阅读说明：本技术 一种刚性转子配平方法及其控制系统 (Rigid rotor balancing method and control system thereof ) 是由 曾辉 于 2019-11-19 设计创作，主要内容包括：本发明涉及刚性转子技术领域,涉及一种刚性转子配平方法及其控制系统,包括以下步骤：S1、采集设备刚性转子的初始振动幅值与初始振动相位、试配重振动幅值与试配重振动相位,并输入至EXCEL表格中；S2、将初始振动幅值与初始振动相位、试配重振动幅值与试配重振动相位转化为直角坐标系的复数形式；S3、得到设备刚性转子的影响因子K和应配重物块G的复数形式；S4、得到设备刚性转子的应配重物块G的内幅值g和度数角W；并将最终所得到的重量为g的应配重物块G按照度数角W的方向放置固定在设备刚性转子上。本发明利用EXCEL内置工程函数和数学三角函数开发的刚性转子影响系数法动平衡计算方法为现场动平衡计算带来更大的便利,并有效提高工作的可靠性。(The invention relates to the technical field of rigid rotors, in particular to a rigid rotor balancing method and a control system thereof, which comprises the following steps: s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and acquiring a trial counterweight vibration amplitude and a trial counterweight vibration phase, and inputting the amplitudes and phases into an EXCEL table; s2, converting the initial vibration amplitude and the initial vibration phase and the trial counterweight vibration amplitude and the trial counterweight vibration phase into a complex form of a rectangular coordinate system; s3, obtaining an influence factor K of the rigid rotor of the equipment and a complex form of the weight block G; s4, obtaining the inner amplitude G and the degree angle W of the object G to be weighed of the rigid rotor of the equipment; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W. The dynamic balance calculation method of the rigid rotor influence coefficient method developed by using the EXCEL built-in engineering function and the mathematical trigonometric function brings greater convenience to the field dynamic balance calculation and effectively improves the reliability of work.)

1. A rigid rotor balancing method, comprising the steps of:

s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added, storing the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the equipment in a database, and then respectively inputting the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the monitoring and measuring equipment stored in the database into an EXCEL table;

s2, converting the initial vibration amplitude and the initial vibration phase, and the trial counterweight vibration amplitude and the trial counterweight vibration phase input in the last step into COMPLEX forms in a rectangular coordinate system respectively by using a COMPLEX function;

s3, calculating a complex difference value before and after the trial balance weight block P by utilizing an IMSUB function, and calculating an influence factor K of the rigid rotor of the equipment and a complex form of the balance weight block G by utilizing an IMDIV function;

s4, obtaining an inner amplitude G and a degree angle W of a weight block G to be weighed of the rigid rotor of the equipment by utilizing an IMABS function, an IMARGUMENT function and a DEGRES function; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W.

2. The rigid rotor balancing method according to claim 1, wherein the specific process of step S1 is as follows: s11, respectively acquiring initial vibration amplitude A of the rigid rotor of the equipment by using a vibration data acquisition analyzer₀And initial vibration phase w₀And stored in a database; s12, adding a trial weight object P to the rigid rotor of the equipment, and then respectively acquiring the trial weight vibration amplitude A of the rigid rotor of the equipment again₁And trial balance vibrationDynamic phase w₁And stored again in the database; s13, acquiring the initial vibration amplitude A of the rigid rotor of the equipment in the database₀With initial vibration phase w₀Trial balance vibration amplitude A₁With trial balance of vibration phase w₁And inputting the trial balance weight blocks P into the EXCEL table respectively.

3. The rigid rotor balancing method according to claim 2, wherein the specific process of step S2 is as follows: s21, utilizing the COMPLEX function to input the initial vibration amplitude A of the previous step₀With initial vibration phase w₀Converting into complex z in rectangular coordinate system₀(ii) a S22, using COMPLEX function to input the trial counterweight vibration amplitude A in the previous step₁With trial balance of vibration phase w₁Converting into complex z in rectangular coordinate system₁(ii) a S23, using COMPLEX function to test the mass G of the mass P_pAnd phase w_pConverting into complex z in rectangular coordinate system_p。

4. A rigid rotor balancing method according to claim 3, wherein the specific process of step S21 is as follows: s211, calculating the complex number z₀Real coefficient of

5. The rigid rotor balancing method according to claim 4, wherein the specific process of step S22 is as follows: s221, first calculating a complex number z₁Real coefficient of

6. The rigid rotor balancing method according to claim 5, wherein the specific process of step S23 is as follows: s221, first calculating a complex number z_pReal coefficient ofS222, recalculating the complex number z_pImaginary coefficient of

7. The rigid rotor balancing method according to claim 6, wherein the specific process of step S3 is as follows: s31, calculating the complex difference z before and after adding the test weight P by using the IMSUB function₂＝z₁-z₀(ii) a S32, calculating the complex form of the influence factor K of the rigid rotor of the equipment by utilizing the IMDIV function

8. The rigid rotor balancing method according to claim 7, wherein the specific process of step S4 is as follows: s41, calculating the complex form of the object G to be weighed of the rigid rotor of the equipment to be converted into the inner amplitude G of the polar coordinate system by utilizing an IMABS function; s42, calculating the arc angle of the polar coordinate system converted from the complex form of the mass G to be weighed of the rigid rotor of the equipment by using an IMARGUMENT function; s43, converting the polar coordinate system arc angle of the object G to be weighed of the rigid rotor of the equipment into a polar coordinate system degree angle W by using a DEGRES function; s44, placing and fixing the weight-to-be-weighed object G with the weight of G on the rigid rotor of the equipment according to the inner amplitude G and the degree angle W of the weight-to-be-weighed object G of the rigid rotor of the equipment.

9. The control system of a rigid rotor balancing method according to claim 8, comprising a rigid rotor of the apparatus, a vibration data acquisition analyzer for measuring vibration amplitude and vibration phase of the rigid rotor of the apparatus, a database for storing data information, and an ECEL table for calculation; the vibration data acquisition analyzer is used for measuring vibration amplitude and vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P and storing the vibration amplitude and the vibration phase in the database, the ECEL table is used for calling the vibration amplitude and the vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P in the database, the internal amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are obtained by calculation through a data function in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W.

10. A control system for a rigid rotor balancing method according to claim 9, wherein the data stored in the database includes the initial vibration amplitude and initial vibration phase of the rigid rotor of the plant, the trial weight vibration amplitude and trial weight vibration phase of the rigid rotor of the plant after adding the trial weight P, the mass and phase of the trial weight P, and the IMSUB function, IMSUM function, impudu function, IMDIV function pair, IMABS function, imargumet function, and degees function.

Technical Field

The invention relates to the technical field of rigid rotors, in particular to a rigid rotor balancing method and a control system thereof.

Background

The event that modern large rotating machines are forced to stop due to excessive vibration in operation often happens. The most common cause of excessive vibration is rotor mass imbalance. It is important to find the vector distribution of the rotor mass unbalance points and balance the weights at the correct positions to eliminate the unbalance. Therefore, how to quickly and efficiently trim a rigid rotor to avoid a shutdown event caused by rotor mass imbalance is a problem that needs to be solved at present.

Disclosure of Invention

In view of the above, the present invention provides a rigid rotor balancing method and a control system thereof, which are used to solve the defect that the vibration of the existing large-scale machine exceeds the standard due to the unbalanced mass of the rigid rotor.

A rigid rotor balancing method, comprising the steps of:

s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added, storing the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the equipment in a database, and then respectively inputting the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the monitoring and measuring equipment stored in the database into an EXCEL table;

s2, converting the initial vibration amplitude and the initial vibration phase, and the trial counterweight vibration amplitude and the trial counterweight vibration phase input in the last step into COMPLEX forms in a rectangular coordinate system respectively by using a COMPLEX function;

s3, calculating a complex difference value before and after the trial balance weight block P by utilizing an IMSUB function, and calculating an influence factor K of the rigid rotor of the equipment and a complex form of the balance weight block G by utilizing an IMDIV function;

s4, obtaining an inner amplitude G and a degree angle W of a weight block G to be weighed of the rigid rotor of the equipment by utilizing an IMABS function, an IMARGUMENT function and a DEGRES function; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W.

Further, as a preferred embodiment of the present invention, the specific process of step S1 is: s11, respectively acquiring initial vibration amplitude A of the rigid rotor of the equipment by using a vibration data acquisition analyzer₀And initial vibration phase w₀And stored in a database; s12, adding a trial weight object P to the rigid rotor of the equipment, and then respectively acquiring the trial weight vibration amplitude A of the rigid rotor of the equipment again₁And trial balance vibration phase w₁And stored again in the database; s13, acquiring the initial vibration amplitude A of the rigid rotor of the equipment in the database₀With initial vibration phase w₀Trial balance vibration amplitude A₁With trial balance of vibration phase w₁And inputting the trial balance weight blocks P into the EXCEL table respectively。

Further, as a preferred embodiment of the present invention, the specific process of step S2 is: s21, utilizing the COMPLEX function to input the initial vibration amplitude A of the previous step₀With initial vibration phase w₀Converting into complex z in rectangular coordinate system₀(ii) a S22, using COMPLEX function to input the trial counterweight vibration amplitude A in the previous step₁With trial balance of vibration phase w₁Converting into complex z in rectangular coordinate system₁(ii) a S23, using COMPLEX function to test the mass G of the mass P_pAnd phase w_pConverting into complex z in rectangular coordinate system_p。

Further, as a preferred embodiment of the present invention, the specific process of step S21 is: s211, calculating the complex number z₀Real coefficient of

S212, recalculating the complex number z₀Imaginary coefficient ofS213, using the COMPLEX function Z ═ a, b, dividing the COMPLEX number Z₀Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z₀＝(x₀,y₀)。

Further, as a preferred embodiment of the present invention, the specific process of step S22 is: s221, first calculating a complex number z₁Real coefficient of

S222, recalculating the complex number z₁Imaginary coefficient of

S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function Z₁Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z₁＝(x₁,y₁)。

Further, as a preferred embodiment of the present invention, the specific process of step S23 is: s221, first calculating a complex number z_pReal coefficient of

S222, recalculating the complex number z_pImaginary coefficient of

S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function Z_pRespectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z_p＝(x_p,y_p)。

Further, as a preferred embodiment of the present invention, the specific process of step S3 is: s31, calculating the complex difference z before and after adding the test weight P by using the IMSUB function₂＝z₁-z₀(ii) a S32, calculating the complex form of the influence factor K of the rigid rotor of the equipment by utilizing the IMDIV functionS33, calculating the complex form of the object G to be weighted of the rigid rotor of the equipment by utilizing the IMDIV function

Further, as a preferred embodiment of the present invention, the specific process of step S4 is: s41, calculating the complex form of the object G to be weighed of the rigid rotor of the equipment to be converted into the inner amplitude G of the polar coordinate system by utilizing an IMABS function; s42, calculating the arc angle of the polar coordinate system converted from the complex form of the mass G to be weighed of the rigid rotor of the equipment by using an IMARGUMENT function; s43, converting the polar coordinate system arc angle of the object G to be weighed of the rigid rotor of the equipment into a polar coordinate system degree angle W by using a DEGRES function; s44, placing and fixing the weight-to-be-weighed object G with the weight of G on the rigid rotor of the equipment according to the inner amplitude G and the degree angle W of the weight-to-be-weighed object G of the rigid rotor of the equipment.

A control system of a rigid rotor balancing method comprises an equipment rigid rotor, a vibration data acquisition analyzer for measuring the vibration amplitude and the vibration phase of the equipment rigid rotor, a database for storing data information and an ECEL table for calculation; the vibration data acquisition analyzer is used for measuring vibration amplitude and vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P and storing the vibration amplitude and the vibration phase in the database, the ECEL table is used for calling the vibration amplitude and the vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P in the database, the internal amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are obtained by calculation through a data function in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W.

Further, as a preferred embodiment of the present invention, the data information stored in the database includes an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, a trial weight vibration amplitude and a trial weight vibration phase of the rigid rotor of the equipment after the trial weight P is added, a mass and a phase of the trial weight P, an IMSUB function, an IMSUM function, an impudu function, an IMDIV function pair, an IMABS function, an IMARGUMENT function, and a degees function.

According to the technical scheme, the invention has the beneficial effects that: compared with the prior art, the rigid rotor balancing method disclosed by the invention has the advantages that the initial vibration amplitude and the initial vibration phase of the rigid rotor of the equipment are utilized, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the rigid rotor of the equipment are converted and calculated after the trial counterweight block P is added, the inner amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are quickly calculated by means of the ECEL table and the functions and data information stored in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W, so that the weight balancing purpose of the rigid rotor is quickly achieved, the defect that the vibration of the existing large-scale machine exceeds the standard due to the mass unbalance of the rigid rotor can be effectively overcome, and the purpose of reducing the vibration times of the large-scale machine exceeding the standard is achieved.

Detailed Description

The following is a detailed description of the above-mentioned aspects of the present invention by way of example, and it is specifically noted that numerous modifications and improvements may be made in accordance with the principles of the present invention, which are also considered to be within the scope of the embodiments of the present invention.

According to the rigid rotor balancing method and the control system thereof disclosed by the invention, the invention specifically discloses the following specific embodiments: