CN104236883B - Parallel axes tooth-like compressor critical load method for diagnosing faults - Google Patents
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Abstract
A kind of parallel axes tooth-like compressor critical load method for diagnosing faults belongs to rotating machinery vibrating condition monitoring and fault diagnosis field.The present invention relates to parallel axes tooth-like compressor real time on-line monitoring, by to compressor rotation shaft vibration signal, key signal and the collection of inlet guide vane feedback signal and process, judge unit operation speed conditions and inlet guide vane feedback condition, further the passband eigenvalue of calculating is compared with value with machine group alarm, judge vibration passband trend condition, the frequency spectrum of rotor oscillation signal is calculated in combination with fast Fourier transform (FFT) algorithm, obtain the ratio turning frequency amplitude with passband eigenvalue, according to the judgement shaft vibration dominant frequency condition that ratio is quantitative, according to decision condition, whether the real-time online diagnosis tooth-like compressor bank of parallel axes there is critical load fault.The present invention has methodological science, and conclusion is reliable, it is possible to realize the diagnosis of parallel axes tooth-like compressor critical load fault real-time online.
Description
Technical field
The invention belongs to rotating machinery vibrating condition monitoring and fault diagnosis field, relate to a kind of tooth-like compressor of parallel axes
Critical load method for diagnosing faults.
Background technology
The tooth-like compressor of parallel axes is due to advantages such as its operational efficiency height, compact conformations, at process industries such as petroleum and petrochemical industry
Middle compressed air and carbon dioxide aspect are widely used.The tooth-like compressor of parallel axes generally there are many roots rotors, vibration
There is stronger coupled relation, and the bearing characteristics of every roots rotor changes along with the adjustment of compressor inlet stator, therefore,
The vibration of such unit is the most complicated, once breaks down and will bring huge loss to enterprise.
At the scene in actual moving process find, the tooth-like compressor of parallel axes when rated speed is run due to tune
Whole airload produces the problem that vibration is excessive, and the fault that this problem causes is exactly critical load fault.China's equipment fault
In diagnostician Gao Jinji academician written mechanical breakdown diagnosis and treatment and spontaneous recoveryization one book for critical load fault carry out inquiring into
Research, and successfully solve the critical load fault of a tooth-like compressor of parallel axes.
Critical load is a kind of oscillation phenomenon caused because service condition changes, due to the change of suction port of compressor stator
Cause airload to change, thus have impact on the stiffness variation of compressed gas acting rotor supports bearing, and bearing rigidity changes
The each rank critical speed rotating speed that can affect rotor changes, when certain first critical speed during stiffness variation with rated speed
During coincidence, resonance will be caused, cause unit vibration abnormal, once vibrate and excessive will cause jumping car, cause production to be forced to stop
Only.In sum, critical load fault can bring production safety problem to enterprise, can affect unit properly functioning, give time serious
Enterprise brings huge economic loss.The parallel axes tooth-like compressor critical load fault real-time diagnosis method that the present invention proposes,
According to the tooth-like compressor of parallel axes each axle system real time execution rotating speed, guide vane opening feedback, shaft vibration signal, vibration frequency spectrum special
The information such as levy, compressor bank critical load fault is carried out analyzing and diagnosing the most automatically, grasps for the tooth-like compressor bank of parallel axes
Diagnosis the most accurately is provided, it is ensured that compressor bank safely and steadily runs as management personnel.
Summary of the invention
Real time execution rotating speed in it is an object of the invention to be run based on the tooth-like compressor bank of parallel axes, guide vane opening are anti-
The information such as feedback, shaft vibration signal and rumble spectrum, carry out real-time diagnostic analysis to such unit critical load fault, are
A kind of a kind of parallel axes tooth-like compressor critical load method for diagnosing faults being capable of real-time Accurate Diagnosis fault.
