CN103115726B - Rotating parts and components dynamic balance method based on strain - Google Patents
Rotating parts and components dynamic balance method based on strain Download PDFInfo
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Abstract
The invention discloses a rotating parts and components dynamic balance method based on strain. The rotating parts and components dynamic balance method based on strain finishes unbalance correction of the rotating parts and components through the strain in the rotating process of the rotating parts and components. The rotating parts and components dynamic balance method based on strain is free from mass test, can directly figure out a scale which is needed to be aggravated and an angle which is needed to be aggravated through strain data, is low in dynamic balance theory level which is required to master and is suitable for all technical staffs. The rotating parts and components dynamic balance method based on strain is an online dynamic balance method, has the advantages of being rapid and convenient and can achieve mass operation of parts and components dynamic balance craft.
Description
Technical field
The present invention relates to a kind of rotating parts dynamic balance method based on strain.
Background technology
Rotating parts is the most frequently used in mechanical system, the most basic, is also most important ingredient, has been widely used in the fields such as aviation, electric power, oil, chemical industry.Its rotor is modal one in rotating part.The movable body of High Rotation Speed is done for such as flywheel, rotating disk, clutch coupling etc., due to the reason such as material character, process and assemble error of rotor, causes the unbalance mass, distribution of differing in size, cause the barycenter of rotor not overlap with actual rotation center.Principal axis of inertia departs from its corresponding rotation, produces very large centrifugal force thereupon, causes equipment to produce larger vibration, thus accelerate the wearing and tearing of element part, affect equipment serviceability, reduce operating accuracy and the serviceable life of equipment, have a strong impact on the normal production of equipment.Therefore, how correcting the unbalancing value of rotating machinery parts fast and accurately, is the problem that people pay close attention to always.
Generally speaking, the method at present for correcting rotating parts unbalancing value mainly contains three kinds.(1) Action of Gravity Field of rotor self is relied on to measure out-of-balance force.Rotor to be measured is placed on the bearing with hydrostatic bearing supporting, setting-in a slice reflective mirror below bearing.When rotor does not exist amount of unbalance, the light beam penetrated by light source, after this mirror reflection, is incident upon the polar coordinates initial point of amount of unbalance indicatior.If rotor exists amount of unbalance, then rotor bearing run-off the straight under the gravitational torque effect of amount of unbalance, the reflective mirror under bearing also tilts thereupon and makes the beam deflection that reflects, and the luminous point that now light beam is thrown on polar coordinates indicator just leaves initial point.According to the coordinate position of this Optical Bean Deflection, size and the position of amount of unbalance can be obtained.This method is only applicable to the not high discoid part of some balance requirement.(2) measure supporting dynamic force and carry out imbalance correction amount.By installing force cell between rotor and block bearing, the stressing conditions measuring rotor rotation process centre bearer measures the size and Orientation of out-of-balance force.Current this method is mainly used on various dynamic balancing machine, and this method needs a set of more accurate and sensitive rocker system, is balanced rotor makes it to vibrate under out-of-balance force for support.The structure of rocker system should can ensure enough rigidity by rocker, also will ensure enough sensitivity.The kinematic behavior of rocker system directly affects the performance of dynamic balancing machine, and therefore its measuring accuracy receives certain restriction.(3) vibration of measuring supporting carrys out imbalance correction amount.In the bearing seat horizontal and vertical direction placement sensor of supporting rotor, first the vibration values of original unbalance at measurement point is measured, then try to increase the weight of to rotor and measure the vibration displacement amount that examination increases the weight of rear bearing block, carrying out imbalance correction power by calculating influence coefficient.The method is a kind of off-line balancing method, and need examination to increase the weight of the correction that just can complete out-of-balance force, counterweight size needs to determine by rule of thumb.
Summary of the invention
The invention provides the rotating parts dynamic balance method based on strain.
In order to solve the problems of the technologies described above, adopt following technical scheme:
Based on a rotating parts dynamic balance method for strain, completed the disequilibrium regulating of rotating parts by the strain in test rotating parts rotary course.
