CN106353035A - Online dynamic balance correction method of large-size draught fan impeller - Google Patents
Online dynamic balance correction method of large-size draught fan impeller Download PDFInfo
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- CN106353035A CN106353035A CN201610929761.4A CN201610929761A CN106353035A CN 106353035 A CN106353035 A CN 106353035A CN 201610929761 A CN201610929761 A CN 201610929761A CN 106353035 A CN106353035 A CN 106353035A
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- impeller
- fan impeller
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- counterweight
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/30—Compensating unbalance
- G01M1/32—Compensating unbalance by adding material to the body to be tested, e.g. by correcting-weights
Abstract
The invention discloses an online dynamic balance correction method of a large-size draught fan impeller, belonging to the field of equipment overhauling, and aiming at reducing impeller assembling and disassembling procedures and shortening an overhauling period. The online dynamic balance correction method comprises the following steps: A, connecting one end of a vibration detection balancing apparatus with a driving end of the draught fan impeller on line and connecting the other end of the vibration detection balancing apparatus with a driven end of the draught fan impeller; marking a vibration starting phase point on a wheel disc of the impeller; B, starting the vibration detection balancing apparatus and detecting an original vibration amplitude and an original phase of a bearing bush at the driving end of the draught fan impeller; C, calculating balance counter weight needing to be added and a phase of the added balance counter weight; and D, adding the balance counter weight to the back surface of the impeller. According to the online dynamic balance correction method of the large-size draught fan impeller, after the balance counter weight and the mounting position of the balance counter weight are measured in a large-size draught fan installation site by utilizing the vibration detection balancing apparatus, the balance counter weight is mounted on the impeller and the draught fan impeller does not need to be assembled and disassembled, so that the impeller assembling and disassembling procedures are reduced and the overhauling period is shortened.
Description
Technical field
The invention belongs to overhaul of the equipments field, a kind of particularly large fan impeller on-line dynamic balancing bearing calibration.
Background technology
Large fan, the ratio referring to impeller length with impeller diameter is less than 1.5, and rotation speed of fan is less than the double of 7500r/min
Fulcrum centrifugal fan.Large fan is one of important production equipments of industry such as mining, metallurgical, generating, its normal operation
Whether direct relation uses the trouble-free operation of the system of large fan, and blower fan generally uses in the higher environment of dust-laden, blower fan
Working system is annual 345 days, daily 24 continuous throughout the twenty-four hour24s, and such long-play, causes draught fan impeller to occur splitting
Stricture of vagina and abrasion, once crackle or abrasion in draught fan impeller, need impeller is repaired, and need impeller is carried out after reparation
Dynamic balance calibration.It was all to entrust the unit having blower fan dynamic balancing machine to enter that large fan impeller repairs laggard action balance correction in the past
Row, need to remove impeller, impeller is installed to the correction of blower fan dynamic balancing machine enterprising action balance, and when dismounting impeller waste
Between, impact is normal to be produced.
Content of the invention
The technical problem to be solved is to provide a kind of large fan impeller on-line dynamic balancing bearing calibration, is used for
Save dismounting impeller operation, shorten maintenance duration, win the production time for normal production.
