01.12.2020  Original Article  Ausgabe 1/2020 Open Access
Residual Stress Relaxation of Thinwalled Long Stringer Made of Aluminum Alloy 7050T7451 under Transportation Vibration
 Zeitschrift:
 Chinese Journal of Mechanical Engineering > Ausgabe 1/2020
1 Introduction
The long stringer is a longitudinal member of the fuselage structure, which is mainly used to bear the axial force caused by the bending of the fuselage. It has high requirements for geometric accuracy and stress status [
1–
4]. The first few natural frequencies of thinwalled long stringer are within the range of the power spectral density of road transport acceleration. The stringer inevitably resonates during road transportation. When the resonance causes residual stress relaxation or the combined stress of vibration stress and initial stress exceeds the yield strength, the stringer will be deformed. This leads to assembly difficulties and impairs service performance [
5–
9].
Many scholars studied the residual stress relaxation problems under cyclic loading such as vibratory stress relief and fatigue [
10–
17]. It has been found that the rate of residual stress relaxation can be drastic in the first few cycles due to the static effect. In the subsequent cyclic loading, the residual stress gradually relaxes. The amount of residual stress relaxation is logarithmically related to the loading cycle. Kodama measured the residual stress relaxation on the surface of shot peened specimens by Xray diffraction [
18]. Experimental data indicates that the residual stress decreases linearly with the loading cycle. Based on the applied stress amplitude and the loading cycle, a concise linear logarithmic analytical model was proposed. Han studied the redistribution of the residual stress around the weld of welded steel members by the applied load [
19]. Under cyclic loading, the residual stress is greatly relaxed in the early cycles, and then gradually relaxes with the increase of the loading cycle. An analytical model was established based on the linear relaxation of the residual stress to quantitatively predict the residual stress relaxation. Zhuang et al. [
20] used the finite element analysis method to simulate the relaxation of surface residual stress according to the Bauschinger effect, and established an analytical model of the residual stress relaxation. The parameters of the model include the magnitude and distribution of residual stress, the cold working, the applied stress and the loading cycle.
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Residual stress relaxation causes the deformation of parts [
21]. The relationship between residual stress and deformation can be studied through experiments or finite element simulations [
22–
24]. Meng et al. proposed a method to measure the equivalent residual stress and depths of the affected layers [
25]. The corresponding deformations caused by the milling induced residual stress can be predicted in workpieces with different rigidities. Huang studied the principal influence factors on the monolithic component deformation by finite element simulations and experiments [
26]. The result shows that the deformation caused by the blank initial residual stress accounted for 90% of the total deformation of the component. Masoudi et al. studied the relationship between residual stress and deformation under different processing conditions by doing turning experiments on 7075T6 aluminum alloy thinwalled cylinders [
27]. The deformation of the thinwalled cylinder increases with the increase of the cutting force and the cutting heat.
The material residual stress relaxation model under complex loading conditions and the residual stress relaxation spatial distribution model on complex structures are essential foundations for evaluating the transportation deformation of structural parts of aviation. In the case of transport resonance, the vibration frequency range is vast, and the distribution of the resonance region is complicated. The vibration cycles and the vibration stress values of each position are greatly different, so the residual stress relaxation at each position and the resulted deformation are also large. In this paper, the vibration modes of long stringer made of aluminum alloy 7050T7451 during transportation were studied. The spatial distribution model of residual stress relaxation was constructed. The deflection of the long stringer was evaluated under typical transportation conditions.
2 Experimental Details
2.1 Random Response Analysis of the Long Stringer
The geometric size of the long stringer is 5000 mm × 200 mm × 50 mm, and the wall thickness is 1.5 mm. The material parameters are shown in Table
1. The constraints of the long stringer during the plant turnover are AB and CD hinges, as shown in Figure
1. PSD curves refer to ASTM D472806 for power spectral density of highway transportation acceleration in Table
2 [
28], the vibration stress and displacement of the long stringer during road transportation were simulated and analyzed.
Table 1
Material parameters of aluminum alloy 7050T7451
Density (g/cm
^{3})

Young’s modulus (GPa)

Poisson’s ratio

Yield strength (MPa)


2.83

70.3

0.33

449

Table 2
PSD of road transport acceleration
Frequency (Hz)

PSD (g
^{2}/Hz)


