# Dynamic Response of Rub Caused by a Shedding Annular Component Happening in a Steam Turbine

Authors: J. M. Chen; D. X. Jiang; N. F. Wang; S. P. An
Journal: Shock and Vibration
 (2015)

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## Abstract

Rub caused by a
shedding annular component is a severe fault
happening in a steam turbine, which could result
in a long-term wearing effect on the shaft. The
shafting abrasion defects shortened the service
life and damaged the unit. To identify the fault
in time, the dynamic response of rub caused by a
shedding annular component was studied as
follows: (I) a rotor-bearing model was
established based on the structural features of
certain steam turbines; node-to-node contact
constraint and penalty method were utilized to
analyze the impact and friction; (II) dynamic
response of the rotor-bearing system and the
shedding component was simulated with the
development of rub after the component was
dropping; (III) fault features were extracted
from the vibration near the bearing position by
time-domain and frequency-domain analysis.  The
results indicate that the shedding annular
component would not only rotate pivoting its
axis but also revolve around the shaft after a
period of time. Under the excitation of the
contact force, the peak-peak vibration
fluctuates greatly. The frequency spectrum
contains two main components, that is, the
working rotating frequency and revolving
frequency. The same phenomenon was observed from
the historical data in the field.


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## Body

## 1. Introduction

Rub is a common fault happening in rotating machinery. Big vibration and abrasion induced by rub would shorten the life of machine and even threaten the safety of operation. Therefore, the dynamic characteristics of rub attract many investigators to study.There are many different types of rub classified by reasons and damaged part. Rotor-to-stator rub is one of the most usual types, which have been studied in a lot of literatures. Jeffcott rotor is the simplest rotor-bearing system, which was used to simulate the nonlinear phenomenon by Choy and Padovan [1]. Chu and Zhang [2] acquired the periodic, quasiperiodic, and chaotic vibration of a rub-impact Jeffcott rotor. The nonlinear phenomenon was validated by experiments in the later literature [3]. The axial degree of freedom is considered in the research of An et al. [4]. The chaotic vibration of a rub-impact rotor was simulated under axial thrust. Kellenberger [5] considered frictional heating in his Jeffcott model. A spiral vibration was observed in the interaction between rotor and stator. Childs [6] revised Kellenberger’s model by considering the angle between the thermal bowing direction and the impact force.In order to study the dynamics of the shafting, transfer matrix method and finite element method were applied to analyze the rotor-to-stator rub. Qin et al. [7] constructed a multielement system to simulate the dynamics of a rub-impact overhung rotor based on transfer matrix method. This method was also used by Huang et al. [8, 9] to analyze the stability of thermal-induced vibration in a rub-impact rotor. Schmied [10] studied the rub between rotor and steam seals in a steam turbine using finite element method. One-dimensional model with multidisk and multijournal was established in the rub problem. Muszynska et al. [11, 12] revealed thermal/mechanical effect of rotor-to-stator rubs by a 1-dimensional finite element model. Bachschmid et al. [13] proposed a 3-dimensional finite element model to simulate the spiral vibration of rub-impact rotor, which was well validated by the experiment results.Comparing with rotor-to-stator rub, the rub caused by a shedding component is less usual in the field. Nevertheless, the damage of this type of rub is much severer, usually with severe wear and abrasion accompanied. A 660 MW low pressure cylinder (LP) rotor was badly abraded by the shedding of the side plate of the coupling guard [14]. The worn groove of the shaft was 10.1 mm wide and 15.2 mm deep. The same problem bothered another steam turbine unit [15]. The problem was not discovered until the unfolding cylinder in an overhaul, which results in an 80 mm wide and 28.8 mm deep worn groove. The abrasion greatly threatened the safety of the steam turbine and repairing of the LP rotor was utilized to reduce the stress concentration [16]. In order to identify the fault in time, it is significant to study the dynamic response of the rub caused by a shedding annular component.The worn LP rotor in [15] was from a supercritical steam turbine unit. The worn groove located on the shaft neck, which was 319 mm away from the coupling end, seen as in Figure 1. The worn groove was generated by the rub between the shaft and a shedding side plate, which is separated from the coupling guard.Figure 1
Worn groove of the LP rotor.In this paper, the case in [15] was studied. Based on finite element method, the dynamic model of rub caused by a shedding annular component was established. The transient analysis was conducted and the motion of the shafting and the shedding component were simulated. The results were well validated by the historical data and typical fault features were extracted from the analysis.


