CN106499665A - A kind of impeller Optimization Design for avoiding targeting energy transmission phenomenon generation in bladed disk vibration - Google Patents
A kind of impeller Optimization Design for avoiding targeting energy transmission phenomenon generation in bladed disk vibration Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The invention discloses a kind of avoid the impeller Optimization Design that targeting energy transmission phenomenon occurs in bladed disk vibration, on the basis of traditional Static Strength Analysis and design, impeller dynamicss in off resonance and ideally are analyzed, identify its forbidden band and passband, then all radio-frequency components of the born exciting source of impeller are listed, determine whether that frequency content is fallen among forbidden band, when there is frequency content to fall among forbidden band, impeller mechanism need to be modified optimization, energy targeting transport phenomena occurs to avoid bladed disk vibration.The method manufacturing and designing with directive significance to centrifugal impeller of new generation, local in impeller running significantly vibration problem can be efficiently solved, reduce and vibrate its harm for causing, reduce the rate of breakdown in impeller running, so that it is guaranteed that centrifugal impeller unit safely and reliably longtime running.The impeller designed using the present invention can have significant improvement in safety, high efficiency.
Description
Technical field
The invention belongs to Analysis Vibration of Impeller Machinery and turbomachine design optimizing field, relate to how to being centrifuged leaf
The energy targeting transport phenomenon occurred in wheel vibration is analyzed, and how to be optimized design to centrifugal impeller, specifically relates to
And a kind of impeller Optimization Design for avoiding targeting energy transmission phenomenon generation in bladed disk vibration.
Background technology
Visual plant of the centrifugal compressor as industrial departments such as metallurgy, building materials, electric power, oil, chemical industry, environmental projects,
Application extremely extensively, all occupies very important status in national economy numerous areas.For a long time, large-scale, high speed centrifugation
The vibration problem of impeller affects the safe and reliable operation of blower fan always, in operation once going wrong, gently then interrupts production,
Cause economic loss；Heavy then cause equipment scrapping even casualties.In recent years, with the high speed development of national economy, unit
The continuous improvement of performance, centrifugal compressor develop towards directions such as maximization, high speed, high pressure ratios, this design to impeller and
The requirement of manufacture is with regard to more and more higher.
Industrial technology development it was verified that traditional Static Strength Design and Empirical Design much can not meet existing
For the needs of engineering development, it is impossible to ensure safety and the reliability of the operation of the rotary parts such as impeller.Due to centrifugal compressed
Machine develops to maximization direction, and impeller size constantly increases, and necessarily causes impeller overall structure reduced stiffness, certainly will exacerbate leaf
The vibration of wheel.Further, since the foozle during welding processing, often destroys this kind of cycle period symmetrical junction of impeller
The characteristic of structure and cause structure off resonance, produce impeller local significantly vibrate, cause some positions that there is larger dynamic stress, and then
Cause impeller that the accident of vibrating fatigue destruction occurs.
Content of the invention
It is an object of the invention to provide a kind of avoid the optimization design that targeting energy transmission phenomenon occurs in bladed disk vibration
Method, the method can provide rational basis to bladed disk vibration control, fault diagnosis and Optimal Structure Designing.
The present invention is to be achieved through the following technical solutions：
A kind of impeller Optimization Design for avoiding targeting energy transmission phenomenon generation in bladed disk vibration, including following step
Suddenly：
Step one：Static strength calculating and fail-safe analysis are carried out to impeller, its safety is checked；
Step 2：Model analyses are carried out respectively under preferable and off resonance situation to impeller, and extracts front some order mode states, arranged
Go out the natural frequency and its corresponding bending vibation mode picture of each order mode state；
Step 3：The natural frequency and its bending vibation mode picture of each order mode state obtained according to step 2, analyzes impeller and shakes
Mode corresponding to energy targeted delivery；
Wherein, in bending vibation mode picture vibration amplitude maximum " closing " in the regional area of very little, these vibration partial zones
Domain is relative " isolating ", then forbidden band of the corresponding frequency band of these mode for impeller, and other vibration deformations divide on whole impeller
Cloth then corresponds to the passband of impeller than the frequency band of more uniform mode；
Step 4：The frequency of exciting factor is compareed with the forbidden band of step 3 gained, is judged whether excited frequency falls
Enter in forbidden band, if the situation that the excited frequency for impeller occur is fallen in forbidden band, change blade wheel structure or change exciting source
Excited frequency, it is to avoid excited frequency is fallen among forbidden band, it is ensured that impeller safe operation.