1

0.00005

4

0.01

16

0.01

40

0.001

80

0.001

200

0.00001

×
The damping ratio of aluminum alloy is generally between 0.01 and 0.03. The random response analysis of the long stringer was simulated under different damping ratios using ABAQUS. As shown in Table
3, the first 21 natural frequencies of the long stringer are all within 0–200 Hz. The first natural frequency of the long stringer is 9.04 Hz. The maximum values of vibration stress
σ
_{x} and displacement
U
_{z} of the long stringer occurs in the first mode, so they are the research objects in this paper. Taking the damping ratio of 0.012 as an example,
σ
_{x} and
U
_{z} of the first mode of the long stringer are shown in the Figure
2. The high residual stress region and the high displacement region in the long stringer are at the top of the middle sidewall.
σ
_{xmax} and
U
_{zmax} of the first mode of the long stringer under different damping ratios are shown in Table
4.
Table 3
Natural frequencies of the long stringer in different modes
Mode

Natural frequency (Hz)

Mode

Natural frequency (Hz)


1

9.0427

12

123.90

2

13.500

13

150.95

3

23.477

14

151.06

4

28.905

15

154.78

5

34.254

16

156.76

6

39.065

17

171.93

7

57.782

18

175.68

8

61.190

19

178.29

9

64.263

20

189.55

10

103.59

21

199.43

11

113.03

22

204.29

Table 4
σ
_{xmax} and
U
_{zmax} of the first mode of the long stringer under different damping ratios
Damping ratio

σ
_{xmax} (MPa)

U
_{zmax} (mm)


0.01

578.0

85.9

0.012

401.4

59.7

0.014

294.9

43.9

0.016

225.8

33.6

0.018

178.4

26.5

0.02

144.5

21.5

0.03

64.3

9.5

×
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As shown in Table
4,
σ
_{xmax} decreases with the increase of the damping ratio. Under different damping ratios, the equivalent stress of resonance stress and initial residual stress may lead to three cases:
(1)
The equivalent stress is low and the material does not undergo irreversible changes;
(2)
The equivalent stress exceeds the yield strength of the material and the material will plastically deform;
(3)
Several cycles of the equivalent stress within a certain range causes local residual stress relaxation. And the rebalance stress leads to deformation of the part.
In order to grasp the local residual stress relaxation law in the case of (3), the cyclic loading experiment of aluminum alloy 7050T7451 samples under different loading stress levels was carried out, and the residual stress relaxation was observed by residual stress tester.
2.2 Sample Preparation and Selection
Aluminum alloy 7050T7451 is a typical solution strengthening wrought aluminum alloy. After heat treatment and prestretching, the internal stress is within ± 20 MPa [
29]. For the milled parts, the stress of the deformation layer is much larger than the internal stress, and stress relaxation is prone to occur. The stress relaxation in the longitudinal direction of the long stringer is the main cause of the deflection. Therefore, this paper simplified the stress of the deformation layer into the twodimensional residual stress and discussed the effect of the stress relaxation in the longitudinal direction on the deflection of the long stringer.
The size of the sample is designed according to the standard of tensile testing. The sample is clamped with a vise and 2 spacers, as shown in Figure
3. The sample was milled using a milling tool under emulsion cooling conditions. The milling tool’s diameter is 12 mm with 2 blades. The blade length is 45 mm. Milling parameters are:
n = 4000 r/min,
f = 4000 mm/min,
a
_{p}= 30 mm. First roughing
a
_{e1}= 0.8 mm, then finishing
a
_{e2}= 1 mm. A total of 18 samples were made. The residual stress was measured with the μX360 Xray diffractometer at the center point of the sample surface shown in Figure
4. The μX360 Xray diffractometer is shown in Figure
5. Five samples with good stress amplitude consistency were selected for subsequent experiments and analysis. Their residual stress values are shown in Table
5.
Table 5
Sample 15 surface residual stress
Sample number

σ
_{x} (MPa)

Stand deviation (MPa)

σ
_{y} (MPa)

Stand deviation (MPa)


1

198

32

190

16

2

206

25

188

18

3

194

18

206

34

4

189

23

205

12

5

197

18

189

14

Mean value

196.8

23.2

195.6

18.8

×
×
×
2.3 Cyclic Loading Experiment Parameters
In general, when the equivalent stress is lower than the cyclic elastic limit, the residual stress does not change. The cyclic elastic limit is considered to be 0.8
σ
_{0.2} [
30,
31]. Therefore, the equivalent stress levels were set at around 0.8
σ
_{0.2}, which were 0.65
σ
_{0.2}, 0.75
σ
_{0.2}, 0.85
σ
_{0.2}, and 0.95
σ
_{0.2}. The residual stress in the depth direction was ignored so that the residual stress in the
Zdirection
σ
_{z} was considered to be 0. The experiment was based on the distortion energy density theory (the fourth strength theory) and the Mises yield criterion to determine the loading stress [
32–
34], the loading stress was calculated in the
Xdirection at different equivalent stress levels as in Eq. (
1):
where
K is the equivalent stress level coefficient, which is 0.65 or 0.75 or 0.85 or 0.95, respectively;
σ
_{0.2} is the nominal yield strength;
σ
_{xsuf} is the surface stress in the
Xdirection of the sample;
σ
_{ysuf} is the surface stress in the
Ydirection of the sample;
σ
_{LK} is loading stress in the
Xdirection.
$$K\sigma_{0.2} = \sqrt {\left( {\sigma_{xsuf} + \sigma_{LK} } \right)^{2} + \sigma_{ysuf}^{2}  \left( {\sigma_{xsuf} + \sigma_{LK} } \right)\sigma_{ysuf} } ,$$
(1)
The cyclic loading experiment waveform is a sine wave with a frequency of 10 Hz. In order to avoid buckling of the samples under compressive stress, only the pulling force was applied in this experiment by the MTS stretching machine, as shown in Figure
6. The stress cycle characteristic
r is 0.1. According to Eq. (
1), the cyclic loading experiment parameters are shown in Table
6. After 10000 cycles, the residual stress on the surface of the samples was measured.
Table 6
Cyclic loading stress parameters
Initial residual stress (MPa)

Sample number

Equivalent stress level

Loading stress (MPa)

Loading force peak (N)

Loading force valley (N)


σ
_{xsuf}= 196.8
σ
_{ysuf}= 195.6

1

0.65σ
_{0.2}

139

5560

556

2

0.75σ
_{0.2}

192

7680

768


3

0.85σ
_{0.2}

243

9720

972


4

0.95σ
_{0.2}

292

11680

1168


5

‒

‒

‒

‒

×
3 Results and Discussion
3.1 Residual Stress on the Surface of the Sample after Cyclic Loading
The residual stress on the surface of the samples 1‒4 before and after cyclic loading is shown in Figure
7.
×
As can be seen from Figure
7, the
σ
_{x} of the samples 1 and 2 slightly increased after cyclic loading for 10000 periods. When the equivalent stress exceeds 0.8
σ
_{0.2}, the
σ
_{x} of the sample 3 decreases by 31 MPa, and the
σ
_{x} of the sample 4 decreases by 43 MPa. The fluctuations of the
σ
_{y} of the samples 1, 2, and 3 are all within 5 MPa, and the surface
σ
_{y} of the sample 4 decreases by 14 MPa. Since the measurement error of the instrument does not exceed 20 MPa, it can be considered that the
σ
_{x} of the samples 3 and 4 exhibits significant residual stress relaxation. It can be seen that when the equivalent stress is between 0.8
σ
_{0.2}‒1.0
σ
_{0.2}, the residual stress is relaxed after cyclic loading. Therefore, the cyclic elastic limit of the aluminum alloy 7050T7451 is about 0.8
σ
_{0.2}. When the equivalent stress is larger than 0.8
σ
_{0.2}, the residual stress relaxation and the stress redistribution occur after cyclic loading.
The material at the center point of the sample surface was removed by electropolishing, and the residual stress in the depth direction was measured. Using the unloaded sample 5 as a reference, the residual stress changes in the depth direction of the 5 samples are shown in Figure
8.
×
As can be seen from Figure
8, the peak of the residual stress
σ
_{x} appears at 7.42 μm below the machined surface, and the peak of the cutting residual stress
σ
_{y} appears on the machined surface. When the depth is about 40 μm, the values of
σ
_{x} and
σ
_{y} are both close to 0. The
σ
_{x} peaks (7.42 μm) of samples 1‒4 after cyclic loading were reduced by 17 MPa, 45 MPa, 67 MPa, and 90 MPa, respectively. The peak equivalent stress levels of samples 1‒4 were calculated based on the peak residual stress of Sample 5, as shown in Table
7. The results show that the peak equivalent stress of samples 1‒4 is not less than 0.8
σ
_{0.2}. The decrease of residual stress peak is mainly due to residual stress relaxation and plastic deformation, and the reduction amplitude increases with the equivalent stress.
Table 7
Surface and peak equivalent stress level
Sample number

