CN103115726A - 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 rotation parts dynamic balance method based on strain.
Background technology
The rotation parts are the most frequently used in mechanical system, the most basic, are also most important ingredients, have been widely used in the fields such as aviation, electric power, oil, chemical industry.Its rotor is modal a kind of in rotating part.Do the movable body of High Rotation Speed for such as flywheel, rotating disk, clutch coupling etc., due to reasons such as the material character of rotor, process and assemble errors, caused the unbalance mass, that differs in size to distribute, cause the barycenter of rotor not overlap with the rotation center of reality.Principal axis of inertia departs from its corresponding rotation, produces very large centrifugal force thereupon, causes equipment to produce larger vibration, thereby accelerate the wearing and tearing of element part, affect the equipment serviceability, reduce operating accuracy and the serviceable life of equipment, have a strong impact on the normal production of equipment.Therefore, how proofreading and correct fast and accurately the unbalancing value of rotating machinery parts, is people's problems of concerns always.
Generally speaking, be used at present proofreading and correct the method for rotating the parts unbalancing value and mainly contain three kinds.(1) rely on the Action of Gravity Field of rotor self to measure out-of-balance force.Rotor to be measured is placed on the bearing that supports with hydrostatic bearing setting-in a slice reflective mirror below bearing.When there was not amount of unbalance in rotor, the light beam that is penetrated by light source was incident upon the polar coordinates initial point of amount of unbalance indicatior, after this reflective mirror reflection.If there is amount of unbalance in rotor, 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, just the luminous point that this moment, light beam was thrown on the polar coordinates indicator leaves initial point.According to the coordinate position of this Optical Bean Deflection, can obtain size and the position of amount of unbalance.This method is only applicable to the less demanding discoid part of some balance.(2) measure the supporting dynamic force and come the imbalance correction amount.By between rotor and block bearing, force cell being installed, the stressing conditions of measuring the rotor rotation process centre bearer is measured the size and Orientation of out-of-balance force.Present this method is mainly used on various dynamic balancing machines, and this method needs one to overlap more accurate and sensitive rocker system, is balanced rotor for support and makes it vibration-generating under out-of-balance force.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, so its measuring accuracy has been subject to certain restriction.The vibration of (3) measuring supporting comes the imbalance correction amount.Bearing seat horizontal and vertical direction placement sensor at supporting rotor, at first measure original unbalance in the vibration values of measurement point, then rotor is tried to increase the weight of and measure the vibration displacement amount that examination increases the weight of rear bearing block, come imbalance correction power by calculating influence coefficient.The method is a kind of off-line balancing method, needs examination to increase the weight of just can complete the correction of out-of-balance force, and the counterweight size needs to determine by rule of thumb.
Summary of the invention
The invention provides the rotation parts dynamic balance method based on strain.
In order to solve the problems of the technologies described above, adopt following technical scheme:
A kind of rotation parts dynamic balance method based on strain completes by the strain that test is rotated in the parts rotary course disequilibrium regulating that rotates parts.
The above-mentioned rotation parts dynamic balance method based on strain is characterized in that: comprise the steps:
A, rotation parts to be measured are arranged on transient equilibrium by universal joint detect on stand;
B, detect in transient equilibrium on the shaft part of stand eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, with this benchmark as the synchronous integer-period sampled analysis of multi-measuring point;
C, select two to measure the cross section strain measuring points are installed on the rotating shaft surface that transient equilibrium detects stand, measure between two block bearings that the cross section lays respectively at two gimbal couplings connecting the rotation parts and transient equilibrium detection stand for these two, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on the same bus with keyway, and another group foil gauge is positioned at clockwise fast direction and becomes the position of 90 ° with keyway;
D, the rotating shaft that detects stand with the driven by motor transient equilibrium are rotated under rotation speed n, record the strain value of respectively organizing the strain measuring point in rotary course, are designated as respectively: ε
1x(t), ε
1y(t), ε
2x(t), ε
2y(t), wherein, the cross section numbering is measured in subscript 1,2 representatives, and x, y represent the strain of two groups of different directions;
E, set up fixedly rectangular coordinate system, the y axle of this fixed coordinate system is the arranged direction of eddy current sensor, and the x axle is that clockwise speed becomes the direction of 90 ° with keyway, and the strain value in the rotary course of measurement is converted to 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 that first strain of measuring the cross section is at the axial component of x, ε
1 ⊥Represent that first strain of measuring the cross section is at the axial component of y, ε
2-Represent that second strain of measuring the cross section is at the axial component of x, ε
2 ⊥Represent that second strain of measuring the cross section is at the axial component of y;
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, and t is the time.
F, according to the strain value under fixed coordinate system, reference axis is to measure the moment of flexure of cross section on x direction of principal axis and y direction of principal axis in rotary course respectively:
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 moment of flexure of measurement cross section on the x direction of principal axis, M
1 ⊥Represent first moment of flexure of measurement cross section on the y direction of principal axis, M
2-Represent that second is measured the moment of flexure of cross section on the x direction of principal axis, M
2 ⊥Represent that second is measured the moment of flexure of cross section on the y direction of principal axis, 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 two shearing Q that measure cross section horizontal directions and vertical direction of cross section calculation of Bending Moment according to two
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)=M
1-(t)/l
1 Q
1⊥(t)=M
1⊥(t)/l
1
Q
2-(t)=M
2-(t)/l
2 Q
2⊥(t)=M
2⊥(t)/l
2 （3）
In formula, l
1, l
2Be the distance of bearing supporting power to the measurement cross section;
H, two poor Δ Q of shearing that measure on cross section horizontal directions and vertical direction of calculating
-(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 big or small G=mr ω of this out-of-balance force
2, r is rotor radius;
According to analyzing as can be known, above-mentioned shearing is poor is the component that acts in out-of-balance force G rotary course on horizontal direction and 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 on horizontal direction and vertical direction just 90 ° of phasic differences mutually in theory, the present invention is take the horizontal direction curve of shearing force as example;
The amplitude of the curve of shearing force is the size of out-of-balance force, so 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, namely with the keyway POS INT, reverse fast direction and become the angle of α size with keyway;
This out-of-balance force component in the horizontal direction is one to do in time the curve of sinusoidal variations, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of out-of-balance force before fixed coordinate system x spindle guide, can be determined by angle pulse starting point first crest to level to the out-of-balance force curve;
Therefore, the phase place α of out-of-balance force is: α=θ-90 °.
K, increase the weight of determining of weight and phase place:
According to above-mentioned calculating as can be known, in order to proofread and correct this amount of unbalance, weight m and the phase beta that need increase the weight of are respectively:
Angle beta is defined as: with the keyway POS INT, reverse fast direction and become 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, the shearing on horizontal direction and vertical direction, M curve, theoretical difference is only to differ 90 °, thus in the present invention take horizontal direction as example research, 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 distributions, and the rotor shaft elastic deformation is different, and each point strain and stress distribution situation is different, therefore, by measuring the rotating shaft strain, just might identify the size and Orientation of rotor unbalance power.Compared with prior art, the present invention has following advantage:
(1) this method need not test mass, can directly calculate the required size that increases the weight of and angle by strain data, require the transient equilibrium theoretical level grasped lower, be applicable to all technician.
(2) this method is a kind of on-line dynamic balancing method, has the characteristics such as quick and easy, can realize parts dynamic balancing technics batched operation.
Description of drawings
Fig. 1 detects the stand sketch;
In figure, 1 is block bearing, and 2 are the strain measuring point, and 3 is gimbal coupling, and 4 is rotation parts to be measured, and 5 is eddy current sensor, and 6 is keyway, and 7 is the flexible universal joint shaft coupling, and 8 is motor;
Fig. 2 is shaft part foil gauge viewpoint definition of living in and fixed coordinate system schematic diagram, 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 axle 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 the pulse starting point to level to the schematic diagram of the angle θ of first crest of the curve of shearing force;
Fig. 7 is this out-of-balance force correction method process flow diagram.
Embodiment
The present embodiment is take rotation parts test-bed shown in Figure 1 as example, analyzes based on the rotor unbalance bearing calibration that strain is carried out.With reference to Fig. 2～7.