A kind of parallel axes tooth-like compressor critical load method for diagnosing faults, it is characterised in that including:
1) signals collecting and process, gathers vibration signal, key signal and the pressure of parallel axes tooth-like compressor bank rotor
Contracting machine inlet guide vane open degree feedback signal, is calculated the tooth-like compressor of parallel axes according to the vibration signal obtained, key signal
Group shaft vibration passband eigenvalue and the rotating speed of rotating shaft；
2) parallel axes tooth-like compressor rotation shaft running speed condition Verification, calculates rotating speed during rotor real time execution, it is judged that
With stable rotating speed operation, whether this rotor compares whether rotating speed is more than the first critical speed of rotor simultaneously, it is determined that generating unit speed
Condition is the essential condition judging critical load fault；
3) parallel axes tooth-like compressor vanes aperture condition Verification, judges pressure according to the feedback signal of suction port of compressor stator
Whether contracting machine, at Load adjustment, is opened big i.e. load up and stator including stator and is turned down i.e. two kinds of situations of load down, it is determined that unit
Guide vane opening condition Verification is also the essential condition judging critical load fault；
4) parallel axes tooth-like compressor drum vibration passband trend condition Verification, according to leading to that shaft vibration signal calculates
Frequently eigenvalue compares with the vibration alarming threshold value of unit factory setting, the change feelings of quantitative analysis shaft vibration passband trend
Condition, it is determined that whether whether vibration passband trend be changed significantly in the load adjustment stage；
5) parallel axes tooth-like compressor drum vibration dominant frequency condition Verification, according to shaft vibration signal, in conjunction with quickly
Fourier's change (FFT) spectrum calculation method calculates shaft vibration signal spectrum, special with vibration signal passband according to turning frequency amplitude
The ratio of value indicative, whether the quantitative dominant frequency in analysis spectrum is to turn frequency, it is determined that the frequency amplitude that turns of shaft vibration signal is
No significantly；
6) parallel axes tooth-like compressor critical load method for diagnosing faults, tests according to compressor rotary speed checking, guide vane opening
The checking of card, vibration trend and dominant frequency verify the result of 4 project checkings, and comprehensive descision show that the tooth-like compressor of parallel axes is
The conclusion of no generation critical load fault.
When gathering parallel axes tooth-like compressor rotation shaft signal, need to gather the radial vibration signal of each rotating shaft: level
Direction vibration signal and vertical vibration signal, axial vibration signal, key signal, the concrete point layout of rotating shaft such as Fig. 2 institute
Show.Passband eigenvalue S (t) of shaft vibration signal w (t)=wmax(t)-wmin(t), wherein wmaxT () is t vibration signal
Peak-peak, wminT () is the minimum peak of t vibration signal.The rotating speed of each rotating shaft is then by gathering the key in rotating shaft
Phase signals is calculated, and (z* Δ t), wherein, z is rotor keyway quantity to rotating speed Rev=60/, and Δ t is between key signal pulse
Interval.
For the tooth-like compressor of parallel axes of reality application, having the rotor of more than 3, these rotors have different one respectively
Rank critical speed Rev1CWith nominal operation rotating speed RevR0, working speed when rotating shaft is properly functioning is Rev, rotating speed allowable error
Threshold value is ThreR, rotating speed allowable error threshold value according to the precision of key phase and in-site installation mode by equipment control work
Cheng Shi determines, typically takes ThreR=10r/min, works as RevR0-ThreR<Rev<RevR0+ThreRTime, rotating shaft operates steadily rotating speed
Constant, working speed when rotating shaft simultaneously runs exceedes first critical speed Rev > Rev1CTime, rotating shaft running speed condition Verification
Pass through, illustrate that this rotor has possessed the essential condition that critical load fault occur relevant to rotating speed.