In step one, when the only effect of consideration centrifugal force, centrifugal force is loaded in impeller static strength computation model, according to meter
Result is calculated, impeller maximum stress value and high-stress area is obtained；
Impeller intensity safety coefficient is considered when simultaneously, then will judge whether maximum stress value meets strength of materials requirement, be
No meet design requirement.
In step 2, the off resonance situation is referred to：For ideally, design with cycle period symmetrical structure
For impeller, as processing and manufacturing error component causes practical structures to there is scrambling to a certain degree, probabilistic lack
Sunken situation；
Wherein, defining impeller blade thickness mismatching angle is：
ε=(b-b0)/b0(1)
In formula, actual (real) thickness mm, b of the b for blade0Design thickness mm for blade；Meeting engineering manufacture mismachining tolerance
In the range of standard, ε≤± 5% is taken；θ≤± 1 ° is measured to blade angle degree off resonance to study；
Meanwhile, defining isolative interval P to weigh the how far of the driving frequency of exciting force and taboo frequency, its expression formula is：
P=(fi-f0)/f0(2)
In formula, fiProhibit frequent rate Hz, f for the i-th order mode state is corresponding0Driving frequency Hz for exciting force.
Added off resonance will produce up to 30% relative error, therefore, after off resonance is added, forbidden band to natural frequency
Isolative interval its expression formula should meet：
|fi-f0|/f0≤ 30% (3)
In formula, fiProhibit frequent rate Hz for the i-th order mode state is corresponding；f0Driving frequency Hz for exciting force.
Compared with prior art, the present invention has following beneficial technique effect：
The Optimization Design for avoiding targeting energy transmission phenomenon generation in bladed disk vibration disclosed by the invention, quiet in tradition
On the basis of intensity analysiss and design, impeller dynamicss in off resonance and ideally are analyzed, which is identified
Forbidden band and passband, then list all radio-frequency components of the born exciting source of impeller, determine whether that frequency content falls into forbidden band
Among, during for there is frequency content to fall among forbidden band, optimization that impeller mechanism need to be modified, to avoid bladed disk vibration
Generation energy targeting transport phenomena.The method manufacturing and designing with directive significance to centrifugal impeller of new generation, can be effectively
The local significantly vibration problem in impeller running is solved, vibration its harm for causing is reduced, is reduced in impeller running
Rate of breakdown, so that it is guaranteed that centrifugal impeller unit safely and reliably longtime running.The impeller designed using the present invention
Can have significant improvement in safety, high efficiency.Therefore, the present invention can make the centrifugal impeller that the method is designed exist
More competitive superiority on market.The industry related to centrifugal impeller machinery is manufactured and application by the application of the present invention, such as
Metallurgy, building materials, electric power, oil, chemical industry, environmental project etc. produce significant impact, improve the production efficiency of association area, reduce life
Cost is produced, national economy is produced and is greatly promoted effect.
Description of the drawings
Fig. 1 is vibration targeting energy transmission schematic diagram；
Fig. 2 a are the bending vibation mode picture under leaf-disc system passband；
Fig. 2 b are that leaf-disc system prohibits the bending vibation mode picture under frequency；
Fig. 3 is impeller FEM (finite element) model mesh generation result figure；
Fig. 4 a are impeller stress scattergram；
Fig. 4 b are impeller Displacements Distribution figure；
Fig. 5 a are the 17th first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 b are the 17th first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 5 c are the 18th first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 d are the 18th first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 5 e are the 19th first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 f are the 19th first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 5 g are the 21st first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 h are the 21st first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 5 i are the 22nd first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 j are the 22nd first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 5 k are the 23rd first order mode figure (wheel cap side) of 2 impeller of example；
Fig. 5 l are the 23rd first order mode figure (wheel disc side) of 2 impeller of example；
Fig. 6 a are the 17th first order mode figure (wheel cap side) under II class off resonance of impeller；
Fig. 6 b are the 17th first order mode figure (wheel disc side) under II class off resonance of impeller；
Fig. 6 c are the 21st first order mode figure (wheel cap side) under II class off resonance of impeller；
Fig. 6 d are the 21st first order mode figure (wheel disc side) under II class off resonance of impeller.
Specific embodiment
With reference to specific embodiment, the present invention is described in further detail, described be explanation of the invention and
It is not to limit.
