CN110926702A - 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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- CN110926702A CN110926702A CN201911085156.3A CN201911085156A CN110926702A CN 110926702 A CN110926702 A CN 110926702A CN 201911085156 A CN201911085156 A CN 201911085156A CN 110926702 A CN110926702 A CN 110926702A
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/30—Compensating unbalance
- G01M1/32—Compensating unbalance by adding material to the body to be tested, e.g. by correcting-weights
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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 unbalance
- G01M1/16—Determining unbalance by oscillating or rotating the body to be tested
Abstract
A dynamic balance correction method includes the steps that the relation between an unbalanced mass α and the vibration amplitude A of a rotor is that A is k α + b, the rotor rotates to a rotating speed omega, and the initial vibration amplitude A is obtained0(ii) a Respectively installing a test weight block with mass m on the rotor at a first position, a second position, a third position and a fourth position which respectively have clockwise angles of 0 degrees, 180 degrees, 90 degrees and 270 degrees with a standard line, and respectively obtaining corresponding first vibration amplitude A when the rotor rotates to a rotating speed omega1A second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4Calculating the mass of balancing weight α0And a sixth position where the weight is mounted on the rotor to adjust the dynamic balance of the rotor, wherein the method can correct the vibration amplitude of the rotor by measuring the vibration amplitude of the rotor, and the unbalanced mass α of the rotor is removed0Other imbalance-causing factors are consideredAnd the correction efficiency and accuracy are high. The invention also provides an automatic device using the method.
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 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.
When the dynamic balance correction is performed, the magnitude and position of the unbalance amount need to be determined for correction. Currently, the rotor is calibrated by a dynamic balance calibration instrument after being installed in the field. However, the field dynamic balance correction instrument obtains the vibration signal of the rotor through the vibration sensor to obtain the magnitude of the unbalance, and obtains the unbalanced angle position through the phase discrimination sensor, so that the vibration sensor and the phase discrimination sensor need to be installed on the equipment to be corrected, and if the equipment does not have a proper installation space, a jig needs to be additionally used for assisting installation. And the installation and adjustment of the phase discrimination sensor are time-consuming, the correction efficiency is not high, and in addition, the price of the special instrument is higher.
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 imbalance of a rotor, the balance correction method comprising:
establishing an unbalance relation formula, wherein the rotor has an unbalance mass α, and the relation between the unbalance mass α and the vibration amplitude A of the rotor is represented by a coefficient k and a constant b, wherein A is k α + b;
rotating the rotor to a rotating speed omega to obtain an initial vibration amplitude A of the rotor0；
Stopping the rotor from rotating, respectively installing a test weight block with the mass of m at a first position, a second position, a third position and a fourth position on the rotor, and respectively obtaining corresponding first vibration amplitude A when the rotor rotates to the rotating speed omega1A second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4；
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 connecting lines of the first position, the second position, the third position and the fourth position with the center of the rotor respectively have clockwise angles of 0 degree, 180 degrees, 90 degrees and 270 degrees with the standard line, and the distances from the first position, the second position, the third position and the fourth 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 sixth position is arranged on the rotor, the distance between the sixth position and the center of the rotor is r, and the clockwise angle between the connecting line of the sixth position and the center of the rotor and the standard line is gamma;
the constant b satisfies:
the coefficient k satisfies:
mass α0Satisfies the following conditions:
the angle γ satisfies:
and mounting the balancing weight on a sixth position of the rotor to adjust the dynamic balance of the rotor.
Further, the initial vibration amplitude A of the rotor is obtained when the rotor is rotated to the rotation speed omega0After 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 mounting the counterweight at a sixth position on the rotor to adjust the dynamic balance of the rotor includes determining a clockwise angle θ between a line connecting the unbalanced mass α and the center of the rotor and the standard line, wherein:
when A is3＞A4The angle θ satisfies: theta is more than 0 degree and less than 180 degrees; otherwise, the angle θ satisfies: theta is more than 180 degrees and less than 360 degrees; the angle gamma is equal to the determined angle gammaAn angle theta plus 180 DEG, said weight mounted on said rotor at said determined angle gamma to adjust the dynamic balance of said rotor.
