anti-force;
M-correcting plane number
N-bearing number Fig. 4: among the rotating machinery dynamic poise device functional-block diagram figure: 401-is balanced rotor, and 402, the left and right supporting system of 403-,
The 404-vibration transducer, 405-eddy current head, the 406-photoelectrical head,
The 407-attenuator, 408-amplifier, 409-shaping amplifier
The 410-wave filter, the 411-phase-locked loop circuit, the 412-analog-digital converter,
The 413-8098 single-chip microcomputer, the 414-RAM storage chip, the 415-EPROM chip,
The 416-host computer, the 417-CRT display device, the computing module of 418-bearing dynamic force,
The computing module of 419-bearing equivalence dynamic rigidity coefficient,
420-becomes the computing module of set of weights and residual oscillation amount,
421-whirler set type size equivalence dynamic rigidity coefficient increases the weight of the database management module of operating mode, Fig. 5: dynamic rigidity coefficient EQUILIBRIUM CALCULATION FOR PROCESS program master block diagram
The invention will be further described with embodiment below:
Embodiment 2, to the calculating that just increases the weight of on two rectifying planes of the northeast second 3# of power plant unit (200MW) spreading axle, it is used accurate equivalent dynamic rigidity coefficient when utilizing Hebei first power plant unit balance of the same type, Approximate Equivalent dynamic rigidity coefficient Kd as this unit, calculate and just increase the weight of, after adding, each vibration of supports amount of unit changes, and then shake and just increase the weight of the vibratory output of each bearing of back according to each bearing of this unit former, just can utilize the accurate equivalent dynamic rigidity coefficient that calculates each bearing of this unit in the special-purpose computer of the present invention, with the best counterweight on these two rectifying planes, after adding, each vibration of supports of unit drops to below 30 microns by 59 microns, and secondary increases the weight of unit and reaches good vibration standard.
Embodiment 3, third 3# of the power plant unit (200MW), six rectifying planes in northeast (are pressed rotor low voltage side rectifying plane P3 promptly, two rectifying plane J3 of spreading axle and J4, two rectifying plane L4 of low pressure rotor and L5, and low pressure rotor and generator amature shaft coupling rectifying plane L6) on the calculating that increases the weight of simultaneously, utilize the equivalent dynamic rigidity coefficient and the original vibration values of each bearing of this unit of the unit of being stored in the special-purpose computer database of the present invention of the same type exactly, calculate the best counterweight on these six rectifying planes, once increase the weight of, each vibration of supports of unit as a result, drop to 17.2 microns by 30 microns, reach outstanding vibration standard.
Embodiment 4, and (hard supporting) carries out dynamic balance running to a 100MW rotor of steam turbo generator on large-scale supercritical rotor dynamic balance running platform.Measure at first, simultaneously at the vibratory output of measuring point on each bearing under the certain load operating mode, under certain balancing speed
With bearing dynamic force R ', then, the position dimension of four selected correcting planes is input in the special-purpose computer of the present invention, very fast, this computer becomes set of weights through the best that the middle distance preface of Fig. 5 calculates on four correcting planes, and has estimated the remaining vibration of supports amount of each bearing, the result, once add restarting, measure rotor, bearing residual oscillation amount is superior, balance finishes.
