CN104458128A - Turbocharger rotor unbalance amount control method based on dynamic characteristics - Google Patents
Turbocharger rotor unbalance amount control method based on dynamic characteristics Download PDFInfo
- Publication number
- CN104458128A CN104458128A CN201510000931.6A CN201510000931A CN104458128A CN 104458128 A CN104458128 A CN 104458128A CN 201510000931 A CN201510000931 A CN 201510000931A CN 104458128 A CN104458128 A CN 104458128A
- Authority
- CN
- China
- Prior art keywords
- unbalance
- amount
- vibration
- rotor
- kinds
- 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
Landscapes
- Supercharger (AREA)
Abstract
The invention discloses a turbocharger rotor unbalance amount control method based on dynamic characteristics. The method comprises the steps that a turbocharger rotor bearing system dynamics finite element solid model is built; (2) different unbalance amount excitation modes are applied to the dynamics finite element solid model, and vibration responses and stability rules of turbocharger rotor unbalance position, size and phase difference to the measuring points of two bearings are summarized; (3) the optimum allocation scheme of unbalance excitation on the rotor position, size and phase difference is determined with the minimum root-mean-square value of the vibration amplitude as the judging criteria; (4) turbocharger rotor structure parameters are optimized until the vibration amplitudes at the positions of the two turbocharger rotor bearings are the minimum and the stability at the positions of the two turbocharger rotor bearings is the best. According to the turbocharger rotor unbalance amount control method, unbalance control is applied in the turbine end and air pressing end structure design and manufacturing process, stable and efficient running of the whole machine can be achieved, and unbalance vibration faults caused in the rotor running process are effectively reduced.
Description
Technical field
The invention belongs to turbosupercharger dynamics and vibration control field, especially relate to a kind of turbocharger rotor amount of unbalance control method based on dynamics.
Background technology
Turbocharging technology is the important channel of automobile energy-saving consumption reduction.At present, engine extensively adopts exhaust turbine pressuring technology, supercharging has become raising engine power performance, improve the effective measures of its economic benefit and emission standard, in the face of energy supply and demand general layout new change, international energy new development trend, base oneself upon the fundamental realities of the country of China, have the Scientific Outlook on Development in mind and closely follow the new new trend of international energy technology lattice, in addition the manufacture production cost of small-sized vehicle turbocharger is low and effectively utilize exhaust gas-driven turbine to make this gordian technique of energy recycling, turbocharging technology will obtain more general exploitation and application in China from now on, must ensure that machine steadily runs safely and efficiently simultaneously.Turbocharger operation turns scooter more than 200,000 turns, and operating rotational speed range is very wide from 20,000 turn-20 ten thousand turns, and the imbalance of the rotor exciting source that to be rotating machinery main, be also the triggering factors of many kinds of autovibrations, the unbalance response of rotor directly affects turbosupercharger runnability.Uneven flexure and the internal stress that can cause rotor, makes machine produce vibration & noise, accelerates the abrasion of the part such as bearing, shaft seal, reduce the work efficiency of machine, even can cause various accident time serious.Therefore, consider the uneven impact on complete machine, especially for the special construction of the wide operating rotational speed range of this high speed light loading lesser trochanter of turbosupercharger, how to eliminate the vibration of rotor unbalance to turbosupercharger, this seems particularly important to during producer's Design and manufacture turbosupercharger.
Method or device how to measure or reduce amount of unbalance are studied by current most of producer, at the beginning of design, do not consider the amount of unbalance of rotor-support-foundation system, just after design is produced, perform corresponding balance scheme.Measuring rotor unbalance degree great majority adopts equilibrator to carry out, and comprises single side method and Double-surfaces Method carries out the multiple dynamic balance method such as balancing to rotating machinery.But rotor unbalance amount control method rare solution always, especially for this special high-speed micro structure of turbosupercharger.The department such as manufacturer or factory carries out high-speed balancing with balancing rotor system after turbocharger design is complete, or vibrate the excessive transient equilibrium measure carrying out corresponding balance again when occurring uneven, all carried out after having designed, not yet take in from turbocharger design and manufacture process, turbosupercharger is caused to need to carry out unbalance vibration control in real work operational process, turbosupercharger is caused to be vibrated excessive, hydraulic performance decline, even increases unnecessary production maintenance cost.
Summary of the invention
In order to solve the problems of the technologies described above, the invention provides a kind of turbocharger rotor amount of unbalance control method based on dynamics, it is by analyzing different uneven exiting form to turbocharger rotor vibratory response size and Role of stability, in turbine end and air end of booster structural design and manufacture process, implement amount of unbalance control, complete machine can be realized steadily run efficiently, effectively reduce unbalance vibration fault in rotor operation process, ensure that turbosupercharger is safe and efficient stable in operational process, save its maintenance cost, extend the serviceable life of turbosupercharger.