The method of completing rotation parts disequilibrium regulating by monitor strain that the present embodiment relates to is:
A, rotation parts to be measured are arranged on transient equilibrium by universal joint detect on stand;
B, detect in transient equilibrium on the shaft part of stand eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, with this benchmark as the synchronous integer-period sampled analysis of multi-measuring point;
C, select two to measure the cross section strain measuring points are installed on the rotating shaft surface that transient equilibrium detects stand, measure between two block bearings that the cross section lays respectively at two gimbal couplings connecting the rotation parts and transient equilibrium detection stand for these two, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on the same bus with keyway, another group foil gauge is positioned at clockwise fast direction and becomes the position of 90 ° with keyway, as shown in Figure 2;
D, the rotating shaft that detects stand with the driven by motor transient equilibrium are rotated under rotation speed n, record the strain value of respectively organizing the strain measuring point in rotary course, are designated as respectively: ε
1x(t), ε
1y(t), ε
2x(t), ε
2y(t), wherein, the cross section numbering is measured in subscript 1,2 representatives, and x, y represent the strain of two groups of different directions;
E, set up fixedly rectangular coordinate system, the y axle of this fixed coordinate system is the arranged direction of eddy current sensor, and the x axle is that clockwise speed becomes the direction of 90 ° with keyway, and the strain value in the rotary course of measurement is converted to 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 that first strain of measuring the cross section is at the axial component of x, ε
1 ⊥Represent that first strain of measuring the cross section is at the axial component of y, ε
2-Represent that second strain of measuring the cross section is at the axial component of x, ε
2 ⊥Represent that second strain of measuring the cross section is at the axial component of y;
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, and t is the time.
F, according to the strain value under fixed coordinate system, reference axis is to measure the moment of flexure of cross section on x direction of principal axis and y direction of principal axis in rotary course respectively:
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 moment of flexure of measurement cross section on the x direction of principal axis, M
1 ⊥Represent first moment of flexure of measurement cross section on the y direction of principal axis, M
2-Represent that second is measured the moment of flexure of cross section on the x direction of principal axis, M
2 ⊥Represent that second is measured the moment of flexure of cross section on the y direction of principal axis, 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 two shearing Q that measure cross section horizontal directions and vertical direction of cross section calculation of Bending Moment according to two
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)=M
1-(t)/l
1 Q
1⊥(t)=M
1⊥(t)/l
1
Q
2-(t)=M
2-(t)/l
2 Q
2⊥(t)=M
2⊥(t)/l
2 （3）
In formula, l
1, l
2To the distance of measuring the cross section, when practical application, moment of flexure shearing reduction coefficient can be demarcated according to architectural characteristic and other factors for the bearing supporting power;
H, two poor Δ Q of shearing that measure on cross section horizontal directions and vertical direction of calculating
-(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 big or small G=mr ω of this out-of-balance force
2, r is rotor radius;
According to analyzing as can be known, above-mentioned shearing is poor is the component that acts in out-of-balance force G rotary course on horizontal direction and 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 on horizontal direction and vertical direction just 90 ° of phasic differences mutually in theory, the present invention is take the horizontal direction curve of shearing force as example;
The amplitude of the curve of shearing force is the size of out-of-balance force, so 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, namely with the keyway POS INT, reverse fast direction and become the angle of α size with keyway, as shown in Figure 3;
This out-of-balance force component in the horizontal direction is one to do in time the curve of sinusoidal variations, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of out-of-balance force before fixed coordinate system x spindle guide, can be determined by angle pulse starting point first crest to level to the 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 determining of weight and phase place:
According to above-mentioned calculating as can be known, in order to proofread and correct this amount of unbalance, weight m and the phase beta that need increase the weight of are respectively:
Angle beta is defined as: with the keyway POS INT, reverse fast direction and become the angle of β size with keyway.
Claims (2)
1. the rotation parts dynamic balance method based on strain, is characterized in that: complete by the strain that test is rotated in the parts rotary course disequilibrium regulating that rotates parts.
2. the rotation parts dynamic balance method based on strain as claimed in claim 1, is characterized in that: comprise the steps:
A, rotation parts to be measured are arranged on transient equilibrium by universal joint detect on stand;
B, detect in transient equilibrium on the shaft part of stand eddy current sensor is installed, eddy current sensor is aimed at keyway, measure rotational speed pulse signal, with this benchmark as the synchronous integer-period sampled analysis of multi-measuring point;
C, select two to measure the cross section strain measuring points are installed on the rotating shaft surface that transient equilibrium detects stand, measure between two block bearings that the cross section lays respectively at two gimbal couplings connecting the rotation parts and transient equilibrium detection stand for these two, two groups of foil gauges need be arranged in each cross section, wherein one group of foil gauge should be on the same bus with keyway, and another group foil gauge is positioned at clockwise fast direction and becomes the position of 90 ° with keyway;
D, the rotating shaft that detects stand with the driven by motor transient equilibrium are rotated under rotation speed n, record the strain value of respectively organizing the strain measuring point in rotary course, be designated as respectively: ε 1x (t), ε 1y (t), ε 2x (t), ε 2y (t), wherein, the cross section numbering is measured in subscript 1,2 representatives, and x, y represent the strain of two groups of different directions;
E, set up fixedly rectangular coordinate system, the y axle of this fixed coordinate system is the arranged direction of eddy current sensor, and the x axle is that clockwise speed becomes the direction of 90 ° with keyway, and the strain value in the rotary course of measurement is converted to strain value under fixed coordinate system, is designated as ε
1-(t), e
1 ⊥(t), ε
2-(t), ε
2 ⊥(t), wherein, ε
1-Represent that first strain of measuring the cross section is at the axial component of x, ε
1 ⊥Represent that first strain of measuring the cross section is at the axial component of y, ε
2-Represent that second strain of measuring the cross section is at the axial component of x, ε
2 ⊥Represent that second strain of measuring the cross section is at the axial component of y;
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, and t is the time
F, according to the strain value under fixed coordinate system, reference axis is to measure the moment of flexure of cross section on x direction of principal axis and y direction of principal axis in rotary course respectively:
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 moment of flexure of measurement cross section on the x direction of principal axis, M
1 ⊥Represent first moment of flexure of measurement cross section on the y direction of principal axis, M
2-Represent that second is measured the moment of flexure of cross section on the x direction of principal axis, M
2 ⊥Represent that second is measured the moment of flexure of cross section on the y direction of principal axis, 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 two shearing Q that measure cross section horizontal directions and vertical direction of cross section calculation of Bending Moment according to two
1-(t), Q
2-(t), Q
1 ⊥(t), Q
2 ⊥(t);
Q
1-(t)=M
1-(t)/l
1 Q
1⊥(t)=M
1⊥(t)/l
1
Q
2-(t)=M
2-(t)/l
2 Q
2⊥(t)=M
2⊥(t)/l
2 （3）
In formula, l
1, l
2Be the distance of bearing supporting power to the measurement cross section;
H, two poor Δ Q of shearing that measure on cross section horizontal directions and vertical direction of calculating
-(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 big or small G=mr ω of this out-of-balance force
2, r is rotor radius;
According to analyzing as can be known, above-mentioned shearing is poor is the component that acts in out-of-balance force G rotary course on horizontal direction and 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, so 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, namely with the keyway POS INT, reverse fast direction and become the angle of α size with keyway;
This out-of-balance force component in the horizontal direction is one to do in time the curve of sinusoidal variations, according to level to out-of-balance force curve and pulse respond, determine angle θ, θ is the angle of out-of-balance force before fixed coordinate system x spindle guide, can be determined by angle pulse starting point first crest to level to the out-of-balance force curve;
Therefore, the phase place α of out-of-balance force is: α=θ-90 °;
K, increase the weight of determining of weight and phase place:
According to above-mentioned calculating as can be known, in order to proofread and correct this amount of unbalance, weight m and the phase beta that need increase the weight of are respectively:
Angle beta is defined as: with the keyway POS INT, reverse fast direction and become the angle of β size with keyway.
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