The technical solution used in the present invention is: a kind of large fan impeller on-line dynamic balancing bearing calibration, enters including order
The following steps of row:
A, online vibration detection equilibristat one end is connected with the drive end of draught fan impeller, the quilt of the other end and draught fan impeller
Moved end is connected；And mark on the wheel disc of impeller, it is labeled as vibrating start-up phase site with this；
B, Vibration on Start-up detection equilibristat, measure the original vibration amplitude of bearing shell and vertical direction at draught fan impeller drive end
Original phase, original vibration amplitude is designated as a1, unit be μm；Original phase is designated as ψ1, unit is degree；Measure draught fan impeller quilt
The original vibration amplitude of bearing shell and the original phase of vertical direction at moved end, original vibration amplitude is designated as a2；Original phase is designated as
ψ2；Find out maximum original vibration amplitude, be designated as a0；
C, pass through q=0.0096 × w × (a0/ r) × (n/4000) × 2 calculate the quality that need to add counterweight；Wherein,
Q represents and need to add counterweight；W represents rotor quality, unit be gram；N represents the rotating speed of rotor, unit be rev/min；R represents
To the vertical dimension of rotor axis, unit is millimeter to weight installing position；a0For maximum original vibration amplitude；
By α=ψSurvey+ 180 ° of+ψ calculate the actual phase of weightless point, wherein, ψSurveyBy survey vertical direction original phase
Position, ψSurvey=(ψ1+ψ2)/2；ψ is oscillation hysteresis angle；
D, counterweight is added to impeller vacuum side of blade weight installing position；
E, it is again started up vibration detection equilibristat, detection large fan impeller increases the counterbalance effect after counterweight, if
It is unsatisfactory for requirement for dynamic balance, then repeat step c and d are until meeting requirement for dynamic balance.
Further, step c is completed by vibration detection equilibristat.
Further, described q is positive integer.
Further, in step d, described counterweight evenly distributes the back of the body in blade along the axis direction parallel to impeller
Face.
The invention has the beneficial effects as follows: a kind of this large fan impeller on-line dynamic balancing bearing calibration, in large fan leaf
After the online reparation of wheel or need to make flat required for dynamically balanced draught fan impeller is measured using vibration detection equilibristat at the scene online
After the installation site of weighing apparatus counterweight and counterweight, then counterweight is installed on impeller, draught fan impeller need not be dismounted, section
About dismounting impeller operation, thus shorten the dynamic balance calibration time.By a kind of this large fan impeller on-line dynamic balancing school
Correction method is carried out during dynamic balance calibration it is only necessary to add once balance counterweight, so that the vibration standard of large fan impeller is reached
Outstanding probability up to more than 99%, dynamic balance calibration efficiency high.
Brief description
Fig. 1 is vibration detection equilibristat and online impeller location schematic diagram.
Fig. 2 is the a-a sectional view of Fig. 1.
In figure, vibration detection equilibristat 1, impeller 2, drive end 21, Partner 22, wheel disc 23, labelling 24, blade 25, flat
Weighing apparatus counterweight 3.
Specific embodiment
It is as follows that the present invention is described further with reference to the accompanying drawings and examples:
A kind of large fan impeller on-line dynamic balancing bearing calibration, comprises the following steps:
A, vibration detection equilibristat 1 one end is connected with the drive end top brass 21 of draught fan impeller 2, the other end and blower fan
The Partner top brass 22 of impeller 2 is connected；And mark 24 on the wheel disc 23 of impeller 2, initial for vibration with this labelling 24
Phase point；
B, Vibration on Start-up detection equilibristat 1, measure at draught fan impeller 2 drive end 21 the original vibration amplitude of bearing shell and vertical
The original phase in direction, original vibration amplitude is designated as a1, unit be μm；Original phase is designated as ψ1, unit is degree；Measure blower fan leaf
Take turns the original vibration amplitude of bearing shell and the original phase of vertical direction at 2 Partner 22, original vibration amplitude is designated as a2；Original phase
Position is designated as ψ2；Find out maximum original vibration amplitude, be designated as a0；
C, pass through q=0.0096 × w × (a0/ r) × (n/4000) × 2 calculate the quality that need to add counterweight 3；Its
In, q represents and need to add counterweight 3；W represents rotor quality, unit be gram；N represents the rotating speed of rotor, unit be rev/min；r
Represent weight installing position to the vertical dimension of rotor axis, unit is millimeter；a0For maximum original vibration amplitude；
By α=ψSurvey+ 180 ° of+ψ calculate the actual phase of weightless point, wherein, ψSurveyBy survey vertical direction original phase
Position, ψSurvey=(ψ1+ψ2)/2；ψ is oscillation hysteresis angle；
D, counterweight 3 is added to impeller 2 blade 25 the back side；
E, it is again started up vibration detection equilibristat 1, detection large fan impeller increases the counterbalance effect after counterweight 3,
If being unsatisfactory for requirement for dynamic balance, repeat step c and d are until meeting requirement for dynamic balance.
