CN201765055U - Shafting vibration phase difference aided diagnosis system of steam turbine generator unit - Google Patents

Abstract

The utility model relates to a shafting vibration phase difference aided diagnosis system of a steam turbine generator unit, comprising a rotor; a reference mark is arranged on the rotor, and the reference mark corresponds to a phase demodulation sensor corresponding to the rotor; meanwhile, vibration measurement sensors are arranged on the rotor along the x and y directions which are vertical mutually, and the phase demodulation sensor, the x-direction vibration measurement sensor and the y-direction vibration measurement sensor are connected with a vibration signal measurement instrument. The shafting vibration phase difference aided diagnosis system can read the vibration measurement information accurately and determine the fault property.

Description

The phase differential assistant diagnosis system of steam-electric generating set shafting vibration

Technical field

The utility model relates to a kind of phase differential assistant diagnosis system of steam-electric generating set shafting vibration.

Background technology

The shafting vibration of Turbo-generator Set is one of fault that incidence and seriousness are the highest in the power plant equipment, and analysis for Vibration Reasons is to carry out the gordian technique foundation that vibration fault is handled correctly, quickly accurately.Cause and comprise in the factor of steam-electric generating set shafting vibration but following aspect is not only arranged: the friction between rotor and static zero, the parts, the mass unbalance of rotor self, the oil whirl at rotor supports bearing place, the steam flow whirling motion in high pressure steam district, the electric generator rotor coil short circuit, the magnetic force off-centring of generator amature.The vibration signal of field measurement is the comprehensive response that the above-mentioned factors stack is produced, how intuitively quickly to the correct decoupling zero of above-mentioned coupling factor, particularly will not produce the local friction of obvious low frequency or high power frequency component and the mass unbalance factor of rotor and carry out decoupling zero, still lack effective analytical approach.

At present, the general analysis thinking when the rotor quality imbalance intercouples with other vibration cause is as follows: when taking place as if (1) abnormal vibrations, rotor speed promptly, is not in υ away from the critical rotary speed district _Critical(υ in the range of speeds of ± 100～150r/min _Critical: expression critical rotary speed); When (2) abnormal vibrations takes place,, present significant nonlinear relationship between amplitude and the rotating speed though rotor speed is in the critical rotary speed district; (3) vibration amplitude and/or phase place random groups start-stop time and/or significant variation takes place with the length of working time on same rotating speed; (4) tangible half-speed vortex phenomenon appears; (5) significant change and/or the variation of random groups working time simultaneously change with the size of exciting current in vibration; (6) significant 2 frequencys multiplication and/or multiple frequence component appear in the spectrum component of vibration survey signal; Then decidable causes that the principal element of abnormal vibration is not the rotor quality imbalance, and then according to the true cause of concrete time domain and/or frequency domain vibration performance contact unit operation parameter decision vibration fault at that time.In fact, above-mentioned Decoupling Analysis can not be separated mass unbalance and other factors fully, for example, the abnormal vibrations that some local friction forms, its rumble spectrum and simple rotor quality imbalance are very close, utilize above-mentioned decoupling zero theory, then be difficult to make the judge that whether has mass unbalance.Like this, gently then increase fault handling time and/or workload, improve the fault handling cost; Heavy then incur loss through delay or lose optimization process opportunity, cause the damage and/or the personal injury of unnecessary economic loss even unit equipment.

The utility model content

The purpose of this utility model is exactly in order to overcome in the above-mentioned general frequency spectrum analysis method the undistinct defective of fault diagnosis directive property, a kind of vibration survey information of understanding more exactly is provided, determine the character of fault, the phase difference aided diagnosis method and the system thereof of steam-electric generating set shafting vibration.

For achieving the above object, the utility model adopts following technical scheme:

A kind of phase differential assistant diagnosis system of steam-electric generating set shafting vibration, it comprises rotor, is provided with reference marker on rotor, reference marker is corresponding with the phase demodulation sensor of rotor relevant position; Simultaneously, the x of rotor to y to being provided with vibration measurement sensor, the phase demodulation sensor all is connected with the vibration signal measuring instrument to vibration measurement sensor with x, y.

Described phase demodulation sensor is current vortex sensor or photoelectric sensor; Described corresponding reference is labeled as groove or cursor; Described orthogonal x is to being current vortex sensor with y to vibration measurement sensor.

Described orthogonal x to y be built-in to vibration measurement sensor, and the prime amplifier by separately is connected with the vibration signal measuring instrument respectively.

Described orthogonal x to y be external to vibration measurement sensor, and respectively directly and external vibration signal measuring instrument be connected.

Adopt phase difference aided diagnosis method of the present utility model to be, a plurality of measuring points are set on rotor, and the phase place between each measuring point vibration signal discerned and judge, the vibration that causes with simple mass unbalance is typical exciting force vibration, and be the vibration of atypia exciting force by the vibration that other factors (be mass unbalance factor beyond) causes: when vibration signal had phase interference each other, it was unusual to produce the vibration phase difference that is different from simple quality imbalance fault to each other; Otherwise, will keep the phase differential normality of simple quality imbalance fault; If satisfying following three conditions simultaneously is the effect that the decidable rotor only is subjected to typical exciting force, otherwise, judge that then axle system is subjected to the effect of tangible atypia exciting force:

(1) same bearing shell place, on same direction, rotor oscillation phase differential criterion: under rotating speed, the vibration phase difference of forward and backward each x of bearing shell place of abnormal vibrations or y direction (in the formula: i=x, y) and stable;

(2) same bearing shell place, two mutually vertical x, y upwards, the mutual drift criterion of rotor oscillation phase place: under rotating speed, forward and backward each x of bearing shell place of abnormal vibrations and y to phase differential

Difference Δ θ _Xy=| θ _{Behind the xy}-θ _{Before the xy}|≤45 ° and stable;

(3), satisfy one of following condition during abnormal vibrations at least with under the rotating speed: (a) different bearing shells, on same direction, the rotor oscillation phase place: the rotating speed of abnormal vibrations near during the odd-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor

In the formula: i=x, y and stable; The rotating speed of abnormal vibrations near during the even-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor

In the formula: i=x, y and stable; (b) same bearing shell place, on two mutually vertical x, the y directions, the rotor oscillation phase place: the rotating speed during abnormal vibrations near during the critical rotary speed of the section of examination rotor, rotor x and y to phase differential

And it is stable.

Its detailed process is:

1) unit brings into operation, and detects rotating speed and whether reaches setting value and stable, if do not have, continues to detect, if then change step 2 over to);

2) judge whether rotating speed equals critical rotary speed, if then change step 3) over to, if not, then change step 5) over to;

3) under critical rotary speed,, continue then to judge that it is still even-order vibration of odd-order vibration if the orthogonal x in same bearing shell place, two ends, the y vibration phase difference of machine group rotor are 90 °; Otherwise, then be the vibration of atypia exciting force;

4) if odd-order vibration, then if the vibration homophase of two ends of rotor; If be the even-order vibration, then if the vibration of two ends of rotor is anti-phase; Then all be judged to be typical exciting force vibration; Otherwise, then be the vibration of atypia exciting force;

5) judge whether rotor oscillation reaches this moment again and/or surpass manufacturing firm or the normal permissible value of the world, domestic vibration standard defined, that is, whether vibration amplitude is unusual; If not unusually, the normal vibration phase value of the record rotor of surveying then so that with carry out bit comparison mutually future during abnormal vibration; If unusual, then change step 6) over to;

6) write down the orthogonal x in each bearing shell place of rotor, the phase value of y direction under this abnormal vibrations state respectively, judge according to the rumble spectrum at each bearing shell place of actual measurement whether the dominant frequency of each bearing shell place rotor oscillation this moment is a frequency multiplication again; If not, then can directly be judged to be the vibration of atypia exciting force; If, then judge rotating speed whether odd-order critical rotary speed value ± the 100r/min scope in; If then change step 7) over to; If not, then change step 8) over to;

7) if a frequency multiplication component phase difference of the equidirectional vibration signal of two ends of rotor and with the phase differential between end orthogonal x, y two directions respectively in 0 ° ± 30 ° and 90 ° ± 30 ° scopes and numerical stability, then be that typical exciting force vibrates; If not, then be the vibration of atypia exciting force;

