CN105547591A - Asymmetric rotor balancing method without phase position - Google Patents
Asymmetric rotor balancing method without phase position Download PDFInfo
- Publication number
- CN105547591A CN105547591A CN201510881822.XA CN201510881822A CN105547591A CN 105547591 A CN105547591 A CN 105547591A CN 201510881822 A CN201510881822 A CN 201510881822A CN 105547591 A CN105547591 A CN 105547591A
- Authority
- CN
- China
- Prior art keywords
- test mass
- trial
- vibration
- mass
- mass point
- 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.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 39
- 238000012360 testing method Methods 0.000 claims abstract description 56
- 230000003252 repetitive effect Effects 0.000 claims description 3
- 238000005259 measurement Methods 0.000 abstract description 9
- 230000001052 transient effect Effects 0.000 description 8
- 238000004088 simulation Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 2
- SMDHCQAYESWHAE-UHFFFAOYSA-N benfluralin Chemical compound CCCCN(CC)C1=C([N+]([O-])=O)C=C(C(F)(F)F)C=C1[N+]([O-])=O SMDHCQAYESWHAE-UHFFFAOYSA-N 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 238000011160 research Methods 0.000 description 1
Classifications
-
- 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 imbalance
- G01M1/32—Compensating imbalance by adding material to the body to be tested, e.g. by correcting-weights
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Testing Of Balance (AREA)
Abstract
The invention provides an asymmetric rotor balancing method without phase position, comprising following steps: step1: original vibrations of two test points of a rotor are measured; step 2:a first trial-mass point at an axial position is selected to perform mass trial, the vibration after mass increasing is measured to obtain an influence coefficient of the two test points after mass trial; step 3: a trial-mass block is taken off, a next trial-mass point is selected for calculating and obtaining an influence coefficient of the second trial-mass point; step 4: step 2 and step 3 are repeated to obtain influence coefficients of a third and a fourth trial-mass point by calculation; step 5: according to the four sets of mass increasing influence coefficients, balance weight required for balancing out the original vibration is obtained by calculation; step 6: according to the balance weight, weight is added to corresponding positions for balancing. According to the balancing method, there is no need to take the phase position of a trial-mass point into consideration so that the measurement of trial-mass point phase positions is not required; therefore the measurement process is simplified, the measurement error during a phase position measurement is reduced, and the accuracy of dynamic balance is increased. The method can be directly operated on a traditional high-speed dynamic balancing machine with ease and simpleness.
Description
Technical field
The present invention is applied to the high-speed balancing of cross section asymmetrical rotor, and there is the horizontal screw centrifuge of groove at side surface in applicable field, has the engine rotor, two blade propeller etc. of line grain.
Background technology
Two cross section unequal rotors of the main moments of inertia are called asymmetrical rotor, and asymmetrical rotor is widely used in engineering, the horizontal screw centrifuge of such as groove at side surface, the engine rotor having line grain, two blade propeller etc.Due to the non-stiffness coefficient cyclical variation to becoming to have cited approvingly of rotating shaft, its vibration equation is different from symmetric rotor, is the second order differential equation with time-varying parameter, and the amount of unbalance at out of phase place, same cross section is different to the contribution of system vibration.Traditional dynamic balance method is mainly divided into influence coefficient method and harmonic component method two class, and wherein the basis of influence coefficient method is that a test mass of a certain phase position obtains in balance cross section influence coefficient is applicable to increasing the weight of of arbitrary phase position in this balance cross section.Unbalance response (comprising amplitude and the phase place) difference increased the weight of for out of phase due to asymmetrical rotor is very large, the influence coefficient obtained at the test mass of out of phase position, same cross section is not definite value, and the concept in the balance cross section therefore in influence coefficient method is not suitable for asymmetrical rotor.In recent years, Chinese scholars pays close attention to several aspect such as asymmetrical rotor vibration characteristics, unstable vibration mechanism and vibration control method, many asymmetric rotors Parametrical excitation characteristic always, still little for the dynamic balance method research with the cross section asymmetrical rotor that very strong engineer applied is worth.