Surface equivalent stress level

Peak equivalent stress level


1

0.65
σ
_{0.2}

0.80
σ
_{0.2}

2

0.75
σ
_{0.2}

0.91
σ
_{0.2}

3

0.85
σ
_{0.2}

1.02
σ
_{0.2}

4

0.95
σ
_{0.2}

1.12
σ
_{0.2}

5

‒

‒

3.2 Residual Stress Relaxation Analytical Model of Aluminum Alloy 7050T7451
Kodama measured the reduction of residual stress on the surface of shotpeened specimens by Xray diffraction method and proposed a linear logarithm model [
9]. However, the experimental data only supports the phenomenon that the residual stress decreases linearly with the loading cycle, and it is impossible to predict a large amount of relaxation of the stress in the first cycle. Therefore, combined with the previous experiment results, the equivalent stress coefficient
K and the cyclic elastic limit 0.8
σ
_{0.2} are used to characterize the relaxation of the
Xdirection residual stress in the first cycle. The logarithmic model of Kodama is modified to obtain an analytical model of residual stress relaxation of aluminum alloy 7050T7451, as shown in Eqs. (
2) and (
3):
where
N is the number of cycles;
\(\sigma_{\text{re}}^{\text{N}}\) is the value of the residual stress relaxation after
N cycles; the coefficient m depends on the material;
A is the value of the first loading residual stress relaxation;
K is the equivalent stress level coefficient;
σ
_{0.2} is the nominal yield strength; the coefficient n is the correction factor.
$$\sigma_{re}^{N} = A + m\lg N,$$
(2)
$$A = n(K  0.8)\sigma_{0.2} ,\;K \ge 0.8,$$
(3)
According to the experiment results, the values of
Xdirection residual stress relaxation after 10000 cycles of loading were obtained. The overdetermined equation was solved by using the data of the residual stress relaxation at the surface and the peak. The residual stress relaxation values exceeding 20 MPa were selected to establish an analytical model. The specific data is shown in Table
8.
Table 8
Residual stress relaxation values
Group

Depth (μm)

Sample number

N

σ
_{0.2} (MPa)

\(\sigma_{re}^{10000}\) (MPa)

K


a

0 (Surface)

3

10000

449

31

0.85

b

0 (Surface)

4

43

0.95


c

7.42 (Peak)

2

39

0.91


d

7.42 (Peak)

3

67

1.02


e

7.42 (Peak)

4

90

1.12

According to the five groups of data, the least squares solutions of m and n were respectively 3.78 and 0.51, and the analytical model is shown in Eq. (
4):
$$\sigma_{re}^{N} = 0.51\left( {K  0.8} \right) \sigma_{0.2} + 3.78\lg N.$$
(4)
In summary, the magnitude of residual stress relaxation is mainly related to the magnitude of the equivalent stress and the loading cycle. The higher the equivalent stress is, the greater the residual stress relaxation is at the first cycle. The larger the loading cycle is, the greater the residual stress relaxation is. According to the analytical model Eq. (
4), the residual stress relaxation values of the five groups under 10000 cycles of loading were calculated. The errors were calculated by comparing the analytical results (
\(\sigma_{an}^{10000}\)) with the experimental results (
\(\sigma_{re}^{10000}\)), which are shown in Table
9.
Table 9
Comparison of analytical results with experimental results
Group

\(\sigma_{re}^{10000}\) (MPa)

\(\sigma_{an}^{10000}\) (MPa)