Suction port of compressor guide vane opening feedback signal p (t) is the percentage ratio of guide vane opening, scope: 0%≤p (t)≤
100%, in the case of operating mode is constant, current time t guide vane opening feedback signal p (t) and previous moment moment tfGuide vane opening
Feedback signal p (tf) equal, i.e. p (t)=p (tf)；As p (t) ≠ p (tf) time, guide vane opening feedback signal changes, compression
Machine guide vane opening condition Verification passes through, illustrate this compressor possessed relevant to guide vane opening there is critical load fault must
Want condition.
Determining sample frequency Fs, sampling number Ns, the interval t second gathers shaft vibration signal w (t).For certain of compressor
Roots rotor obtains t radial vibration signal and includes: horizontal direction vibration signal wx(t), vertical vibration signal wy(t), with
And axial vibration signal wa(t)；According to vibration signal passband eigenvalue calculation formula S (t)=wmax(t)-wminT () calculates respectively
Obtain t horizontal direction vibration signal wxThe horizontal vibration passband eigenvalue S of (t)x(t), vertical vibration signal wy(t)
Vertical vibration passband eigenvalue Sy(t) and axial vibration signal waThe axial vibration passband eigenvalue S of (t)a(t), if
Level pressure contracting unit vibration alarm threshold value Thre.Alarm threshold value Thre is parallel axes tooth-like compressor factory settings when dispatching from the factory, and is turning
Under conditions of speed condition Verification all passes through with guide vane opening condition Verification, work as Sx(t) >=Thre or Sy>=Thre, simultaneously Sa(t)<
During Thre, it is determined that compressor bank vibration passband trend condition Verification passes through.
Certain roots rotor acquisition t radial vibration signal for compressor includes: horizontal direction vibration signal wx(t)、
Vertical vibration signal wyT (), uses fast Fourier change (FFT) spectrum calculation mode to obtain horizontal direction vibration respectively
Signal wxThe amplitude-frequency spectrum A of (t)x(f) and vertical vibration signal wyThe amplitude-frequency spectrum A of (t)yF (), wherein, f represents frequency
Point, A (f) represents the amplitude of f frequency content.T shaft vibration signal is w (t), and the frequency that turns of rotor is f0, turn the amplitude of frequency
For A (f0), the passband eigenvalue of shaft vibration signal is S (t), turns the ratio R=A (f of frequency amplitude and passband eigenvalue0)/S
T (), it is determined that dominant frequency threshold value is Thref, this threshold value is determined according to rotating shaft operating condition by equipment control engineer, typically takes
Thref >=0.6, when ratio R is more than or equal to when setting threshold value Thref, it is believed that turn frequency amplitude A (f0) notable in frequency spectrum, turn frequency
f0Take frequency as the leading factor.Turn frequency amplitude A when horizontal direction vibration signalx(f0) and its passband eigenvalue Sx(t) ratio Rx=Ax
(f0)/SxT () turns frequency amplitude A with vertical vibration signaly(f0) and its passband eigenvalue SyThe ratio R of (t)y=Ay
(f0)/SyWhen () is all higher than threshold value Thref set t, it is determined that compressor bank rotor oscillation dominant pilot spectral condition is verified.
Parallel axes tooth-like compressor critical load method for diagnosing faults, according to diagnostic flow chart, checking compressor rotation shaft fortune
The result of row speed conditions, compressor vanes aperture condition, vibration passband trend condition, vibration dominant pilot spectral condition etc. 4 is right
Whether compressor bank occurs critical load fault to be identified diagnosis.
Accompanying drawing explanation
Fig. 1 parallel axes tooth-like compressor critical load Troubleshooting Flowchart；
Fig. 2 generating unit speed trendgram；
Fig. 3 unit guide vane opening feedback trendgram；
Fig. 4 unit a certain rotor horizontal direction vibration passband trend；
Fig. 5 unit a certain rotors normal direction vibration passband trend；
Fig. 6 unit a certain rotor axial vibration passband trend；
Fig. 7 machine group alarm moment horizontal vibration signal spectrum；
Fig. 8 machine group alarm moment vertical vibration signal spectrum；
Detailed description of the invention
With example, the present invention is specifically described below in conjunction with the accompanying drawings.
A kind of parallel axes tooth-like compressor critical load method for diagnosing faults flow chart is as it is shown in figure 1, specifically include that
(1) signal of the parallel axes each rotating shaft of tooth-like compressor is obtained in real time, including vibration signal: the level of rotating shaft
Vibration signal wx(t), vertical vibration signal wy(t) and axial vibration signal wa(t)；Key phase tach signal；Guide vane opening is fed back
Signal；
(2) calculate the real-time rotating speed Rev of rotating shaft according to the key phase tach signal of the compressor rotation shaft obtained, and change rotor
First critical speed contrasts, and if greater than first critical speed, when the stable rotating speed of this rotating shaft is constant simultaneously, then passes through rotating shaft
Running speed condition Verification, enters next step, otherwise reacquires the signal of the tooth-like compressor of parallel axes；
(3) suction port of compressor guide vane opening feedback signal p (t) is obtained, according to suction port of compressor stator feedback signal, when entering
When mouth guide vane opening signal changes, by guide vane opening condition Verification, enter next step, otherwise reacquire parallel axes tooth
Formula signal compressor；
(4) compressor rotation shaft vibration signal prepares, and calculates rotating shaft horizontal direction vibration signal w according to formulaxThe vibration of (t)
Passband eigenvalue Sx(t) and amplitude-frequency spectrum Ax(f), vertical vibration signal wyThe vibration passband eigenvalue S of (t)y(t) and
Amplitude-frequency spectrum Ay(f), axial vibration signal waThe vibration passband eigenvalue S of (t)a(t)；
(5) compressor drum vibration passband trend, obtains unit alarm threshold value Thre, calculated horizontal direction is shaken
Dynamic passband eigenvalue Sx(t), vertical vibration passband eigenvalue Sy(t) and axial vibration passband eigenvalue Sa(t) respectively with
Alarm threshold value compares, and works as Sx(t) >=Thre or Sy>=Thre, simultaneously SaT () is < during Thre, it is determined that compressor bank vibration passband trend
Condition Verification passes through, and does not passes through；
(6) compressor drum vibration dominant frequency, sets dominant frequency threshold value Thref, and the vibration of calculated level direction turns frequency
Amplitude Ax(f0) and passband eigenvalue SxT () is compared and is obtained Rx=Ax(f0)/SxT () and vertical vibration turn frequency amplitude Ay
(f0) and passband eigenvalue SyT () is compared and is obtained Ry=Ay(f0)/SyT (), works as Rx>=Thref R simultaneouslyyDuring >=Thref, it is determined that pressure
Contracting unit rotor vibration dominant frequency is for turning frequency, and condition Verification passes through, and does not passes through；
(7) judge that compressor drum vibration passband trend condition Verification vibrates dominant frequency condition Verification with compressor drum
Meet by condition the most simultaneously, if it is judge parallel axes tooth-like compressor generation critical load fault, otherwise judge flat
There is not critical load fault in the tooth-like compressor of row axle.
The tooth-like compressor of parallel axes that the present invention produces with certain petroleum chemical enterprise graceful turbine is for object compression tooth-like to parallel axes
Machine critical load method for diagnosing faults is verified.The tooth-like compressor of this parallel axes has 5 rotors, and wherein 3 turn for output
Son, running speed is all higher than first critical speed, takes the most a certain rotor generation critical load fault and is analyzed diagnosis.
Believed by the vibration of the on-the-spot high speed data acquisition system Real-time Collection five axle parallel axes each rotor of tooth-like compressor
Number, key signal and inlet guide vane opening amount signal.