## 2. Methods

### 2.1. The Structure of the Steam Turbines

The steam turbine unit where the rub happens is a supercritical steam turbine unit. The scheme of the shafting is showed in Figure2. Location of the wearing is close to Bearing #3, which is between the high intermediate pressure (HIP) cylinder and the low pressure (LP) cylinder.Figure 2
Scheme of the shafting.The shedding annular component is from side plate of the coupling guard, which is a welded structure, showed in Figure3. The excitation of the blowing air generates fatigue crack at the root of the side plate and finally the side plate falls apart from the coupling guard and impact on the shaft neck of the LP rotor.Figure 3
Structure of the coupling guard.


### 2.2. Dynamics Model

#### 2.2.1. Rotor Model

Finite element method was applied to establish the rotor model. Shafting of the steam turbines could be simplified as several shaft segments. Timoshenko beam element was used for the shafting; lumped mass element was used for the blades; spring damper element was used for the journal bearing. Therefore, the rotor model was showed in Figure4.Figure 4
Finite element model of the shafting.


#### 2.2.2. Contact Condition

The shedding annular component could be regarded as a lumped mass, which includes three DOFs (degrees of freedom), that is, UX (translational DOF in horizontal direction), UY (translational DOF in vertical direction), and ROTZ (rotational DOF via the axis).The inner surface of the shedding annular component rubs with the shaft neck of the LP rotor. Figure5 shows the schematic motion, where O is the original point in the absolute coordinate system. O
1 is the center of the shaft at the rubbing plane, O
2 is the center of the shedding component, and P
1 and P
2 are, respectively, rubbing points in the rotor surface and the inner surface of the shedding component. Natural coordinate system is constructed at point P
1
(
P
2
), where n
→ is the normal unit vector, τ
→ is the tangential unit vector, and ω
→ is the unit angular velocity in the counterclockwise direction. They satisfy the equation τ
→
=
ω
→
×
n
→. θ
˙
2 is the angular velocity of the shedding annular component. δ
→
1
,
p is the displacement vector of the rotor center at the rubbing plane. δ
→
2 is the displacement vector of the shedding component.Figure 5
Schematic motion of the rotor and the shedding annular component.Node-to-node contact constraint was utilized. Contact constraint condition can be written as(1)
δ
→
1
,
p
-
δ
→
2
≤
εin which ε is the radial gap, which represents the maximum allowable distance projected on the cross-section.


### 2.3. Solution Method

The motion vector set of the shafting at every node satisfies the motion equation as follows:(2)
M
δ
→
¨
1
+
C
+
Ω
G
δ
→
˙
1
+
K
δ
→
1
=
F
→
0
+
F
→
τ
+
F
→
n
,where δ
→
1 is the translational motion vector set at every node, M is the mass matrix, C is the damping matrix, G is the gyroscopic matrix caused by gyroscopic effect, K is the stiffness matrix, Ω is the rotational speed of the rotor, F
→
0 is the harmonic excitation due to unbalance in the normal condition, F
→
τ is the frictional force vector due to rub, and F
→
n is the normal contact force vector due to rub.Pure penalty method and Coulomb Friction Law were implemented in the contact algorithm as follows:(3)
F
→
n
=
0
,
δ
→
1
,
p
-
δ
→
2
<
ε
k
δ
→
1
,
p
-
δ
→
2
-
ε
n
→
,
δ
→
1
,
p
-
δ
→
2
≥
ε
,
(4)
F
→
τ
=
-
μ
s
F
→
n
sgn
⁡
v
→
p
1
·
τ
→
-
v
→
p
2
·
τ
→
τ
→
,where k is the contact stiffness, μ
s is the frictional coefficient, the direction of F
→
τ is based on the tangential relative velocity of both contact bodies at the rubbing point, and v
→
P
1 and v
→
P
2 are, respectively, the velocity of the rotor and the shedding component at the rubbing point:(5)
v
→
P
1
=
δ
→
˙
1
,
p
+
Ω
ω
→
×
O
1
P
1
→
,
v
→
P
2
=
δ
→
˙
2
+
θ
˙
2
ω
→
×
O
2
P
2
→
.The motion equation of the shedding annular component is presented as(6)
m
2
δ
→
¨
2
=
m
2
g
→
-
F
→
τ
-
F
→
n
,
(7)
J
2
θ
¨
2
=
-
sgn
⁡
F
→
τ
·
τ
→
O
2
P
2
→
F
→
τ
,where m
2
g
→ is the gravity.Equations (2)–(7) were derived by Newmark-β method. Therefore, dynamic response of the rub caused by a shedding annular component was simulated.