As shown in Figure 1, particular content comprises for the ultimate principle of this method and implementing procedure:
(1) according to turbocharger rotor parameters of structural dimension, in conjunction with bearing shell assemblage gap, lubricating oil temperature, lubricating oil viscosity, floating-ring bearing rotating speed and two bearings place static load actual operation parameters, adopt the dynamics software DyRoBeS based on finite element method, build turbocharger rotor bearing system dynamics solid finite element model, with the critical rotary speed measured value of actual rotor for reference, according to the criterion of simulation calculation value error within 5% of itself and turbocharger rotor bearing system dynamics solid finite element model, kinetic parameters is verified;
(2) on the dynamics solid finite element model basis built, in conjunction with turbocharger rotor transient equilibrium G2.5 class requirement, the numerical range of amount of unbalance is determined; Then different amount of unbalance exiting forms is implemented to dynamics solid finite element model; Calculate the once per revolution vibration amplitude at two bearings place in operating rotational speed range under different amount of unbalance exiting form, full range vibration amplitude and subharmonic vibration amplitude respectively, show that turbocharger rotor non-equilibrium site, size, phase differential are to the place's vibratory response of two bearings measuring point and Role of stability;
(3) based on the decomposition and synthesis principle of obtained uneven excited vibration response pattern and out-of-balance force, in conjunction with turbocharger turbine end and air end of booster blade wheel structure actual conditions, minimum for judgment criterion with the root-mean-square value of vibration amplitude, determine that imbalance is activated at the best configuration scheme of position on rotor, size and phase differential respectively;
(4) according to the amount of unbalance best configuration scheme that step (3) obtains, in conjunction with turbocharger rotor design feature and practical operation situation, turbocharger rotor structural parameters are optimized;
(5) step 1 is repeated)-5), according to API vibration standard, until the vibration amplitude at turbocharger rotor two bearings place is minimum, and stability is best.
The above-mentioned turbocharger rotor amount of unbalance control method based on dynamics, the concrete operation method of step (2) is as follows:
(1) by two schemes, amount of unbalance is applied to turbocharger rotor bearing system dynamics solid finite element model: apply amount of unbalance in turbine end separately and apply onesize amount of unbalance at air end of booster separately; The analysis of stable state sync response is carried out respectively to the vibration that two kinds of schemes applying amount of unbalance cause, show that the scheme of two kinds of applying amount of unbalances is the vibration amplitudes in operating rotational speed range, by comparing the root-mean-square value of vibration amplitude, judge that amount of unbalance is applied to turbine end and plays the strong or amount of unbalance of the susceptibility of once per revolution vibration and be applied to air end of booster and cause the susceptibility of once per revolution vibration strong; Then, to the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under time domain respectively, draw in the working rotor range of speeds, two kinds of full range vibration amplitudes applying the vibration that the scheme of amount of unbalances causes, same by comparing the root-mean-square value of full range vibration amplitude, judge amount of unbalance be applied to susceptibility that turbine end plays full range vibration by force still amount of unbalance to be applied to the susceptibility that air end of booster causes full range to vibrate strong; To the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under frequency domain respectively, under drawing the scheme of two kinds of applying amount of unbalances, rotor is with the full range vibration Waterfall plot of rotation speed change, apply track that the schemes of amount of unbalances cause the frequency division of vibration to occur and magnitude of vibrations by comparing two kinds, draw amount of unbalance be applied to turbine end on the impact of turbocharger rotor system stability greatly still amount of unbalance to be applied to the impact of air end of booster on turbocharger rotor system stability large;
(2) based on the turbocharger rotor bearing system dynamics finite element model set up, repeatedly amount of unbalance is added according to equipartition principle in the numerical range of amount of unbalance, amount of unbalance is applied to turbine end and air end of booster simultaneously, turbine end and air end of booster are applied to the amount of unbalance of formed objects at every turn, the analysis of stable state sync response is carried out respectively to the vibration that different size amount of unbalance causes, draw the vibration amplitude in operating rotational speed range, the amount of unbalance of more different size causes the vibration amplitude root-mean-square value of vibration; The time transients analysis under time domain is carried out in the vibration caused different size amount of unbalance respectively, draw the full range vibration amplitude of the vibration that different size amount of unbalance causes in the working rotor range of speeds, the root value of the full range vibration amplitude of the vibration that more different size amount of unbalance causes; The time transients analysis under frequency domain is carried out in the vibration caused different size amount of unbalance respectively, when drawing rotor with rotation speed change, the full range vibration Waterfall plot of the vibration that different size amount of unbalance causes, track and the magnitude of vibrations of the frequency division appearance of the vibration caused by more different size amount of unbalance show that amount of unbalance size is not to the affecting laws of turbocharger rotor system stability; The principle minimum based on full range vibration values and subharmonic vibration value is minimum, summary and induction amount of unbalance size is to turbocharger rotor vibratory response size and Role of stability;
(3) simultaneously to turbine end and air end of booster, point two kinds of modes apply amount of unbalance: air end of booster and turbine end applying amount of unbalance phase differential are respectively 0 ° and air end of booster and turbine end applying amount of unbalance phase differential and are respectively 180 °; The analysis of stable state sync response is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draws the vibration amplitude in operating rotational speed range under two kinds of modes, and compares the root-mean-square value of vibration amplitude; Then, the time transients analysis under time domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, and draw in the working rotor range of speeds, the full range vibration amplitude of the vibration that amount of unbalance causes under two kinds of modes, compares the root-mean-square value of full range vibration amplitude; The time transients analysis under frequency domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draw the full range vibration Waterfall plot of two kinds of mode lower rotor parts with rotation speed change, the track occurred by the frequency division comparing the vibration that amount of unbalance under two kinds of modes causes and magnitude of vibrations, show that air end of booster and turbine end apply amount of unbalance phase differential and be respectively 0 ° and air end of booster and turbine end and apply under amount of unbalance phase differential is respectively 180 ° of two kinds of situations, amount of unbalance is to the affecting laws of turbocharger rotor system stability.