The invention further provides automation equipment which comprises a driving piece and a rotor, wherein the rotor is connected with the driving piece, the driving piece is used for driving the rotor to rotate, and the dynamic balance of the rotor 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 sixth 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 rotor by the dynamic balance correction method0The first vibration amplitude A1The second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4The acquisition card is electrically connected with the sensor and the processor, and 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.
The invention further provides automation equipment which comprises a driving part, a main shaft and a rotor, wherein the driving part is connected with the main shaft and used for driving the main shaft to rotate, the rotor is arranged on the main shaft, and the dynamic balance of the rotor is adjusted by the dynamic balance correction method.
Compared with the prior art, the dynamic balance correction method provided by the invention respectively uses four times of correction on the rotor 19The test weight blocks with the same quality are installed at 0 degrees, 180 degrees, 90 degrees and 270 degrees, and five vibration amplitudes are obtained: the initial vibration amplitude A0The first vibration amplitude A1The second vibration amplitude A2The third vibration amplitude A3And the fourth vibration amplitude A4And a constant b is determined, except for the unbalanced mass α of the rotor 19 itself0Besides other factors causing unbalance, the correction accuracy is high. And the mass and the mounting position of the balancing weight 30 required by correction can be obtained only by measuring the vibration amplitude of the rotor 19, a phase discrimination sensor is not needed, the correction structure is simplified, and the cost is reduced.
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, 4C, 4D and 4E are schematic diagrams of vector decomposition of the unbalance amount in the dynamic balance correction step according to 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, one embodiment of the dynamic balance calibration method of the present invention is used to adjust the dynamic balance of a rotor of 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 comprises a support 11, a bearing 13, a drive 15, a main shaft 17 and a rotor 19. The bearing 13 is disposed in the support 11. The main shaft 17 is rotatably inserted through the bearing 13. The driving member 15 is disposed on the supporting member 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 support 11 and is configured to measure vibration signals of the spindle 17 and the rotor 19. In an embodiment, the sensor 21 is magnetically fixed to the supporting member 11, 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 by the same distance. 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, establishing an unbalance relation formula, wherein the unbalance amount exists in the rotor 19
The unbalance amount
Is an unbalanced mass α. the unbalance amount
The relationship with the vibration amplitude a of the rotor 19 is expressed by a coefficient k and a constant b as:
step 2, rotating the rotor 19 to a rotational speed ω. The sensor 21 measures the initial vibration amplitude a of the rotor 190。
In the initial state, the rotor 19 itself generates an initial unbalance
The initial unbalance amount
With an initial vibration amplitude A0The relationship of (1) is:
wherein, α0Is the initial unbalance amount and is equal to the initial unbalance amount
The die of (1).
In an embodiment, the rotation speed ω is a rated rotation speed of 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 3, 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 dynamic balance correction on the rotor 19.
If the initial vibration amplitude A0Less than or equal to the allowable vibration amplitude AmaxIndicating that the rotor 19 does not need to be corrected and that the rotor 19 can be used normally. The initial vibration amplitude A0Greater than the allowable vibration amplitude AmaThen it indicates that the rotor 19 needs to be corrected to achieve dynamic balance, and the subsequent correction step 4 is entered.
Step 4, stopping the rotation of the rotor 19, respectively installing a test weight block with mass m at a first position, a second position, a third position and a fourth position on the rotor 19, and respectively obtaining a corresponding first vibration amplitude A when the rotor 19 rotates to the rotation speed omega1A second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4. The clockwise angles of the connecting lines of the first position, the second position, the third position and the fourth position with the center of the rotor 19 and the standard line are 0 degree, 180 degree, 90 degree and 270 degree, and the distances from the center of the rotor 19 to the connecting lines are r. The method comprises the following specific steps:
and 41, stopping rotating the rotor 19, and installing a test weight block with the 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. Rotating the rotor 19 to the rotational speed ω. The sensor 21 detects a first vibration amplitude a of the rotor 191。
The rotor 19 being mounted to the counterweight in the first positionThe first unbalance amount is generated at 30 DEG C
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 42, stopping rotating the rotor 19, 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. Rotating the rotor 19 to the rotational speed ω. The sensor 21 detects a second vibration amplitude a of the rotor 192。
A second unbalance is generated when the rotor 19 is mounted on the counterweight 30 at the second position
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:
and 43, stopping rotating the rotor 19, and installing a test weight block with the mass m at a third position on the rotor 19. The third position andthe line connecting the centers of the rotors 19 is at a 90 ° clockwise angle to the standard line. Rotating the rotor 19 to the rotational speed ω. The sensor 21 measures a third vibration amplitude a of the rotor 193。
A third unbalance is generated when the rotor 19 is mounted on the counterweight 30 at a third position
Third amount of unbalance
Is the third unbalanced mass α3. Third amount of unbalance
And a third vibration amplitude A3The relationship of (1) is:
and 44, stopping rotating the rotor 19, and installing a test weight block with the mass m at a fourth position on the rotor 19. The line connecting the fourth position with the center of the rotor 19 is at a 270 ° clockwise angle to the standard line. Rotating the rotor 19 to the rotational speed ω. The sensor 21 measures a fourth vibration amplitude a of the rotor 194。
The fourth unbalance amount is generated when the rotor 19 is installed on the weight block 30 at the fourth position
Fourth amount of unbalance
Is the fourth unbalanced mass α4. Fourth amount of unbalance
And a fourth vibration amplitude A3The relationship of (1) is:
in one embodiment, the first position, the second position, the third position and the fourth position are respectively at the corresponding mounting holes 191 of the rotor 19.
Step 5, the processor 25 calculates the initial vibration amplitude A0The first vibration amplitude A1The second vibration amplitude A2The third vibration amplitude A3The fourth vibration amplitude A4And the mass m of the weight block, and calculating to obtain an initial balance mass α0And initial unbalance amount
In a fifth position of the rotor 19. The line connecting the fifth position and the center of the rotor 19 is at a clockwise angle θ to the standard line.
Fig. 4A is a vector exploded view of the unbalance amount of the rotor 19 itself. Fig. 4B, 4C, 4D and 4E are vector exploded views of the unbalance amount of the rotor 19 when the weight is mounted on the rotor 19 at the first position, the second position, the third position and the fourth position, respectively.
Referring to fig. 4A, fig. 4B, fig. 4C, fig. 4D and fig. 4E, by applying the vector synthesis and decomposition principle, the following can be obtained:
the mass of the weight piece is unchanged, so that the weight piece comprises:
computing
The following equation can be obtained:
equation 1:
equation 2:
equation 3:
from equation 2 and equation 3, equation 4 can be obtained:
computing
The following equation can be obtained:
equation 5:
equation 6:
from equations 5 and 6, equation 7 can be obtained:
from equation 4 and equation 7, equation 8 can be obtained:
(A1-b)2+(A2-b)2＝(A3-b)2+(A4-b)2the constant b is found according to equation 8:
from equation 1 and equation 4, equation 9 can be obtained:
the coefficient k is found according to equation 9:
from equation 2 and equation 3, equation 10 can be obtained:
α is obtained according to equation 10y：
The initial imbalance mass α is calculated0And the angle θ is:
obviously, the angle θ can take a value within 0,360 °, and two values can be solved, and the only correct value of the angle θ can be confirmed by the following judgment conditions:
when A is3＞A4If the angle theta is more than 0 degree and less than 180 degrees, otherwise, the angle theta is more than 180 degrees and less than 360 degrees, substituting the correct value of the angle theta into a formula to calculate the initial unbalanced mass α0The mass of the weight 30 is desired.
Step 6, removing the test weight block with the mass m and installing the test weight block with the mass α0In a sixth position of said rotor 19. The clockwise angle γ of the line connecting the sixth position and the center of the rotor 19 and the standard line satisfies: γ is 180+ θ.
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.
In one embodiment, the rotor 19 is a load structure mounted on the main shaft 17, but is not limited thereto. It is understood that in other embodiments, the rotor 19 may be a unitary structure including the main shaft 17, and the driving member 15 is connected to the main shaft 17 such that the driving member 15 drives the rotor 19 to rotate. The dynamic balance correction method can also be applied to correct the dynamic balance of the whole rotor 19 including the main shaft 17 connected to the driving member 15 at the time of no load.
Compared with the prior art, the dynamic balance correction method provided by the invention has the advantages that the test weight blocks with the same quality are respectively arranged on the rotor 19 for 0 degrees, 180 degrees, 90 degrees and 270 degrees four times, and five vibration amplitudes are obtained: the initial vibration amplitude A0The first vibration amplitude A1The second vibration amplitude A2The third vibration amplitude A3And the fourth vibration amplitudeValue A4And a constant b is determined, except for the unbalanced mass α of the rotor 19 itself0Besides other factors causing unbalance, the correction accuracy is high. And the mass and the mounting position of the balancing weight 30 required by correction can be obtained only by measuring the vibration amplitude of the rotor 19, a phase discrimination sensor is not needed, the correction structure is simplified, and the cost is reduced.
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.
Claims (10)
1. A dynamic balance correction method for correcting imbalance of a rotor, the balance correction method comprising:
establishing an unbalance relation formula, wherein the rotor has an unbalance mass α, and the relation between the unbalance mass α and the vibration amplitude A of the rotor is represented by a coefficient k and a constant b, wherein A is k α + b;
rotating the rotor to a rotating speed omega to obtain an initial vibration amplitude A of the rotor0；
Stopping the rotor from rotating, respectively installing a test weight block with the mass of m at a first position, a second position, a third position and a fourth position on the rotor, and respectively obtaining corresponding first vibration amplitude A when the rotor rotates to the rotating speed omega1A second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4；
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 connecting lines of the first position, the second position, the third position and the fourth position with the center of the rotor respectively have clockwise angles of 0 degree, 180 degrees, 90 degrees and 270 degrees with the standard line, and the distances from the first position, the second position, the third position and the fourth 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 sixth position is arranged on the rotor, the distance between the sixth position and the center of the rotor is r, and the clockwise angle between the connecting line of the sixth position and the center of the rotor and the standard line is gamma;
the constant b satisfies:
the coefficient k satisfies:
mass α0Satisfies the following conditions:
the angle γ satisfies:
and mounting the balancing weight on a sixth position of the rotor to adjust the dynamic balance of the rotor.
2. The dynamic balance correction method according to claim 1, wherein an initial vibration amplitude a of the rotor is obtained at the time of the rotation of the rotor to a rotation speed ω0After 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 counterweight at a sixth position on the rotor to adjust the dynamic balance of the rotor comprises determining a clockwise angle θ between a line connecting the unbalanced mass α and the center of the rotor and the reference line, wherein:
when A is3＞A4The angle θ satisfies: theta is more than 0 degree and less than 180 degrees; otherwise, the angle θ satisfies: theta is more than 180 degrees and less than 360 degrees; the angle gamma is equal to the determined angle theta plus 180 DEG, and the balancing weight is mounted on the rotor at the determined angle gamma to adjust the dynamic balance of the rotor.
5. An automation device comprising a drive member and a rotor, the rotor being connected to the drive member, the drive member being adapted to drive the rotor in rotation, characterized in that the dynamic balance of the rotor is adjusted by a dynamic balance correction method as claimed in any one of claims 1-4.
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 sixth 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. An automated apparatus according to 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 rotor in a dynamic balance correction method according to any one of claims 1 to 40The first vibration amplitude A1The second vibration amplitude A2Third vibration amplitude A3And a fourth vibration amplitude A4The acquisition card is electrically connected with the sensor and the processor, the acquisition card is used for acquiring the 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 according to any one of claims 1 to 4.
10. An automation device comprising a drive member, a spindle and a rotor, wherein the drive member is connected to the spindle and is used for driving the spindle to rotate, and the rotor is arranged on the spindle, characterized in that the dynamic balance of the rotor is adjusted by the dynamic balance correction method according to any one of claims 1 to 4.
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| CN114184321A (en) * | 2021-11-30 | 2022-03-15 | 珠海华粤传动科技有限公司 | Balance detection method, device and equipment for centrifugal pendulum shock absorber |
| CN114184321B (en) * | 2021-11-30 | 2024-04-05 | 珠海华粤传动科技有限公司 | Balance detection method, device and equipment for centrifugal pendulum vibration absorber |
| CN116907729A (en) * | 2023-07-13 | 2023-10-20 | 东莞市卓茂仪器有限公司 | Impeller balance correction method based on dispensing and quality improvement |
| CN116907729B (en) * | 2023-07-13 | 2024-05-14 | 东莞市卓茂仪器有限公司 | Impeller balance correction method based on dispensing and quality improvement |
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