Correlation theory according to the present invention：
1st, targeted energy transmission
In Structural Dynamicses, the targeted delivery problem of energy mainly reflects both ways：One is unipolarity；Two is target
Property.During unipolarity is mainly shown as that energy is transferred to subsystem by main system, due to there is damping, then energy exchange
Balance is broken, and energy transfers to be transferred in subsystem by main system in the way of unidirectional.And targeted is then embodied in vibration mould
In the localization of state, mode localization turns to two kinds of physical phenomenons comprising Mode Shape localization and model frequency.
The localization of the vibration shape refer to the Mode Shape of system be not " extension " to total, but concentrate on less son
In structure, the at this moment amplitude very little of most minor structures, and the amplitude of the minority minor structure for " having been localized " substantially exceeds
The corresponding value of " extension " mode, so as to by Mode Shape " localization " in a small amount of minor structure.And vibrate the local of transmission
Change and then refer to that the excitation in the system of acting on is limited in regional area, make energy be not easy to be delivered to other positions.Therefore, defeated
The energy for entering system can not be propagated far, and be simply limited in the region for being close to vibration source, produce local oscillation.
For bladed discs, above-mentioned significantly being vibrated by local caused by targeted energy transmission often shows as one
Individual or several vane sectors produce larger vibration, and remaining sector then occurs without substantially vibration, so as to cause minority blade vibration
Excessive and have higher dynamic stress, cause then to rupture.
2nd, Vibration Localization mechanism
Transmission using ripple is illustrating the mechanism of Vibration Localization, it is assumed that the Children abused of given blade can regard as with
The superposition of the ripple that friction speed is circumferentially transmitted in blade-wheeling disk structure system, if system is linear, only can be analyzed completely
The propagation of unicast produces the mechanism for localizing to discuss.As shown in figure 1, setting certain vibration wave by wheel disc from a blade to another
The propagation of blade is modeled as by when " multilayer dielectricity ", by one layer to another layer of propagation, velocity of wave c wherein in media as well is corresponding
In physical characteristics H (ω) (transmission function) of blade, this is because, due to the transmission of the vibration wave along disk true by frequencies omega
Fixed, its impact to ripple preferably can be defined by corresponding transfer function H (ω), therefore have corresponding relation H (ω)
→c.
If system is harmony, all blade (corresponding to all layers) are identicals, and the propagation of vibration wave is just by layer
Between interface impact；If system is off resonance, blade (corresponding to layer) is inconsistent, then vibration wave just portion on interface
Divide and be passed, partly reflected.For reflecting component therein, its amplitude typically with formed interface two-layer property (namely
The frequency response function of two blades) inconsistent and increase, if it be on high reflection interface (namely be equivalent to frequency response function difference
Two larger adjacent blades), then may the vibration wave can be suppressed in several layers (blade), it is clear that repressed shake with this
Dynamic ripple is that the vibratory response amplitude of some blades is very big accordingly, and this is the mechanism of Vibration Localization.
3rd, frequency passband, forbidden band
There is mode localization during in targeted energy transmission and must be fulfilled for two conditions：One to be that system must have weak
Coupling or highly dense mode；Two is there must be some off resonances in system.Under these conditions, geometry, mechanics and inertial properties
Small variations can all cause the significant changes of system vibration performance, i.e. system is extremely sensitive to off resonance.On the other hand, cycle knot
Structure has many mechanical characteristics for being different from aperiodic structure, and one of them important mechanical characteristic is exactly that periodic structure has frequency
Rate passband and forbidden band phenomenon.Show as, when vibration frequency is in pass band areas, unrestrictedly to spread all over total, its width
Value and energy will not decay (damping that disregards in structure)；When vibration frequency is in forbidden band section, which will not spread all over entirely
Structure, i.e. amplitude and energy production decay.And the angle from Structural Dynamicses, this vibration frequency is in frequency forbidden band institute
The energy of embodiment can not spread all over the phenomenon of total and just be consistent with the Localization Phenomenon of the vibration shape.From the point of view of Mode Shape, table
It is not now the vibration shape of " extension " for the vibration shape, but the vibration shape of " localization ", the frequency corresponding to the vibration shape of those " localization " is i.e.
For prohibiting frequency, frequency forbidden band is exactly all set for prohibiting frequency composition；Frequency corresponding to the vibration shape of those " extension " is passband, frequently
Rate passband is the set of all passband compositions.The passband of typical leaf-dish structure system, taboo frequency vibration type such as Fig. 2 a and Fig. 2 b institutes
Show.
4th, mismatching angle and isolative interval
For the impeller with cycle period symmetrical structure for ideally designing, due to processing and manufacturing error etc.
Factor causes practical structures to be referred to as off resonance with scrambling to a certain degree, probabilistic defect.Thick in order to study blade
The impact of frequency band is led to, is prohibited in degree off resonance, the off resonance of blade angle degree to large centrifugal impeller.Now mismatching angle is defined.
Vane thickness mismatching angle：
ε=(b-b0)/b0(1)
In formula：The actual (real) thickness mm of b blades
b0The design thickness mm of blade
Meeting in the range of engineering manufacture mismachining tolerance standard, taking ε≤± 5%；θ is measured to blade angle degree off resonance
≤ ± 1 ° is studied.
Define isolative interval P simultaneously to weigh the how far of the driving frequency of exciting force and taboo frequency, its expression formula is：
P=(fi-f0)/f0(2)
In formula：fiI-th order mode state is corresponding to prohibit frequent rate Hz
f0Driving frequency Hz of exciting force
5th, forbidden band isolation criterion
According to analysis above, added off resonance (nominal error scope 10%) will produce up to 30% to natural frequency
Relative error, therefore, after off resonance is added, isolative interval its expression formula of forbidden band should meet：
|fi-f0|/f0≤ 30% (3)
In formula：fiI-th order mode state is corresponding to prohibit frequent rate Hz；
f0Driving frequency Hz of exciting force.
The method of targeting energy transmission in the analysis centrifugal bladed disk vibration of disclosure of the invention, and avoid impeller local big
The method for designing of width vibration, comprises the following steps that：
The first step；The static characteristic of analysis impeller, differentiates whether which meets requirement.
Second step；The resonable dynamicss that thinks of in the case of off resonance of analysis impeller, identify forbidden band therein, passband.
3rd step；According to the exciting source born by impeller, the radio-frequency component of all exciting factors is listed.
4th step；Whether analysis impeller has excited frequency to fall in forbidden band.
5th step；When impeller has excited frequency to fall in forbidden band, set structure need to be changed, it is to avoid local occurs
Significantly vibrate.
In conjunction with Figure of description include following be embodied as case, technical scheme is described further.
The present embodiment with Centrufugal compressor impeller as object of study, by COSMOS finite element analysis softwares to practical engineering application in
The impeller of compressor bank, is analyzed from the mode in the case of different off resonances to ideal respectively.
The inventive method is mainly included the following steps that：
The first step, carries out static strength calculating to impeller, carries out Analysis of Static Strength Reliability, checks its safety.In calculating
Only consider the effect of centrifugal force, according to impeller static strength result of calculation, impeller maximum stress σ=5.36 × 108Pa, high-stress area
Enter at mouth circle for wheel cap, impeller intensity safety coefficient is 1.59.Enclosing cover for impeller and enter poor rigidity at mouth circle, deform larger.Consideration
Impeller intensity safety coefficient, maximum stress are far below Materials Yield Limit σs, meet design requirement.
Second step, for impeller, under ideal state and off resonance situation carries out model analyses respectively, is extracted front 25 order mode
State, according to forbidden band and passband that bending vibation mode picture determines impeller.During ideal state, the 14th, 15,17 ranks, the 19th～24 rank corresponding solid
There is frequency to constitute near the frequency forbidden band of impeller, i.e. 1478.1～1679.7Hz, 1805.3Hz and 1823.4～2329.1Hz
Constitute the frequency forbidden band of the impeller.
3rd step, for impeller, due to there is inlet vane return channel, the exciting source for being born includes：Circumfluence device
Exciting force caused by blade at caused exciting force, impeller outlet.The frequency of the two exciting factors be respectively 1862Hz and
1764Hz.
4th step, the frequency of the exciting source of the 3rd step gained is compareed with the forbidden band determined in second step, judges to swash
Whether vibration frequency is fallen in forbidden band.Impeller in for specific embodiment, in an ideal case, is caused by entrance return channel
Excitation force frequencyFrequency forbidden band is not fallen within.It is computed, isolative interval is 0.73%.Leaf at impeller outlet
The frequency of exciting force caused by pieceFall into frequency forbidden band.In off resonance situation, frequency forbidden band value and return channel
Caused by prerotator blade, excitation force frequency value 1764Hz is closely.From the point of view of the vibration shape, cause in return channel prerotator blade
Excitation force frequency value be that Mode Shape near 1764Hz produces the position that significantly vibrates of local and is at impeller inlet mouth circle,
And this position also worst position of rigidity in exactly whole impeller.