Compared with prior art, the invention has the beneficial effects as follows:
The present invention proposes to solve how to distribute turbocharger rotor amount of unbalance rationally from dynamics design angle, and then ensures that the turbosupercharger of High Rotation Speed is steady in wider operating rotational speed range internal vibration, safe operation; The present invention controls turbocharger rotor amount of unbalance targetedly in rotor structure, manufacture process, effectively reduce unbalance vibration fault in rotor operation process, ensure that turbosupercharger is safe and efficient stable in operational process, save its maintenance cost, extend the serviceable life of turbosupercharger.
Accompanying drawing explanation
Fig. 1 is ultimate principle of the present invention and process flow diagram.
Fig. 2 is turbocharger rotor system architecture schematic diagram.
Fig. 3 is air end of booster floating-ring bearing kinetic model.
Fig. 4 is turbine end floating-ring bearing kinetic model.
Fig. 5 is turbocharger rotor bearing system dynamics solid finite element model.
Fig. 6 is that only compressor impeller end applies the rotor schematic diagram of amount of unbalance.
Fig. 7 is that only turbine end applies the rotor schematic diagram of amount of unbalance.
Fig. 8 is the rotor schematic diagram that air end of booster and turbine end apply amount of unbalance simultaneously.
Fig. 9 is the rotor schematic diagram that air end of booster and turbine end apply that amount of unbalance differential seat angle is 0 °.
Figure 10 is the rotor schematic diagram that air end of booster and turbine end apply that amount of unbalance differential seat angle is 180 °.
Figure 11 is the decomposition and synthesis of out-of-balance force.
In figure: 1-nut, 2-compressor impeller, 3-floating-ring bearing, 4-bearing seat and intermediate, 5-turbine, 6-armature spindle.
Embodiment
Below in conjunction with accompanying drawing, the present invention is further illustrated.
As shown in Figure 1, the present invention includes following steps:
1) when turbocharger design, analyze the rotor bearing arrangement feature of turbosupercharger, set up rotor-support-foundation system motion control equation
wherein M is mass matrix, and C is system external damping matrix, and G is gyroscopic couple battle array, and K is system stiffness matrix, q,
with
represent displacement, speed and acceleration respectively, F
ifor supporting oil-film force in axle journal, F
ubfor out-of-balance force, F
sfor static load gravity.According to floating-ring bearing parameters of structural dimension, in conjunction with bearing shell assemblage gap, lubricating oil temperature, lubricating oil viscosity, floating-ring bearing rotating speed and two bearings place static load actual operation parameters, DyRoBeS_BePerf module software is adopted to carry out modeling to turbine end and air end of booster floating-ring bearing respectively, the floating-ring bearing kinetic model set up as shown in Figure 3 and Figure 4, based on set up bearing system dynamics model, analytical calculation goes out bearing rigidity and dampened power characteristic coefficient.According to rotor-support-foundation system parameters of structural dimension and rotor-support-foundation system each parts material properties parameter, adopt the dynamics software DyRoBeS based on finite element method, build turbocharger rotor bearing system dynamics solid finite element model, turbocharger rotor bearing system dynamics solid finite element model as shown in Figure 5.DyRoBeS_BePerf module is run the rigidity, the damping characteristic coefficient document .brg that obtain and bring Bearings in Rotor module into, can set up for the rotor bearing kinetic model carrying out critical rotor speed, stability, stable state sync response are analyzed.Bearings place directly in DyRoBeS_Rotor module carries out two floating-ring bearing structures and operational factor is arranged, can set up the dynamical model of rotor for carrying out the time transients numerical analysis under frequency-domain and time-domain, turbocharger rotor bearing system dynamics solid finite element model as shown in Figure 5.With the critical rotary speed measured value of actual rotor for reference, undamped critical rotary speed and vibration modal analysis are carried out to the finite element dynamics set up, according to the criterion of critical rotary speed measurement error within 5% of itself and border rotor, kinetic parameters is verified, the validity of Modling model to determine.