According to the key signal of Real-time Collection, obtain the rotating speed trend of unit operation, as in figure 2 it is shown, the rotating speed of this rotating shaft
Be far above the first critical speed 5780r/min of this rotor for 14150r/min, generating unit speed is constant simultaneously, and unit operation is steady
Fixed, rotating shaft running speed condition Verification passes through；
According to the stator entrance feedback signal obtained in real time, obtain stator entrance feedback trend during unit operation, such as Fig. 3
Shown in, in the stage of unit even running, inlet guide vane feedback signal persistently rises, and illustrates that unit is carrying out Load Regulation, logical
Cross guide vane opening condition Verification.
Calculate passband eigenvalue and its frequency spectrum according to obtaining shaft vibration signal in real time, be illustrated in figure 4 radial level
Direction vibration passband trend, Fig. 5 show radially vertical vibration passband trend, and Fig. 6 show axial vibration passband trend,
Fig. 7 is the spectrogram of 2013-04-24 11:43:37 horizontal direction vibrational waveform, and Fig. 8 is that 2013-04-24 11:43:37 is vertical
Direction vibrational waveform spectrogram.
The alarm threshold value Thre=28 μm of this parallel axes tooth-like compressor factory setting, by being calculated t=2013/
Horizontal direction vibration passband feature S during 04/24 11:43:37x(t)=28.53 μm, vertical vibration passband feature Sy(t)=
29.87 μm, axial vibration passband feature Sa(t)=10.97 μm；This moment, Sx(t) >=Thre and Sy>=Thre, simultaneously Sa(t)<
Thre, it is determined that compressor bank vibration passband trend condition Verification passes through.
Set dominant frequency threshold value Thref=0.6, obtain t=2013/04/24 11:43:37 according to spectrogram 8 and Fig. 7
The vibration of moment horizontal direction turns frequency amplitude Ax(f0)=20.2 μm, vertical vibration turns frequency amplitude Ay(f0)=22.2 μm, level
Direction turns the ratio R of frequency amplitude and passband eigenvaluex=Ax(f0)/SxT ()=0.708, vertical direction turns frequency amplitude and passband
The ratio R of eigenvaluey=Ay(f0)/Sy(t)=0.7432；In this moment, work as Rx>=Thref R simultaneouslyy>=Thref, it is determined that compressor
Group rotor vibration dominant frequency is for turning frequency, and condition Verification passes through.
Compressor drum vibration passband trend condition Verification is simultaneously full with compressor drum vibration dominant frequency condition Verification
Foot is by condition, therefore, this moment parallel axes tooth-like compressor bank generation critical load fault.
Claims (4)
1. a parallel axes tooth-like compressor critical load method for diagnosing faults, it is characterised in that including:
1) signals collecting and process, gathers vibration signal, key signal and the compressor of parallel axes tooth-like compressor bank rotor
Inlet guide vane open degree feedback signal, is calculated the tooth-like compressor bank of parallel axes turns according to the vibration signal obtained, key signal
Shaft vibration passband eigenvalue and the rotating speed of rotating shaft；
2) parallel axes tooth-like compressor rotation shaft running speed condition Verification, calculates rotating speed during rotor real time execution, it is judged that this turn
With stable rotating speed operation, whether son compares whether rotating speed is more than the first critical speed of rotor simultaneously, it is determined that generating unit speed condition
It it is the essential condition judging critical load fault；
3) parallel axes tooth-like compressor vanes aperture condition Verification, judges compressor according to the feedback signal of suction port of compressor stator
Whether at Load adjustment, open big i.e. load up and stator including stator and turn down i.e. two kinds of situations of load down, it is determined that unit stator
Aperture condition Verification is also the essential condition judging critical load fault；
4) parallel axes tooth-like compressor drum vibration passband trend condition Verification, the passband feature calculated according to shaft vibration signal
