CN110926700A - Dynamic balance correction method and automation equipment using same - Google Patents
Dynamic balance correction method and automation equipment using same Download PDFInfo
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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 imbalance
- G01M1/32—Compensating imbalance by adding material to the body to be tested, e.g. by correcting-weights
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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
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
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Abstract
A dynamic balance correction method includes the steps of rotating a main shaft to a rotating speed omega to obtain a vibration amplitude b of the main shaft, enabling a relation between an unbalanced mass α and a vibration amplitude A of a rotor to be k α + b, installing the rotor on the main shaft, rotating the rotating component to the rotating speed omega, and obtaining an initial vibration amplitude A0(ii) a Respectively installing a test weight block with mass m on a first position and a second position of the rotor, wherein the clockwise angles between the test weight block and the standard line are 0 degree and 180 degrees, and respectively obtaining corresponding first vibration amplitude A when the rotating component rotates to the rotating speed omega1And a second vibration amplitude A2Calculating the mass of balancing weight α0And a fourth position in which it is mounted on the rotor; the balancing weight is installed on the rotor to adjust the dynamic balance of the rotor. The method considers the factors of unbalance caused by unbalanced mass generated by the coupling of the main shaft, the rotor and the main shaft, and has high correction efficiency and precision. The invention also provides an automatic device using the methodAnd (4) preparing.
Description
Technical Field
The invention relates to a dynamic balance correction method.
Background
The rotor generates unbalanced forces when rotating due to the fact that the center of gravity of the rotor deviates from the axis, so that the phenomenon of rotor system vibration is caused, and mechanical failure is caused when the phenomenon is serious. The rotor is generally installed on the main shaft, and the unbalance amount of the rotor and the coupling unbalance between the rotor and the main shaft cause the rotor to vibrate during working. The dynamic balance is corrected by changing the mass distribution of the rotor so that its center of gravity is returned to the axis to eliminate the imbalance. The dynamic balance correction is generally carried out at the stage of rotor production and manufacturing, or under the actual working conditions after the rotor is installed on site.
However, in actual operation, in order to simplify the correction process, only the factor of vibration caused by the unbalance of the rotor itself is considered, and the influence of unbalance coupling between the rotor and the main shaft is ignored, which results in the reduction of correction accuracy. In addition, when performing dynamic balance correction, the magnitude and position of the unbalance amount need to be determined to perform correction. At present, a vibration sensor is required to be installed on equipment to be corrected to measure a vibration signal and a phase discrimination sensor is required to measure a vibration deflection angle, the installation and adjustment of the phase discrimination sensor are time-consuming, the correction efficiency is not high, and the cost is high.
Disclosure of Invention
In view of the above, it is desirable to provide a dynamic balance calibration method with high efficiency, simple operation and low cost.
A dynamic balance correction method for correcting an imbalance of a rotating member including a main shaft and a rotor mounted to the main shaft, the balance correction method comprising:
rotating the main shaft to a rotating speed omega to obtain a vibration amplitude b of the main shaft;
establishing an unbalance relation formula, wherein the rotating component has an unbalance mass α, and the relation between the unbalance mass α and the vibration amplitude A of the rotating component is represented by a coefficient k, wherein A is k α + b;
mounting the rotor on the main shaft, rotating the rotating component to a rotating speed omega, and obtaining the initial vibration amplitude A of the rotating component0；
Stopping the rotation of the rotating component, respectively installing a test weight block with mass m at a first position and a second position on the rotor, and respectively obtaining a corresponding first vibration amplitude A when the rotating component rotates to the rotating speed omega1And a second vibration amplitude A2；
A standard line is arranged on the cross section of the rotor, the standard line is a radius line passing through the center of a vertical line of the center of the rotor, the clockwise angles between the connecting line of the first position and the second position with the center of the rotor and the standard line are 0 degree and 180 degrees respectively, and the distances from the first position and the second position to the center of the rotor are r respectively;
the mass α of the counterweight needed for dynamic balance correction is calculated by the following formula0The fourth position is arranged on the rotor, the distance from the fourth position to the center of the rotor is r, and the clockwise angle between the connecting line of the fourth position and the center of the rotor and the standard line is gamma;
the coefficient k satisfies:
mass α0Satisfies the following conditions:
the angle γ satisfies:
and mounting the balancing weight on a fourth position of the rotor to adjust the dynamic balance of the rotor.
