Performance of PIDFuzzy control for cab isolation mounts of soil compactors
Vanliem Nguyen^{1} , Renqiang Jiao^{2} , Vanquynh Le^{3} , Anhtan Hoang^{4}
^{1, 2}Hubei Polytechnic University, Huangshi City, China
^{1, 3, 4}Thai Nguyen University of Technology, Thai Nguyen City, Vietnam
^{2}Corresponding author
Mathematical Models in Engineering, Vol. 5, Issue 4, 2019, p. 137145.
https://doi.org/10.21595/mme.2019.21213
Received 7 December 2019; accepted 17 December 2019; published 31 December 2019
To improve the soil compactor ride comfort, a combined control method of Fuzzy and PID control is proposed to control the cab isolation system of soil compactor based on the nonlinear vehicle dynamic model. The vibration excitation sources are concerned by the vibrator drum and elastoplastic soil (EPS) interactions in the compression process. The powerspectraldensity (PSD) and weighted rootmeansquare (RMS) of acceleration responses of both the vertical driver’s seat and pitching cab angle are chosen as the objective functions. The research results show that both the PSD and weighted RMS values of the vertical driver’s seat and pitching cab angle are significantly reduced by using the PIDFuzzy control under various EPSs in the lowfrequency region, especially on the EPS with highdensity.
 A combined control method of Fuzzy and PID control has successfully developed to control the cab isolation system of soil compactor.
 The powerspectraldensity (PSD) of the vertical driver’s seat and pitching cab angle is remarkably improved under various compaction conditions of the soil compactor, especially under a lowfrequency.
 The weighted rootmeansquare (RMS) of acceleration responses of both the vertical driver’s seat and pitching cab angle is greatly reduced, thus, the driver’s ride comfort and health is significantly improved.
 The PIDFuzzy control not only improves the ride comfort of the soil compactor but also controls the cab shaking under various working conditions.
 The research results also show that the PIDFuzzy control is not only effective for vehicles moving on the rigid roads, but also effective for vehicles moving on offroad roads.
Keywords: soil compactor, cab isolation mount, PIDFuzzy control, EPS ground.
1. Introduction
The soil compactor performance was evaluated not only by the compression efficiency of the vibratory drum on the soil, asphalt and other materials but also by the driver’s ride comfort [1, 2]. Therefore, in order to achieve the maximum excitation force of the vibrator drum, the drumelastoplastic soil (EPS) interaction models were studied and analyzed [3, 4], the research results showed that the compression performance of the soil compactor was maximum at the excitation frequency region from 1540 Hz of the vibratory drum [5], especially at a low frequency 28.5 Hz and high frequency 33 Hz of the vibratory drum [1, 3]. However, these vibration excitations transmitted to the driver via the cab isolation system were very high, so the driver’s feel was very uncomfortable. To solve this issue, to improve the cab isolation system was one of the most important problems.
The cab isolation system of the soil compactor equipped with the rubber mounts was analyzed and evaluated on the driver’s ride comfort [1]. The design parameters were then optimized to improve the ride comfort [6]. However, the weighted RMS values of the driver and cab were high under various working conditions, especially the cab shaking. Three cab isolation systems including rubber, hydraulic, and pneumatic mounts to increase the ride comfort were proposed [2]. The research results showed that the driver’s rider comfort and the cab shaking were significantly reduced by the cab isolation system used the hydraulic mounts in the lowfrequency region. However, the vibrations of the vertical driver’s seat and cab pitch angle are still great in the moving condition of the vehicle according to the ISO 36151 [7]. Therefore, to reduce the vibration of the driver’s seat and cab, the cab hydraulic mount should be controlled.
The hydraulic mounts applied for engine isolation mount [8] were controlled to decrease the engine vibrations [9]. Besides, some construction vehicles cab using the hydraulic mounts [10, 11] were optimized and controlled to improve the ride comfort. However, the researches only concerned under the vibration excitations of the rigid road surface roughness. Nowadays, the combined control methods such as PIDFuzzy [12, 13], H_{inf}Fuzzy, or SkyhookNFLC control [14, 15]^{}were applied to control the damping forces for the semiactive suspension system or active suspension system of vehicles and seat. The results showed that the ride comfort was significantly increased by using the above control methods. Therefore, this paper, based the combined control method of the PIDFuzzy, the cab isolation system equipped with the hydraulic mounts is controlled via the nonlinear dynamic model of the soil compactor to improve the ride comfort. The performance of the cab hydraulic mounts with the PIDFuzzy control is then evaluated via the powerspecialdensity (PSD) and weighted rootmeansquare (RMS) of acceleration responses of both the vertical driver’s seat and pitching cab angle under the various compression conditions of the drumEPS interactions and in the lowfrequency region of the soil compactor.
2. Materials and methods
2.1. Dynamic model and motion equations
Based on the actual structure of the soil compactor, a nonlinear dynamic model of a single drum vibratory roller with 7DOF is built to evaluate the control performance of the PIDFuzzy control for cab isolation system equipped with the hydraulic mount (HM) [2, 6, 11], as plotted in Fig. 1.
Fig. 1. Dynamic model of soil compactor
Where ${z}_{s}$, ${z}_{c}$, ${z}_{f}$, ${z}_{b}$ and ${z}_{d}$ are the vertical displacements of the driver’s seat, cab, framefront, framerear, and drum; ${\phi}_{c}$ and ${\phi}_{b}$ are the angular displacements of the cab and framerear; ${m}_{s}$, ${m}_{c}$, ${m}_{f}$, ${m}_{b}$ and ${m}_{d}$ are the mass of the driver’s seat, cab, framefront, framerear and drum, respectively; ${F}_{s}$, ${F}_{ci}$, ${F}_{d}$ and ${F}_{t}$ are the vertical dynamic forces of the vibration isolations of the seat, cab, drum and wheel, respectively; ${k}_{se}$ and ${k}_{sp}$ are the elastic and compression stiffness, and ${c}_{se}$ is the compression damper of the EPS; ${q}_{t}$ is the excitation of the terrain surface; ${l}_{v}$ is the distances of the vibratory roller, ($i$ = 1, 2; $v$ = $s$, $c1$, $c2$, $b1$; $b2$, $d$, $t$).
The motion equations of the soil compaction dynamic model are given by:
where ${F}_{s}={c}_{s}({\dot{z}}_{c}+{l}_{s}{\dot{\phi}}_{c}{\dot{z}}_{s})+{k}_{s}({z}_{c}+{l}_{s}{\phi}_{c}{z}_{s})$, ${F}_{c}={F}_{s}{F}_{c1}{F}_{c2}$, ${F}_{b}={F}_{c1}+{F}_{c2}{F}_{t}{F}_{d};{F}_{f}={F}_{d};{F}_{d}={c}_{d}({\dot{z}}_{d}{\dot{z}}_{f})+{k}_{d}({z}_{d}{z}_{f})$, ${M}_{c}={F}_{s}{l}_{s}+{F}_{c1}{l}_{c1}{F}_{c2}{l}_{c2}$, ${M}_{b}={F}_{d}{l}_{d}+{M}_{d}{F}_{t}{l}_{t}{F}_{c1}{l}_{b1}{F}_{c2}{l}_{b2}.$
The equation of the dynamic forces of cab hydraulic mounts is determined by [2]:
where ${c}_{hi}$ is the damping values of HM; ${k}_{s}$, ${k}_{ri}$ and ${c}_{s}$, ${c}_{ri}$ are the stiffness and damping values of the seat suspension and the rubber of HM; ${c}_{ctrli}$ is the control damping values of HM; ${z}_{i}$ is the relative displacements of HM are given by:
To improve the driver’s ride comfort, the damping values of the HM is then controlled based on PIDFuzzy control.
The equations of the excitation forces of the drum (${F}_{d}$) and the wheel (${F}_{t}$) are also determined as follows:
where ${k}_{d}$, ${k}_{t}$ and ${c}_{d}$, ${c}_{t}$ are the stiffness and damping values of drum’s rubber mount and wheel.
2.2. Vibration excitations of the soil compactor
In order to determine the vertical excitation forces from the road surface on the soil compactor, two types of excitations are chosen to simulate including:
Excitation of the wheel on the terrain surface: Under the compaction condition of the soil compactor, the vehicle often travels on the poor terrain surface of offroad terrain. Therefore, to determine the poor terrain surface, the PSD of the offroad terrain in the frequency range [16, 17] was used to calculate the spatial PSD of the terrain surface. According to the ISO proposal [18], the spectral density of the offroad terrain was given by:
According to the Gaussian random process, the terrain surface roughness could be calculated through the Fourier transformation as follow:
where $n$ is space frequency; ${n}_{0}$ is reference spacefrequency; $Q\left({n}_{0}\right)$ is the surface roughness coefficient; $\omega $ is the frequency index of the terrain surface; $N$ is the number of intervals; ${\varphi}_{i}$ is a random phase uniformly distributed from 0 to 2π. According to tho the Mitschke’s research results [19, 21], a poor terrain surface of offroad terrain with ${\omega}_{0}$ = 2.14, $Q\left({n}_{0}\right)$ = 3782.5×10^{6} m^{3}/cyc was used to determine the vibration excitation of the terrain on the wheel. The spectral density of the poor terrain surface in a lowfrequency below 10 Hz is plotted in Fig. 2.