8) judge rotating speed whether even-order critical rotary speed ± the 100r/min scope in; If then change step 9) over to; If not, then change step 10) over to;

9) if a frequency multiplication component phase difference of the equidirectional vibration signal of two ends of rotor and with the phase differential between end orthogonal x, y two directions respectively in 180 ° ± 30 ° and 90 ° ± 30 ° scopes and numerical stability, then be that typical exciting force vibrates; If not, then be the vibration of atypia exciting force;

10) judge difference that phase place when institute the surveys the rotor abnormal vibrations same rotating speed corresponding with it time vibrate the phase place that is just often write down whether in ± 45 ° of scopes, and the difference of the normal vibration phase differential under the same rotating speed corresponding with it of the phase differential between the orthogonal x in same bearing shell place, y direction abnormal transient vibration signal is also in ± 45 ° of scopes and numerical stability; If then be typical exciting force vibration; If not then being the vibration of atypia exciting force.

Caused for some reason its feature of shafting vibration is closely similar with the vibration performance that simple rotor quality imbalance causes, general frequency spectrum analysis method is undistinct to the directive property of this type of fault diagnosis, in order to understand this type of vibration survey information more exactly, determine the character of fault, the utility model proposes the phase differential auxiliary diagnosis method of shafting vibration, promptly, the method that adopts general vibration analysis and combine with this phase difference phase separation, vibration fault is comprehensively judged, realized the decoupling zero diagnosis of vibration information.

Its principle is as follows: the vibration that supposition is caused by simple mass unbalance is called typical exciting force vibration, and be called the vibration of atypia exciting force by the vibration that other factors causes, so, the response of multifactorial coupled vibrations then is the result by typical exciting force and atypia exciting force superposition.The scene wishes that the result who obtains is that clear and definite abnormal vibrations comes from typical exciting force or atypia exciting force, can directly adopt spot dynamic balance to handle for the vibration that is caused by typical exciting force most; Then need further frequency domain, time-domain analysis and determine concrete reason one by one and make measures areput for the latter with the variation relation of unit operation and structural parameters according to vibration.Half frequency component of rotor oscillation in most cases, frequency multiplication component and axle shake with vibration of bearings, with metal watt temperature, with generating unit speed, with unit load, are carrying the clear and definite failure cause that causes abnormal vibration with relationship between parameters such as exciting current, times, yet do not possess tangible correlativity between its amplitude versus frequency characte of the vibration that some fault causes and axle amplitude and above-mentioned unit operation and the structural parameters, but its phase information includes fault signature, utilizes these phase informations and just reasonably handle to obtain fault diagnosis accurately.Specifically be described below from theoretical and actual measurement two aspects:

The rotor oscillation differential equation and separating:

Turbine rotor is by rotary part in multi-stage impeller, shaft coupling and the cylinder of two supports on sliding bearing of forming, and impeller drives rotor and makes high speed rotating under vapor action.Rectangular coordinate system (x, y, z) in, be transverse axis with the z axle, establish in the rotor-support-foundation system, rotor length is l, the moment of inertia of its mass density, cross-sectional area, unit length diameter is the function of z coordinate, uses ρ (z) respectively, A (z), I (z) expression; In addition, respectively at coordinate points z=z _δ, δ=1,2 ..., s, the impeller quality of locating to install is made as m _δ, total s impeller, its moment of inertia to orthogonal x, y axle is used J respectively _{Dx δ}, J _{Dy δ}Represent, and to the moment of inertia J of z axle _{P δ}Expression; Suppose at coordinate points z=z _η(η=1,2 ..., r) locate also to act on concentrated spring along orthogonal x, y direction, total η, its rigidity is used k respectively _{X η}And k _{Y η}Expression; Suppose at last also to be subjected to distributed force f respectively in orthogonal x, y direction _x(z, t) and f _y(z, effect t); According to the Rayleigh-Rize method, suppose axle distortion x (z, t), y (z, t) linear superposition of amassing of the corresponding mode main coordinate with it of available respectively each first order mode is similar to, then the oscillatory differential equation of system is as follows:

$\left(\begin{array}{cc}{M}_x+J_x& 0\\ 0& M_y+J_y\end{array}\right)\left(\begin{array}{c}{\stackrel{\·\·}{q}}_x\\ {\stackrel{\·\·}{q}}_y\end{array}\right)+\left(\begin{array}{cc}{C}_x& \mathrm{\ω}{J}_z/2\\ -\mathrm{\ω}{J}_z/2& C_y\end{array}\right)\left(\begin{array}{c}{\stackrel{\·}{q}}_x\\ {\stackrel{\·}{q}}_y\end{array}\right)+\left(\begin{array}{c}{K}_{x}0\\ K_{y}0\end{array}\right)\left(\begin{array}{c}{q}_x\\ q_y\end{array}\right)=\left(\begin{array}{c}{p}_x\\ p_y\end{array}\right)---\left(1\right)$

In the formula: M _i, K _i, C _i, J _i, p _i, q _iRepresent i=x respectively, the modal mass on the y direction, modal stiffness, modal damping, mode moment of inertia, generalized force, generalized coordinate matrix, J _zBe polar moment of inertia matrix vertically.

Suppose generalized force

Be the dull continuous cyclic force of segmentation in one-period, in the formula, Γ _{I λ}Be meant the amplitude of i to λ rank generalized force component; Subscript λ is meant order; ω is meant angular frequency; α _{I λ}Be meant the starting phase angle of i to λ rank generalized force; Obtain thus equation (1) separate for:

$i(z,t)=\underset{k=1}{\overset{\∞}{\mathrm{\Σ}}}{\mathrm{\φ}}_{\mathrm{ik}}\left(z\right)\underset{\mathrm{\λ}=1}{\overset{\∞}{\mathrm{\Σ}}}{A}_{\mathrm{i\λ}}\sin (\mathrm{\λ\ωt}+{\mathrm{\α}}_{\mathrm{i\λ}}-{\mathrm{\ζ}}_{\mathrm{i\λ}})---\left(2\right)$

In the formula: φ _Ik(z) be respectively rotor at i=x, y to model function of vibration; Subscript k represents vibration shape order;

ω _IkI is to the k rank natural frequency of vibration, K in expression _iBe i rank modal stiffness, M _iI is to k rank modal mass in expression;

ξ _Ik=C _i/ 2M _iω _Ik, C _iBe i rank modal damping, ξ _IkI is to k rank modal damping ratio in expression;

Represent λ rank frequency ratio;

ζ _{I λ}Show the starting phase angle of i to λ rank vibration displacement; (3)

p _i(t) fourier decomposition, a _{I λ}Be real part, b _{I λ}Be imaginary part;

I is to the amplitude of λ rank generalized force component;

I is to the starting phase angle of λ rank generalized force;

A _iλ＝Γ _iλυ _iλ/K _i；

The vibration analysis of ideal rotor:

Undamped uniform cross section homogeneous cylindrical rotor is long to be l, and the quality of unit length is m, and rotor is suffered is actuated to linear time invariant stable state acting force, and the vibration displacement that this condition substitution (2) formula gets ideal rotor is separated:

$i(z,t)=\sqrt{\frac{2}{\mathrm{ml}}}\underset{k=1}{\overset{\∞}{\mathrm{\Σ}}}\underset{\mathrm{\λ}=1}{\overset{\∞}{\mathrm{\Σ}}}{A}_{\mathrm{i\λ}}\sin (\mathrm{\λ\ωt}+{\mathrm{\α}}_{\mathrm{i\λ}}-\mathrm{\ζi\λ})\sin \frac{\mathrm{k\πz}}{l}---\left(4\right)$

By (4) formula as can be known: the phase place of rotor oscillation signal is that the variation with the exciting force phase place changes, and under the desirable exciting force effect, rotor is when odd-order, and the vibration phase at two ends is identical; The vibration phase at two ends is opposite when even-order.And ω ≠ ω in the ordinary course of things _k, ω _kWhen representing the k rank natural frequency of vibration, the phase differential between amplitude and the uneven exciting force I=x, y are i direction resistance coefficient and frequency ratio ω/ω _kFunction, rotating speed and damping one regularly, amplitude lags behind the phasing degree of uneven exciting force

Also certain.The analysis principle of phase differential is: because the variation of typical exciting force vibration can not causing SR coefficient, therefore, rotating speed one regularly, the difference of the vibration phase of two ends of rotor can be not in time change with the variation of amplitude, when k was odd-order, the vibration phase at two ends was identical; The vibration phase at two ends was opposite when k was even number; Simultaneously, at synchronization, the phase differential between i=x direction and the i=y direction can be not in time yet with the variation of amplitude and change, and, as frequency ratio ω/ω _k=1, rotor self and support stiffness thereof each when identical, the i=x at each bearing shell place and i=y to phase differential

Based on the above-mentioned theory conclusion and consider the manufacturing of field apparatus and alignment error, unit actual motion in typical exciting force phase place α _{I λ}Factor such as unsteady error, vibration signal measuring error, generally speaking, if satisfying following three conditions simultaneously is the effect that the decidable rotor only is subjected to typical exciting force, otherwise, judge that then axle system is subjected to the effect of tangible atypia exciting force: (1) same bearing shell place, on same direction, rotor oscillation phase differential criterion: under rotating speed, the vibration phase difference of forward and backward each x of bearing shell place of abnormal vibrations or y direction

(in the formula: i=x, y) and stable.(2) same bearing shell place, two mutually vertical x, y upwards, the mutual drift criterion of rotor oscillation phase place: under rotating speed, forward and backward each x of bearing shell place of abnormal vibrations and y to phase differential

Poor

And it is stable.(3), satisfy one of following condition during abnormal vibrations at least with under the rotating speed: (a) different bearing shells, on same direction, the rotor oscillation phase place: the rotating speed of abnormal vibrations near during the odd-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor

(in the formula: i=x, y) and stable; The rotating speed of abnormal vibrations near during the even-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor (in the formula: i=x, y) and stable; (b) same bearing shell place, on two mutually vertical x, the y directions, the rotor oscillation phase place: the rotating speed during abnormal vibrations near during the critical rotary speed of the section of examination rotor, rotor x and y to phase differential

And it is stable.

The in-site measurement of the vibration phase of rotor and phase analysis thereof

As previously mentioned, (ω ≠ ω in the ordinary course of things _kThe time), the phase differential between amplitude and the uneven exciting force is measured direction resistance coefficient and frequency ratio ω/ω _kFunction, rotating speed and damping one regularly, it is also certain that amplitude lags behind the phasing degree of uneven exciting force.In order to measure this phasing degree, should reference marker be set in epitrochanterian certain proper site during actual measurement, as: on the outside surface of rotor somewhere axle journal, paste cursor or open phase demodulation groove or manufacturing phase demodulation boss etc. to produce the rotor phase signal in the journal surface of correct position, reference marker is in case set, and it has just been fixed with the angle between the uneven exciting force.Like this, as long as sensor is loaded onto in the relevant position on casing, just can measure the phase discrimination signal of rotor.Sensor commonly used has photoelectric sensor and current vortex sensor.In theory, need only with the sampling trigger signal of this phase discrimination signal as vibration, it is exactly the fundamental frequency phase place of vibration signal fundamental component that the vibration signal that collects is carried out its phase place of the resulting fundamental frequency signal of FFT computing, uses α _LiExpression, the phase place of its λ frequency multiplication component is then used α _{λ i}Expression.In fact, owing to have bearing rigidity, instrument characteristic equal error, from the phase place of vibration analyzer output is not the actual phase of rotor, but the measuring error that this phase place comprises all exists on each is measured watt and is basic identical, when carrying out cancelling each other out when phase differential is analyzed, therefore, the phase place by on-the-spot vibration survey analytic system output can be directly used in the above-mentioned phase differential analysis.

The beneficial effects of the utility model are: because phase information has distinct physical meaning and directive property, phase place (poor) changes again can be according to concrete physical construction or physical media by clear division, therefore, the phase differential analysis can be used as rotor oscillation fault diagnosis " visual " instrument; Can find out whether there is phase interference between signal rapidly by the analysis phase differential, thereby can determine the character of vibration fault more quickly and accurately, in time take correct measure that vibration fault is controlled and/or handled, effectively avoid wrong operation and fault to enlarge, reduce the fault handling cost greatly; The analysis that changes trend by phase differential also can be made vibration equipment fault pre-alarming accurately; for example; if find that there is obvious variation trend in phase differential; even this moment, vibration amplitude was still obviously not unusual; also should in time search reason; take suitable treatment measures, do not wait until that amplitude increase suddenly causes device damage or disorderly closedown, thereby effectively take precautions against the generation of pernicious equipment breakdown.