The above-mentioned rotating parts dynamic balance method based on strain, is characterized in that: comprise the steps:
A, rotating parts to be measured is arranged on transient equilibrium by universal joint detects on stand;
B, transient equilibrium detect stand shaft part on eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, in this, as multi-measuring point normal rolling analyze benchmark;
C, transient equilibrium detect stand rotating shaft surface select two measure cross sections install strain measuring points, measure cross section for these two to lay respectively at and connect two gimbal couplings of rotating parts and transient equilibrium detects between two block bearings of stand, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on same bus with keyway, and another group foil gauge is positioned at along rotary speed direction and keyway position in 90 °;
D, detect the rotating shaft of stand rotate under rotating speed n with driven by motor transient equilibrium, in record rotary course, the strain value of each group strain measuring point, is designated as: ε respectively
1x(t), ε
1y(t), ε
2x(t), ε
2y(t), wherein, subscript 1,2 represents measures cross section numbering, and x, y represent the strain of two groups of different directions;
E, set up fixing rectangular coordinate system, the y-axis of this fixed coordinate system is the arranged direction of eddy current sensor, and x-axis is clockwise speed and keyway direction in 90 °, the strain value in the rotary course of measurement is converted to the strain value under fixed coordinate system, is designated as ε
1-(t), ε
1 ⊥(t), ε
2-(t), ε
2 ⊥(t), wherein, ε
1-represent the component of strain in x-axis direction that first is measured cross section, ε
1 ⊥represent the component of strain in y-axis direction that first is measured cross section, ε
2-represent the component of strain in x-axis direction that second is measured cross section, ε
2 ⊥represent the component of strain in y-axis direction that second is measured cross section;
ε
1-(t)=ε
1x·cosωt+ε
1y·sinωt
ε
1⊥(t)=-ε
1x·sinωt+ε
1y·cosωt
ε
2-(t)=ε
2x·cosωt+ε
2y·sinωt
ε
2⊥(t)=-ε
2x·sinωt+ε
2y·cost （1）
In formula, ω is rotor angular velocity of rotation, and t is the time.
F, according to the strain value under fixed coordinate system, calculate in axle system rotary course respectively and measure the moment of flexure of cross section on x-axis direction and y-axis direction:
M
1⊥(t)=E·W·ε
1⊥(t)
M
1-(t)=E·W·ε
1-(t)
M
2⊥(t)=E·W·ε
2⊥(t) （2）
M
2-(t)=E·W·ε
2-(t)
Wherein: M
1-represent first and measure cross section moment of flexure in the direction of the x axis, M
1 ⊥represent first and measure cross section moment of flexure in the y-axis direction, M
2-represent second and measure cross section moment of flexure in the direction of the x axis, M
2 ⊥represent second and measure cross section moment of flexure in the y-axis direction, E, W are respectively rotating shaft elastic modulus and section modulus, for circular shaft,
d, d are respectively external diameter and the internal diameter of circular shaft;
G, measure section turn moment according to two and calculate the shearing Q that two are measured cross section horizontal directions and vertical direction
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)=M
1-(t)/l
1Q
1⊥(t)=M
1⊥(t)/l
1
Q
2-(t)=M
2-(t)/l
2Q
2⊥(t)=M
2⊥(t)/l
2（3）
In formula, l
1, l
2for bearing supporting power is to the distance measuring cross section;
H, the shearing difference Δ Q calculated in two measurement cross section horizontal directions and vertical direction
-(t), Δ Q
⊥(t).
ΔQ
-(t)=Q
1-(t)-Q
2-(t) ΔQ
⊥(t)=Q
1⊥(t)-Q
2⊥(t) （4）
The size of I, calculating unbalance mass, m, the size G=mr ω of this out-of-balance force
2, r is rotor radius;
Known according to analysis, above-mentioned shearing difference is the component acted in out-of-balance force G rotary course in the horizontal direction and the vertical direction, that is: G
-(t)=-mr ω
2sin (ω t-α), G
⊥(t)=mr ω
2cos (ω t-α), in formula, α is the phase place of out-of-balance force.And the difference of the curve of shearing force in horizontal direction and vertical direction just phase 90 ° in theory, the present invention is for the horizontal direction curve of shearing force;
The amplitude of the curve of shearing force is the size of out-of-balance force, and therefore unbalance mass, is:
The phase place α of J, calculating out-of-balance force, phase place α is defined as: the angle of pulse front edge leading vibration signal positive peak, and namely with keyway POS INT, inverse rotary speed direction becomes the angle of α size with keyway;
This out-of-balance force component is in the horizontal direction a curve doing sinusoidal variations in time, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of fixed coordinate system x-axis leading out-of-balance force, can be determined by angle first crest of pulse starting point to level to out-of-balance force curve;
Therefore, the phase place α of out-of-balance force is: α=θ-90 °.