Excitation of the drum on the EPS: Based on the rigid drumEPS interaction model in Refs. [6, 22], the characteristic of EPS was described by a plasticity factor $\epsilon ={k}_{sp}/({k}_{sp}+{k}_{se})$ and a soil damping to plasticity ratio $\gamma ={c}_{se}/{k}_{sp}$. The excitation of the drum was then determined by:
In a vibration excitation cycle of the drumEPS interaction, the motion of the drum on a soil patch of given density may exhibit, over each cycle of the drum, two or more often three distinct phases including (1) Loading phase: The gravelsoil ground is compressed by roller drum, the elastic stiffness and compression stiffness of the gravelsoil ground are then increased while the compression damper is decreased, (2) Unloading phase: The vibratory drum moves upward, the gravelsoil ground is then restored, and (3) DrumHope phase: The gravelsoil ground has become elasticity, the roller drum is easy to separate from the soil ground surface. In order to describe the relation of ${z}_{d}$, $\epsilon $ and $\gamma $, the vibration equations of the drum on the EPS was given as follows:
${m}_{d}{\ddot{z}}_{d}={F}_{d}{F}_{0}\mathrm{s}\mathrm{i}\mathrm{n}\omega t.$
By combining Eqs. 4 and 7, we can determine the vibration excitation of the drum.
Fig. 2. The spectral density of a poor terrain surface
2.3. Appling PIDFuzzy control for cab isolation system
The proportional integral derivate (PID) control is one the controller not only simple structure but also robust performance. The PID’s transfer function is written by:
where ${K}_{p}$, ${K}_{i}$ and ${K}_{d}$ are the proportional, integral and derivative parameters, respectively. The PID’s performance depends on the PID’s parameters which are chosen. The wellknown ZieglerNichols technique is used to determine the optimal values of PID, but it is efficiency only when the system works at the designed operating condition [12]. In order to solve this problem, the proportionality factors of PID is controlled by the Fuzzy control as follows:
where ${K}_{p}^{\text{'}}$, ${K}_{i}^{\text{'}}$ and ${K}_{d}^{\text{'}}$ are the control parameters of the Fuzzy control in the variable ranges of the PID control of $\{{K}_{p}^{min}\le {K}_{p}^{}\le {K}_{p}^{max}\}$, $\{{K}_{i}^{min}\le {K}_{i}^{}\le {K}_{i}^{max}\}$ and $\left\{{K}_{d}^{min}\le {K}_{d}^{}\le {K}_{d}^{max}\right\}.$
The variable ranges of the PID control are chosen by 1000 ≤ ${K}_{p}$ ≤ 10000, 100 ≤ ${K}_{i}$ ≤ 1000, and 10 ≤ ${K}_{d}$ ≤ 100, respectively [22], their values are then replaced into Eq. 9 as follows:
By replacing Eq. 10 into Eq. 8, the PID’s transfer function is rewritten by:
In order to find the optimal proportionality factors of ${K}_{p}^{\text{'}}$, ${K}_{i}^{\text{'}}$ and ${K}_{d}^{\text{'}}$, the Fuzzy control is used to control the model.
The Fuzzy control consists of Fuzzification interface (FI), Fuzzy inference system (FIS) and Defuzzification interface (DI). First, the crisp values in FI are transformed into linguistic variables (LVs). The FIS is then used by fuzzy rule in accordance with inference rule. Finally, the LVs are transformed back to crisp values through DI for use by the physical plant [13, 20]. This paper, the relative displacement and its velocity in Eq. 3 are considered as two input variables and they are denoted by $E=e\left(t\right)$ and $EC=\dot{e}\left(t\right)$, while the parameters of ${K}_{p}^{\text{'}}$, ${K}_{i}^{\text{'}}$ and ${K}_{d}^{\text{'}}$ are the output values, and the FLCPID control model is shown in Fig. 3.
Fig. 3. PIDFuzzy control model for subsystem
The LVs of input variables are defined by the negative big and small (nb and ns), zero (z), positive big and small (pb and ps), and of output variables are small (s), medium small (ms), medium (m), medium big (mb), and big (b); and the membership functions for their variables are represented by a fuzzy set. The shape of membership functions is the Triangular function and their values are between 0 and 1.
The ifthen rules are then applied to describe according to expertise experiences and the designer’s knowledge. The fuzzy rules are listed in Table 1 and written as follows:
${R}_{x}$: if E is ${\mathbf{A}}_{x}$ and EC is ${\mathbf{B}}_{x}$ then ${K}_{p}^{\text{'}}$ is ${C}_{x}$, ${K}_{i}^{\text{'}}$ is ${D}_{x}$ and ${K}_{d}^{\text{'}}$ is ${F}_{x}$.
The FIS is selected by the minimum function and the centroid method of Mamdani [20]. This paper, we used the FIS of Mamdani for control system model.
Table 1. Control rules of PIDFuzzy control [12]
${K}_{p}^{\text{'}}$

E

${K}_{i}^{\text{'}}$

E

${K}_{d}^{\text{'}}$

E


EC

nb

ns

z

ps

pb

nb

ns

z

ps

pb

nb

ns

z

ps

pb


nb

m

mb

b

ms

s

s

s

m

mb

S

s

m

b

mb

b


ns

mb

m

m

m

ms

s

b

mb

ms

m

ms

s

m

m

s


z

m

s

s

s

m

ms

ms

s

m

mb

m

b

s

s

ms


ps

ms

m

ms

m

b

ms

s

m

mb

s

mb

ms

s

ms

ms


pb

s

ms

m

mb

mb

m

m

ms

s

s

ms

b

s

s

m

Table 2. The numerical values of the EPS
EPS

$\epsilon $

${k}_{sp}$ (N/m)

${k}_{se}$ (N/m)

${c}_{se}$ (Ns/m)

Lowdensity

0.34

6.44×10^{6}

12.5×10^{6}

70.0×10^{3}

Highdensity

0.87

283×10^{6}

42.3×10^{6}

37.1×10^{3}

3. Numerical simulation and result analysis
In compaction condition of the soil compactor, under the excitation force of the drum ${F}_{e}={F}_{0}\mathrm{s}\mathrm{i}\mathrm{n}2\pi f$on the EPS, the characteristics of the EPS was changed from the low to medium and highdensities [3]. The effect of the mediumdensity on the ride comfort was researched [1, 2, 12]. To evaluate the performance of PIDFuzzy control, two types of the EPS with low and highdensities are chosen to simulate under the excitation drum 28 and 35 Hz at a speed 5 km·h^{1}. The numerical values of the EPS are listed in Table 2.
Fig. 4. Control results of PIDFuzzy control on the EPS with lowdensity
a) Vertical driver’s seat
b) Pitching angle of cab
Fig. 5. Control results of PIDFuzzy control on the EPS with highdensity
a) Vertical driver’s seat
b) Pitching angle of cab
In order to analyze the performance of cab hydraulic mounts with PIDFuzzy control, the reduction of the maximum PSD and weighted RMS accelerations of the vertical driver’s seat and pitching cab angle are calculated in [11, 21] are chosen as the objective functions. The simulation results of the PSD accelerations of the driver’s seat and pitching cab angle with the PIDFuzzy control at the frequencies of the drum 28 Hz and 35 Hz under the EPS with the low and highdensities are shown in Figs. 4 and 5. Under the EPS with lowdensity, observing Fig. 4, we can see that the PSD values with the control are clearly reduced in comparison with the passive under all the excitations of the drum 28 and 35 Hz in the lowfrequency region below 10 Hz. Especially a lowfrequency range below 4 Hz, the maximum PSD values of the driver’s seat and pitching cab angle with the control are greatly decreased by 28 % and 30 % at an excitation 28 Hz; and by 38 % and 67 % at an excitation 35 Hz of the vibratory drum in comparison with the passive. Similarly, under the EPS with highdensity, the maximum PSD values of the driver’s seat and pitching cab angle with the control are also smaller than the passive by 26 % and 60 % at an excitation 28 Hz; and by 29 % and 58 % at an excitation 35 Hz of the vibratory drum, especially the reduction of the PSD value of the pitching cab angle at both the EPS with low and highdensities, as listed in Table 3. Therefore, the driver’s health is significantly reduced by the cab hydraulic mounts using PIDFuzzy control in the lowfrequency region below 4 Hz.
Table 3. Maximum PSD values of the driver and cab
Excitation

MaxPSD

Lowdensity ground soil

Highdensity ground soil


Passive

Control

Reduction %

Passive

Control

Reduction %


28 Hz

PSD_{z}

0.61

0.44

28 %

0.65

0.48

26 %

PSD_{φ}

0.30

0.21

30 %

0.25

0.10

60 %


35 Hz

PSD_{z}

0.64

0.40

38 %

0.66

0.47

29 %

PSD_{φ}

0.30

0.10

67 %

0.26

0.11

58 %

Table 4. Reducing RMS values of PIDFuzzy control
Reduction (Re.) %

Lowdensity

Highdensity


28 Hz

35 Hz

28 Hz

35 Hz


Re. ${a}_{z}$

26 %

31 %

32 %

20 %

Re. ${a}_{\phi c}$

30 %

35 %

42 %

52 %

Fig. 6. Weighted RMS results of PIDFuzzy control on the EPS
a) Vertical driver’s seat
b) Pitching angle of cab
Additionally, the performance of the PIDFuzzy control is evaluated via the weighted RMS value on the ride comfort. The comparison and simulation results of the weighted RMS values of the driver’s and cab with the control are plotted in Figs. 6(a) and (b). Observing Fig. 6, both the weighted RMS values of the driver’s seat and pitching cab angle with the control are obviously reduced comparable with the passive under the various excitations of the drum and EPSs. The results in Fig. 6(a) and Table 4 show that the weighted RMS values of the vertical driver’s seat with the control are reduced by 26 % at 28 Hz and 31 % at 35 Hz of the excitation drum on the EPS with lowdensity; and by 32 % at 28 Hz and 20 % at 35 Hz of the excitation drum on the EPS with highdensity in comparison with the passive. Similarly, the results in Fig. 6(b) and Table 4 also show that the weighted RMS values of the pitching cab angle with the control are also lower than the passive by 30 % at 28 Hz and 35 % at 35 Hz of the excitation drum on the EPS with lowdensity; and by 42 % at 28 Hz and 52 % at 35 Hz of the excitation drum on the EPS with highdensity. Therefore, under various compression conditions of the excitation frequencies 28 Hz and 35 Hz of the vibratory drum and on the EPS with low and highdensities of the soil compactor, both the maximum PSD and weighted RMS values of the driver’s seat and pitching cab angle are strongly reduced by using the PIDFuzzy control. It implies that the ride comfort of the soil compactor is significantly improved by the cab hydraulic mounts with the control.
4. Conclusions
This paper, the ride comfort of the soil compactor is studied based the PIDFuzzy control for the soil compactor cab hydraulic mounts. The main conclusions can be given by:
The ride comfort of the driver is remarkably improved by the PIDFuzzy control under various compaction conditions of the soil compactor, especially under a lowfrequency region below 4 Hz.
Both the maximum PSD and weighted RMS values of the pitching cab angle are strongly reduced with the control under different operation conditions and on the EPS with low and highdensities, especially on the EPS with highdensity. Consequently, the PIDFuzzy control not only improves the ride comfort of the soil compactor but also controls the cab shaking under various working conditions.
The research results also show that the PIDFuzzy control is not only effective for vehicles moving on the rigid roads, but also effective for vehicles moving on offroad roads.
Acknowledgements
This study is supported by Hubei Polytechnic University Teaching and Research Projects (No. 19XJK17R).
References
 Kordestani A., Rakheja S., et al. Analysis of ride vibration environment of soil compactors. SAE International Journal of Commercial Vehicles, Vol. 3, 2010, p. 259272. [Publisher]
 Nguyen V., Zhang J., et al. Vibration analysis and modeling of an offroad vibratory roller equipped with three different cab’s isolation mounts. Shock and Vibration, Vol. 2018, 2018, p. 117, https://doi.org/10.1155/2018/8527574. [Publisher]
 Adam D., Kopf F. Theoretical analysis of dynamically loaded soils. Proceedings of the European Workshop Compaction of Soils and Granular Materials, Paris, France, 2000, p. 207217. [Search CrossRef]
 Li J., Zhang Z., et al. Dynamic characteristics of the vibratory roller testbed vibration isolation system: simulation and experiment. Journal of Terramechanics, Vol. 56, 2014, p. 139156, https://doi.org/10.1016/j.jterra.2014.10.002. [Publisher]
 Paul J., Michael A. Capturing nonlinear vibratory roller compactor behavior through lumped parameter modeling. Journal of Engineering Mechanics, Vol. 134, 2008, p. 684693, https://doi.org/10.1061/(ASCE)07339399 (2008)134:8(684). [Publisher]
 Nguyen V., Zhang J., et al. Ride quality evaluation of the soil compactor cab supplemented the auxiliary hydraulic mounts via simulation and experiment, Journal of Southeast University, Vol. 35, Issue 3, 2019, p. 273280, https://doi.org/10.3969/j.issn.10037985.2019.03.001. [Search CrossRef]
 International Organization for Standardization, Mechanical vibration and shockevaluation of human exposure to whole body vibration – Part 1: General requirements. ISO 26311:1997, Geneva, Switzerland, 1997. [Search CrossRef]
 Marzbani H., Jazar R., et al. Hydraulic engine mounts: a survey. Journal of Vibration and Control, Vol. 20, 2010, p. 14391463, https://doi.org/10.1177/1077546310380432. [Publisher]
 Wang M., et al. A novel design of semiactive hydraulic mount with wideband tunable notch frequency. Journal of Vibration and Control, Vol. 333, 2014, p. 21962211, https://doi.org/10.1016/j.jsv.2013.12.004. [Search CrossRef]
 Lee P., Vogt J., Han S. Application of hydraulic body mounts to reduce the freeway hop shake of pickup truck. SAE Technical Paper Series, 2009, https://doi.org/10.4271/2009012126. [Publisher]
 Nguyen V., Nguyen K. Enhancing the ride comfort of the offroad vibratory roller cab by adding damper hydraulic mount. Vibroengineering Procedia, Vol. 21, 2018, p. 8995, https://doi.org/10.21595/vp.2018.20339. [Publisher]
 Nguyen V., Zhang J., Yang X. Lowfrequency performance analysis of semiactive cab’s hydraulic mounts of an offroad vibratory roller. Shock and Vibration, Vol. 2019, 2019, p. 115, https://doi.org/10.1155/2019/8725382. [Search CrossRef]
 Nguyen V., Zhang J., Le Q., et al. Performance analysis of air suspension of heavy truck with semiactive fuzzy control. Journal of Southeast University (English Edition), Vol. 33, 2017, p. 159165, https://doi.org/10.3969/j.issn.10037985.2017.02.006. [Search CrossRef]
 FélixHerrán L., Mehdi D., RodríguezOrtizc J., et al. Hinf control of a suspension with a magnetorheological damper. International Journal of Control, 2012, p. 13665820, https://doi.org/10.1080/00207179.2012.674216. [Search CrossRef]
 Nguyen S., et al. A hybrid clustering based fuzzy structure for vibration control – Part 2: An application to semiactive vehicle seatsuspension system. Mechanical systems and signal processing, Vol. 450, 2015, p. 288301, https://doi.org/10.1016/j.ymssp.2014.10.019. [Search CrossRef]
 Wong J. Theory of Ground Vehicles. John Wiley and Sons, New York, NY, USA, 2001. [Search CrossRef]
 Robson J. Road surface description and vehicle response. International Journal of Vehicle Design, Vol. 1, 1979, p. 2535, https://doi.org/10.1504/IJVD.1979.061223. [Search CrossRef]
 International Organization for Standardization. Reporting Vehicle Road Surface Irregularities. ISO/TC108/SC2/WG4 N57, Tieme Medical Publishers, Stuttgart, Germany, 1982. [Search CrossRef]
 Mitschke M. Dynamik der Kraffahrzeuge. SpringerVerlag, Berlin, Germany, 1972. [Publisher]
 Mamdani H. Assilian An Experiment in linguistic synthesis with a fuzzy logic controller. International Journal of ManMachine Studies, Vol. 7, 1975, p. 113, https://doi.org/10.1016/S00207373(75)800022. [Publisher]
 Nguyen V., Zhang J., Jiao R., et al. Effect of the offroad terrains on the ride comfort of construction vehicles. Journal of Southeast University (English Edition), Vol. 35, 2019, p. 191197, https://doi.org/10.3969/j.issn.10037985.2019.02.008. [Search CrossRef]
 Nguyen V., Zhang J., et al. Performance analysis of semiactive hydraulic system of the offroad vibratory roller cab using optimal fuzzyPID control. Journal of Southeast University, Vol. 35, Issue 4, 2019, p. 19, https://doi.org/10.3969/j.issn.10037985.2019.04.001. [Search CrossRef]
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