Claims (10)
1, the dynamically balanced dynamic rigidity coefficient method of a kind of rotating machinery, it is characterized in that: the basis of its measurements and calculations is to set up one to reflect that the continuous rotor multispan of distributed mass is bearing in the Equivalent Elasticity damping supporting seat model on several same orientation, it is rotor-supporting system dynamic model, rotor-supporting system is divided into two subtense angles, be rotor-support-foundation system and support system, two subtense angles are set up the motion equation of oneself respectively, its separating surface is taken on rotor journal and the bearing bearing shell oil film surface of contact, therebetween by a pair of bonding force: { R}=-{R ' } relation of bearing dynamic anti-force R and bearing dynamic force R ' interrelates, and uses the vibration matrix equation of bearing: [K
d] { X
s}={ R ' } calculating bearing dynamic force R ', the accurate equivalent dynamic rigidity coefficient K of bearing
dAnd vibration of supports amount X
sBe characterized in: with an equivalent flexible damping support model, replaced four stiffness coefficients of anisotropy bearing and the bearing model of four damping constants, this Equivalent Elasticity damping support model only needs a stiffness coefficient and a damping constant, therefore, each vibration of supports amount X
sMeasuring point only need one, the measuring point of bearing dynamic force R ' also only needs one, these two measuring points must be placed on same the radial line of supporting point; Measuring point on each bearing all will be placed on the plane of same axis excessively, and promptly its azimythal angle is ; Equivalence dynamic rigidity coefficient K
dIn (1) corresponding to V
cPlant under the operating load situation, (2) are at selected ω
kUnder the rotating speed, (3) have under the situation of definite selected correcting plane position and number m is a constant, with rotor-supporting system dynamical balancing condition and condition of compatible deformation:
∑ M
x=0, ∑ M
y=0, [δ
Ij] { R
i}+{ S
Ip}={ X
Si, and the transfer matrix that calculates the rotor-support-foundation system unbalance response:
{ Z}
i={ T}
I-1[T]
I-2..., [T]
1[P] { Z}
1Calculate bearing dynamic force and vibration of supports amount, use balance target equation again:
max{| ε
si(ω
k，V
c，m，)|}→min
Come computation optimization the best on selected correcting plane to become set of weights U, like this, the dynamically balanced dynamic rigidity coefficient method of rotating machinery is finished by following three steps at least: the first step: measure the original vibration of supports quantity of state of each bearing in unbalanced rotor and the axle system, said vibration of supports quantity of state comprises vibration of supports amount X
sWith bearing dynamic force R '; And original vibration of supports quantity of state is meant original vibration of supports amount X
0With original bearing dynamic force R
0'; And be confirmed to be mass unbalance with conventional means;
Second step: according to each the original vibration of supports amount X that measures
0With each the original bearing dynamic force R that measures
0' calculate the accurate equivalent dynamic rigidity coefficient K of each bearing
dThereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing
Si
The 3rd step: after selected plane adds the best set of weights U of one-tenth, measure the remaining vibration of supports amount ε of each bearing
SiLess than permitted value, balance finishes.
2, the dynamically balanced dynamic rigidity coefficient method of rotating machinery as claimed in claim 1 is characterized in that: the vibrational state amount of each measured bearing is only measured original vibration of supports amount X in the first step
0, then second step just needed the original vibration of supports amount X according to each bearing of measuring
0With a selected Approximate Equivalent dynamic rigidity coefficient K
d, calculate and on selected correcting plane, be approximated to set of weights U
1, the 3rd step added at selected correcting plane and is approximated to set of weights U
1After (as just increasing the weight of), measure the first vibration of supports amount X that increases the weight of of each bearing
1, if X
1Value is less than permitted value, and then balance finishes, if X
1Value just need be carried out for the 4th step, according to each the original vibration of supports amount X that measures still greater than permitted value
0With each the first vibration of supports amount X that increases the weight of that measures
1Between variable quantity X
sCalculate the accurate equivalent dynamic rigidity coefficient K of each bearing
dThereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing
SiThe 5th step added the best set of weights U of one-tenth at selected correcting plane, measured the remaining vibration of supports amount ε of each bearing
SiLess than permitted value, balance finishes.
3, the dynamically balanced dynamic rigidity coefficient method of rotating machinery as claimed in claim 1 or 2 is characterized in that: Approximate Equivalent dynamic rigidity coefficient K
dBe to take to have same model unit in the database, unit of the same type once used accurate equivalent dynamic rigidity coefficient K on its balance history
dNumerical value, can obtain the scene with it and be balanced the rotation unit and on selected correcting plane, be approximated to set of weights U
1, as just increasing the weight of.
4, as claim 1 or 2 or 3, the dynamically balanced dynamic rigidity coefficient method of described rotating machinery is characterized in that: all calculation procedures also need measure the position of distance between each measuring point, each selected rectifying plane and increase the weight of radius, axle is the axial dimension of each section and the inside and outside footpath size of rotating shaft.
5, the dynamically balanced dynamic rigidity coefficient Equilibrator of a kind of rotating machinery is characterized in that: it comprises conventional vibratory output sensor, vibration force sensor (404), eddy current head (405) and photoelectrical head measuring elements such as (406); A vibration measurement signal front processor (407)～(415); With a special-purpose host computer (416); Wherein special-purpose computer (416) has and vibration measurement signal front processor special purpose interface, display interface device, printer interface, and have the computer that comprises bearing dynamic force computing module (418), bearing equivalence dynamic rigidity coefficient computing module (419), becomes set of weights and remaining vibration of supports amount computing module (420) and exclusive data library management and dimension program module four software modules such as (421), preferably a portable computer.