K, increase the weight of the determination of weight and phase place:
According to above-mentioned calculating, in order to correct this amount of unbalance, the weight m that need increase the weight of and phase beta are respectively:
Angle beta is defined as: with keyway POS INT, and inverse rotary speed direction becomes the angle of β size with keyway.
In above-mentioned steps G, when practical application, moment of flexure shearing reduction coefficient can be demarcated according to architectural characteristic and other factors; In step I, shearing, M curve in horizontal direction and vertical direction, theoretical difference is only difference 90 °, therefore study for horizontal direction in the present invention, but protection scope of the present invention is not limited only to horizontal direction.。
The technology that the present invention is not particularly limited is prior art.
The present invention is under different load diatibution states, and rotor shaft elastic deformation is different, and each point strain and stress distribution situation is different, therefore, by measuring rotating shaft strain, just likely identifies the size and Orientation of rotor unbalance power.Compared with prior art, tool of the present invention has the following advantages:
(1) this method is without the need to test mass, and the size that can increase the weight of needed for strain data directly calculates and angle, the transient equilibrium theoretical level of required grasp is lower, is applicable to all technician.
(2) this method is a kind of on-line dynamic balancing method, has the features such as quick and easy, can realize parts dynamic balancing technics batched operation.
Accompanying drawing explanation
Fig. 1 detects stand sketch;
In figure, 1 is block bearing, and 2 is strain measuring point, and 3 is gimbal coupling, and 4 is rotating parts to be measured, and 5 is eddy current sensor, and 6 is keyway, and 7 is flexible universal joint shaft coupling, and 8 is motor;
Fig. 2 is angle definition and fixed coordinate system schematic diagram residing for shaft part foil gauge, and in figure, 9 is foil gauge;
Fig. 3 is out-of-balance force phase place α, increases the weight of phase beta, the schematic diagram of out-of-balance force G and stationary coordinate x-axis angle theta;
Fig. 4 is the original strain signal in the rotary course of rotating shaft cross section;
Fig. 5 is the strain signal of rotating shaft cross section under fixed coordinate system;
Fig. 6 is for from pulse starting point to level to the schematic diagram of the angle θ of first of the curve of shearing force crest;
Fig. 7 is this out-of-balance force correction method process flow diagram.
Embodiment
The present embodiment is for the rotating parts test-bed shown in Fig. 1, analyzes based on straining the rotor unbalance bearing calibration carried out.With reference to Fig. 2 ~ 7.
The method completing rotating parts disequilibrium regulating by monitor strain that the present embodiment relates to is:
A, rotating parts to be measured is arranged on transient equilibrium by universal joint detects on stand;
B, transient equilibrium detect stand shaft part on eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, in this, as multi-measuring point normal rolling analyze benchmark;
C, transient equilibrium detect stand rotating shaft surface select two measure cross sections install strain measuring points, measure cross section for these two to lay respectively at and connect two gimbal couplings of rotating parts and transient equilibrium detects between two block bearings of stand, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on same bus with keyway, another group foil gauge is positioned at along rotary speed direction and keyway position in 90 °, as shown in Figure 2;
D, detect the rotating shaft of stand rotate under rotating speed n with driven by motor transient equilibrium, in record rotary course, the strain value of each group strain measuring point, is designated as: ε respectively
1x(t), ε
1y(t), ε
2x(t), ε
2y(t), wherein, subscript 1,2 represents measures cross section numbering, and x, y represent the strain of two groups of different directions;
E, set up fixing rectangular coordinate system, the y-axis of this fixed coordinate system is the arranged direction of eddy current sensor, and x-axis is clockwise speed and keyway direction in 90 °, the strain value in the rotary course of measurement is converted to the strain value under fixed coordinate system, is designated as ε
1-(t), ε
1 ⊥(t), ε
2-(t), ε
2 ⊥(t), wherein, ε
1-represent the component of strain in x-axis direction that first is measured cross section, ε
1 ⊥represent the component of strain in y-axis direction that first is measured cross section, ε
2-represent the component of strain in x-axis direction that second is measured cross section, ε
2 ⊥represent the component of strain in y-axis direction that second is measured cross section;
ε
1-(t)=ε
1x·cosωt+ε
1y·sinωt
ε
1⊥(t)=-ε
1x·sinωt+ε
1y·cosωt
ε
2-(t)=ε
2x·cosωt+ε
2y·sinωt
ε
2⊥(t)=-ε
2x·sinωt+ε
2y·cost （1）
In formula, ω is rotor angular velocity of rotation, and t is the time.