Further, the rotor is installed on the main shaft, the rotating component is rotated to a rotating speed omega, and the initial vibration amplitude A of the rotating component is obtained0After the step (2), further comprising: given the permissible vibration amplitude A of the rotormaxWhen judging the initial vibration amplitude A0Less than or equal to the allowable vibration amplitude AmaxAnd ending, otherwise, carrying out dynamic balance correction on the rotor.
Further, the rotation speed ω is a rated rotation speed at which the rotor operates.
Further, the step of installing the weight block at a sixth position of the rotor to adjust the dynamic balance of the rotor includes:
removing the weight block, and setting the allowable vibration amplitude A of the rotor vibrationmax；
Mounting the balancing weight on the rotor at one of the two solved angles gamma, and obtaining a third vibration amplitude A when the rotor rotates to the rotating speed omega3When the third vibration amplitude A3Not greater than the allowable vibration amplitude AmaxWhen the correction is finished, the correction is finished; otherwise, the balancing weight is installed on the rotor at the other angle of the two solved angles gamma to perform dynamic balance correction on the rotor. The invention also provides an automatic device and a bagThe dynamic balance correction method comprises a driving part and a rotating part, wherein the rotating part comprises a main shaft and a rotor arranged on the main shaft, the main shaft is connected with the driving part, the driving part drives the main shaft to rotate and drives the rotor to rotate, and the dynamic balance of the rotating part is adjusted by the dynamic balance correction method.
Further, the rotor is provided with a plurality of mounting holes, and the distances from the mounting holes to the center of the rotor are the same.
Further, the automation equipment also comprises a balancing weight, and the mass of the balancing weight is α0And the balancing weight is connected to the mounting hole on the rotor corresponding to the fourth position.
Further, the mounting hole is a threaded hole, a threaded portion is convexly formed in the balancing weight, and the threaded portion is in threaded connection with the mounting hole.
Further, the automation equipment further comprises a data processing mechanism, the data processing mechanism comprises a sensor, an acquisition card and a processor, and the sensor measures the initial vibration amplitude A of the rotating component by the dynamic balance correction method0The first vibration amplitude A1And the second vibration amplitude A2The acquisition card is connected with the sensor and the processor, the acquisition card is used for acquiring vibration signals measured by the sensor and transmitting the vibration signals to the processor, and the processor processes the vibration signal data acquired by the acquisition card by the dynamic balance correction method.
Compared with the prior art, the dynamic balance correction method provided by the invention has the advantages that the vibration amplitude b of the main shaft without the rotor is measured, the unbalance generated by the main shaft is taken into consideration, the test weight blocks with the same mass are arranged on the rotor at 0 degree and 180 degrees, and three vibration amplitudes are obtained: the initial vibration amplitude A0The first vibration amplitude A1And the second vibration amplitude A2Calculating and solving a coefficient k, and correcting the unbalance amount generated by the rotor and the unbalance amount generated by the coupling of the rotor and the main shaft by taking the unbalance amount into accountThe positive accuracy is high. The size and the position of the balancing weight required by correction can be calculated by trial weighing twice, the quality and the mounting position of the balancing weight required by correction can be solved by measuring the vibration amplitude of the rotor, a phase discrimination sensor is not needed, the correction structure is simplified, the cost is reduced, and the method has the advantages of simple process, easiness in implementation, wide applicability, high correction efficiency and high precision.
Drawings
Fig. 1 is a perspective view of an automated apparatus according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view of the automated apparatus shown in FIG. 1 taken along line II-II.