Error (%)


a

31

27

− 12.90

b

43

49

13.95

c

39

40

2.56

d

67

65

− 2.99

e

90

88

− 2.22

It can be seen from Table
9 that the errors of the analytical model are within 15%, which can accurately quantify the relaxation of residual stress and characterize the evolution of residual stress relaxation.
4 Transport Deformation Assessment of the Long Stringer
According to the random response analysis results, the high residual stress region in the long stringer is at the top of the middle sidewall. It can be considered as an applied stress. The residual stress relaxation is caused by the equivalent stress. This paper calculated the deformation of the part caused by the residual stress relaxation of the surface layer. According to Table
4, Table
6 and Table
7, when the damping ratio is less than 0.016, the part undergoes plastic deformation and residual stress relaxation; between 0.016 and 0.02, the stress is relaxed; if it is greater than 0.02, there is no change. Taking the damping ratio of 0.012 as an example, the equivalent stress levels which are greater than 0.65
σ
_{0.2} are the regions of red, yellow, green and blue. The regions 1‒7 correspond to different levels of residual stress relaxation regions, as shown in Figure
9. According to the location and size of the residual stress relaxation, the bending deformation of the long stringer under random vibration was calculated. In order to facilitate the calculation, the model was simplified, and the ribs in the long stringer were ignored. A schematic cross section is shown in Figure
10.
×
×
The calculation results of the centroid (
z
_{c}) and the moment of inertia (
I
_{y}) of the part are shown in Eqs. (
5) and (
6), respectively. The deflection and the end section angle are calculated according to the deflection curve equation:
where
H is the height of the part;
W is the width of the part;
b
_{1} is the thickness of the side wall;
b
_{2} is the thickness of the web;
h
_{1} is the depth of the residual stress relaxation region;
h
_{2} is the height of the residual stress relaxation region;
M is the bending moment due to residual stress relaxation;
\(\sigma_{re}^{N} ( {h)}\) is the function of the residual stress relaxation in depth;
z is the height of the residual stress relaxation region from the
Y axis;
ω is the deflection of the residual stress relaxation region;
L is the length of the residual stress relaxation region;
E is Young’s modulus;
θ is the end section angle of the residual stress relaxation region.
$$z_{c} = \frac{{2b_{1} H^{2} + \left( {W  2b_{1} } \right)b_{2}^{2} }}{{4b_{1} H + 2\left( {W  2b_{1} } \right)b_{2} }},$$
(5)
$$I_{y} = \frac{{Wz_{c}^{3} + \left( {W  2b_{1} } \right)\left( {b_{2}  z_{c} } \right)^{3} + 2b_{1} \left( {H  z_{c} } \right)^{3} }}{3},$$
(6)
$$M = \mathop \int \limits_{{H  h_{2} }}^{H} \mathop \int \limits_{0}^{{h_{1} }} 4\sigma_{re}^{N} \left( h \right)\left( {z  z_{c} } \right){\text{d}}h{\text{d}}z,$$
(7)
$$\omega = \left\{ \begin{array}{l} \frac{{ML^{2} }}{{8EI_{y} }},\quad (\text{region}\;4), \hfill \\ \frac{{ML^{2} }}{{2EI_{y} }},\quad ({\text{regions }}1{ } 3,\;5 {} 7), \hfill \\ \end{array} \right.$$
(8)
$$\theta = \left\{ \begin{array}{l} \frac{ML}{{2EI_{y} }},\quad (\text{region}\; 4), \hfill \\ \frac{ML}{{EI_{y} }},\quad ({\text{regions}}\;1{ } 3,\;5 {} 7), \hfill \\ \end{array} \right.$$
(9)
According to the residual stress distribution model of the long stringer, the stress distribution region was simplified to be symmetrical at both ends. The maximum deflection of the long stringer is divided into two parts: the deflection of the different regions and the deflection caused by the angle of the end section. The schematic diagram of the total deflection of the long stringer is shown in Figure
11, and the calculation formula is shown in Eq. (
10):
where
ω
_{max} is the maximum deflection of the part;
ω
_{i} is the deflection of different regions;
θ
_{i} is the end section angle of different regions;
L
_{i} is the length from the end section of different regions to one side.
$$\omega_{ \text{max} } \approx \mathop \sum \limits_{i = 1}^{4} \omega_{i} + \mathop \sum \limits_{i = 1}^{4} L_{i} { \tan }\theta_{i} \approx \mathop \sum \limits_{i = 1}^{4} \omega_{i} + \mathop \sum \limits_{i = 1}^{4} L_{i} \theta_{i} ,$$
(10)
×
The actual size of the long stringer is:
H = 50 mm,
W = 200 mm,
b
_{1}= 1.5 mm,
b
_{2}= 1.5 mm. Since the residual stress value is close to 0 at the depth of about 40 μm, the subsequent residual stress value fluctuates around 0, so it is considered that
h
_{1}= 0.04 mm.
\(\mathop \smallint \nolimits_{ 0}^{ 0. 0 4} \sigma_{re}^{N} ( {h)\text{d}h}\) was calculated from the difference between the stress curve of the sample 5 and the stress curve of the samples 1‒4.
M is the sum of the bending moments generated by the residual stress relaxation in different residual stress relaxation regions. The calculation formula is shown in Eq. (
11):
$$M_{i} = M_{i}^{0.65} + M_{i}^{0.75} + M_{i}^{0.85} + M_{i}^{0.95} .$$
(11)
The subscript
i indicates the different residual stress relaxation regions;
M
_{i} is the bending moment of different residual stress relaxation regions;
\(M_{i}^{0.65} ,\, M_{i}^{0.75} ,\, M_{i}^{0.85}\, {\text{and}}\, M_{i}^{0.95}\) are the bending moments of the different equivalent stress level at different positions of the same residual stress relaxation region.
The result was approximately calculated based on the data of the simulation results. The ABAQUS query function was used to obtain the height values of
\(M_{i}^{0.65} ,\, M_{i}^{0.75} ,\, M_{i}^{0.85}\, {\text{and }}\,M_{i}^{0.95}\) and the length values of Li. According to Eqs. (
5)‒(
11), deflections of the long stringer under different damping ratios were calculated. The results are shown in Table
10.
Table 10
Deflections of the long stringer under different damping ratios
Damping ratios