## 2.1. The Structure of the Steam Turbines

The steam turbine unit where the rub happens is a supercritical steam turbine unit. The scheme of the shafting is showed in Figure2. Location of the wearing is close to Bearing #3, which is between the high intermediate pressure (HIP) cylinder and the low pressure (LP) cylinder.Figure 2
Scheme of the shafting.The shedding annular component is from side plate of the coupling guard, which is a welded structure, showed in Figure3. The excitation of the blowing air generates fatigue crack at the root of the side plate and finally the side plate falls apart from the coupling guard and impact on the shaft neck of the LP rotor.Figure 3
Structure of the coupling guard.


## 2.2. Dynamics Model

### 2.2.1. Rotor Model

Finite element method was applied to establish the rotor model. Shafting of the steam turbines could be simplified as several shaft segments. Timoshenko beam element was used for the shafting; lumped mass element was used for the blades; spring damper element was used for the journal bearing. Therefore, the rotor model was showed in Figure4.Figure 4
Finite element model of the shafting.


### 2.2.2. Contact Condition

The shedding annular component could be regarded as a lumped mass, which includes three DOFs (degrees of freedom), that is, UX (translational DOF in horizontal direction), UY (translational DOF in vertical direction), and ROTZ (rotational DOF via the axis).The inner surface of the shedding annular component rubs with the shaft neck of the LP rotor. Figure5 shows the schematic motion, where O is the original point in the absolute coordinate system. O
1 is the center of the shaft at the rubbing plane, O
2 is the center of the shedding component, and P
1 and P
2 are, respectively, rubbing points in the rotor surface and the inner surface of the shedding component. Natural coordinate system is constructed at point P
1
(
P
2
), where n
→ is the normal unit vector, τ
→ is the tangential unit vector, and ω
→ is the unit angular velocity in the counterclockwise direction. They satisfy the equation τ
→
=
ω
→
×
n
→. θ
˙
2 is the angular velocity of the shedding annular component. δ
→
1
,
p is the displacement vector of the rotor center at the rubbing plane. δ
→
2 is the displacement vector of the shedding component.Figure 5
Schematic motion of the rotor and the shedding annular component.Node-to-node contact constraint was utilized. Contact constraint condition can be written as(1)
δ
→
1
,
p
-
δ
→
2
≤
εin which ε is the radial gap, which represents the maximum allowable distance projected on the cross-section.


## 2.2.1. Rotor Model

Finite element method was applied to establish the rotor model. Shafting of the steam turbines could be simplified as several shaft segments. Timoshenko beam element was used for the shafting; lumped mass element was used for the blades; spring damper element was used for the journal bearing. Therefore, the rotor model was showed in Figure4.Figure 4
Finite element model of the shafting.


## 2.2.2. Contact Condition

The shedding annular component could be regarded as a lumped mass, which includes three DOFs (degrees of freedom), that is, UX (translational DOF in horizontal direction), UY (translational DOF in vertical direction), and ROTZ (rotational DOF via the axis).The inner surface of the shedding annular component rubs with the shaft neck of the LP rotor. Figure5 shows the schematic motion, where O is the original point in the absolute coordinate system. O
1 is the center of the shaft at the rubbing plane, O
2 is the center of the shedding component, and P
1 and P
2 are, respectively, rubbing points in the rotor surface and the inner surface of the shedding component. Natural coordinate system is constructed at point P
1
(
P
2
), where n
→ is the normal unit vector, τ
→ is the tangential unit vector, and ω
→ is the unit angular velocity in the counterclockwise direction. They satisfy the equation τ
→
=
ω
→
×
n
→. θ
˙
2 is the angular velocity of the shedding annular component. δ
→
1
,
p is the displacement vector of the rotor center at the rubbing plane. δ
→
2 is the displacement vector of the shedding component.Figure 5
Schematic motion of the rotor and the shedding annular component.Node-to-node contact constraint was utilized. Contact constraint condition can be written as(1)
δ
→
1
,
p
-
δ
→
2
≤
εin which ε is the radial gap, which represents the maximum allowable distance projected on the cross-section.


## 2.3. Solution Method

The motion vector set of the shafting at every node satisfies the motion equation as follows:(2)
M
δ
→
¨
1
+
C
+
Ω
G
δ
→
˙
1
+
K
δ
→
1
=
F
→
0
+
F
→
τ
+
F
→
n
,where δ
→
1 is the translational motion vector set at every node, M is the mass matrix, C is the damping matrix, G is the gyroscopic matrix caused by gyroscopic effect, K is the stiffness matrix, Ω is the rotational speed of the rotor, F
→
0 is the harmonic excitation due to unbalance in the normal condition, F
→
τ is the frictional force vector due to rub, and F
→
n is the normal contact force vector due to rub.Pure penalty method and Coulomb Friction Law were implemented in the contact algorithm as follows:(3)
F
→
n
=
0
,
δ
→
1
,
p
-
δ
→
2
<
ε
k
δ
→
1
,
p
-
δ
→
2
-
ε
n
→
,
δ
→
1
,
p
-
δ
→
2
≥
ε
,
(4)
F
→
τ
=
-
μ
s
F
→
n
sgn
⁡
v
→
p
1
·
τ
→
-
v
→
p
2
·
τ
→
τ
→
,where k is the contact stiffness, μ
s is the frictional coefficient, the direction of F
→
τ is based on the tangential relative velocity of both contact bodies at the rubbing point, and v
→
P
1 and v
→
P
2 are, respectively, the velocity of the rotor and the shedding component at the rubbing point:(5)
v
→
P
1
=
δ
→
˙
1
,
p
+
Ω
ω
→
×
O
1
P
1
→
,
v
→
P
2
=
δ
→
˙
2
+
θ
˙
2
ω
→
×
O
2
P
2
→
.The motion equation of the shedding annular component is presented as(6)
m
2
δ
→
¨
2
=
m
2
g
→
-
F
→
τ
-
F
→
n
,
(7)
J
2
θ
¨
2
=
-
sgn
⁡
F
→
τ
·
τ
→
O
2
P
2
→
F
→
τ
,where m
2
g
→ is the gravity.Equations (2)–(7) were derived by Newmark-β method. Therefore, dynamic response of the rub caused by a shedding annular component was simulated.


## 3. Results and Discussion

### 3.1. Dynamics of the Shedding Annular Component

Dynamics of the shedding annular component was acquired from the simulated results. Figure6 shows the contact status after the shedding, where “1” represents contact and “0” represents separation. In the beginning, partial rub happens and the time between every two contacts is becoming shorter with the development of rub. Finally, the partial rub develops into full annular rub.Figure 6
Contact status.
(a)
0–80 s
(b)
2-3 sBased on (6) and (7), the shedding annular component functions by the contact and frictional force and gravity, whose trajectory is showed in Figure 7. After several contacts with the shaft neck of LP rotor, the shedding component makes revolving motion in clockwise direction. The radius of the trajectory is the radius gap ε. The revolving speed is showed in Figure 8. In the full annular rub state, the revolving speed ω
r decreases with the development of rub and finally stays in a steady value.Figure 7
Trajectory of the shedding annular component.Figure 8
Rotating speed and revolving speed.Different from the revolving speed, the rotating speedθ
˙
2 rises rapidly while entering the full annular rub state and then increases slowly approaching a steady value. The rotating speed and revolving speed of the shedding component are controlled by (4)-(5), (7), which approximately satisfy(8)
ε
O
1
P
1
→
ω
r
+
O
2
P
2
→
O
1
P
1
→
θ
˙
2
=
Ω
.


### 3.2. Dynamics of the Rotor-Bearing System

Dynamic response of the rotor-bearing system was influenced by the contact force and frictional force. Figure9 shows the displacement vibration of the rotor in Y direction at the rubbing plane (vibration in X direction got similar characteristics). From the figure, the rub results in a big vibration fluctuation after developing into the full annular rub state. Beat vibration is observed, which indicates that the frequency of the contact and frictional force is different from the working rotating frequency. The frequency is actually the revolving frequency of the shedding annular component.Figure 9
Y vibration of the rotor at the rubbing plane.
(a)
0–80 s
(b)
2.5–3.5 sWith the development of the rub, the fluctuation is becoming small, which is due to the decrease of the contact force, seen as in Figure10.Figure 10
Contact force.As only vibration near the bearing position could be monitored, it is more important to analyze the vibration at Bearings #1–7, which is displayed in Figure11. The vibration at Bearing #3 is the most sensitive to the rub. Therefore, it is necessary to extract fault feature from the vibration at Bearing #3.Figure 11
Y vibration of the rotor near each bearing.


### 3.3. Fault Feature and Validation

The peak-peak value of the vibration is the most useful index to evaluate the operation status in the field. Figure12 shows the peak-peak value of the simulated vibration at Bearing #3. The envelope curve indicates that a sharp fluctuation exists while entering full annular rub state. After a short period of decrease, the fluctuation amplitude reaches an extreme small value until ω
r
≈
0.5
Ω, which is introduced by the superposition of the vibration in 1x and 0.5x frequency. After the extreme small point, the fluctuation amplitude increases in some extent and then reduces slowly into the steady state with the development of rub.Figure 12
Peak-peakY vibration value of the rotor at Bearing #3 (simulated).
(a)
0–80 s
(b)
2–5 sThe same phenomenon was observed based on the monitoring system of this unit, as seen in Figure13. The fluctuation takes about 40 days to reach a relative stable state, while in the simulated results, it takes less than 80 seconds. The reason for the difference in stabilization time is that a higher frictional coefficient μ
s is given in the simulation. The stabilization time depends on μ
s. However, it is impossible to simulate such a real long time in a transient analysis, because the time step should be small enough to acquire the dynamic characteristics in a revolution.Figure 13
Time history of peak-peakY vibration of Bearing #3.Despite the difference in stabilization time, the simulated results could reflect the dynamic feature of the rub caused by a shedding annular component in real situation. Therefore, the fault feature in the peak-peak curve is the big fluctuation.The fault feature could also be extracted in the spectrum analysis. Figure14 shows the spectrum waterfall of the Y vibration at Bearing #3. Despite the 1x frequency component, an extra frequency component appears after the rub happens, which changes from 0.875x to 0.25x. The corresponding amplitude of the extra frequency component decreases from 40.7 μm to 4.1 μm. The extra frequency could be regarded as a fault feature to identify the rub caused by a shedding annular component.Figure 14
Spectrum waterfall ofY vibration at Bearing #3.


## 3.1. Dynamics of the Shedding Annular Component

Dynamics of the shedding annular component was acquired from the simulated results. Figure6 shows the contact status after the shedding, where “1” represents contact and “0” represents separation. In the beginning, partial rub happens and the time between every two contacts is becoming shorter with the development of rub. Finally, the partial rub develops into full annular rub.Figure 6
Contact status.
(a)
0–80 s
(b)
2-3 sBased on (6) and (7), the shedding annular component functions by the contact and frictional force and gravity, whose trajectory is showed in Figure 7. After several contacts with the shaft neck of LP rotor, the shedding component makes revolving motion in clockwise direction. The radius of the trajectory is the radius gap ε. The revolving speed is showed in Figure 8. In the full annular rub state, the revolving speed ω
r decreases with the development of rub and finally stays in a steady value.Figure 7
Trajectory of the shedding annular component.Figure 8
Rotating speed and revolving speed.Different from the revolving speed, the rotating speedθ
˙
2 rises rapidly while entering the full annular rub state and then increases slowly approaching a steady value. The rotating speed and revolving speed of the shedding component are controlled by (4)-(5), (7), which approximately satisfy(8)
ε
O
1
P
1
→
ω
r
+
O
2
P
2
→
O
1
P
1
→
θ
˙
2
=
Ω
.


## 3.2. Dynamics of the Rotor-Bearing System

Dynamic response of the rotor-bearing system was influenced by the contact force and frictional force. Figure9 shows the displacement vibration of the rotor in Y direction at the rubbing plane (vibration in X direction got similar characteristics). From the figure, the rub results in a big vibration fluctuation after developing into the full annular rub state. Beat vibration is observed, which indicates that the frequency of the contact and frictional force is different from the working rotating frequency. The frequency is actually the revolving frequency of the shedding annular component.Figure 9
Y vibration of the rotor at the rubbing plane.
(a)
0–80 s
(b)
2.5–3.5 sWith the development of the rub, the fluctuation is becoming small, which is due to the decrease of the contact force, seen as in Figure10.Figure 10
Contact force.As only vibration near the bearing position could be monitored, it is more important to analyze the vibration at Bearings #1–7, which is displayed in Figure11. The vibration at Bearing #3 is the most sensitive to the rub. Therefore, it is necessary to extract fault feature from the vibration at Bearing #3.Figure 11
Y vibration of the rotor near each bearing.


## 3.3. Fault Feature and Validation

The peak-peak value of the vibration is the most useful index to evaluate the operation status in the field. Figure12 shows the peak-peak value of the simulated vibration at Bearing #3. The envelope curve indicates that a sharp fluctuation exists while entering full annular rub state. After a short period of decrease, the fluctuation amplitude reaches an extreme small value until ω
r
≈
0.5
Ω, which is introduced by the superposition of the vibration in 1x and 0.5x frequency. After the extreme small point, the fluctuation amplitude increases in some extent and then reduces slowly into the steady state with the development of rub.Figure 12
Peak-peakY vibration value of the rotor at Bearing #3 (simulated).
(a)
0–80 s
(b)
2–5 sThe same phenomenon was observed based on the monitoring system of this unit, as seen in Figure13. The fluctuation takes about 40 days to reach a relative stable state, while in the simulated results, it takes less than 80 seconds. The reason for the difference in stabilization time is that a higher frictional coefficient μ
s is given in the simulation. The stabilization time depends on μ
s. However, it is impossible to simulate such a real long time in a transient analysis, because the time step should be small enough to acquire the dynamic characteristics in a revolution.Figure 13
Time history of peak-peakY vibration of Bearing #3.Despite the difference in stabilization time, the simulated results could reflect the dynamic feature of the rub caused by a shedding annular component in real situation. Therefore, the fault feature in the peak-peak curve is the big fluctuation.The fault feature could also be extracted in the spectrum analysis. Figure14 shows the spectrum waterfall of the Y vibration at Bearing #3. Despite the 1x frequency component, an extra frequency component appears after the rub happens, which changes from 0.875x to 0.25x. The corresponding amplitude of the extra frequency component decreases from 40.7 μm to 4.1 μm. The extra frequency could be regarded as a fault feature to identify the rub caused by a shedding annular component.Figure 14
Spectrum waterfall ofY vibration at Bearing #3.


## 4. Conclusion

The rub caused by a shedding annular component was studied in this paper. Based on a real case, finite element method was used to establish the dynamic model of the rotor-bearing system and the shedding component. Node-to-node contact constraint condition was applied. Pure penalty algorithm and Coulomb Friction Law were utilized to control the behavior of contact and friction. As a result, the dynamic response of rub caused by a shedding annular component was simulated.Simulated results show that the rub would develop into full annular rub and the shedding component would revolve pivoting the shaft after dropping. The contact force periodically functions on the rotor-bearing system, which results in beat vibration. As a result, a big fluctuation in peak-peak vibration and an extra decreasing frequency component in the spectrum could be observed, which could be validated by the time history data in the field. Therefore, these two fault features could be used to identify the rub caused by a shedding annular component.



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*Source: 607674-2015-05-28.xml*