2) based on step 1) the turbocharger rotor bearing system dynamics finite element model set up, in conjunction with rotor structure feature and practical operation situation, based on API standard and turbosupercharger transient equilibrium G2.5 class requirement, determine the amount of unbalance of turbine end and air end of booster allowed band (uneven qualified amount computing formula:
, wherein M is quality, and G is dynamic balance grade, and r is for increasing the weight of radius, and n is rotating speed); Apply amount of unbalance in turbine end separately and apply onesize amount of unbalance at air end of booster separately, two kinds apply the scheme of amount of unbalance as shown in Figure 6 and Figure 7.The analysis of stable state sync response is carried out respectively to the vibration that two kinds of schemes applying amount of unbalance cause, show that the scheme of two kinds of applying amount of unbalances is the vibration amplitudes in operating rotational speed range, by comparing the root-mean-square value of vibration amplitude, judge that amount of unbalance is applied to turbine end and plays the strong or amount of unbalance of the susceptibility of once per revolution vibration and be applied to air end of booster and cause the susceptibility of once per revolution vibration strong; Then, to the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under time domain respectively, draw in the working rotor range of speeds, two kinds of full range vibration amplitudes applying the vibration that the scheme of amount of unbalances causes, same by comparing the root-mean-square value of full range vibration amplitude, judge amount of unbalance be applied to susceptibility that turbine end plays full range vibration by force still amount of unbalance to be applied to the susceptibility that air end of booster causes full range to vibrate strong; To the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under frequency domain respectively, under drawing the scheme of two kinds of applying amount of unbalances, rotor is with the full range vibration Waterfall plot of rotation speed change, apply track that the schemes of amount of unbalances cause the frequency division of vibration to occur and magnitude of vibrations by comparing two kinds, draw amount of unbalance be applied to turbine end on the impact of turbocharger rotor system stability greatly still amount of unbalance to be applied to the impact of air end of booster on turbocharger rotor system stability large.
3) based on step 2) determined non-equilibrium site is on the basis of turbocharger rotor vibration characteristics, in conjunction with rotor structure feature and practical operation situation, based on API standard and turbosupercharger transient equilibrium G2.5 class requirement, determine the amount of unbalance of turbine end and air end of booster allowed band (uneven qualified amount computing formula:
, wherein M is quality, and G is dynamic balance grade, and r is for increasing the weight of radius, and n is rotating speed); Based on the turbocharger rotor bearing system dynamics finite element model set up, according to equipartition principle (0.1U in the numerical range of amount of unbalance, 0.2U, 0.4U, 0.6U, 0.8U, 1U) repeatedly apply amount of unbalance, apply amount of unbalance to turbine end and air end of booster, turbine end and air end of booster are applied to the amount of unbalance of formed objects, the uneven mode of applying as shown in Figure 8 at every turn simultaneously.Carry out the analysis of stable state sync response respectively to the vibration that different size amount of unbalance causes, draw the vibration amplitude in operating rotational speed range, the amount of unbalance of more different size causes the vibration amplitude root-mean-square value of vibration; The time transients analysis under time domain is carried out in the vibration caused different size amount of unbalance respectively, draw the full range vibration amplitude of the vibration that different size amount of unbalance causes in the working rotor range of speeds, the root value of the full range vibration amplitude of the vibration that more different size amount of unbalance causes; The time transients analysis under frequency domain is carried out in the vibration caused different size amount of unbalance respectively, when drawing rotor with rotation speed change, the full range vibration Waterfall plot of the vibration that different size amount of unbalance causes, track and the magnitude of vibrations of the frequency division appearance of the vibration caused by more different size amount of unbalance show that amount of unbalance size is not to the affecting laws of turbocharger rotor system stability; The principle minimum based on full range vibration values and subharmonic vibration value is minimum, summary and induction amount of unbalance size is to turbocharger rotor vibratory response size and Role of stability.
4) this step divides two kinds of modes to apply amount of unbalance: air end of booster and turbine end applying amount of unbalance phase differential are respectively 0 ° and air end of booster and turbine end applying amount of unbalance phase differential and are respectively 180 °, and the uneven mode of applying as shown in Figure 9 and Figure 10.The analysis of stable state sync response is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draws the vibration amplitude in operating rotational speed range under two kinds of modes, and compares the root-mean-square value of vibration amplitude; Then, the time transients analysis under time domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, and draw in the working rotor range of speeds, the full range vibration amplitude of the vibration that amount of unbalance causes under two kinds of modes, compares the root-mean-square value of full range vibration amplitude; The time transients analysis under frequency domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draw the full range vibration Waterfall plot of two kinds of mode lower rotor parts with rotation speed change, the track occurred by the frequency division comparing the vibration that amount of unbalance under two kinds of modes causes and magnitude of vibrations, show that air end of booster and turbine end apply amount of unbalance phase differential and be respectively 0 ° and air end of booster and turbine end and apply under amount of unbalance phase differential is respectively 180 ° of two kinds of situations, amount of unbalance is to the affecting laws of turbocharger rotor system stability.
Relatively air end of booster and turbine end apply amount of unbalance phase differential is under 0 ° and air end of booster and turbine end apply amount of unbalance phase differential 180 ° of two kinds of situations, amount of unbalance is on the impact of the vibration amplitude of rotor, amount of unbalance vibrates the impact of width earthquake intensity size on the impact of turbocharger rotor system stability and amount of unbalance to bearing place, specify the impact of unbalance phase difference on turbosupercharger dynamics, only form out-of-balance force and not form couple good when namely applying unbalanced, or apply uneven after existing out-of-balance force better and vibrate minimum to the stability of complete machine when having again a unbalanced couple.
5) based on step 2)-4) amount of unbalance (comprising non-equilibrium site, uneven size and uneven differential seat angle) that draws is to turbocharger rotor system responses rule, based on the decomposition and synthesis principle of out-of-balance force, as shown in figure 11: F
1and F
2be respectively two out-of-balance forces on rotor, planar I and plane II are two optional balanced surfaces, and the principle equal according to force and moment, can by F
1, F
2decompose two planes to get on, namely
Wherein l
1, l
2, l
3represent corresponding shaft part distance respectively, the power synthesis in planar I and plane II is obtained equivalent out-of-balance force A and B, A=F
11+ F
21, B=F
12+ F
22, how complicated regardless of distribution uneven on rotor, can be decomposed as stated above on two end faces for each out-of-balance force, be obtained the equivalent out-of-balance force on two end faces.Effect on two planar can be decomposed into again the identical symmetric force A in equal and opposite in direction, direction with joint efforts
d, B
d(A
d=B
d) the antisymmetry power A contrary with equal and opposite in direction, direction
f, B
f(A
f=B
f), wherein A=A
d+ A
f, B=B
d+ B
f, A
d=B
d=(A+B)/2, A
f=-B
f=(A-B)/2, in conjunction with turbocharger turbine end and air end of booster blade wheel structure actual conditions, namely turbine and compressor impeller are with irregular blade and thickness is different, on blade, loss of weight is increased the weight of more difficult when eliminating uneven, unbalanced applying or elimination are all generally that edge and trailing edge perform before the impeller, namely by the decomposition and synthesis method of out-of-balance force power decomposed the equivalent force on impeller leading edge and rear surface, increase the weight of loss of weight accordingly, then minimum for judgment criterion with the root-mean-square value of vibration amplitude, determine that imbalance is activated at position on rotor respectively, the best configuration scheme of size and phase differential, show that the control strategy of amount of unbalance (comprises structural design, manufacture, installation and operation aspect controls accordingly), implement to increase the weight of loss of weight scheme accordingly, optimize turbocharger rotor structural parameters, reach in rotor operation process and vibrate minimum object.
6) repeat step 1-5, according to API vibration standard, until the vibration amplitude at turbocharger rotor two bearings place is minimum, and stability is best.
Claims (2)
1., based on a turbocharger rotor amount of unbalance control method for dynamics, comprise the steps:
(1) according to turbocharger rotor parameters of structural dimension, in conjunction with bearing shell assemblage gap, lubricating oil temperature, lubricating oil viscosity, floating-ring bearing rotating speed and two bearings place static load actual operation parameters, adopt the dynamics software DyRoBeS based on finite element method, build turbocharger rotor bearing system dynamics solid finite element model, with the critical rotary speed measured value of actual rotor for reference, according to the criterion of simulation calculation value error within 5% of itself and turbocharger rotor bearing system dynamics solid finite element model, kinetic parameters is verified;
(2) on the dynamics solid finite element model basis built, in conjunction with turbocharger rotor transient equilibrium G2.5 class requirement, the numerical range of amount of unbalance is determined; Then different amount of unbalance exiting forms is implemented to dynamics solid finite element model; Calculate the once per revolution vibration amplitude at two bearings place in operating rotational speed range under different amount of unbalance exiting form, full range vibration amplitude and subharmonic vibration amplitude respectively, show that turbocharger rotor non-equilibrium site, size, phase differential are to the place's vibratory response of two bearings measuring point and Role of stability;
(3) based on the decomposition and synthesis principle of obtained uneven excited vibration response pattern and out-of-balance force, in conjunction with turbocharger turbine end and air end of booster blade wheel structure actual conditions, minimum for judgment criterion with the root-mean-square value of vibration amplitude, determine that imbalance is activated at the best configuration scheme of position on rotor, size and phase differential;
(4) according to the amount of unbalance best configuration scheme that step (3) obtains, in conjunction with turbocharger rotor design feature and practical operation situation, turbocharger rotor structural parameters are optimized;
(5) step 1)-5 is repeated), according to API vibration standard, until the vibration amplitude at turbocharger rotor two bearings place is minimum, and stability is best.