F, according to the strain value under fixed coordinate system, calculate in axle system rotary course respectively and measure the moment of flexure of cross section on x-axis direction and y-axis direction:
M
1⊥(t)=E·W·ε
1⊥(t)
M
1-(t)=E·W·ε
1-(t)
M
2⊥(t)=E·W·ε
2⊥(t) （2）
M
2-(t)=E·W·ε
2-(t)
Wherein: M
1-represent first and measure cross section moment of flexure in the direction of the x axis, M
1 ⊥represent first and measure cross section moment of flexure in the y-axis direction, M
2-represent second and measure cross section moment of flexure in the direction of the x axis, M
2 ⊥represent second and measure cross section moment of flexure in the y-axis direction, E, W are respectively rotating shaft elastic modulus and section modulus, for circular shaft,
d, d are respectively external diameter and the internal diameter of circular shaft;
G, measure section turn moment according to two and calculate the shearing Q that two are measured cross section horizontal directions and vertical direction
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)=M
1-(t)/l
1Q
1⊥(t)=M
1⊥(t)/l
1
Q
2-(t)=M
2-(t)/l
2Q
2⊥(t)=M
2⊥(t)/l
2（3）
In formula, l
1, l
2for bearing supporting power is to the distance measuring cross section, when practical application, moment of flexure shearing reduction coefficient can be demarcated according to architectural characteristic and other factors;
H, the shearing difference Δ Q calculated in two measurement cross section horizontal directions and vertical direction
-(t), Δ Q
⊥(t).
ΔQ
-(t)=Q
1-(t)-Q
2-(t) ΔQ
⊥(t)=Q
1⊥(t)-Q
2⊥(t) （4）
The size of I, calculating unbalance mass, m, the size G=mr ω of this out-of-balance force
2, r is rotor radius;
Known according to analysis, above-mentioned shearing difference is the component acted in out-of-balance force G rotary course in the horizontal direction and the vertical direction, that is: G
-(t)=-mr ω
2sin (ω t-α), G
⊥(t)=mr ω
2cos (ω t-α), and the difference of the curve of shearing force in horizontal direction and vertical direction just phase 90 ° in theory, the present invention is for the horizontal direction curve of shearing force;
The amplitude of the curve of shearing force is the size of out-of-balance force, and therefore unbalance mass, is:
The phase place α of J, calculating out-of-balance force, phase place α is defined as: the angle of pulse front edge leading vibration signal positive peak, and namely with keyway POS INT, inverse rotary speed direction becomes the angle of α size with keyway, as shown in Figure 3;
This out-of-balance force component is in the horizontal direction a curve doing sinusoidal variations in time, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of fixed coordinate system x-axis leading out-of-balance force, can be determined by angle first crest of pulse starting point to level to out-of-balance force curve, as shown in Figure 6;
Therefore, the phase place α of out-of-balance force is: α=θ-90 °.
K, increase the weight of the determination of weight and phase place:
According to above-mentioned calculating, in order to correct this amount of unbalance, the weight m that need increase the weight of and phase beta are respectively:
Angle beta is defined as: with keyway POS INT, and inverse rotary speed direction becomes the angle of β size with keyway.