FIG. 3 is a flow chart of dynamic balance correction according to the present invention.
Fig. 4A, 4B and 4C are exploded views of the mass vectors in the dynamic balance correction step of the present invention.
Description of the main elements
Bearing 13
Driving member 15
Data processing means 20
Screw part 31
The following detailed description will further illustrate the invention in conjunction with the above-described figures.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that when one component is referred to as being "connected" to another component, it can be directly connected to the other component or intervening components may also be present. When a component is referred to as being "disposed on" another component, it can be directly on the other component or intervening components may also be present.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
Some embodiments of the invention are described in detail below with reference to the accompanying drawings. In the following embodiments, features of the embodiments may be combined with each other without conflict.
Referring to fig. 1 and fig. 2, an embodiment of the dynamic balance calibration method according to the present invention is applied to dynamic balance of a rotating component in an automation apparatus 100. The automation device 100 comprises a rotation mechanism 10, a data processing mechanism 20 and a counterweight 30. The rotary mechanism 10 includes a bearing housing 11, a bearing 13, a driver 15, and a rotary member. The rotating parts comprise a main shaft 17 and a rotor 19. The bearing 13 is disposed in the bearing housing 11. The main shaft 17 is rotatably inserted through the bearing 13. The driving member 15 is disposed on the bearing seat 11 and connected to the main shaft 17. The driving member 15 is used for driving the main shaft 17 to rotate. The rotor 19 is disposed on the main shaft 17 and rotates synchronously with the main shaft 17. The rotor 19 is collinear with the central axis of rotation of the main shaft 17.
The data processing means 20 comprises a sensor 21, an acquisition card 23 and a processor 25. The sensor 21 is disposed on the outer peripheral wall of the bearing housing 11 and is configured to measure vibration signals of the spindle 17 and the rotor 19. In an embodiment, the sensor 21 is fixed to the bearing seat 11 by a magnetic attraction method, but not limited thereto. The acquisition card 23 is electrically connected to the sensor 21, and is configured to acquire the vibration signal and transmit the vibration signal to the processor 25. The processor 25 is configured to analyze the signal data collected by the acquisition card 23 to obtain the mass of the counterweight 30 and the mounting position thereof on the rotor 19 for correcting the imbalance.
In one embodiment, the rotor 19 is a grinding wheel, and the rotor 19 is a substantially circular cylinder, but not limited thereto. For example, in other embodiments, the rotor 19 may be configured as a milling cutter, a drill, a mounting seat for adapter, or the like.
The rotor 19 is provided with a plurality of mounting holes 191. The centers of the plurality of mounting holes 191 are spaced apart from the central axis of the rotor 19 during rotation. In an embodiment, the plurality of mounting holes 191 are uniformly distributed on an end surface of the rotor 19 facing away from the main shaft 17, but not limited thereto. For example, in other embodiments, the mounting holes 191 may be disposed on the circumferential surface of the rotor 19. And selecting a matched balancing weight 30 according to the mass of the balancing weight analyzed by the processor 25, and installing the balancing weight 30 in the corresponding installation hole 191 of the rotor 19 according to the installation position analyzed by the processor 25.
In one embodiment, the mounting holes 191 are threaded hole structures, but not limited thereto. The weight 30 is provided with a threaded portion 31, and the threaded portion 31 can be screwed with the mounting hole 191 to fix the weight 30 to the rotor 19.
Referring to fig. 3, the purpose of the dynamic balance correction method is to obtain the mass of the weight 30 required for dynamic balance adjustment and the installation position of the weight 30 on the rotor 19. The dynamic balance correction method comprises the following steps:
step 1, rotating the main shaft 17 to a rotation speed omega to obtain a vibration amplitude b of the main shaft 17.
Rotating the main shaft 17 to the rotational speed ω when the main shaft 17 is not mounted with the rotor 19. The sensor 21 measures the vibration amplitude b of the spindle 17.
Step 2, establishing an unbalance relation formula, wherein the rotating part has unbalance
The unbalance amount
Is an unbalanced mass α. the unbalance amount
The relationship with the vibration amplitude a of the rotating member is represented by a coefficient k as:
and 3, mounting the rotor 19 on the main shaft 17, and rotating the rotating component to the rotating speed omega. The sensor 21 measures the initial vibration amplitude A of the rotating component0。
Stopping the rotation of the main shaft 17, installing the rotor 19 on the main shaft 17, and when the main shaft 17 and the rotor 19 rotate synchronously to the rotation speed ω, the rotating component generates an initial unbalance amount
The initial unbalance amount
With an initial vibration amplitude A0The relationship of (1) is:
wherein, α0Is an initial unbalanced mass and is equal to the initial imbalanceBalance weight
The die of (1).
In an embodiment, the rotation speed ω is a rated rotation speed of the main shaft 17 and the rotor 19, but is not limited thereto.
A standard line is provided on the cross section of the rotor 19, and the standard line is a radius line above the center of a vertical line passing through the center of the rotor 19.
Step 4, giving the permissible vibration amplitude A of the rotor 19maxWhen judging the initial vibration amplitude A0Less than or equal to the allowable vibration amplitude AmaxAnd ending, otherwise, carrying out counterweight to dynamically balance the rotor 19.
If the initial vibration amplitude A0Less than or equal to the allowable vibration amplitude AmaxThe rotor 19 can be used normally. If the initial vibration amplitude A0Greater than the allowable vibration amplitude AmaxThen the rotor 19 needs to be calibrated to achieve dynamic balance.
Step 5, stopping the rotation of the rotating component, respectively installing a test weight block with mass m at a first position and a second position on the rotor 19, and respectively obtaining a corresponding first vibration amplitude A when the rotating component rotates to the rotating speed omega1And a second vibration amplitude A2. The clockwise angles between the connecting lines of the first position and the second position with the center of the rotor 19 and the standard line are 0 degree and 180 degrees respectively, and the distances from the connecting lines to the center of the rotor 19 are r respectively. The method comprises the following specific steps:
and step 51, stopping rotating the rotating component, and installing a test weight block with mass m at a first position on the rotor 19. The line connecting the first position with the centre of the rotor 19 is at an angle of 0 ° clockwise to the standard line. When the rotating component is rotated to the rotating speed omega, the rotating component generates a first unbalance amount
The sensor 21 measures a first vibration amplitude of the rotating componentA1。
First unbalance amount
Is modeled as a first unbalanced mass α1. First unbalance amount
And a first vibration amplitude A1The relationship of (1) is:
and step 52, stopping rotating the rotating component, and installing a test weight block with the mass m at a second position on the rotor 19. The line connecting the second position with the centre of the rotor 19 is at an angle of 180 ° clockwise to the standard line. When the rotating member is rotated to the rotational speed ω, the rotor 19 generates a second unbalance amount
The sensor 21 measures a second vibration amplitude A of the rotating component2。
Second amount of unbalance
Is modeled as a second unbalanced mass α2. Second amount of unbalance
And a second vibration amplitude A2The relationship of (1) is:
in one embodiment, the first position and the second position are respectively corresponding mounting holes 191 of the rotor 19.
Step 6, the processor 25 calculates the initial vibration amplitude A0The first vibration amplitude A1The secondAmplitude of vibration A2And the mass m of the weight block, and calculating to obtain an initial balance mass α0And initial unbalance amount
In a third position of the rotor 19. The clockwise angle of the line connecting the third position and the center of the rotor 19 and the standard line is marked as theta.
Fig. 4A is a vector exploded view of the unbalance amount of the rotating member itself. Fig. 4B and 4C are vector exploded views of the amount of unbalance of the rotating member when the weight is mounted on the rotor 19 in the first position and the second position, respectively.
Referring to fig. 4A, fig. 4B and fig. 4C, the following can be obtained by applying the vector synthesis and decomposition principle:
computing
The following equation can be obtained:
equation 1:
equation 2:
equation 3:
from equation 2 and equation 3, equation 4 can be obtained:
from equation 1 and equation 4, equation 5 can be obtained:
the coefficient k is found according to equation 5:
from equation 2 and equation 3, equation 6 can be obtained:
α is obtained according to equation 6y：
The initial imbalance mass α is calculated0And the angle θ is:
obviously, the angle θ can take values within (0, 360 °), and thus, there are two solutions to the angle θ, which are θ1And theta2。
The initial imbalance α calculated0The amount is the desired mass of the weight 30.
Step 7, removing the weight block and installing α mass0In a fourth position of the rotor 19. The clockwise angle γ between the center line of the fourth position and the rotor 19 and the standard line satisfies:
the angle gamma has two values corresponding to the angle theta, each being gamma1＝180+θ1And gamma2＝180+θ2。
Step 71, removing the weight 30 with mass m at the first position at an angle γ1The mass of addition is α0Starting the rotor 19 to a rotational speed ω, and measuring a third vibration amplitude a of the rotor 19 by the sensor 213。
At step 72, processor 25 determines a third vibration amplitude A3And allowable vibration amplitude AmaxThe size of (2). If the third vibration amplitude A3Less than or equal to the allowable vibration amplitude AmaxThen the dynamic balance of the correction rotor 19 is completed, otherwise step 73 is entered.
In step 73, processor 25 determines a third vibration amplitude A3Greater than the allowable vibration amplitude AmaxAt an angle of gamma on the rotor 192Has an installation mass of α0And a weight member 30.
It will be appreciated that the weight blocks and the weight block 30 may be selected from a plurality of different mass block-like structural components.
Compared with the prior art, the dynamic balance correction method provided by the invention takes the unbalance generated by the main shaft 17 into account by measuring the vibration amplitude b when the rotor 19 is not installed on the main shaft 17, andby mounting test weight blocks of the same mass at 0 ° and 180 ° on the rotor 19, three vibration amplitudes were obtained: the initial vibration amplitude A0The first vibration amplitude A1And the second vibration amplitude A2And calculating and solving the coefficient k, and taking the unbalance generated by the rotor 19 and the unbalance generated by the coupling of the rotor 19 and the main shaft 17 into consideration, the correction accuracy is high. The size and the position of the balancing weight required by correction can be calculated by trial weighing twice, the mass and the mounting position of the balancing weight 30 required by correction can be calculated by measuring the vibration amplitude of the rotor 19, a phase discrimination sensor is not needed, the correction structure is simplified, the cost is reduced, and the method has the advantages of simple process, easy realization, wide applicability, high correction efficiency and high precision.
Although the present invention has been described in detail with reference to the preferred embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted without departing from the spirit and scope of the invention. Those skilled in the art can also make other changes and the like in the design of the present invention within the spirit of the present invention as long as they do not depart from the technical effects of the present invention. Such variations are intended to be included within the scope of the invention as claimed.
Claims (9)
1. A dynamic balance correction method for correcting an imbalance of a rotating member including a main shaft and a rotor mounted to the main shaft, the balance correction method comprising:
rotating the main shaft to a rotating speed omega to obtain a vibration amplitude b of the main shaft;
establishing an unbalance relation formula, wherein the rotating component has an unbalance mass α, and the relation between the unbalance mass α and the vibration amplitude A of the rotating component is represented by a coefficient k, wherein A is k α + b;
mounting the rotor on the spindle, rotating the rotary member to a rotational speed omega, obtaining the rotary memberInitial vibration amplitude A0；
Stopping the rotation of the rotating component, respectively installing a test weight block with mass m at a first position and a second position on the rotor, and respectively obtaining a corresponding first vibration amplitude A when the rotating component rotates to the rotating speed omega1And a second vibration amplitude A2；
A standard line is arranged on the cross section of the rotor, the standard line is a radius line passing through the center of a vertical line of the center of the rotor, the clockwise angles between the connecting line of the first position and the second position with the center of the rotor and the standard line are 0 degree and 180 degrees respectively, and the distances from the first position and the second position to the center of the rotor are r respectively;
the mass α of the counterweight needed for dynamic balance correction is calculated by the following formula0The fourth position is arranged on the rotor, the distance from the fourth position to the center of the rotor is r, and the clockwise angle between the connecting line of the fourth position and the center of the rotor and the standard line is gamma;
the coefficient k satisfies:
mass α0Satisfies the following conditions:
the angle γ satisfies:
and mounting the balancing weight on a fourth position of the rotor to adjust the dynamic balance of the rotor.
2. The dynamic balance correction method according to claim 1, wherein in said mounting of said rotor to said main shaft, said rotating member is rotated to a rotation speed ω,obtaining an initial vibration amplitude A of the rotating component0After the step (2), further comprising: given the permissible vibration amplitude A of the rotormaxWhen judging the initial vibration amplitude A0Less than or equal to the allowable vibration amplitude AmaxAnd ending, otherwise, carrying out dynamic balance correction on the rotor.
3. The dynamic balance correction method of claim 1, wherein the rotation speed ω is a rated rotation speed at which the rotor operates.
4. The method of claim 1, wherein the step of mounting the weight at a sixth position of the rotor to adjust the dynamic balance of the rotor comprises:
removing the weight block, and setting the allowable vibration amplitude A of the rotor vibrationmax；
Mounting the balancing weight on the rotor at one of the two solved angles gamma, and obtaining a third vibration amplitude A when the rotor rotates to the rotating speed omega3When the third vibration amplitude A3Not greater than the allowable vibration amplitude AmaxWhen the correction is finished, the correction is finished; otherwise, the balancing weight is installed on the rotor at the other angle of the two solved angles gamma to perform dynamic balance correction on the rotor.
5. An automation device comprising a drive member and a rotary member, said rotary member comprising a main shaft and a rotor mounted on said main shaft, said main shaft being connected to said drive member, said drive member driving said main shaft in rotation and said rotor in rotation, characterized in that the dynamic balance of said rotary member is adjusted by a dynamic balance correction method as claimed in any one of claims 1 to 4.
6. The automated apparatus of claim 5, wherein the rotor is provided with a plurality of mounting holes, the plurality of mounting holes being located at the same distance from a center of the rotor.
7. The automated apparatus of claim 6, further comprising a clump weight having a mass of α0And the balancing weight is connected to the mounting hole on the rotor corresponding to the fourth position.
8. The automated apparatus of claim 7, wherein the mounting hole is a threaded hole, and the weight block is provided with a threaded portion protruding therefrom, the threaded portion being threadedly coupled to the mounting hole.
9. The automated apparatus of claim 5, further comprising a data processing mechanism comprising a sensor, an acquisition card and a processor, wherein the sensor measures the initial vibration amplitude A of the rotating component in a dynamic balance correction method as claimed in any one of claims 1 to 40The first vibration amplitude A1And the second vibration amplitude A2The acquisition card is connected with the sensor and the processor, the acquisition card is used for acquiring the vibration signal measured by the sensor and transmitting the vibration signal to the processor, and the processor processes the vibration signal data acquired by the acquisition card according to the dynamic balance correction method of any one of claims 1 to 4.
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| CN113237599A (en) * | 2021-06-07 | 2021-08-10 | 重庆大学 | Clamp suitable for dynamic balance compensation of asymmetric transmission shaft with radial structure |
| CN113280978A (en) * | 2021-05-31 | 2021-08-20 | 湖南汇力科技有限公司 | On-site dynamic balancing method for ultra-high-speed permanent magnet synchronous motor |
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| CN114279634A (en) * | 2021-12-22 | 2022-04-05 | 中船重工（上海）节能技术发展有限公司 | Dynamic balance correction method of wind power boosting rotor |
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