2. the turbocharger rotor amount of unbalance control method based on dynamics according to claim 1, the concrete operation method of step (2) is as follows:
(1) by two schemes, amount of unbalance is applied to turbocharger rotor bearing system dynamics solid finite element model: apply amount of unbalance in turbine end separately and apply onesize amount of unbalance at air end of booster separately; The analysis of stable state sync response is carried out respectively to the vibration that two kinds of schemes applying amount of unbalance cause, show that the scheme of two kinds of applying amount of unbalances is the vibration amplitudes in operating rotational speed range, by comparing the root-mean-square value of vibration amplitude, judge that amount of unbalance is applied to turbine end and plays the strong or amount of unbalance of the susceptibility of once per revolution vibration and be applied to air end of booster and cause the susceptibility of once per revolution vibration strong; Then, to the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under time domain respectively, draw in the working rotor range of speeds, two kinds of full range vibration amplitudes applying the vibration that the scheme of amount of unbalances causes, same by comparing the root-mean-square value of full range vibration amplitude, judge amount of unbalance be applied to susceptibility that turbine end plays full range vibration by force still amount of unbalance to be applied to the susceptibility that air end of booster causes full range to vibrate strong; To the time transients analysis that two kinds apply vibration that the schemes of amount of unbalances cause and carry out under frequency domain respectively, under drawing the scheme of two kinds of applying amount of unbalances, rotor is with the full range vibration Waterfall plot of rotation speed change, apply track that the schemes of amount of unbalances cause the frequency division of vibration to occur and magnitude of vibrations by comparing two kinds, draw amount of unbalance be applied to turbine end on the impact of turbocharger rotor system stability greatly still amount of unbalance to be applied to the impact of air end of booster on turbocharger rotor system stability large;
(2) based on the turbocharger rotor bearing system dynamics finite element model set up, repeatedly amount of unbalance is added according to equipartition principle in the numerical range of amount of unbalance, amount of unbalance is applied to turbine end and air end of booster simultaneously, turbine end and air end of booster are applied to the amount of unbalance of formed objects at every turn, the analysis of stable state sync response is carried out respectively to the vibration that different size amount of unbalance causes, draw the vibration amplitude in operating rotational speed range, the amount of unbalance of more different size causes the vibration amplitude root-mean-square value of vibration; The time transients analysis under time domain is carried out in the vibration caused different size amount of unbalance respectively, draw the full range vibration amplitude of the vibration that different size amount of unbalance causes in the working rotor range of speeds, the root value of the full range vibration amplitude of the vibration that more different size amount of unbalance causes; The time transients analysis under frequency domain is carried out in the vibration caused different size amount of unbalance respectively, when drawing rotor with rotation speed change, the full range vibration Waterfall plot of the vibration that different size amount of unbalance causes, track and the magnitude of vibrations of the frequency division appearance of the vibration caused by more different size amount of unbalance show that amount of unbalance size is not to the affecting laws of turbocharger rotor system stability; The principle minimum based on full range vibration values and subharmonic vibration value is minimum, summary and induction amount of unbalance size is to turbocharger rotor vibratory response size and Role of stability;
(3) simultaneously to turbine end and air end of booster, point two kinds of modes apply amount of unbalance: air end of booster and turbine end applying amount of unbalance phase differential are respectively 0 ° and air end of booster and turbine end applying amount of unbalance phase differential and are respectively 180 °; The analysis of stable state sync response is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draws the vibration amplitude in operating rotational speed range under two kinds of modes, and compares the root-mean-square value of vibration amplitude; Then, the time transients analysis under time domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, and draw in the working rotor range of speeds, the full range vibration amplitude of the vibration that amount of unbalance causes under two kinds of modes, compares the root-mean-square value of full range vibration amplitude; The time transients analysis under frequency domain is carried out in the vibration caused amount of unbalance under two kinds of modes respectively, draw the full range vibration Waterfall plot of two kinds of mode lower rotor parts with rotation speed change, the track occurred by the frequency division comparing the vibration that amount of unbalance under two kinds of modes causes and magnitude of vibrations, show that air end of booster and turbine end apply amount of unbalance phase differential and be respectively 0 ° and air end of booster and turbine end and apply under amount of unbalance phase differential is respectively 180 ° of two kinds of situations, amount of unbalance is to the affecting laws of turbocharger rotor system stability.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510000931.6A CN104458128B (en) | 2015-01-04 | 2015-01-04 | A kind of turbocharger rotor amount of unbalance control method based on dynamics |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510000931.6A CN104458128B (en) | 2015-01-04 | 2015-01-04 | A kind of turbocharger rotor amount of unbalance control method based on dynamics |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104458128A true CN104458128A (en) | 2015-03-25 |