Large fan, the ratio referring to impeller length with impeller diameter is less than 1.5, and rotation speed of fan is less than the double of 7500r/min
Fulcrum centrifugal fan.A kind of this large fan impeller on-line dynamic balancing bearing calibration, in large fan erecting bed using shaking
Dynamic detection equilibristat 1 is measured vibration amplitude and is calculated the peace of required counterweight 3 and counterweight 3 according to vibration amplitude
After holding position, then counterweight 3 is installed on impeller 2, draught fan impeller 2 need not be dismounted, saved impeller 2 dismounting work
Sequence, thus shorten the dynamic balance calibration time.Action is entered by a kind of this large fan impeller on-line dynamic balancing bearing calibration flat
Weighing apparatus timing, it is only necessary to add once balance counterweight 3, just enables the vibration standard of large fan impeller reach outstanding probability and is up to
More than 99.9%, dynamic balance calibration efficiency high.
In above-mentioned embodiment, step c can manually calculate, but, in order to save labour force it is preferred that step c is passed through
Vibration detection equilibristat 1 completes.Not only save labour force, also improve computational efficiency.
Preferably, described q is positive integer.
Preferably, in step d, described counterweight 3 evenly distributes in blade 25 along the axis direction parallel to impeller 2
The back side.Described counterweight 3 evenly distributes in the back side of blade 25 along the axis direction parallel to impeller 2, refers to join balance
Weigh 3 and be divided into n part counterweight element, n part counterweight element is located on the same line, and this straight line parallel is in the axis of impeller 2,
Blade 25 is divided into n+1 section by n part counterweight element.So counterweight 3 is allocated on blade 25, improves the steady of blade 25
Qualitative.
Embodiment 1:
Certain iron-smelter successively takes said method for three times to be carried out to the dry quenching system air circulation fan impeller after repairing
Live on-line dynamic balancing correction.Blower fan model: 25151z/1024, rotation speed of fan n=1500r/min, blower fan quality w=
7800kg.
For the first time:
First, record the former of bearing shell at draught fan impeller drive end 21 and Partner 22 with vibration detection equilibristat 1 at the scene
Beginning vibration amplitude and phase place, are shown in Table one:
The original vibration amplitude of table one blower fan bearing shell and phase place
In table one: ⊥ represents vertical direction, represent horizontal direction, ⊙ represents along impeller axially.
As can be seen from Table I: the vertical vibration phase place of drive end bearing shell and Partner bearing shell is essentially identical but vibrates width
Value difference is different big.It is typical unbalance dynamic, need to carry out vibration balancing.
For dry quenching system air circulation fan impeller, its rotor quality w=7800kg；Radius r=1200mm；Rotating speed n=
1500r/min；Above-mentioned parameter is brought into q=0.0096 × w × (a0/ r) in × (n/4000) × 2, draw q=46.8a0(g),
Round numbers is 47a0(g), that is, blower fan often vibrate 1,47g counterweight 3 should be added.
Knowable to table one: measured original vibration amplitude is 16,66,4,7,33,16, blower fan peak swing value a0=66
μm, 1mm=100 silk, therefore, a0=6.6, then, should add counterweight 3 is 6.6 × 47g=310.2g, and round numbers is 310g.