Claims (1)
1. based on a rotating parts dynamic balance method for strain, it is characterized in that: the disequilibrium regulating being completed rotating parts by the strain in test rotating parts rotary course;
Comprise the steps:
A, rotating parts to be measured is arranged on transient equilibrium by universal joint detects on stand;
B, transient equilibrium detect stand shaft part on eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, in this, as multi-measuring point normal rolling analyze benchmark;
C, the rotating shaft surface detecting stand in transient equilibrium selects two to measure cross section installation strain measuring point, measuring first gimbal coupling and transient equilibrium that cross section is connecting rotating parts for first detects between first block bearing of stand, measuring second gimbal coupling and transient equilibrium that cross section is connecting rotating parts for second detects between second block bearing of stand, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on same bus with keyway, another group foil gauge is positioned at along rotary speed direction and keyway position in 90 °,
D, detect the rotating shaft of stand rotate under rotating speed n with driven by motor transient equilibrium, in record rotary course, the strain value of each group strain measuring point, is designated as: ε respectively
1x(t), ε
1y(t), ε
2x(t), ε
2y(t), wherein, subscript 1,2 represents measures cross section numbering, and x, y represent the strain of two groups of different directions;
E, set up fixing rectangular coordinate system, the y-axis of this fixing rectangular coordinate system is the arranged direction of eddy current sensor, and x-axis is clockwise speed and keyway direction in 90 °, the strain value in the rotary course of measurement is converted to the strain value under fixing rectangular coordinate system, is designated as ε
1-(t), ε
1 ⊥(t), ε
2-(t), ε
2 ⊥(t), wherein, ε
1-represent the component of strain in x-axis direction that first is measured cross section, ε
1 ⊥represent the component of strain in y-axis direction that first is measured cross section, ε
2-represent the component of strain in x-axis direction that second is measured cross section, ε
2 ⊥represent the component of strain in y-axis direction that second is measured cross section;
ε
1-(t)＝ε
1x·cosωt+ε
1y·sinωt
ε
1⊥(t)＝-ε
1x·sinωt+ε
1y·cosωt
ε
2-(t)＝ε
2x·cosωt+ε
2y·sinωt (1)
ε
2⊥(t)＝-ε
2x·sinωt+ε
2y·cost
In formula, ω is rotor angular velocity of rotation, and t is the time;
Strain value under the fixing rectangular coordinate system of F, basis, calculates in axle system rotary course respectively and measures the moment of flexure of cross section on x-axis direction and y-axis direction:
M
1⊥(t)＝E·W·ε
1⊥(t)
M
1-(t)＝E·W·ε
1-(t)
M
2⊥(t)＝E·W·ε
2⊥(t) (2)
M
2-(t)＝E·W·ε
2-(t)
Wherein: M
1-represent first and measure cross section moment of flexure in the direction of the x axis, M
1 ⊥represent first and measure cross section moment of flexure in the y-axis direction, M
2-represent second and measure cross section moment of flexure in the direction of the x axis, M
2 ⊥represent second and measure cross section moment of flexure in the y-axis direction, E, W are respectively rotating shaft elastic modulus and section modulus, for circular shaft,
d, d are respectively external diameter and the internal diameter of circular shaft;
G, measure section turn moment according to two and calculate the shearing Q that two are measured cross section horizontal directions and vertical direction
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)＝M
1-(t)/l
1Q
1⊥(t)＝M
1⊥(t)/l
1
Q
2-(t)＝M
2-(t)/l
2Q
2⊥(t)＝M
2⊥(t)/l
2(3)
In formula, l
1be first distance measuring between cross section to corresponding side bearing supporting power, l
2be second distance measuring between cross section to corresponding side bearing supporting power; Q
1-t () is first shearing measuring cross section horizontal direction, Q
2-t () is second shearing measuring cross section horizontal direction, Q
1 ⊥t () is first shearing measuring cross section orthogonal direction, Q
2 ⊥t () is second shearing measuring cross section orthogonal direction;
H, the shearing difference Δ Q calculated in two measurement cross section horizontal directions and vertical direction
-(t), Δ Q
⊥(t);
ΔQ
-(t)＝Q
1-(t)-Q
2-(t) ΔQ
⊥(t)＝Q
1⊥(t)-Q
2⊥(t) (4)
The size of I, calculating unbalance mass, m, the size G=mr ω of out-of-balance force
2, r is rotor radius;
Known according to analysis, above-mentioned shearing difference is the component acted in out-of-balance force G rotary course in the horizontal direction and the vertical direction, that is: G
-(t)=-mr ω
2sin (ω t-α), G
⊥(t)=mr ω
2cos (ω t-α), in formula, α is the phase place of out-of-balance force;
The amplitude of the curve of shearing force is the size of out-of-balance force, and therefore unbalance mass, is:
The phase place α of J, calculating out-of-balance force, phase place α is defined as: the angle of pulse front edge leading vibration signal positive peak, and namely with keyway POS INT, inverse rotary speed direction becomes the angle of α size with keyway;
This out-of-balance force component is in the horizontal direction a curve doing sinusoidal variations in time, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of fixing rectangular coordinate system x-axis leading out-of-balance force, can be determined by angle first crest of pulse starting point to level to out-of-balance force curve;
Therefore, the phase place α of out-of-balance force is: α=θ-90 °;
K, increase the weight of the determination of unbalance mass, and phase place:
According to above-mentioned calculating, in order to imbalance correction amount, the unbalance mass, m that need increase the weight of and phase beta are respectively:
Angle beta is defined as: with keyway POS INT, and inverse rotary speed direction becomes the angle of β size with keyway.
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