| CN104458128B CN104458128B (en) | 2017-03-15 |
Family
ID=52904546
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510000931.6A Active CN104458128B (en) | 2015-01-04 | 2015-01-04 | A kind of turbocharger rotor amount of unbalance control method based on dynamics |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104458128B (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104899878A (en) * | 2015-05-21 | 2015-09-09 | 北京工业大学 | Method for detecting reasonable establishment of locomotive turbocharger rotor three-dimensional model |
| CN106323548A (en) * | 2016-08-08 | 2017-01-11 | 浙江大学 | Double vibration sensor-based rotor imbalance vibration response identification method |
| CN106338363A (en) * | 2015-05-16 | 2017-01-18 | 江苏思维福特机械科技股份有限公司 | Dynamic balancing correction process |
| CN106484990A (en) * | 2016-09-30 | 2017-03-08 | 西安航天动力试验技术研究所 | A kind of engine test data three-dimensional Waterfall plot is rebuild, is shown and analysis method |
| CN107702854A (en) * | 2017-07-10 | 2018-02-16 | 北京航天动力研究所 | A kind of high-speed balancing method for meeting rocket engine turbopump assembling and using |
| CN107939902A (en) * | 2017-11-15 | 2018-04-20 | 合肥动联自动化科技有限公司 | A kind of integrated damping test fixture of turbocharger dynamic balance testing machine |
| CN108161336A (en) * | 2018-01-25 | 2018-06-15 | 宁波丰沃涡轮增压系统有限公司 | A kind of assembly technology for reducing the initial computing ballance correction of core component |
| CN108827536A (en) * | 2018-03-27 | 2018-11-16 | 江苏大学 | Online dynamic balance detection system and detection method are assembled by a kind of combination revolution system |
| CN109580231A (en) * | 2018-12-12 | 2019-04-05 | 中国北方发动机研究所(天津) | A kind of pressure shell rotation failure test method of identification diesel engine matching turbocharger |
| CN110188514A (en) * | 2019-07-10 | 2019-08-30 | 湖南科技大学 | The rotor annular components floor error of division causes rotor unbalance value analytic approach |
| CN111473859A (en) * | 2020-05-21 | 2020-07-31 | 中国航发湖南动力机械研究所 | Method for making vibration limit value of whole machine |
| CN111751051A (en) * | 2020-06-24 | 2020-10-09 | 贵州永红航空机械有限责任公司 | Dynamic balancing method for double-disc flexible rotor of supercharged turbine |
| CN112668123A (en) * | 2020-12-31 | 2021-04-16 | 沈阳鼓风机集团股份有限公司 | Vibration characteristic analysis method, device and equipment of cantilever sensitive type single-shaft rotor |
| CN115795716A (en) * | 2022-11-15 | 2023-03-14 | 中国航发沈阳发动机研究所 | Method for determining requirement of unbalance amount of rotor |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020029085A1 (en) * | 2000-09-01 | 2002-03-07 | Park Kang Duk | System for automatic control of building |
| JP2005121580A (en) * | 2003-10-20 | 2005-05-12 | Akashi Corp | Balance testing method |
| CN101949753B (en) * | 2010-09-16 | 2011-11-16 | 西北工业大学 | High-speed flexible rotor dynamic balance method |
| CN102680172A (en) * | 2011-12-15 | 2012-09-19 | 上海卫星工程研究所 | Dynamic balance control method of large rotary load |
| CN103592081A (en) * | 2013-11-01 | 2014-02-19 | 西安电子科技大学 | Rotor non-trial-weight dynamic balancing method suitable for distributed unbalance |
| CN103913272A (en) * | 2014-04-03 | 2014-07-09 | 华北电力大学 | Quantitative diagnosis method for rotor mass unbalance fault of steam turbine generator unit |
-
2015
- 2015-01-04 CN CN201510000931.6A patent/CN104458128B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020029085A1 (en) * | 2000-09-01 | 2002-03-07 | Park Kang Duk | System for automatic control of building |
| JP2005121580A (en) * | 2003-10-20 | 2005-05-12 | Akashi Corp | Balance testing method |
| CN101949753B (en) * | 2010-09-16 | 2011-11-16 | 西北工业大学 | High-speed flexible rotor dynamic balance method |
| CN102680172A (en) * | 2011-12-15 | 2012-09-19 | 上海卫星工程研究所 | Dynamic balance control method of large rotary load |
| CN103592081A (en) * | 2013-11-01 | 2014-02-19 | 西安电子科技大学 | Rotor non-trial-weight dynamic balancing method suitable for distributed unbalance |
| CN103913272A (en) * | 2014-04-03 | 2014-07-09 | 华北电力大学 | Quantitative diagnosis method for rotor mass unbalance fault of steam turbine generator unit |
Non-Patent Citations (3)
| Title |
|---|
| 宾光富 等: "基于有限元模型的转子动平衡影响系数求解法", 《振动、测试与诊断》 * |
| 李波波 等: "基于有限元的多转子串联轴系扭转振动特性分析", 《湖南科技大学学报（自然科学版）》 * |
| 石薇薇: "虚拟动平衡法实现在线转子动平衡的研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106338363A (en) * | 2015-05-16 | 2017-01-18 | 江苏思维福特机械科技股份有限公司 | Dynamic balancing correction process |
| CN104899878A (en) * | 2015-05-21 | 2015-09-09 | 北京工业大学 | Method for detecting reasonable establishment of locomotive turbocharger rotor three-dimensional model |
| CN106323548A (en) * | 2016-08-08 | 2017-01-11 | 浙江大学 | Double vibration sensor-based rotor imbalance vibration response identification method |
| CN106484990A (en) * | 2016-09-30 | 2017-03-08 | 西安航天动力试验技术研究所 | A kind of engine test data three-dimensional Waterfall plot is rebuild, is shown and analysis method |
| CN106484990B (en) * | 2016-09-30 | 2019-08-30 | 西安航天动力试验技术研究所 | A kind of engine test data three-dimensional Waterfall plot rebuilds, display and analysis method |
| CN107702854B (en) * | 2017-07-10 | 2019-02-15 | 北京航天动力研究所 | A kind of high-speed balancing method for meeting rocket engine turbopump assembly and using |
| CN107702854A (en) * | 2017-07-10 | 2018-02-16 | 北京航天动力研究所 | A kind of high-speed balancing method for meeting rocket engine turbopump assembling and using |
| CN107939902B (en) * | 2017-11-15 | 2019-07-02 | 安徽博联自动化工程技术有限公司 | A kind of integrated damping test fixture of turbocharger dynamic balance testing machine |
| CN107939902A (en) * | 2017-11-15 | 2018-04-20 | 合肥动联自动化科技有限公司 | A kind of integrated damping test fixture of turbocharger dynamic balance testing machine |
| CN108161336A (en) * | 2018-01-25 | 2018-06-15 | 宁波丰沃涡轮增压系统有限公司 | A kind of assembly technology for reducing the initial computing ballance correction of core component |
| CN108827536A (en) * | 2018-03-27 | 2018-11-16 | 江苏大学 | Online dynamic balance detection system and detection method are assembled by a kind of combination revolution system |
| CN109580231A (en) * | 2018-12-12 | 2019-04-05 | 中国北方发动机研究所(天津) | A kind of pressure shell rotation failure test method of identification diesel engine matching turbocharger |
| CN109580231B (en) * | 2018-12-12 | 2020-11-06 | 中国北方发动机研究所(天津) | Test method for identifying rotating fault of pressure shell of diesel engine matched with turbocharger |
| CN110188514A (en) * | 2019-07-10 | 2019-08-30 | 湖南科技大学 | The rotor annular components floor error of division causes rotor unbalance value analytic approach |
| CN111473859A (en) * | 2020-05-21 | 2020-07-31 | 中国航发湖南动力机械研究所 | Method for making vibration limit value of whole machine |
| CN111751051A (en) * | 2020-06-24 | 2020-10-09 | 贵州永红航空机械有限责任公司 | Dynamic balancing method for double-disc flexible rotor of supercharged turbine |
| CN112668123A (en) * | 2020-12-31 | 2021-04-16 | 沈阳鼓风机集团股份有限公司 | Vibration characteristic analysis method, device and equipment of cantilever sensitive type single-shaft rotor |
| CN112668123B (en) * | 2020-12-31 | 2024-02-20 | 沈鼓集团股份有限公司 | Vibration characteristic analysis method, device and equipment for cantilever sensitive type single-shaft rotor |
| CN115795716A (en) * | 2022-11-15 | 2023-03-14 | 中国航发沈阳发动机研究所 | Method for determining requirement of unbalance amount of rotor |
| CN115795716B (en) * | 2022-11-15 | 2024-03-19 | 中国航发沈阳发动机研究所 | Method for determining rotor unbalance amount requirement |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104458128B (en) | 2017-03-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104458128A (en) | Turbocharger rotor unbalance amount control method based on dynamic characteristics | |
| Fu et al. | Imbalance–misalignment–rubbing coupling faults in hydraulic turbine vibration | |
| Ying et al. | Turbocharger rotor dynamics with foundation excitation | |
| Bonello | Transient modal analysis of the non-linear dynamics of a turbocharger on floating ring bearings | |
| Bin et al. | Investigation of induced unbalance magnitude on dynamic characteristics of high-speed turbocharger with floating ring bearings | |
| Lu et al. | Dynamic modeling and bifurcation analysis of blade-disk rotor system supported by rolling bearing | |
| Liu et al. | Nonlinear vibration response of a complex aeroengine under the rubbing fault | |
| Yang et al. | Dynamic analysis of flexible shaft and elastic disk rotor system based on the effect of Alford force | |
| Sun et al. | Influence of unbalanced electromagnetic force and air supply pressure fluctuation in air bearing spindles on machining surface topography | |
| Zhang et al. | Stability analysis of a turbocharger rotor system supported on floating ring bearings | |
| Lu et al. | Dynamic characteristics analysis of rotor-bearing system considering bearing clearance and hybrid eccentricity | |
| Yang et al. | Dynamic performance of a rotor system with an initial bow and coupling faults of imbalance-rub during whirling motion | |
| Shen et al. | Nonlinear analysis of a rub-impact rotor-bearing system with initial permanent rotor bow | |
| Yang et al. | A method for modeling and analyzing the rotor dynamics of a locomotive turbocharger | |
| Al-Khazali et al. | The experimental analysis of vibration monitoring in system rotor dynamic with validate results using simulation data | |
| Nan et al. | Nonlinear dynamic analysis of rotor-bearing system with cubic nonlinearity | |
| Hong et al. | Vibration Failure Analysis of Multi-Disk High-Speed Rotor Based on Rotary Inertia Load Model | |
| Shen et al. | Effect of parameters on the rubbing condition of an unbalanced rotor system with initial permanent deflection | |
| Lu et al. | Study on the vibration control method of a turboshaft engine rotor based on piezoelectric squeeze film damper oil film clearance | |
| Shuming et al. | Damping Optimization of High Pressure Rotor Support Based on Harmonic Response Analysis | |
| Deng et al. | Vibration improvement and dynamic balance automatic optimization of rotor compressor | |
| Xu et al. | Unbalance response analysis of the circumferential tie-rod combined rotor considering different support | |
| Teyi et al. | Study of active magnetic bearings (AMB) on non–synchronous rotors | |
| Jia et al. | Effect of the initial deflection on vibration characteristics of the rub-impact rotor system | |
| Sui et al. | Laser-based measurement for micro-unbalance of cylindrical rollers of the high-speed precision rolling bearings |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20210118 Address after: No. 433, xingciqi Road, Hangzhou Bay New District, Ningbo City, Zhejiang Province Patentee after: Ningbo Fengwo booster Technology Co.,Ltd. Address before: 411100 Taoyuan Road, Yuhu District, Xiangtan City, Hunan Province Patentee before: Hunan University of Science and Technology |
|
| TR01 | Transfer of patent right |