5th step, in the case of off resonance, due to the impact of air-flow, circumfluence device produces the excitation of bladed disk vibration by becoming
Source, makes impeller local large-amplitude vibration can occur and then cause fatigue rupture.Cause for avoiding impeller that targeted energy transmission occurs
Local vibration, the circumfluence device number of blade is adjusted to Z=14, the frequency of exciting force caused by circumfluence device is changed,
Efficiently avoid destruction of the local large-amplitude vibration to impeller.
The frequency passband of 1 preferable impeller of embodiment and forbidden band
Certain centrifugal impeller
Phenomenon of the failure：Enclosing cover for impeller enters
Method for removing：The circumfluence device number of blade is adjusted to Z=14
Impeller key dimension and technical parameter：Diameter D=Φ 1020mm, number of blade Z=19, vane thickness δ=8mm, work
Make rotating speed n=5545r/min, material：Steel alloy.
Compressor bank relevant parameter：Total series：3 grades, series residing for impeller：3rd level, inlet vane return channel number of blade Z1
=18.
Driving source：The frequency of exciting force caused by circumfluence deviceExciting caused by blade at impeller outlet
The frequency of power
Impeller FEM (finite element) model：Adopt 10 node tetrahedral solid elements discrete in whole impeller, totally 19183 nodes,
15178 units, its FEM meshing are shown in Fig. 3.
First, fail-safe analysis is carried out to impeller static strength, checks its safety.The work of centrifugal force is only considered in calculating
With result of calculation is as shown in figures 4 a and 4b.According to impeller static strength result of calculation, impeller maximum stress σ3=5.18 ×
108Pa, high-stress area enter at mouth circle for wheel cap, and impeller intensity safety coefficient is 1.64, meets design requirement.Can from figure
Go out, enclosing cover for impeller and to enter at mouth circle rigidity weaker deforms larger.
Model analyses are carried out to impeller, front 25 order mode state is extracted, impeller in the 17th～19,21～23 first order mode figures,
Vibration amplitude maximum " closing " is occurred in that in the regional area of very little, and these vibration areas are relative " isolating ", i.e.,
Occur in that mode localization phenomenon.So the 17th～19 rank, the corresponding natural frequency of the 21st～23 rank：I.e. 1675.6～
1833.7Hz and 1974.5～2031.8Hz constitute the frequency forbidden band of the impeller.17th～19 rank, the 21st～23 first order mode figure
As shown in Fig. 5 a～Fig. 5 l.From bending vibation mode picture as can be seen that the position of taboo frequency 1675.6Hz generation localization is at mouth circle.By frequency
Value compares, by excitation force frequency caused by the return channel of entranceFrequency forbidden band is not fallen within.It is computed, isolates
Nargin is only 0.73%.And at impeller outlet caused by blade exciting force frequencyFall into frequency forbidden band.
The impact that 2 off resonance of embodiment is transmitted to targeted energy
Analysis impeller is in the different off resonance forms such as vane thickness change and blade angle change, different mismatching angles to targeting
The impact of the impeller mode localization occurred in energy transfer process.
Impeller mode is very sensitive to some off resonances, although model frequency value changes are little, but the vibration shape there occurs very big change
Change.In the case where off resonance is caused, excitation force frequency value 1663.5Hz caused by frequency forbidden band value and return channel prerotator blade
Closely.The minor variations that off resonance is caused to blade wheel structure, result in the very big difference with preferable impeller frequency forbidden band, performance
Become frequency forbidden band in the case of off resonance for some frequencies for falling in frequency passband in the ideal case.From the point of view of the vibration shape,
Caused by return channel prerotator blade, excitation force frequency value is the portion of the Mode Shape generation mode localization near 1663.5Hz
Position is at impeller inlet mouth circle, and this position also worst position of rigidity in exactly whole impeller.
Above-mentioned analysis is based on, in the case of off resonance, due to the impact of air-flow, circumfluence device will become generation bladed disk vibration
Driving source, make impeller can occur localization vibration so that cause fatigue rupture.Therefore, it is to avoid impeller occurs localization vibration,
Must take into the interference of circumfluence device.In the case of impeller off resonance II, the 17th, 21 first order mode figures are as shown in Fig. 6 a～Fig. 6 d.