Summary of the invention
Object of the present invention, for the transient equilibrium response characteristic of cross section asymmetrical rotor, provides a kind of scientific and effective high-speed balancing method being applicable to asymmetrical rotor.
The technical scheme of invention is as follows:
Asymmetrical rotor, without phase equilibrium method, is characterized in that, comprises transient equilibrium operation and Computing Principle, comprises following steps, as shown in Figure 1:
1. measure the original vibration of rotor two measuring points;
2. first the test mass point choosing axial location carries out test mass, measures the vibration after increasing the weight of, calculates the influence coefficient of latter two measuring point of test mass;
3. take off test mass block, choose next test mass point, calculate the influence coefficient of second test mass point;
4. repetitive process 2 and 3, calculates the influence coefficient of the 3rd, the 4th test mass point;
5. increase the weight of influence coefficient according to four groups of test mass points obtaining, calculate the counterweight amount eliminated needed for original vibration;
6. according to the counterweight amount obtained, hamming on a corresponding position.
The balance of described two measuring points at least needs four test mass points, and carry out four balance test mass, maximum two the test mass points in four test mass points can be positioned on same cross section, and each influence coefficient is only applicable to the counterweight on the position corresponding with test mass point.
Be described as follows:
1. paste reflective tape in rotor one end, the photoelectric sensor being used for measuring vibrations phase place is installed.Bearing seat installs and measures the photoelectric sensor of vibration, and each sensor connects rotor vialog;
2. measure two measuring point original vibration A
0and B
0, as shown in Figure 2, A
0for original vibration, A
1for the vibration after first time test mass, A
2for the vibration after second time test mass, by that analogy, B in like manner;
3. choose four test mass point P
1, P
2, P
3, P
4.At test mass point P
1examination increases the weight of m
1, measure the vibration A after increasing the weight of
1and B
1;
4. take off m
1, at test mass point P
2upper examination increases the weight of m
2, measure the vibration A after increasing the weight of
2and B
2;
5. take off m
2, at test mass point P
3, P
4upper repetitive process 2 and 3, obtains A
3and B
3, A
4and B
4;
6. calculate and increase the weight of influence coefficient:
7. should use the same method and can obtain
with
with
with
the influence coefficient matrix of system is shown below:
8. be located at P
1, P
2, P
3, P
4place is counterweight Q respectively
1, Q
2, Q
3, Q
4, for eliminating the vibration of two measuring points, counterweight should be made to cause the original vibration of the vibration of measuring point and measuring point to be 0, namely meets:
9. solve the equation in (4), obtain Q
1, Q
2, Q
3, Q
4value, and counterweight on a corresponding position; If calculate the counterweight amount of gained be on the occasion of, counterweight amount is directly added in test mass point place; If the counterweight amount calculating gained is negative value, then counterweight is in the opposite in cross section, test mass point place.
Effect of the present invention is as follows:
1. do not need the phase place considering test mass point position, do not need measurement test mass point being carried out to phase place, simplify process of measurement, decrease the error in phase measurement process, improve dynamically balanced precision;
Not only 2. the present invention does not need the equipment increasing, reduce measurement point but also do not need specialty, can on traditional high-speed dynamic balance machine direct control, simple and convenient;
3. the present invention is directed to the high-speed balancing method of asymmetrical rotor, effectively can reduce the vibration of rotor, thus improve the life-span of rotor, improve the security that machine runs.
Accompanying drawing explanation
Fig. 1 is that asymmetrical rotor is without phase equilibrium method process flow diagram;
Fig. 2 is test mass point schematic diagram;
Fig. 3 is the asymmetric helical rotor structure figure of certain horizontal screw centrifuge groove at side surface;
Fig. 4 is the asymmetric helical rotor spot dynamic balance Test Drawing of certain horizontal screw centrifuge groove at side surface.
