An analytical investigation on the dynamic stability of a rotor filled with liquid
Bobo Li^{1} , Guangding Wang^{2} , Huiqun Yuan^{3}
^{1, 2}School of Mechanical Engineering and Automation, Northeastern University, Shenyang, China
^{3}School of Science, Northeastern University, Shenyang, China
^{3}Corresponding author
Journal of Vibroengineering, Vol. 20, Issue 6, 2018, p. 22532267.
https://doi.org/10.21595/jve.2018.19886
Received 13 April 2018; received in revised form 19 June 2018; accepted 1 July 2018; published 30 September 2018
This paper deals with the dynamic stability of a rigid rotor arbitrarily filled with liquid. On the basis of the established coupledfield equations of the rotor system, the general whirling eigenequation, which is a quartic complex coefficients equation, is derived. In order to obtain the solutions of the general whirling eigenequation, a mathematical method is proposed. To illustrate the precision of calculating results, a comparison is carried out between the present analysis and the numerical results. The results show that two calculation results are in good agreement. Then the stability of the rotor system is analyzed. It is shown that the dynamic instability occurs at a particular bound of the spinning speed. Moreover, the effects of system parameters, such as fluidfill ratio and mass ratio, on the unstable regions are discussed.
 A mathematical method for obtaining the solutions of the general whirling eigenequation was proposed.
 The whirling frequency equation of the rigid liquidfilled rotor was presented to predict the system stability.
 The dynamic instability occurs at a particular bound of the spinning speed.
 The effects of some main parameters on system stability were discussed.
Keywords: rotor filled with liquid, dynamic stability, parameters, unstable region, critical speed.
1. Introduction
Rotor filled with liquid is applied widely in engineering. The inside of rotor is hollow, and the chamber contains liquid. When the rotating cylinder suffers the perturbation in working, the whirling motion occurs. An additional pressure, which acts on rotating cylinder internal surface, results from the relative rotation between liquid and rotor. This forms a complex fluidsolid coupling problems. Meanwhile, due to the interaction between rotating fluid and rotor, the phenomenon of rotor system instability happens at a certain RPM range. Therefore, it has very important significance to study dynamic stability of rotor filled with liquid.
The dynamic stability of rotor filled with liquid was first studied by Kollmann, Jlnnouchi, and Crandall [14]. The critical speed of Jeffcott singledisc rotor filled with liquid was calculated by Kollmann. The instability phenomenon was observed on the rotor partially filled with liquid in the experiment. Crandall analyzed the dynamic stability of a flexible rotor filled with liquid. After that, the dynamic characteristics of parallel whirling motion were analyzed for rotor filled with liquid by Wolf [5]. In the early study, the liquid of rotor chamber was assumed to be ideal and rotor body was rigid. For this reason, the dynamic stability was investigated for rotor filled with viscous liquid by Hendricks, Daich and Bar, Saito and HolmChristensen [69]. Furthermore, rigid body angular displacement was introduced by Hendricks and Lichtenberg, the research on rotor filled with liquid was extended to three dimensions [10, 11]. Hiroshi Ota et al. made experiments on the vibration of rotor filled with liquid, the effect of viscosity and specific gravity on the unstable vibration were studied simultaneously [12]. Yuichi SATO proposed a dynamic absorber using a hollow rotor partially filled with liquid, a kind of technique was described to suppress structure vibration, and the effectiveness of proposed absorber was showed experimentally [13].^{}Kuipers analyzed the stability of a flexibly mounted rotating cylinder partially filled with liquid. The rotor was assumed to rotate around its axis of symmetry with a constant angular velocity and the liquid was ideal in the chamber. The unstable region was derived and the effect of combined action of dissipative and gyroscopic terms was researched by him [14]. Zhang et al. further discussed the dynamic stability of rigid and flexible rotor filled with liquid [15].
In recent years, there are many related researches on the stability of rotor filled with liquid. The experimental investigation was made on the dynamic characteristics of an overhung rigid centrifuge rotor partially filled with liquid by Zhu [16].^{}The influence of fluidfill ratio on rotor whirl frequency, the range of unstable region, and the rotor imbalance were researched. Furtherly, the stability of rotor filled with viscous incompressible fluid was analyzed by him. The dynamic stability was investigated on flexible rotating cylinder partially filled with liquid by Tao and Zhang, they proposed that the three dimensional flow can be simplified to two dimensional flow problem in the chamber [17]. Yukio Ishida et al. applied a method, which utilizes discontinuous spring characteristics, to suppress unstable vibrations in an asymmetrical rotor system, an asymmetrical shaft system, and a rotor system partially filled with liquid [18].^{}N. V. Derendyaev et al. investigated the stability of a cylinder filled with different kinds of liquid, including viscous incompressible liquid, a stratified viscous incompressible liquid and a stratified nonuniform viscous incompressible liquid [1922]. In 1988, Derendyaev proved that AndronovHopf bifurcations may occur in a rotor system filled with liquid [23]. In his work, the methodological mistakes made by Wolf Jr. et al. were analyzed [24].
Many researchers have investigated the vibration and fault diagnosis for a rotor system, but little information is available on the analytical solutions of the general whirling eigenequation [2533]. In this paper, considering the complex form of the equation, a mathematical analysis method is proposed to obtain the solutions of the general whirling eigenequation. The effective of the method is verified by comparing with numerical method. Then, according to whirling eigenequation, the dynamic stability of a liquidfilled rotor system is analyzed, and the effects of fluidfill ratio and mass ratio on unstable region and critical speed of rotor system are discussed.
2. General whirling eigenequation
The structure of rotor filled with liquid is shown in Fig. 1. Rotor is a hollow cylinder, the length of cylinder is $L$, inner diameter is $a$, mass is ${m}_{R}$, centroid is $c$. The liquid is filled in cylinder chamber, both ends of rotor are supported on bearings symmetrically through two flexible shafts, the distance between rotating shaft and liquid level is $b$. Static coordinate $o$$xyz$ is established based on the axis of rotor under static state. When rotor rotates at an angular velocity $\mathrm{\Omega}$, the rotation is assumed to be steady and unperturbed, rotor and liquid rotate synchronously, rotor axis $o$ coincides with liquid centroid $c$, as shown in Fig. 1(b).
Fig. 1. Structure of rotor filled with liquid
a)
b)
When rotor suffers perturbation in working, whirling motion is formed in chamber. We assume that the radial deviation of axis is $\epsilon $, rotor whirling frequency is $\omega $. Here, liquid centroid and rotor axis do not coincide with each other, rotor of centroid $c$ rotates with angular velocity $\omega $, which is shown in Fig. 2.
It is assumed that the liquid is ideal; in addition, $\eta \left(t\right)$ and $\xi \left(t\right)$ are relative perturbation displacements of the centroid $c$ in the direction of $\eta $ and $\xi $. Then, the whirling kinetic equation of rotor centroid $c$ can be written as follows:
where $c$ is external damping coefficient, $k$ is elastic support stiffness, ${F}_{\eta}$ and ${F}_{\xi}$ are force caused by fluid acts on the rotor, $\mathrm{\Omega}$ is selfrotation angular velocity.
Fig. 2. Parallel whirling of a rotor filled with liquid
Based on fluid mechanics, Euler's equation of fluid in rotor chamber can be expressed as:
where the parameter $G$ is given by:
where ${p}_{1}$ is perturbation pressure, ${a}_{\eta}$ and ${a}_{\xi}$ are components of centroid $c$ absolute acceleration along the direction of $\eta $ and $\xi $.
The continuity equation of fluid in rotor chamber can be written as:
For solving the fluidsolid coupling equation of rotor whirling motion above, first and foremost, boundary conditions should be determined. We assume that fluid free surface is $r=b+\xi \left(\theta ,t\right)$, here $\xi \left(\theta ,t\right)$ is perturbation infinitesimal displacement. Then boundary condition of fluid free surface can be represented as:
and fluid displacement boundary condition takes the form:
Based on Eqs. (1), (2) and (4), external damping coefficient is neglected, we can derive the general whirling motion eigenequation for rigid rotor arbitrarily filled with liquid by using boundary conditions Eqs. (5) and (6). The eigenequation is as follows:
where $\delta $, $\mu $ and $s$ are defined as:
where ${m}_{c}$ is the liquid mass, ${\omega}_{0}$ is the nature frequency of a solid rotor. Then, we can expand Eq. (7) as follows:
where $\gamma $ and $\alpha $ can be shown as:
3. Analytical solution for general whirling eigenequation
3.1. Solution procedure
Dynamic stability of rotor arbitrary filled with liquid is a quite complex problem. Furthermore, the general whirling eigenequation is a quartic complex coefficients equation. In order to investigate rotor dynamic stability, the eigenequation needs to be analyzed further. To this end, derivational process for the analytical solution of the eigenequation is given as below.
Eq. (8) takes the form:
Let $a=\frac{(\gamma +1){s}^{2}}{\gamma +\mu}$, $b=i\left[\frac{2\left(\gamma +1\right)s}{\gamma +\mu}\right]$, $c=\left(\frac{\gamma \alpha s}{\gamma +\mu}\right)$ and $d=i\left(\frac{2\alpha s}{\gamma +\mu}\right)$, Eq. (9) can be written in the simplified form:
We assume that ${z}_{1}$, ${z}_{2}$, ${z}_{3}$ and ${z}_{4}$ are four unknown roots of Eq. (10), let $({z}_{1}+{z}_{2})=A$, ${z}_{1}{z}_{2}=B$, $({z}_{3}+{z}_{4})=C$ and ${z}_{3}{z}_{4}=D$, Eq. (10) can be written as:
Then, Eq. (11) can be expanded as follows:
Let us suppose that eigenequation has two conjugate complex roots, or two real roots. There is an independent complex root inevitably among the others. Therefore, if $A$ and $B$ are real numbers, $C$ and $D$ become complex numbers certainly.
Let $a={a}_{1}+i{a}_{2}\text{,}$$b={b}_{1}+i{b}_{2}\text{,}$$c={c}_{1}+i{c}_{2}\text{,}$$d={d}_{1}+i{d}_{2}\text{,}$$C={C}_{1}+i{C}_{2}$ and $D={D}_{1}+i{D}_{2}$, because Eq. (12) is equal to Eq. (10), the coefficients of two equations should be equal. According to complex number algebra, the relationships of coefficients real part for two equations are given by:
In addition, we introduce an unknown quantity $P$, which gives that:
Substituting Eq. (17) into Eq. (14), we obtain:
By Eq. (14) and Eq. (16), we can derive:
Then we can square both sides of Eq. (15):
For eliminating $A$, $B$, $C$ and $D$, the Eq. (19) and Eq. (20) are added:
Square both sides of Eq. (13), and multiply by ${a}_{1}$, we have:
Adding to Eq. (19), then we get:
Add Eq. (21) to get:
Here, removing $({A}^{2}{D}_{1}+B{C}_{1}^{2})$, by Eq. (13) and Eq. (15), we obtain:
Both sides are multiplied by $P$, then the Eq. (25) becomes:
Subtract Eq. (24) to get:
Both sides of Eq. (18) are multiplied by ${P}^{2}$ so that:
Add Eq. (27) to get:
Eq. (29) can be solved and the roots take the form:
where:
Then, $B$ and ${D}_{1}$ can be determined from Eq. (16) and Eq. (17), respectively:
$A$ and ${C}_{1}$ are solved by Eq. (13), Eq. (14) and Eq. (17), respectively:
The values of $A$, $B$, ${C}_{1}$, ${D}_{1}$ should satisfy Eq. (15). According to the values of $P$, we can have a discussion as follows.
Case 1:
In this case, two sets of values are obtained, respectively:
and:
Case 2:
In this condition, we get:
and:
Case 3:
If $P$ takes this value, accordingly, the values of $A$, $B$, ${C}_{1}$, ${D}_{1}$ take the form:
Due to ${c}_{1}2\sqrt{{a}_{1}}<$ 0, such situation does not exist. Only case 1 and case 2 are logical.
Now let us consider the imaginary parts of $C$ and $D$. From Eq. (14), Eq. (15) and Eq. (16), we obtain:
Because $A$, $B$, $C$, $D$ can’t all be real, ${C}_{2}\ne $ 0, it follows that:
In conclusion, $A$, $B$, $C$, $D$ can be solved, we have:
$A=0,\mathrm{}\mathrm{}\mathrm{}B={c}_{1}\frac{\sqrt{{c}_{1}^{2}4{a}_{1}}}{2},\mathrm{}\mathrm{}\mathrm{}C=\frac{i{b}_{2}}{B},\mathrm{}\mathrm{}\mathrm{}D={c}_{1}+\frac{\sqrt{{c}_{1}^{2}4{a}_{1}}}{2},$
where:
The roots of Eq. (8) take the form:
Finally, substituting the values for $A$, $B$, $C$, $D$ into Eq. (31), four roots of Eq. (8) can be obtained.
3.2. Precision analysis
In Sec. 3.1, the method is utilized to solve general whirling eigenequation of rotor arbitrarily filled with liquid. To verify the precision of analytical results, a comparison is carried out between analytical solution and numeric results.
Let $\mu =$ 0.206 and $\gamma =$ 2.6, here, $\mu $ is mass ratio and $\gamma $ is fill parameter, eigenequation can be written in the form:
If $s=$ 1, we can get the results of Eq. (32) by using analytical and numerical methods respectively. The comparison results are shown in Table 1.
Table 1. Comparison results of two methods
Eigenvalue  Numerical results  Analytical results  Error (%) 
${z}_{1}$  0.95002$i$  0.95326$i$  0.33 
${z}_{2}$  –0.90932$i$  –0.95326$i$  4.8 
${z}_{3}$  –0.66415$i$  –0.64935$i$  –2.2 
${z}_{4}$  –2.23614$i$  –2.17435$i$  –2.3 
From Table 1, we can observe that the analytical results accord with numerical results well, maximum error is only 4.8 %. Consequently, the derived analytical results can achieve a high accuracy, which shows the effective of the calculation method for solving general whirling motion eigenequation of rotor arbitrarily filled with liquid.
4. Dynamic stability analysis for rotor filled with liquid
4.1. System stability analysis
For researching dynamic stability of a rotor filled with liquid, we assume that the mass ratio $\mu =$ 0.206 and the parameter $\gamma =$ 2.6, let $s=$ 0, 1, 2, 3, 4 and 5, respectively. Then the roots of eigenequation can be obtained. Fig. 3 shows the polar diagram of the root. From Fig. 3, it can be observed that the polar angles of roots are 0, $\pi $ and $\pi $, which explains that eigenvalues only contain imaginary part. Therefore, the solution for eigenequation can be represented as:
Substituting Eq. (33) into Eq. (8), we have:
Based on Eq. (34), the plot of dimensionless whirling frequency $\xi $ versus dimensionless spinning frequency $S$ for $\mu =$ 0.206 and $\gamma =$ 2.6 can be obtained, as shown in Fig. 4. We can see that there are two real roots and a pair of conjugate complex roots in the interval [${a}_{1}$, ${a}_{2}$], which illustrates that the system is unstable. Moreover, point A denotes the rotor firstorder critical speed in the Fig. 4 when $\xi =S$, the critical spinning speed can be obtained as:
Point A is on the left side of ${a}_{1}$, namely, instability rotating speed is greater than first order critical speed. Therefore, one can say that rotor passes critical speed first and then system instability is occurred. Let $\xi =$ 1, we obtain $s=1\pm \sqrt{2}/2$, which is corresponding to point ${b}_{1}$ and ${b}_{2}$ in Fig. 4. Thus, the estimation range of unstable region is:
From Eq. (34), it can be found that the system stability is related to the fluidfill ratio and the mass ratio. In the following section, we will discuss the influences of system parameters on the stability of a liquidfilled rotor system.
Fig. 3. Polar diagram of the roots for the system eigenequation
a)$S=$ 0
b)$S=$ 1
c)$S=$ 2
d)$S=$ 3
e)$S=$ 4
f)$S=$ 5
Fig. 4. Dimensionless whirling frequency $\xi $ versus dimensionless spinning frequency $S$
4.2. The influence of parameters on the system stability
4.2.1. Fluidfill ratio
In this paper, the function of external damping coefficient is neglected in parameters discussion. Let $x=1b/a$; here $x$ is fluidfill ratio, then we have:
We assume that the mass ratio is a constant, given that $\mu =$ 0.206. Thus, the effects of the fluidfill ratio on system stability are shown in Figs. 57.
Fig. 5. The effects of the fluidfill ratio $x$ on system stability at $\mu =$0.206
Fig. 6. Variation of unstable region when fluidfill ratio $x$ is small
Fig. 7. Variation of unstable region when fluidfill ratio $x$ is large
In Fig. 5, we can see that when fluidfill ratio x is small, unstable region increases with $x$. On the contrary, if the fluidfill ratio is large, the unstable region will decrease gradually. Fig. 6 shows the variation of unstable region when fluidfill ratio is small. It can be observed that when fluidfill ratio is changed in the range of (0, 0.3], the lower and upper bounds of unstable region increase with $x$. Due to the increasing speed of upper bound is greater than that of lower bound, the unstable region increases with fluidfill ratio and moves towards high speed zone gradually.
Fig. 8. Variation of the width of unstable region versus fluidfill ratio $x$
Fig. 7 shows the variation of unstable region when fluidfill ratio $x$ is large. When fluidfill ratio $x$ is changed in the range of (0.3, 1], the lower bound of unstable region increases as $x$ increases. However, the upper bound increases firstly, and then decreases. As a result, unstable region becomes smaller with the increasing of fluidfill ratio $x$. When $x=$ 1, unstable region is almost disappeared, which indicates that the rotor system is stable. The width of unstable region changes with fluidfilled ratio $x$ is shown in Fig. 8. The results show that as fluidfill ratio $x$ increases, the unstable region first expand, then narrow. If the chamber of rotor is fully filled with fluid, the instable phenomenon is disappeared.
4.2.2. Mass ratio
When we discuss the influence of mass ratio $\mu $ on the system stability, fluidfill ratio $x$ should be taken as a constant. Let fluidfill parameter $\gamma =$ 2.6, the effects of mass ratio $\mu $ on unstable region can be obtained, as shown in Fig. 9. It shows that with the growth of mass ratio $\mu $, the unstable region increases gradually.
Fig. 9. The effects of the mass ratio $\mu $ on system stability for $\gamma =$2.6
Fig. 10. Variation of the width of unstable region versus mass ratio $\mu $
The variation of the width of unstable region versus with mass ratio $\mu $ is shown in Fig. 10. One can observe that when mass ratio $\mu $ increases, the upper bound of unstable region has little changed, but lower bound decreases obviously. Therefore, unstable region presents the tendency of increase. Moreover, the unstable region moves towards low speed zone gradually.
4.2.3. The effects of parameters changed together on unstable region
In Section 4.2.1 and Section 4.2.2, we have analyzed the effects of individual parameter on unstable region. In this section, we will take into account the combined action of fluidfill ratio $x$ and mass ratio $\mu $. The variations of unstable region are shown in Fig. 11 and Fig. 12.
Fig. 11 shows the effects of fluidfill ratio $x$ on unstable region under different mass ratio $\mu $. It can be observed that as fluidfill ratio $x$ increases, the unstable region first expands, then narrows. When the rotor chamber is fully filled with liquid, unstable region disappears, and the rotor system is stable. As mass ratio increases, unstable region moves to low speed zone gradually. From Fig. 11, it can be seen that the mass ratio $\mu $ has little influence on the width of unstable region. However, the fluidfill ratio x gives great effects, which illustrates that fluidfill ratio is the primary factor to affect the system stability. Moreover, as fluidfill ratio $x$ increases, the first critical speed of the system does not vary.
Fig. 12 gives the effects of mass ratio $\mu $ on unstable region for different fluidfill ratio $x$. It shows that the unstable region increases with the growth of mass ratio $\mu $. The fluidfill ratio $x$ has a great influence on the width of unstable region, as shown in Fig. 12. As fluidfill ratio $x$ increases, the width of unstable region increases obviously. From Fig. 12, it can be clearly seen that the first order critical speed decreases with the increase in mass ratio $\mu $, which indicates that the first order critical speed is only determined by mass ratio $\mu $.
Fig. 11. The effects of fluidfill ratio $x$ on unstable region under different mass ratio $\mu $: a) $\mu =$ 0.206, b) $\mu =$ 0.4, c) $\mu =$ 0.6, d) $\mu =$ 0.8
a)
b)
c)
d)
Fig. 12. The effects of mass ratio $\mu $ on unstable region under different fluidfill ratio $x$: a) $x=$ 0.1, b) $x=$ 0.2, c) $x=$ 0.3, d) $x=$ 0.4
a)
b)
c)
d)
5. Conclusions
An analytical solution has been introduced to solve the general whirling eigenequation of a rotor filled with liquid. The analytical results of the eigenequation was obtained and the validity of the proposed method was illustrated in the paper. A comparison was carried out between analytical calculation and numerical method. The results show that the maximum error of the two results is only 4.8 %, which illustrates the reasonability of the present calculation method. On the basis of whirling eigenequation, the system stability was analyzed and the effects of system parameters on unstable region were discussed. The performed investigations show that the dynamic instability occurs at a particular bound of the rotating speed for a rotor filled with liquid. The first order critical speed, which is only related to the mass ratio $\mu $, is less than the instability spinning speed for the rotor system. Based on the present work, it could be found that the unstable region moves to the low speed zone as mass ratio $\mu $ increases. The fluidfill ratio $x$ is the prime factor affecting the width of the unstable region. When the rotor chamber is fully filled with liquid, unstable region disappears, and the system is stable.
Acknowledgements
The authors disclosed receipt of the following financial support for the research, authorship, and/or publication of this article: The work is supported by the National Science Foundation of China (Grant No. 51775093) and the National Science Foundation of China (Grant No. 51335003).
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