Claims (4)
1. a kind of impeller Optimization Design for avoiding targeting energy transmission phenomenon in bladed disk vibration from occurring, it is characterised in that bag
Include following steps：
Step one：Static strength calculating and fail-safe analysis are carried out to impeller, its safety is checked；
Step 2：Model analyses are carried out respectively under preferable and off resonance situation to impeller, and extracts front some order mode states, listed each
The natural frequency of order mode state and its corresponding bending vibation mode picture；
Step 3：The natural frequency and its bending vibation mode picture of each order mode state obtained according to step 2, analyzes impeller and vibrational energy occurs
Mode corresponding to amount targeted delivery；
Wherein, in bending vibation mode picture vibration amplitude maximum " closing " in the regional area of very little, these vibration regional area phases
To " isolating ", then the corresponding frequency band of these mode is the forbidden band of impeller, and other vibration deformations are distributed ratio on whole impeller
The frequency band of more uniform mode then corresponds to the passband of impeller；
Step 4：The frequency of exciting factor is compareed with the forbidden band of step 3 gained, is judged whether excited frequency falls into taboo
In band, if the situation that the excited frequency for impeller occur is fallen in forbidden band, change blade wheel structure or change the exciting of exciting source
Frequency, it is to avoid excited frequency is fallen among forbidden band, it is ensured that impeller safe operation.
2. the impeller optimization design side for avoiding targeting energy transmission phenomenon in bladed disk vibration from occurring according to claim 1
Method, it is characterised in that in step one, when the only effect of consideration centrifugal force, loads centrifugal force in impeller static strength computation model,
According to result of calculation, impeller maximum stress value and high-stress area is obtained；
Impeller intensity safety coefficient is considered when simultaneously, then will judge whether maximum stress value meets strength of materials requirement, if full
Sufficient design requirement.
3. the impeller optimization design side for avoiding targeting energy transmission phenomenon in bladed disk vibration from occurring according to claim 1
Method, it is characterised in that in step 2, the off resonance situation are referred to：For ideally, design symmetrical with cycle period
For the impeller of structure, as processing and manufacturing error component causes practical structures with scrambling to a certain degree, does not know
The situation of the defect of property；
Wherein, defining impeller blade thickness mismatching angle is：
ε=(b-b0)/b0(1)
In formula, actual (real) thickness mm, b of the b for blade0Design thickness mm for blade；Meeting engineering manufacture mismachining tolerance standard
In the range of, take ε≤± 5%；θ≤± 1 ° is measured to blade angle degree off resonance to study；
Meanwhile, defining isolative interval P to weigh the how far of the driving frequency of exciting force and taboo frequency, its expression formula is：
P=(fi-f0)/f0(2)
In formula, fiProhibit frequent rate Hz, f for the i-th order mode state is corresponding0Driving frequency Hz for exciting force.
4. the impeller optimization design side for avoiding targeting energy transmission phenomenon in bladed disk vibration from occurring according to claim 3
Method, it is characterised in that added off resonance will produce up to 30% relative error to natural frequency, therefore, after off resonance is added,
The isolative interval of forbidden band its expression formula should meet：
|fi-f0|/f0≤ 30% (3)
In formula, fiProhibit frequent rate Hz for the i-th order mode state is corresponding；f0Driving frequency Hz for exciting force.
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| CN110298117A (en) * | 2019-07-02 | 2019-10-01 | 中国船舶重工集团公司第七0三研究所 | A kind of gas turbine blower blade frequency modulation design method |
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| WO2005054681A1 (en) * | 2003-12-03 | 2005-06-16 | Mitsubishi Heavy Industries, Ltd. | Impeller for compressor |
| US20100278632A1 (en) * | 2009-05-04 | 2010-11-04 | Hamilton Sundstrand Corporation | Radial compressor of asymmetric cyclic sector with coupled blades tuned at anti-nodes |
| CN102374190A (en) * | 2011-11-08 | 2012-03-14 | 西安交通大学 | Centrifugal impeller optimal design method for preventing vibration localization for happening |
| CN105352586A (en) * | 2015-11-20 | 2016-02-24 | 天津大学 | Method used for realizing blade fatigue crack detection through resonance frequency detection |
| CN105447272A (en) * | 2015-12-17 | 2016-03-30 | 北京航空航天大学 | Design method of vibration reliability of turbine leaf disc structure |
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| CN110298117A (en) * | 2019-07-02 | 2019-10-01 | 中国船舶重工集团公司第七0三研究所 | A kind of gas turbine blower blade frequency modulation design method |
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