Embodiment
Embodiment 1
The dynamic balance method that this example utilizes the present invention to propose, for the asymmetric helical rotor of certain horizontal screw centrifuge groove at side surface, application business general finite element software ANSYS carries out transient equilibrium analogue simulation to it.The asymmetric helical rotor structure schematic diagram of this horizontal screw centrifuge groove at side surface as shown in Figure 3.During 3300rpm, the dynamically balanced detailed process of ANSYS software simulation is as follows:
1. provide the original vibration A of measuring point
0=11.02 ∠ 146 μm pp ∠ ° and B
0=9.02 ∠ 136 μm pp ∠ °;
2. as shown in Figure 3, at test mass point P
1examination increases the weight of m
1=16.8g, simulation obtains the vibration A after increasing the weight of
1=9.5968 ∠ 157 μm pp ∠ ° and B
1=13.3187 ∠ 158 μm pp ∠ °;
3. take off m
1, at test mass point P
2upper examination increases the weight of m
2, simulation obtains the vibration A after increasing the weight of
2=12.4194 ∠ 143 μm pp ∠ ° and B
2=12.0361 ∠ 124 μm pp ∠ °;
4. take off m
2, at test mass point P
3upper examination increases the weight of m
3, simulation obtains the vibration A after increasing the weight of
3=19.4023 ∠ 165 μm pp ∠ ° and B
3=12.7454 ∠ 159 μm pp ∠ °;
5. take off m
3, at test mass point P
4upper examination increases the weight of m
4, simulation obtains the vibration A after increasing the weight of
4=15.4350 ∠ 134 μm pp ∠ ° and B
4=10.3023 ∠ 133 μm pp ∠ °;
6., according to (1) formula, (2) formula, calculate and increase the weight of influence coefficient
7. in like manner, apply same method to obtain
8. solve the equation in (4), obtain Q
1=-5.788g, Q
2=-28.90g, Q
3=-10.74g, Q
4=-18.58g;
9. obtaining Q
1, Q
2, Q
3, Q
4value be input to corresponding position in ANSYS software, again do transient equilibrium analogue simulation, obtain vibration A=0.2047 ∠ 135 μm of pp ∠ ° and the B=0.1 ∠ 48 μm of pp ∠ ° of measuring point after new balance.
Table one is transient equilibrium process during 3300rpm and result (amount of overstriking is vector).As can be seen from table, after transient equilibrium, the vibration of measuring point A and measuring point B reduces 98.1% and 98.8% respectively, illustrates that the dynamic balance method that the present invention carries is accurately feasible in theory.
Table one
Embodiment 2
The dynamic balance method that this example utilizes the present invention to propose carries out spot dynamic balance experiment, as shown in Figure 4.Adopt the hard bearing balan of Shanghai Schiak Testing Machinery Co., Ltd. under 2700rpm, to carry out asymmetrical rotor to certain horizontal screw centrifuge helical rotor to test without phase equilibrium method.Concrete transient equilibrium process is as follows:
1. measure the original vibration A of measuring point
0=3.024 ∠ 89 μm pp ∠ ° and B
0=3.51 ∠ 93 μm pp ∠ °;
2. as shown in Figure 3, at test mass point P
1examination increases the weight of m
1=30g, test obtains the vibration A after increasing the weight of
1=2.967 ∠ 131 μm pp ∠ ° and B
1=2.385 ∠ 96 μm pp ∠ °;
3. take off m
1, at test mass point P
2upper examination increases the weight of m
2=30g, test obtains the vibration A after increasing the weight of
2=2.993 ∠ 82 μm pp ∠ ° and B
2=3.484 ∠ 107 μm pp ∠ °;
4. take off m
2, at test mass point P
3upper examination increases the weight of m
3=30g, test obtains the vibration A after increasing the weight of
3=7.619 ∠ 112 μm pp ∠ ° and B
3=5.328 ∠ 102 μm pp ∠ °;
5. take off m
3, at test mass point P
4upper examination increases the weight of m
4=30g, test obtains the vibration A after increasing the weight of
4=4.659 ∠ 115 μm pp ∠ ° and B
4=5.814 ∠ 122 μm pp ∠ °;
6., according to (1) formula, (2) formula, calculate and increase the weight of influence coefficient
7. in like manner, apply same method to obtain
8. solve the equation in (4), obtain Q
1=45g, Q
2=-6.7g, Q
3=72.3g, Q
4=-21g;
9. at corresponding Weight Q
1, Q
2, Q
3, Q
4, again do dynamic balancing measurement, obtain vibration A=0.514 ∠ 135 μm of pp ∠ ° and B=0.386 ∠ 48 μm of pp ∠ ° of the rear measuring point of new balance.