Value compares with the vibration alarming threshold value of group setup, the situation of change of quantitative analysis shaft vibration passband trend, it is determined that shake
Dynamic passband trend whether being changed significantly at guide vane opening changes phase；
Particularly as follows: described parallel axes tooth-like compressor drum vibration passband trend condition Verification, determine sample frequency Fs, sampling
Points N s, interval the t second gather shaft vibration signal w (t)；Certain roots rotor for compressor obtains t radial vibration signal
Including: horizontal direction vibration signal wx(t), vertical vibration signal wy(t), and axial vibration signal wa(t)；According to shaking
Dynamic signal passband eigenvalue calculation formula S (t)=wmax(t)-wminT () calculates acquisition t horizontal direction vibration signal respectively
wxThe horizontal vibration passband eigenvalue S of (t)x(t), vertical vibration signal wyThe vertical vibration passband eigenvalue S of (t)y
(t) and axial vibration signal waThe axial vibration passband eigenvalue S of (t)aT (), sets compressor bank vibration alarming threshold value
Thre；Alarm threshold value Thre is parallel axes tooth-like compressor factory settings when dispatching from the factory, at speed conditions checking and guide vane opening bar
Under conditions of part checking is all passed through, work as Sx(t) >=Thre or Sy>=Thre, simultaneously SaT () is < during Thre, it is determined that compressor bank is vibrated
Passband trend condition Verification passes through；
5) parallel axes tooth-like compressor drum vibration dominant frequency condition Verification, according to shaft vibration signal, in conjunction with in quick Fu
Leaf change (FFT) spectrum calculation method calculates shaft vibration signal spectrum, according to turning frequency amplitude and vibration signal passband eigenvalue
Ratio, whether the quantitative dominant frequency in analysis spectrum is to turn frequency, it is determined that shaft vibration signal turn whether a frequency amplitude shows
Write；
Particularly as follows: described compressor drum vibration dominant pilot spectral condition checking, certain roots rotor for compressor obtains t
Radial vibration signal includes: horizontal direction vibration signal wx(t), vertical vibration signal wyT (), uses fast Fourier to become
(FFT) the spectrum calculation mode of change obtains horizontal direction vibration signal w respectivelyxThe amplitude-frequency spectrum A of (t)x(f) and vertical vibration
Signal wyThe amplitude-frequency spectrum A of (t)yF (), wherein, f represents frequency content, and A (f) represents the amplitude of f frequency content；T rotating shaft is shaken
Dynamic signal is w (t), and the frequency that turns of rotor is f0, the amplitude turning frequency is A (f0), the passband eigenvalue of shaft vibration signal is S (t),
Turn the ratio R=A (f of frequency amplitude and passband eigenvalue0)/S (t), it is determined that dominant frequency threshold value is Thref, takes Thref >=
0.6, when ratio R is more than or equal to when setting threshold value Thref, it is believed that turn frequency amplitude A (f0) notable in frequency spectrum, turn frequency f0Take as the leading factor
Frequency；Turn frequency amplitude A when horizontal direction vibration signalx(f0) and its passband eigenvalue Sx(t) ratio Rx=Ax(f0)/Sx(t)
Turn frequency amplitude A with vertical vibration signaly(f0) and its passband eigenvalue SyThe ratio R of (t)y=Ay(f0)/SyT () is the biggest
When threshold value Thref set, it is determined that compressor bank rotor oscillation dominant pilot spectral condition is verified；
6) parallel axes tooth-like compressor critical load method for diagnosing faults, opens according to the checking of compressor operating speed conditions, stator
Degree condition Verification, vibration passband trend condition Verification and the result of dominant frequency condition Verification 4 project checking, comprehensive descision obtains
It has whether the tooth-like compressor of parallel axes occurs the conclusion of critical load fault.
Parallel axes the most according to claim 1 tooth-like compressor critical load method for diagnosing faults, it is characterised in that: described
Signal acquiring and processing, gather parallel axes tooth-like compressor rotation shaft signal time, need to gather the radial vibration of each rotating shaft
Signal: horizontal direction vibration signal and vertical vibration signal, axial vibration signal, key signal, shaft vibration signal w
Passband eigenvalue S (t) of (t)=wmax(t)-wmin(t), wherein wmaxT () is the peak-peak of t vibration signal, wmin(t)
Minimum peak for t vibration signal；The rotating speed of each rotating shaft is then calculated by the key signal in collection rotating shaft, turns
(z* Δ t), wherein, z is rotor keyway quantity to speed Rev=60/, and Δ t is the interval between key signal pulse.
Parallel axes the most according to claim 1 tooth-like compressor critical load method for diagnosing faults, it is characterised in that: described
Compressor bank rotating shaft running speed condition Verification, for the tooth-like compressor of parallel axes of reality application, has the rotor of more than 3,
These rotors have different first critical speed Rev respectively1CWith nominal operation rotating speed RevR0, work when rotating shaft is properly functioning
Rotating speed is Rev, and rotating speed allowable error threshold value is ThreR, take ThreR=10r/min, works as RevR0-ThreR<Rev<RevR0+ThreR
Time, the rotating shaft rotating speed that operates steadily is constant, and working speed when rotating shaft simultaneously runs exceedes first critical speed Rev > Rev1CTime, turn
Axle running speed condition Verification passes through, and illustrates that this rotor has possessed the necessary bar that critical load fault occur relevant to rotating speed
Part.
Parallel axes the most according to claim 1 tooth-like compressor critical load method for diagnosing faults, it is characterised in that: described
Compressor vanes aperture condition Verification, suction port of compressor guide vane opening feedback signal p (t) is the percentage ratio of guide vane opening, scope:
0%≤p (t)≤100%, in the case of operating mode is constant, current time t guide vane opening feedback signal p (t) and previous moment moment
tfGuide vane opening feedback signal p (tf) equal, i.e. p (t)=p (tf)；As p (t) ≠ p (tf) time, guide vane opening feedback signal occurs
Change, compressor vanes aperture condition Verification passes through, and illustrates that this compressor has possessed the generation relevant to guide vane opening critical negative
The essential condition of lotus fault.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410441460.8A CN104236883B (en) | 2014-09-02 | Parallel axes tooth-like compressor critical load method for diagnosing faults |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410441460.8A CN104236883B (en) | 2014-09-02 | Parallel axes tooth-like compressor critical load method for diagnosing faults |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104236883A CN104236883A (en) | 2014-12-24 |
| CN104236883B true CN104236883B (en) | 2017-01-04 |
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ID=
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013009258A1 (en) * | 2011-07-14 | 2013-01-17 | S.P.M. Instrument Ab | A method and a system for analysing the condition of a rotating machine part |
| WO2013115716A1 (en) * | 2012-01-30 | 2013-08-08 | S.P.M. Instrument Ab | Apparatus and method for analysing the condition of a machine having a rotating part |
| CN103437992A (en) * | 2013-08-06 | 2013-12-11 | 大连理工大学 | Dynamic characteristic simulation experiment set of five-parallel-shaft tooth-type compressor |
| CN203732252U (en) * | 2013-12-30 | 2014-07-23 | 天津市宝涞精密机械有限公司 | Multichannel oil orifice detection clamp for compressor crankshaft |
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013009258A1 (en) * | 2011-07-14 | 2013-01-17 | S.P.M. Instrument Ab | A method and a system for analysing the condition of a rotating machine part |
| WO2013115716A1 (en) * | 2012-01-30 | 2013-08-08 | S.P.M. Instrument Ab | Apparatus and method for analysing the condition of a machine having a rotating part |
| CN103437992A (en) * | 2013-08-06 | 2013-12-11 | 大连理工大学 | Dynamic characteristic simulation experiment set of five-parallel-shaft tooth-type compressor |
| CN203732252U (en) * | 2013-12-30 | 2014-07-23 | 天津市宝涞精密机械有限公司 | Multichannel oil orifice detection clamp for compressor crankshaft |
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