Description of drawings

Fig. 1 is a process flow diagram of the present utility model;

Fig. 2 is a system diagram of the present utility model.

Wherein, 1. rotor, 2. reference marker, 3. phase demodulation sensor, 4.x be to sensor, and 5.y is to sensor, 6. horizontal direction vibration measurement sensor, 7. vertical vibration survey sensor, 8. prime amplifier, 9. vibration signal measuring instrument.

Embodiment

Below in conjunction with accompanying drawing and embodiment the utility model is described further.

Among Fig. 1, the phase difference aided diagnosis method of steam-electric generating set shafting vibration, it is provided with a plurality of measuring points on rotor, and the phase place between each measuring point vibration signal discerned and judge, the vibration that causes with simple mass unbalance is typical exciting force vibration, and be the vibration of atypia exciting force by the vibration that other factors causes: when vibration signal had phase interference each other, it was unusual to produce the vibration phase difference that is different from simple unbalance dynamic fault to each other; Otherwise, will keep the phase differential normality of simple unbalance dynamic fault; If satisfying following three conditions simultaneously is the effect that the decidable rotor only is subjected to typical exciting force, otherwise, judge that then axle system is subjected to the effect of tangible atypia exciting force:

(1) same bearing shell place, on same direction, rotor oscillation phase differential criterion: under rotating speed, the vibration phase difference of forward and backward each x of bearing shell place of abnormal vibrations or y direction

(in the formula: i=x, y) and stable;

(2) same bearing shell place, two mutually vertical x, y upwards, the mutual drift criterion of rotor oscillation phase place: under rotating speed, forward and backward each x of bearing shell place of abnormal vibrations and y to phase differential

Difference Δ θ _Xy=| θ _{Behind the xy}-θ _{Before the xy}|≤45 ° and stable;

(3), satisfy one of following condition during abnormal vibrations at least with under the rotating speed: (a) different bearing shells, on same direction, the rotor oscillation phase place: the rotating speed of abnormal vibrations near during the odd-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor

(in the formula: i=x, y) and stable; The rotating speed of abnormal vibrations near during the even-order critical rotary speed of the section of examination rotor, the vibration phase of two ends of rotor poor

(in the formula: i=x, y) and stable; (b) same bearing shell place, on two mutually vertical x, the y directions, the rotor oscillation phase place: the rotating speed during abnormal vibrations near during the critical rotary speed of the section of examination rotor, rotor x and y to phase differential

And it is stable.

Detailed process is:

1) unit brings into operation, and detects rotating speed and whether reaches setting value and stable, if do not have, continues to detect, if then change step 2 over to);

2) judge whether rotating speed equals critical rotary speed, if then change step 3) over to, if not, then change step 5) over to;

3) under critical rotary speed,, continue then to judge that it is still even-order vibration of odd-order vibration if the orthogonal x in same bearing shell place, two ends, the y vibration phase difference of machine group rotor are 90 °; Otherwise, then be the vibration of atypia exciting force;

4) if odd-order vibration, then if the vibration homophase of two ends of rotor; If be the even-order vibration, then if the vibration of two ends of rotor is anti-phase; Then all be judged to be typical exciting force vibration; Otherwise, then be the vibration of atypia exciting force;

5) judge again whether rotor oscillation reaches this moment and/or surpass manufacturing firm or the normal permissible value of the world, domestic vibration standard defined, promptly, whether vibration amplitude unusual? if not unusually, the normal vibration phase value of the record rotor of surveying then, so as with carry out bit comparison mutually future during abnormal vibration; If unusual, then change step 6) over to;

6) write down the orthogonal x in each bearing shell place of rotor, the phase value of y direction under this abnormal vibrations state respectively, judge according to the rumble spectrum at each bearing shell place of actual measurement whether the dominant frequency of each bearing shell place rotor oscillation this moment is a frequency multiplication again; If not, then can directly be judged to be the vibration of atypia exciting force; If, then judge rotating speed whether odd-order critical rotary speed value ± the 100r/min scope in; If then change step 7) over to; If not, then change step 8) over to;

7) if a frequency multiplication component phase difference of the equidirectional vibration signal of two ends of rotor and with the phase differential between end orthogonal x, y two directions respectively in 0 ° ± 30 ° and 90 ° ± 30 ° scopes and numerical stability, then be that typical exciting force vibrates; If not, then be the vibration of atypia exciting force;

8) judge rotating speed whether even-order critical rotary speed ± the 100r/min scope in; If then change step 9) over to; If not, then change step 10) over to;

9) if a frequency multiplication component phase difference of the equidirectional vibration signal of two ends of rotor and with the phase differential between end orthogonal x, y two directions respectively in 180 ° ± 30 ° and 90 ° ± 30 ° scopes and numerical stability, then be that typical exciting force vibrates; If not, then be the vibration of atypia exciting force;

10) judge difference that phase place when institute the surveys the rotor abnormal vibrations same rotating speed corresponding with it time vibrate the phase place that is just often write down whether in ± 45 ° of scopes, and the difference of the normal vibration phase differential under the same rotating speed corresponding with it of the phase differential between the orthogonal x in same bearing shell place, y direction abnormal transient vibration signal is also in ± 45 ° of scopes and numerical stability; If then be typical exciting force vibration; Otherwise, then be the vibration of atypia exciting force.

Among Fig. 2, the phase difference aided diagnosis method system of steam-electric generating set shafting vibration comprises rotor 1, is provided with reference marker 2 on rotor 1, and reference marker 2 is corresponding with the phase demodulation sensor 3 of relevant position in the casing; Simultaneously, rotor 1 orthogonal x to y to being provided with vibration measurement sensor 4,5, phase demodulation sensor 3 all is connected with vibration signal measuring instrument 9 to vibration measurement sensor 4,5 with orthogonal x, y.

Described phase demodulation sensor 3 is current vortex sensor or photoelectric sensor; Described corresponding reference mark 2 is groove, boss or cursor; Described orthogonal x is to being current vortex sensor with y to vibration measurement sensor 4,5.

Described orthogonal x to y be built-in to vibration measurement sensor 4,5, and the prime amplifier 8 by separately is connected with vibration signal measuring instrument 9 respectively.

Described orthogonal x to y be external to vibration measurement sensor 6,7, and respectively directly and external vibration signal measuring instrument 9 be connected.

In sum, the phase differential analysis of vibration signal is exactly that the phase interference chain between each measuring point of rotor is discerned and judged, when vibration signal has phase interference each other, it is unusual that cross-correlation function value to each other and phase differential will produce the vibration phase difference that is different from simple unbalance dynamic fault, otherwise, to keep the phase differential normality of simple unbalance dynamic fault, the principle and the foundation of phase differential analysis that Here it is.

Claims (4)

1. the phase differential assistant diagnosis system of a steam-electric generating set shafting vibration is characterized in that it comprises rotor, is provided with reference marker on rotor, and reference marker is corresponding with the phase demodulation sensor of rotor relevant position; Simultaneously, the orthogonal x of rotor to y to being provided with vibration measurement sensor, the phase demodulation sensor all is connected with the vibration signal measuring instrument to vibration measurement sensor with x, y.

2. the phase differential assistant diagnosis system of steam-electric generating set shafting vibration as claimed in claim 1 is characterized in that described phase demodulation sensor is current vortex sensor or photoelectric sensor; Described corresponding reference is labeled as groove or cursor; Described orthogonal x is to being current vortex sensor with y to vibration measurement sensor.

3. the phase difference aided diagnosis method system of steam-electric generating set shafting vibration as claimed in claim 1 or 2, it is characterized in that, described orthogonal x to y be built-in to vibration measurement sensor, and the prime amplifier by separately is connected with the vibration signal measuring instrument respectively.

4. the phase differential assistant diagnosis system of steam-electric generating set shafting as claimed in claim 1 or 2 vibration is characterized in that, described orthogonal x to y be external to vibration measurement sensor, and respectively directly and external vibration signal measuring instrument be connected.

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