Table two is experiment of dynamic balancing process during 2700rpm and result (amount of overstriking is vector):
Table two
In this test, two measuring points are positioned on bearing seat, and its vibration speed value and phase place corresponding to vibration velocity can directly read on dynamic balancing machine, just can obtain vibration amplitude to vibration velocity integration, by the judge value of vibration amplitude as vibration.As can be seen from table, after transient equilibrium, the vibration of measuring point A and measuring point B reduces 83% and 89% respectively, illustrates that the dynamic balance method that the present invention carries is accurately feasible in practice.
Claims (4)
1. asymmetrical rotor is without phase equilibrium method, it is characterized in that, comprises following steps:
(1) the original vibration of rotor two measuring points is measured;
(2) first the test mass point choosing axial location carries out test mass, measures the vibration after increasing the weight of, calculates the influence coefficient of latter two measuring point of test mass;
(3) take off test mass block, choose next test mass point, calculate the influence coefficient of second test mass point;
(4) repetitive process (2) and (3), calculate the influence coefficient of the 3rd, the 4th test mass point;
(5) increase the weight of influence coefficient according to four groups of test mass points obtaining, calculate the counterweight amount eliminated needed for original vibration;
(6) according to the counterweight amount obtained, hamming on a corresponding position.
2. asymmetrical rotor as claimed in claim 1 is without phase equilibrium method, it is characterized in that the balance of two measuring points at least needs four test mass points.
3. asymmetrical rotor as claimed in claim 1 is without phase equilibrium method, it is characterized in that maximum two the test mass points in four test mass points can be positioned on same cross section.
4. asymmetrical rotor as claimed in claim 1 is without phase equilibrium method, it is characterized in that each influence coefficient is only applicable to the counterweight on the position corresponding with test mass point.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510881822.XA CN105547591A (en) | 2015-12-03 | 2015-12-03 | Asymmetric rotor balancing method without phase position |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510881822.XA CN105547591A (en) | 2015-12-03 | 2015-12-03 | Asymmetric rotor balancing method without phase position |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105547591A true CN105547591A (en) | 2016-05-04 |
Family
ID=55826935
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510881822.XA Pending CN105547591A (en) | 2015-12-03 | 2015-12-03 | Asymmetric rotor balancing method without phase position |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105547591A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108801550A (en) * | 2017-04-26 | 2018-11-13 | 江铃汽车股份有限公司 | A kind of equivalent uneven test method of automotive transmission |
| CN109406053A (en) * | 2018-12-06 | 2019-03-01 | 浙江大学 | Without duplicate removal rotor dynamic balancing method |
| CN109855801A (en) * | 2019-03-29 | 2019-06-07 | 国网山东省电力公司电力科学研究院 | The pump-storage generator rapid dynamic balance method of accurate test mass combination influence coefficient method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0375538A (en) * | 1989-06-30 | 1991-03-29 | General Electric Co <Ge> | Method of balancing rotor |
| CN1264035A (en) * | 2000-03-09 | 2000-08-23 | 西安交通大学 | Holographic dynamic balance method for asymmetric rotor |
| CN101059386A (en) * | 2007-06-04 | 2007-10-24 | 西安交通大学 | Precession vector based holographic on-spot dynamic balance method |
| CN101387567A (en) * | 2008-10-29 | 2009-03-18 | 西北工业大学 | Double surface transient equilibration method for flexible rotor |
-
2015
- 2015-12-03 CN CN201510881822.XA patent/CN105547591A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0375538A (en) * | 1989-06-30 | 1991-03-29 | General Electric Co <Ge> | Method of balancing rotor |
| CN1264035A (en) * | 2000-03-09 | 2000-08-23 | 西安交通大学 | Holographic dynamic balance method for asymmetric rotor |
| CN101059386A (en) * | 2007-06-04 | 2007-10-24 | 西安交通大学 | Precession vector based holographic on-spot dynamic balance method |
| CN101387567A (en) * | 2008-10-29 | 2009-03-18 | 西北工业大学 | Double surface transient equilibration method for flexible rotor |
Non-Patent Citations (1)
| Title |
|---|
| 谭蔚等: "非对称转子动力学特性数值模拟研究", 《天津大学学报(自然科学与工程技术版)》 * |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108801550A (en) * | 2017-04-26 | 2018-11-13 | 江铃汽车股份有限公司 | A kind of equivalent uneven test method of automotive transmission |
| CN109406053A (en) * | 2018-12-06 | 2019-03-01 | 浙江大学 | Without duplicate removal rotor dynamic balancing method |
| CN109406053B (en) * | 2018-12-06 | 2019-12-06 | 浙江大学 | dynamic balancing method for rotor without removing weight |
| CN109855801A (en) * | 2019-03-29 | 2019-06-07 | 国网山东省电力公司电力科学研究院 | The pump-storage generator rapid dynamic balance method of accurate test mass combination influence coefficient method |
| CN109855801B (en) * | 2019-03-29 | 2020-12-15 | 国网山东省电力公司电力科学研究院 | Quick dynamic balance method of pumped storage unit by combining accurate test weight with influence coefficient method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101639395B (en) | Improved holographic dynamic balancing method of high-speed main shaft | |
| CN105426644B (en) | Modal damping recognition methods, device and system | |
| CN201514306U (en) | Dynamic balance testing device | |
| CN102928222B (en) | Method for testing and identifying dynamic characteristic coefficients of sliding bearing | |
| Kammerer et al. | Blade forcing function and aerodynamic work measurements in a high speed centrifugal compressor with inlet distortion | |
| CN105547591A (en) | Asymmetric rotor balancing method without phase position | |
| CN103592081A (en) | Rotor non-trial-weight dynamic balancing method suitable for distributed unbalance | |
| CN105403364A (en) | Dual-trail-weight balancing method of asymmetric rotor | |
| CN102778335A (en) | Anisotropic rotor holographic dynamic balancing method based on equivalent initial phase vector | |
| CN103105266B (en) | Dynamic balance method of bending moment of rotating mechanical rotor biplane | |
| CN109115408B (en) | Dynamic balance test method of large hydroelectric generating set based on centrifugal force equation | |
| CN103115726A (en) | Rotating parts and components dynamic balance method based on strain | |
| CN109063404A (en) | A kind of dynamic prediction method of Aerostatic thrust bearing rigidity | |
| CN104101464A (en) | Multi-wheel-disc rotor dynamic balancing test method based on rotating coordinate system | |
| Kammerer et al. | Experimental study on impeller blade vibration during resonance—Part II: Blade damping | |
| Zhou et al. | The analytical imbalance response of Jeffcott rotor during acceleration | |
| CN103712746B (en) | The acquiring method of Hysteresis phase lag in a kind of dynamic balance test of rotor | |
| CN104165729B (en) | A kind of dynamic balance method of high speed rotor | |
| CN105478245A (en) | Identification method on basis of vibration detection of main shaft and for dynamic unbalance value of auxiliary shaft of double-freedom degree precision centrifugal machine | |
| CN103257018A (en) | Rigid rotor dynamic balance obtaining method | |
| CN112327957B (en) | Method and device for controlling low-frequency vibration multi-order line spectrum of rotor | |
| CN102928611A (en) | Second harmonic generation-based method for obtaining critical rotation speed of steam turbine rotor | |
| CN110646139A (en) | Method for determining the unbalance of a shaft-elastic rotor on the basis of the degree of curvature | |
| CN106503375B (en) | Based on CNMethod and system for determining critical rotating speed of steam turbine rotor by group theory | |
| CN103344385A (en) | Crankshaft dynamic balance acquisition method based on finite elements |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20160504 |
|
| RJ01 | Rejection of invention patent application after publication |