Status

\(\omega_{ \text{max} }\) (mm)


0.01

Residual stress relaxation + plastic deformation

1.55

0.012

Residual stress relaxation + plastic deformation

0.85

0.014

Residual stress relaxation + plastic deformation

0.34

0.016

Residual stress relaxation

0.12

0.018

Residual stress relaxation

0.02

0.02

No change

0

0.03

No change

0

It can be seen from Table
10 that under different damping ratios, the deflection of the long stringer is varied by the transport resonance stress, and the deflection decreases as the damping ratio increases. It is obvious from Eq. (
8) that the deflection of the part due to residual stress relaxation is proportional to the bending moment of the stress rebalance and the square of the length of the part, and inversely proportional to the moment of inertia of the part structure. As the damping ratio decreases from 0.03 to 0.01, the total deflection of the long stringer increases from 0 to above 1.55 mm. When the long stringer is under severe transportation conditions, the residual stress relaxation will occur, which results in deformation. Therefore, the deformation of large thinwalled parts during transportation vibration should be prevented.
5 Conclusions
In this paper, random response analysis of the long stringer under transportation vibration was carried out. The residual stress evolution law of aluminum alloy 7050T7451 under 10000 cycles of different equivalent stress levels was studied. The residual stress relaxation was quantified and a reasonable analytical model was established. The deflection of the long stringer was evaluated. The conclusions below have been arrived at:
(1)
Resonance occurs in the transportation of long stringer made of aluminum alloy 7050T7451. The resonance stress is the largest at the first natural frequency, which is prone to causing deformation. The resonance stress decreases with the increase of the damping ratio.
(2)
When the equivalent stress exceeds 0.8
σ
_{0.2}, the stress of the samples begins to relax. The amount of residual stress relaxation increases with the equivalent stress, which is linearly logarithmically related to the loading cycle. Based on the traditional logarithmic model, an analytical model related to the equivalent stress coefficient and the cyclic elastic limit is proposed. Compared with the experimental results, the errors are within 15%.
(3)
The residual stress relaxation of the surface layer caused the deformation of the long stringer. The deflection of the part due to residual stress relaxation is proportional to the bending moment of the stress rebalance and the square of the length of the part, and inversely proportional to the moment of inertia of the part structure. As the damping ratio decreases from 0.03 to 0.01, the total deflection of the long stringer increases from 0 to above 1.55 mm.
Acknowledgements
The authors sincerely thank to Xuming Niu and Xihui Chen of College of Energy and Power for their critical discussion and reading during manuscript preparation.
Competing Interests
The authors declare no competing financial interests.
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