Oscillation hysteresis angle ψ=40 ° of dry quenching circulating fan, then the counterpoise position adding needed for blower fan dynamic balancing is:
α ⊥=(330 °+320 °)/2+180 °+40 °=545 ° i.e. 185 °
According to above-mentioned result of calculation, determining that blowing machine answers the size and location of add weight is 185 ° of 310g ∠；
Plus after counterweight, start blower fan second, draught fan impeller drive end, Partner vibration amplitude and phase place are shown in Table
Two:
Table two impeller adds counterweight rear fan bearing shell vibration amplitude and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 7∠340° | 15 | 6 |
| Partner bearing shell (a2∠ψ2) | 4∠330° | 11 | 5 |
According to fan vibration standard, 3 is excellent, and 6 is good, 9 be can, as shown in Table 2, plus after counterweight 3,
Big vibration values are 1.5, and surveyed vibration data is outstanding therefore plus after counterweight 3.
Second:
The original vibration amplitude of bearing shell and phase place at draught fan impeller drive end 21 and Partner 22, are shown in Table three:
The original vibration amplitude of table three blower fan bearing shell and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 20∠340° | 50 | 10 |
| Partner bearing shell (a2∠ψ2) | 15∠315° | 33 | 14 |
Knowable to table three, blower fan peak swing value a0=50 μm, 1mm=100 silk, therefore, a0=5, then, balance should be added
Counterweight 3 is 5 × 47g=235g.
Oscillation hysteresis angle ψ=40 ° of dry quenching circulating fan, then the counterpoise position adding needed for blower fan dynamic balancing is:
α ⊥=(340 °+315 °)/2+180 °+40 °=547.5 ° i.e. 187.5 °
According to above-mentioned result of calculation, determining that blowing machine answers the size and location of add weight is 187.5 ° of 235g ∠；
After counterweight is added, it is again started up blower fan, draught fan impeller drive end, Partner vibration amplitude and phase place are shown in Table
Four:
Table four impeller adds counterweight rear fan bearing shell vibration amplitude and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 12∠340° | 20 | 10 |
| Partner bearing shell (a2∠ψ2) | 11∠330° | 18 | 9 |
According to fan vibration standard, 3 is excellent, and 6 is good, 9 be can, as shown in Table 2, plus after counterweight 3,
Big vibration values are 2, and surveyed vibration data is outstanding therefore plus after counterweight 3.
For the third time: record the original vibration amplitude of bearing shell and phase place at draught fan impeller drive end 21 and Partner 22, be shown in Table
Five
The original vibration amplitude of table five fan shaft watt and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 24∠340° | 67 | 10 |
| Partner bearing shell (a2∠ψ2) | 19∠330° | 40 | 14 |
Knowable to table five, blower fan peak swing value a0=67 μm, 1mm=100 silk, therefore, a0=6, then, balance should be added
Counterweight 3 is 6.7 × 47g=314.9g, and round numbers is 315g.
Oscillation hysteresis angle ψ=40 ° of dry quenching circulating fan, then the counterpoise position adding needed for blower fan dynamic balancing is:
α ⊥=(340 °+330 °)/2+180 °+40 °=555 ° i.e. 195 °
According to above-mentioned result of calculation, determining that blowing machine answers the size and location of add weight is 195 ° of 315g ∠；
After counterweight is added, it is again started up blower fan, draught fan impeller drive end, Partner vibration amplitude and phase place are shown in Table
Six:
Table six impeller adds counterweight rear fan bearing shell vibration amplitude and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 8∠340° | 13 | 6 |
| Partner bearing shell (a2∠ψ2) | 6∠330° | 12 | 5 |
According to fan vibration standard, 3 is excellent, and 6 is good, 9 be can, as shown in Table 6, plus after counterweight 3,
Big vibration values are 1.3, and surveyed vibration data is outstanding therefore plus after counterweight 3.
Embodiment 2: certain iron-smelter takes said method and carried out scene to the impeller of the burnt dedusting fan of the sieve after repairing
On-line dynamic balancing corrects.This sieve Jiao dedusting fan model: cgr218-73dif, pumped (conveying) medium is coke dust and flue gas；Blower fan
Rotating speed n=1600r/min, rotor quality w=8100kg；Radius r=1250mm.