6, the dynamically balanced dynamic rigidity coefficient Equilibrator of a kind of rotating machinery as claimed in claim 5, it is characterized in that: its measurement signal front processor is made up of attenuator (407), amplifier (408), shaping amplifier (409), wave filter (410), phase-locked loop circuit (411), analog-digital converter (412), central data processing single chip (413), RAM storage chip (414) and EPROM chip (415), and their single line annexation is: the one tunnel is that (407) connect (409) and connect (411) and connect (412) and be connected to (413); Same (408) of two-way connect (410) and are connected to (413) in addition, and two feedback lines of (413) are connected to two (408) respectively; (411) the two other line is connected to respectively on two (410); (414), (415) have bidirectional cable to be connected with (413) respectively; The interface that vibration transducer (404) are arranged on two (408) has the interface of eddy current head (405) on (407), the interface of photoelectrical head is arranged on (409), and the interface that links to each other with private host calculation machine is arranged on (413).
7, as claim 5 or the dynamically balanced dynamic rigidity coefficient Equilibrator of 6 described a kind of rotating machineries, it is characterized in that: the computing module (418) of bearing dynamic force R ' is to have the vibration of supports amount X that measures according to the vibratory output sensor
0Calculate bearing dynamic force R ' and utilize bearing dynamic force R ' data computing software that the vibration force sensor directly measures therein module admittedly.
8, as claim 5 or the dynamically balanced dynamic rigidity coefficient Equilibrator of 6 or 7 described a kind of rotating machineries, it is characterized in that: bearing equivalence dynamic rigidity coefficient computing module (419) is to have the original vibration of supports amount X that measures according to the vibratory output sensor
0Value and the bearing dynamic force R ' value that calculates by bearing dynamic force computing module or be solidificated in wherein module with the software for calculation that bearing dynamic force R ' value that the vibration force sensor is directly measured calculates bearing equivalence dynamic rigidity coefficient.
9, as claim 5 or the dynamically balanced dynamic rigidity coefficient Equilibrator of 6 or 7 or 8 described a kind of rotating machineries, it is characterized in that: becoming set of weights and remaining vibration of supports amount computing module (420) is to have the original vibration of supports amount X that measures according to the vibratory output sensor
0Value, each bearing equivalence dynamic rigidity coefficient K
dNumerical value, selected correcting plane position and number m and V
cKind of operation conditions parameter comes computation optimization to go out the best that need add at selected correcting plane to become the software for calculation of set of weights and remaining vibration of supports amount to be solidificated in wherein module.
10, as claim 5 or 6 or 7 or the 8 or 9 dynamically balanced dynamic rigidity coefficient Equilibrators of described a kind of rotating machinery, it is characterized in that: exclusive data library management and maintenance program module (421) are to have storage and call the structural parameter of various rotary machine rotor-supporting systems and the management of the accurate equivalent dynamic rigidity coefficient of each bearing of dynamic balancing history record and maintenance program are solidificated in wherein module.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95102823 CN1067764C (en) | 1995-03-27 | 1995-03-27 | Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95102823 CN1067764C (en) | 1995-03-27 | 1995-03-27 | Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1132323A true CN1132323A (en) | 1996-10-02 |
| CN1067764C CN1067764C (en) | 2001-06-27 |
Family
ID=5074475
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 95102823 Expired - Fee Related CN1067764C (en) | 1995-03-27 | 1995-03-27 | Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1067764C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102042903A (en) * | 2010-10-18 | 2011-05-04 | 西安瑞特快速制造工程研究有限公司 | Finite element model based rotating equipment supporting dynamic stiffness parameter measurement method |
| CN103592125A (en) * | 2013-10-08 | 2014-02-19 | 东北大学 | Method for measuring radial dynamic flexibility of rolling bearing |
| CN104460728A (en) * | 2014-10-31 | 2015-03-25 | 西安电子科技大学 | Dynamic balance suppression method for spatial vibration of high-speed rotor bearing system |
| CN105136394A (en) * | 2014-05-26 | 2015-12-09 | 国家电网公司 | Method and device for rapidly handling boiler fan vibration fault |
| CN108982012A (en) * | 2018-09-25 | 2018-12-11 | 国网新疆电力有限公司电力科学研究院 | Vertical pump dynamic balance running method based on virtual-sensor |
| CN110702313A (en) * | 2019-10-10 | 2020-01-17 | 西北工业大学 | Method for high-precision identification of unbalanced excitation force of flexible rotor based on variable-speed starting |
| CN110702314A (en) * | 2019-10-10 | 2020-01-17 | 西北工业大学 | Non-trial-weight transient high-speed dynamic balancing method based on flexible rotor acceleration response information |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006052115A1 (en) * | 2006-11-06 | 2008-05-08 | Robert Bosch Gmbh | Machine tool and tool, each with automatic balancing device |
-
1995
- 1995-03-27 CN CN 95102823 patent/CN1067764C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102042903A (en) * | 2010-10-18 | 2011-05-04 | 西安瑞特快速制造工程研究有限公司 | Finite element model based rotating equipment supporting dynamic stiffness parameter measurement method |
| CN103592125A (en) * | 2013-10-08 | 2014-02-19 | 东北大学 | Method for measuring radial dynamic flexibility of rolling bearing |
| CN103592125B (en) * | 2013-10-08 | 2016-03-16 | 东北大学 | A kind of method measuring the radial dynamic flexibility of rolling bearing |
| CN105136394A (en) * | 2014-05-26 | 2015-12-09 | 国家电网公司 | Method and device for rapidly handling boiler fan vibration fault |
| CN105136394B (en) * | 2014-05-26 | 2019-03-05 | 国家电网公司 | The quickly method and device of processing boiler fan vibration fault |
| CN104460728A (en) * | 2014-10-31 | 2015-03-25 | 西安电子科技大学 | Dynamic balance suppression method for spatial vibration of high-speed rotor bearing system |
| CN108982012A (en) * | 2018-09-25 | 2018-12-11 | 国网新疆电力有限公司电力科学研究院 | Vertical pump dynamic balance running method based on virtual-sensor |
| CN110702313A (en) * | 2019-10-10 | 2020-01-17 | 西北工业大学 | Method for high-precision identification of unbalanced excitation force of flexible rotor based on variable-speed starting |
| CN110702314A (en) * | 2019-10-10 | 2020-01-17 | 西北工业大学 | Non-trial-weight transient high-speed dynamic balancing method based on flexible rotor acceleration response information |
| CN110702314B (en) * | 2019-10-10 | 2021-04-20 | 西北工业大学 | Non-trial-weight transient high-speed dynamic balancing method based on flexible rotor acceleration response information |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1067764C (en) | 2001-06-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102564763B (en) | Dynamic pre-tightening force measurement method of main shaft bearing of machine tool | |
| O¨ zgu¨ ven et al. | Whirl speeds and unbalance response of multibearing rotors using finite elements | |
| US8504338B2 (en) | Method for measuring shafting mechanical fatigue of turbine generator set | |
| CN109632188B (en) | Flexible rotor dynamic balance double optimization method and system considering multi-rotating speed state | |
| CN1067764C (en) | Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance | |
| Kirchgäßner | Finite elements in rotordynamics | |
| CN109374209A (en) | A kind of Rotor Low-speed Dynamic platform and critical speed prediction technique | |
| Patel et al. | Nonlinear dynamic response of cylindrical roller bearing–rotor system with 9 degree of freedom model having a combined localized defect at inner–outer races of bearing | |
| Lam et al. | Vibrations of thick rotating laminated composite cylindrical shells | |
| Li et al. | Dynamics modeling and modal experimental study of high speed motorized spindle | |
| CN103292958A (en) | Model based rotor non-trial-mass unbalance parameter identification method | |
| CN114357661A (en) | Method for establishing plunger-slipper assembly coupling dynamic model | |
| Klanner et al. | Quasi-analytical solutions for the whirling motion of multi-stepped rotors with arbitrarily distributed mass unbalance running in anisotropic linear bearings | |
| CN108509661A (en) | A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient | |
| CN112211812A (en) | Method for constant-power variable-speed operation of beam-pumping unit | |
| Gordeev et al. | Reducing transient vibrations due to rotating shafts | |
| Kärkkäinen et al. | Dynamic analysis of rotor system with misaligned retainer bearings | |
| CN111005832A (en) | Dynamic balance method for water pump turbine runner | |
| Sonone et al. | Design and Analyis of Balancer Shaft for a Four Stroke Single Cylinder Diesel Engine | |
| Hoffman et al. | Fully coupled rigid internal combustion engine dynamics and vibration—Part I: model development | |
| CN1103443C (en) | Holographic dynamic balance method for asymmetric rotor | |
| Hong et al. | Vibration failure analysis of multi-disk high-speed rotor based on rotary inertia load model | |
| CN109847952B (en) | Dynamic balance method of double-shaft precision centrifuge turntable based on driving current | |
| CN114577397A (en) | Dynamic balance method and system for high-speed permanent magnet motor rotor | |
| CN112836312B (en) | Design method of damping pad of heavy buoyancy adjusting device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |