CN104330214A - Simple field dynamic balancing method - Google Patents

Abstract

The invention relates to the field of maintenance of rotary machineries and particularly relates to a simple field dynamic balancing method which carries out dynamic balancing on a machine mainly through a calculation method. When the method is used, corresponding imbalance masses and phases can be obtained without key-phase signals or a significantly professional dynamic balancing instrument and a field dynamic balance can be realized, and only one instrument which can detect vibration is needed and the field dynamic balance of the machine can be completed conveniently; and through one field dynamic balance, key inherent characteristic parameters of the machine can be obtained so that demands of large quantity of field dynamic balance are met.

Description

A kind of simple and easy spot dynamic balance method

Technical field

The present invention relates to rotating machinery area of maintenance, particularly relate to a kind of simple and easy spot dynamic balance method.

Background technology

Rotor unbalance fault is one of modal typical fault in rotating machinery.Dynamic balance technology is the most effective means solving rotor unbalance fault, is also the most time saving means.Therefore, the dynamic balance methods such as influence coefficient method, method of model balancing, ternary balancing method are in succession suggested and are successfully applied in spot dynamic balance, and the spot dynamic balance method wherein based on influence coefficient method is most widely used.

But, because influence coefficient method needs install or be provided with key phase in advance to obtain phase information, and need key phase triggering collection, therefore need special spot dynamic balance instrument or there is the instrument of similar functions or system just can carry out spot dynamic balance, those be there is no in advance to the rotating machinery of fitting key phase, as most blower fan, all easily, in time can not carry out spot dynamic balance, for processing imbalance fault in time, support equipment safe operation is very unfavorable.

Summary of the invention

The object of the present invention is to provide a kind of that do not need phase information, conveniently can be calculated corresponding unbalance mass, and phase place by numerical evaluation simple and easy spot dynamic balance method, to meet the needs of a large amount of spot dynamic balance.

In order to achieve the above object, simple and easy spot dynamic balance method of the present invention is by the following technical solutions: a kind of simple and easy spot dynamic balance method, the method comprises the following steps: 1) to preparing the machine carrying out spot dynamic balance, determine that a transient equilibrium rotating speed Ω (is generally working speed, unit rad/s), the test mass m of a vibration measuring point V, counterweight face P, counterweight radius R and a standard, wherein transient equilibrium rotating speed Ω is the working speed of machine, its unit is rad/s, and test mass m estimates to draw according to the dynamic balance grade of machine and Vibration Condition at that time; 2) the original passband vibration values V of vibration measuring point V is measured ₀, and calculate 1X amplitude A according to transient equilibrium rotating speed Ω ₀; 3) shutting down, is any circumferential position of R the radius that preprepared test mass m temporarily anchors to counterweight face, add good after as 0 degree of phase point; 4) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that first time adds measuring point V after test mass m ₁, and calculate corresponding 1X amplitude A ₁; 5) shut down, test mass m is taken off and is fixed to the opposite location of first test mass position on counterweight face, described opposite location radius R, phase point 180 degree; 6) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that second time adds measuring point V after test mass m ₂, and calculate corresponding 1X amplitude A ₂; 7) according to rotor unbalance response amplitude versus frequency characte and phase-frequency characteristic derive calculate original unbalance mass, m ₀and the formula of phasing degree θ, now balance position may at 180+ θ or 180-θ place;

$A=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\ω}}^2}{\sqrt{{({\mathrm{\ω}}_n^2-{\mathrm{\ω}}^2)}^2+{\left(\frac{\mathrm{C\ω}}{M}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\λ}}^2}{\sqrt{{(1-{\mathrm{\λ}}^2)}^2+{\left(2\mathrm{\ζ\λ}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\mathrm{\β}=m{\mathrm{\β}}^{\′}---\left(1\right)$

$\left\{\begin{array}{c}{A}_0=m_0\mathrm{\β}\\ A_1=\left(\sqrt{{(m_0\cos \mathrm{\θ}+m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\\ A_2=\left(\sqrt{{(m_0\cos \mathrm{\θ}-m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\end{array}\right.---\left(3\right)$

$\left\{\begin{array}{c}{m}_0=m/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\\ \cos \mathrm{\θ}=\left(\frac{A_1^2-A_2^2}{{4A}_0^2}\right)/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\end{array}\right.---\left(4\right)$

8) test mass m is taken off, and counterweight m ₁=m ₀be added to a place in 180+ θ and 180-θ, after restarting, record A point passband vibration values V ₂, and obtain A ₃if, A ₃remarkable reduction, then illustrate that position is correct, otherwise take off m ₁be added to another place in 180+ θ and 180-θ; 9) if counterbalance effect is unsatisfied with, can according to formula (4) and A ₀, A ₁, A ₃calculate new counterweight and phase place, be satisfied with counterbalance effect until obtain.

Be vibration displacement signal, vibration velocity signal or vibration acceleration signal to the vibration signal of the vibration detection of machine.

When using method of the present invention, do not need key signal, do not need very professional transient equilibrium instrument can draw corresponding unbalance mass, and phase place, realize spot dynamic balance, as long as there is one the instrument of vibration measuring can complete the spot dynamic balance of machine easily, the crucial inherent characteristic parameter of machine can be obtained by spot dynamic balance, meet the needs of a large amount of spot dynamic balance.

Accompanying drawing explanation

Fig. 1 is the front view of unbalanced rotor system;

Fig. 2 is the left front view of unbalanced rotor system;

Fig. 3 is out-of-balance force amplitude change schematic diagram in transient equilibrium process.

In figure: V-vibration measuring point; P-balanced surface; R-equilibrium radius; K-rotor equivalent rigidity; M-rotor equivalent quality; Ω-balancing rotor system rotating speed (unit: rad/s); ω _n-Critical Speed of Rotor System (unit: rad/s); M-unbalance mass, (unit: g); θ-unbalance mass, phasing degree (unit: degree); m ₀-rotor test mass quality (unit: g); -rotor-support-foundation system damping ratio; F-original unbalance mass, m and test mass quality m ₀the bonding force amplitude produced; F _m0the bonding force amplitude that-original unbalance mass, m produces; F _m-test mass quality m ₀the power amplitude produced.

Embodiment

The embodiment of simple and easy spot dynamic balance method, as Figure 1-3, the method comprises the following steps: 1) to preparing the machine carrying out spot dynamic balance, determine that a transient equilibrium rotating speed Ω (is generally working speed, unit rad/s), the test mass m of a vibration measuring point V, counterweight face P, counterweight radius R and a standard, wherein transient equilibrium rotating speed Ω is the working speed of machine, its unit is rad/s, test mass m estimates to draw according to the dynamic balance grade of machine and Vibration Condition at that time, step 1) can refer to Fig. 1,2; 2) the original passband vibration values V of vibration measuring point V is measured ₀, and calculate 1X amplitude A according to transient equilibrium rotating speed Ω ₀; 3) shutting down, is any circumferential position of R the radius that preprepared test mass m temporarily anchors to counterweight face, add good after as 0 degree of phase point; 4) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that first time adds measuring point V after test mass m ₁, and calculate corresponding 1X amplitude A ₁; 5) shut down, test mass m is taken off and is fixed to the opposite location of first test mass position on counterweight face, described opposite location radius R, phase point 180 degree; 6) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that second time adds measuring point V after test mass m ₂, and calculate corresponding 1X amplitude A ₂; 7) according to rotor unbalance response amplitude versus frequency characte (formula 1) and phase-frequency characteristic (formula 2) derive calculating original unbalance mass, m ₀and the formula of phasing degree θ (formula 4), now balance position may at 180+ θ or 180-θ place;

$A=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\ω}}^2}{\sqrt{{({\mathrm{\ω}}_n^2-{\mathrm{\ω}}^2)}^2+{\left(\frac{\mathrm{C\ω}}{M}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\λ}}^2}{\sqrt{{(1-{\mathrm{\λ}}^2)}^2+{\left(2\mathrm{\ζ\λ}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\mathrm{\β}=m{\mathrm{\β}}^{\′}---\left(1\right)$

$\left\{\begin{array}{c}{A}_0=m_0\mathrm{\β}\\ A_1=\left(\sqrt{{(m_0\cos \mathrm{\θ}+m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\\ A_2=\left(\sqrt{{(m_0\cos \mathrm{\θ}-m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\end{array}\right.---\left(3\right)$

$\left\{\begin{array}{c}{m}_0=m/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\\ \cos \mathrm{\θ}=\left(\frac{A_1^2-A_2^2}{{4A}_0^2}\right)/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\end{array}\right.---\left(4\right)$

8) test mass m is taken off, and counterweight m ₁=m ₀be added to a place in 180+ θ and 180-θ, after restarting, record A point passband vibration values V ₂, and obtain A ₃if, A ₃remarkable reduction, then illustrate that position is correct, otherwise take off m ₁be added to another place in 180+ θ and 180-θ; 9) if counterbalance effect is unsatisfied with, can according to formula (4) and A ₀, A ₁, A ₃calculate new counterweight and phase place, be satisfied with counterbalance effect until obtain.

Can be wherein vibration displacement signal to the vibration signal of the vibration detection of machine, also can be vibration velocity signal or vibration acceleration signal.The method does not need key signal, very professional transient equilibrium instrument is not needed to realize spot dynamic balance by the method, as long as have one vibration measuring, the instrument that carries out spectrum analysis can complete the spot dynamic balance of machine easily, wherein spectrum analysis neither be necessary.

Claims (2)

1. a simple and easy spot dynamic balance method, it is characterized in that, the method comprises the following steps: 1) to preparing the machine carrying out spot dynamic balance, determine a transient equilibrium rotating speed Ω, the test mass m of a vibration measuring point V, counterweight face P, counterweight radius R and a standard, wherein transient equilibrium rotating speed Ω is the working speed of machine, and its unit is rad/s, and test mass m estimates to draw according to the dynamic balance grade of machine and Vibration Condition at that time; 2) the original passband vibration values V of vibration measuring point V is measured ₀, and calculate 1X amplitude A according to transient equilibrium rotating speed Ω ₀; 3) shutting down, is any circumferential position of R the radius that preprepared test mass m temporarily anchors to counterweight face, add good after as 0 degree of phase point; 4) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that first time adds measuring point V after test mass m ₁, and calculate corresponding 1X amplitude A ₁; 5) shut down, test mass m is taken off and is fixed to the opposite location of first test mass position on counterweight face, described opposite location radius R, phase point 180 degree; 6) again machine startup to transient equilibrium rotating speed, measure the passband vibration values V that second time adds measuring point V after test mass m ₂, and calculate corresponding 1X amplitude A ₂; 7) according to rotor unbalance response amplitude versus frequency characte and phase-frequency characteristic derive calculate original unbalance mass, m ₀and the formula of phasing degree θ, now balance position may at 180+ θ or 180-θ place;

$A=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\ω}}^2}{\sqrt{{({\mathrm{\ω}}_n^2-{\mathrm{\ω}}^2)}^2+{\left(\frac{\mathrm{C\ω}}{M}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\frac{{\mathrm{\λ}}^2}{\sqrt{{(1-{\mathrm{\λ}}^2)}^2+{\left(2\mathrm{\ζ\λ}\right)}^2}}=\frac{\mathrm{mR}}{M}\·\mathrm{\β}=m{\mathrm{\β}}^{\′}---\left(1\right)$

$\left\{\begin{array}{c}{A}_0=m_0\mathrm{\β}\\ A_1=\left(\sqrt{{(m_0\cos \mathrm{\θ}+m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\\ A_2=\left(\sqrt{{(m_0\cos \mathrm{\θ}-m)}^2+{\left(m_0\sin \mathrm{\θ}\right)}^2}\right)\mathrm{\β}\end{array}\right.---\left(3\right)$

$\left\{\begin{array}{c}{m}_0=m/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\\ \cos \mathrm{\θ}=\left(\frac{A_1^2-A_2^2}{{4A}_0^2}\right)/\sqrt{\frac{A_2^2+A_1^2}{{2A}_0^2}-1}\end{array}\right.---\left(4\right)$

8) test mass m is taken off, and counterweight m ₁=m ₀be added to a place in 180+ θ and 180-θ, after restarting, record V point passband vibration values V ₂, and obtain A ₃if, A ₃remarkable reduction, then illustrate that position is correct, otherwise take off m ₁be added to another place in 180+ θ and 180-θ; 9) if counterbalance effect is unsatisfied with, can according to formula (4) and A ₀, A ₁, A ₃calculate new counterweight and phase place, be satisfied with counterbalance effect until obtain.

2. simple and easy spot dynamic balance method according to claim 1, is characterized in that, is vibration displacement signal, vibration velocity signal or vibration acceleration signal to the vibration signal of the vibration detection of machine.