First, record the original of bearing shell at draught fan impeller drive end 21 and Partner 22 with vibration measuring dynamic balance instrument 1 at the scene
Vibration amplitude and phase place, are shown in Table seven:
The original vibration amplitude of table seven blower fan bearing shell and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 17∠330° | 67 | 5 |
| Partner bearing shell (a2∠ψ2) | 9∠320° | 35 | 18 |
Burnt dedusting fan impeller, its rotor quality w=8100kg are sieved for c system；Radius r=1250mm；Rotating speed n=
1600r/min；Above-mentioned parameter is brought into q=0.0096 × w × (a0/ r) in × (n/4000) × 2, draw q=49.725a0
G (), round numbers is 50a0(g), that is, blower fan often vibrate 1,50a should be added0(g) counterweight 3.
Knowable to table seven: measured original vibration amplitude is 17,67,5,9,35,18, blower fan peak swing value a0=67
μm, 1mm=100 silk, therefore, a0=6.7, then, should add counterweight 3 is 6.7 × 50g=335g.
Oscillation hysteresis angle ψ=42 ° of the burnt dedusting fan of c system sieve, then the counterpoise position adding needed for blower fan dynamic balancing is:
α ⊥=(330 °+320 °)/2+180 °+42 °=547 ° i.e. 187 °
According to above-mentioned result of calculation, determining that blowing machine answers the size and location of add weight is 187 ° of 335g ∠；
Plus after counterweight, it is again started up blower fan, record draught fan impeller drive end, Partner vibration amplitude and phase place and be shown in Table
Eight.
Table eight impeller adds counterweight rear fan bearing shell vibration amplitude and phase place
| Measure direction | ⊥ | — | ⊙ |
| Drive end bearing shell (a1∠ψ1) | 8∠340° | 16 | 5 |
| Partner bearing shell (a2∠ψ2) | 4∠330° | 12 | 4 |
According to fan vibration standard, 3 is excellent, and 6 is good, 9 be can, as shown in Table 8, plus after counterweight 3,
Big vibration values are 1.6, and surveyed vibration data is outstanding therefore plus after counterweight 3.
All only add once balance counterweight when above-mentioned reparation situation can be seen that four times and repairs, so that impeller has been reached dynamic
Balance.
Claims (4)
1. a kind of large fan impeller on-line dynamic balancing bearing calibration it is characterised in that: the following steps that inclusion order is carried out:
A, online vibration detection equilibristat (1) one end is connected with the drive end (21) of draught fan impeller (2), the other end and blower fan leaf
The Partner (22) of wheel (2) is connected；And mark on the wheel disc (23) of impeller (2) (24), with this labelling (24) for vibrating
Beginning phase point；
B, Vibration on Start-up detection equilibristat (1), measure the original vibration amplitude of draught fan impeller (2) drive end (21) place bearing shell and hang down
Nogata to original phase, original vibration amplitude is designated as a1, unit be μm；Original phase is designated as ψ1, unit is degree；Measure blower fan
The original vibration amplitude of impeller (2) Partner (22) place bearing shell and the original phase of vertical direction, original vibration amplitude is designated as a2；
Original phase is designated as ψ2；Find out maximum original vibration amplitude, be designated as a0；
C, pass through q=0.0096 × w × (a0/ r) × (n/4000) × 2 calculate the quality that need to add counterweight (3)；Wherein, q
Expression need to add counterweight (3)；W represents rotor quality, unit be gram；N represents the rotating speed of rotor, unit be rev/min；R table
Show that weight installing position arrives the vertical dimension of rotor axis, unit is millimeter；a0For maximum original vibration amplitude；
By α=ψSurvey+ 180 ° of+ψ calculate the actual phase of weightless point, wherein, ψSurveyBy survey vertical direction original phase, ψSurvey
=(ψ1+ψ2)/2；ψ is oscillation hysteresis angle；
D, counterweight (3) is added to impeller (2) blade (25) back side weight installing position；
E, it is again started up vibration detection equilibristat (1), detection large fan impeller increases the counterbalance effect after counterweight (3),
If being unsatisfactory for requirement for dynamic balance, repeat step c and d are until meeting requirement for dynamic balance.
2. as claimed in claim 1 a kind of large fan impeller on-line dynamic balancing bearing calibration it is characterised in that: step c lead to
Cross vibration detection equilibristat (1) to complete.
3. as claimed in claim 1 a kind of large fan impeller on-line dynamic balancing bearing calibration it is characterised in that: described q is
Positive integer.
4. a kind of large fan impeller on-line dynamic balancing bearing calibration as described in claim 1-3 any one claim,
It is characterized in that: in step d, described counterweight (3) evenly distributes in blade (25) along the axis direction parallel to impeller (2)
The back side.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107966243A (en) * | 2017-11-23 | 2018-04-27 | 中国航发沈阳黎明航空发动机有限责任公司 | A kind of method of on-line tuning heavy combustion engine rotor residual unbalance, |
| CN108443235A (en) * | 2018-05-24 | 2018-08-24 | 山东禹王生态食业有限公司 | The method for quickly solving bladed disk vibration |
| CN110243541A (en) * | 2019-07-18 | 2019-09-17 | 新兴铸管股份有限公司 | Blower on-line dynamic balancing calculation method |
| CN110722326A (en) * | 2019-10-25 | 2020-01-24 | 浙江上风高科专风实业有限公司 | Production method based on closed centrifugal fan simulation test |
| CN110985450A (en) * | 2019-12-10 | 2020-04-10 | 西安交通大学 | Large-balance-capacity high-precision online dynamic balance terminal suitable for fan rotor |
| CN111219350A (en) * | 2020-01-09 | 2020-06-02 | 中铁第十八工程局涿州水泵厂 | Conversion method of fan environment parameters |
| CN113029436A (en) * | 2021-03-01 | 2021-06-25 | 大唐东北电力试验研究院有限公司 | Extension shaft dynamic balance method for three-cylinder two-steam-exhaust 200MW steam turbine generator unit |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107966243A (en) * | 2017-11-23 | 2018-04-27 | 中国航发沈阳黎明航空发动机有限责任公司 | A kind of method of on-line tuning heavy combustion engine rotor residual unbalance, |
| CN108443235A (en) * | 2018-05-24 | 2018-08-24 | 山东禹王生态食业有限公司 | The method for quickly solving bladed disk vibration |
| CN110243541A (en) * | 2019-07-18 | 2019-09-17 | 新兴铸管股份有限公司 | Blower on-line dynamic balancing calculation method |
| CN110722326A (en) * | 2019-10-25 | 2020-01-24 | 浙江上风高科专风实业有限公司 | Production method based on closed centrifugal fan simulation test |
| CN110985450A (en) * | 2019-12-10 | 2020-04-10 | 西安交通大学 | Large-balance-capacity high-precision online dynamic balance terminal suitable for fan rotor |
| CN110985450B (en) * | 2019-12-10 | 2020-11-17 | 西安交通大学 | Large-balance-capacity high-precision online dynamic balance terminal suitable for fan rotor |
| CN111219350A (en) * | 2020-01-09 | 2020-06-02 | 中铁第十八工程局涿州水泵厂 | Conversion method of fan environment parameters |
| CN113029436A (en) * | 2021-03-01 | 2021-06-25 | 大唐东北电力试验研究院有限公司 | Extension shaft dynamic balance method for three-cylinder two-steam-exhaust 200MW steam turbine generator unit |
| CN113029436B (en) * | 2021-03-01 | 2023-10-20 | 大唐东北电力试验研究院有限公司 | Method for dynamically balancing long shaft of three-cylinder two-exhaust 200MW steam turbine generator assembly |
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Application publication date: 20170125 |