Open AccessFeature PaperArticle

Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology

Department of Electronic Engineering, Feng-Chia University, Taichung 40724, Taiwan

Department of Automatic Control Engineering, Feng-Chia University, Taichung 40724, Taiwan

Department of Electrical Engineering, Behbahan Khatam Alanbia University of Technology, Behbahan 47189-63616, Iran

Author to whom correspondence should be addressed.

Electronics 2022, 11(1), 132; https://doi.org/10.3390/electronics11010132

Submission received: 3 December 2021 / Revised: 21 December 2021 / Accepted: 22 December 2021 / Published: 1 January 2022

(This article belongs to the Special Issue Intelligent Systems and Control Application in Autonomous Vehicle)

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Figure 1
The prototype of a light rail vehicle. (a) Pantograph–catenary system components; (b) lumped-mass model. Reprinted with permission from ref. [<a href="#B18-electronics-11-00132" class="html-bibr">18</a>]. Copyright 2016 IEEE. "> Figure 2
Block diagram of the proposed intelligent IT2AFLC scheme. "> Figure 3
The membership functions for <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <msub> <mi>F</mi> <mrow> <mi>u</mi> <mi>p</mi> </mrow> </msub> </mrow> </msub> </mrow> </semantics></math> and <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <msub> <mi>F</mi> <mi>c</mi> </msub> </mrow> </msub> </mrow> </semantics></math>. (a) The membership function <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <msub> <mi>F</mi> <mrow> <mi>u</mi> <mi>p</mi> </mrow> </msub> </mrow> </msub> </mrow> </semantics></math>. (b) The membership function <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <msub> <mi>F</mi> <mi>c</mi> </msub> </mrow> </msub> </mrow> </semantics></math>. "> Figure 4
The IT2AFNNI simulation performance. "> Figure 5
The membership functions for <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mi>e</mi> </msub> </mrow> </semantics></math> and <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <mi>d</mi> <mi>e</mi> </mrow> </msub> </mrow> </semantics></math>. (a) The membership function <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mi>e</mi> </msub> </mrow> </semantics></math>. (b) The membership function <math display="inline"><semantics> <mrow> <msub> <mi>μ</mi> <mrow> <mi>d</mi> <mi>e</mi> </mrow> </msub> </mrow> </semantics></math>. "> Figure 6
The contact force regulation performance. (a) The contact force for T1AFLC and the proposed IT2AFLC. (b) The contact force for passive control and the proposed IT2AFLC. "> Figure 7
The dynamic uplift force. (a) The dynamic uplift force for T1AFLC. (b) The dynamic uplift force for proposed IT2AFLC. "> Figure 8
The definition of the <math display="inline"><semantics> <mi mathvariant="normal">Φ</mi> </semantics></math> and <math display="inline"><semantics> <mrow> <msub> <mi mathvariant="normal">Φ</mi> <mn>0</mn> </msub> </mrow> </semantics></math> for VSE. "> Figure 9
The contact force regulation performance for IT2AFLC with three different type reduction methods. "> Figure 10
The resulting vertical position, velocity, and acceleration of the pantograph head. "> Figure 11
The resulting vertical position, velocity, and acceleration of the pantograph frame. "> Figure 12
The dynamic uplift force. "> Figure 13
Bar-line chart showing the comparative results (bar—CC, line—VSE). ">

Versions Notes

Abstract

In this paper, an intelligent control scheme is proposed to suppress vibrations between the pantograph and the catenary by regulating the contact force to a reference value, thereby achieving stable current collection. In order to reduce the computational cost, an interval Type-2 adaptive fuzzy logic control with the Moradi–Zirhohi–Lin type reduction method is applied to deal with model uncertainties and exterior interference. Based on a simplified pantograph–catenary system model, the comparative simulation results show that variation of the contact force can be attenuated and variation disturbances can be repressed simultaneously. Furthermore, in terms of computational burden, the proposed type reduction method outperforms other type reduction methods.

Keywords:

contact force; pantograph; catenary; Moradi–Zirhohi–Lin (MZL) algorithm; intelligent control

1. Introduction

Railway electrification systems that transmit electrical energy from the traction substation to the moving high-speed trains are an efficient alternative to highway and air transportation. The vital subsystem of high-speed railways is the pantograph–catenary system (PCS). When the train moves, the pantograph on its roof slides along and sends electrical current from contact wires, the so-called catenary, to the train motors. The catenary lines are fixed to the irregular-interval support point along the railway line. Moreover, an appropriate contact force between the pantograph and the catenary makes the current collection process effective. However, some main factors affect the contact force between the pantograph and the catenary. To keep the contact force stable, the system output feedback considers the stiffness of the contact wires along each span, the speed of the train, and the distance of adjacent catenary lines. Unfortunately, this may result in loss of contact, wear, and arc, which can severely damage the pantograph and the catenary, whether or not the contact force is too large or too small. Generally, the quality of electric transmission is directly dependent on the interaction performance between the pantograph and the catenary.

Some research results focused on pantograph–catenary structure analysis and experimental aspects have been published. The vertical effect of the vehicle–track vibration on the pantograph–catenary interaction was presented in [1], and both pantograph–catenary and the vehicle–track models were conducted in [2]. The contact wire irregulation stochastics and effect on high-speed railway pantograph–catenary interaction was analyzed in [1]. The dynamic characteristics of the pantograph and catenary components, the systems’ dynamic properties, and the environmental influences on the pantograph–catenary interaction were demonstrated in the review article [3]. The simulation of pantograph–catenary interaction benchmarks proposed by researchers from nine countries across Europe and Asia was accomplished in [4]. Meanwhile, [5] describes line testing methods for the certification of pantographs and catenaries and covers the reliability and availability of the pantograph–overhead line system and life-cycle costs. The effect of locomotive vibrations on pantograph–catenary interactions is investigated in [6]. A pantograph test rig developed for fault detection and diagnosis of high-speed pantograph dynamic behavior is provided in [7]. In this paper, we focus attention on the content of pantograph–catenary dynamics and the main objective to provide a novel type reduction (TR) technology for intelligent contact force regulation of the PCS.

Therefore, to effectively decrease the uncertain fluctuation of the contact force, the dynamic uplift force which is applied to pantograph frame by actuator plays an important part in the PCS. In the previous research, three methods achieve uniformity of the contact force. One is to consider the PCS in detail, including uncertain factors. In [8], performance to evaluate the contact quality adopted the dynamic behavior of the pantograph based on a multibody dynamics theory. In [9], contact resistance temperature distribution and microstructure were analyzed to address the evolutionary process of the sliding electric contact of the PCS. Meeting maintenance requirements by using automatic intelligent detection was also analyzed. In [10], online intelligent perception of the adaptive parameter PCS status was proposed using robust positioning of the PCS image contact point. In [11], automatically extracting the contact point combined with the deep pantograph network under complex backgrounds was proposed. Another proposal was the simple and effective concept of active control of PCS. The control strategy robustly overcame external disturbances by using a linear time-varying uncertain system [12]. A combination of a backstepping robust controller [13], a model predictive controller [14], and an optimal controller [15] made the fluctuation of the contact force achieve minimization in the amplitude of the oscillations with good tracking performance. To regulate the fluctuation of the contact force, it is very important to apply adequate uplift force.

By using the advantages of fuzzy logic control (FLC) [16], intelligent management systems have been used for active control of PCS [17,18,19]. Although Type-1 fuzzy logic controllers (T1FLCs) have been successfully applied in many application, they cannot fully handle linguistic uncertainties and noisy training data [20]. Fortunately, the interval Type-2 fuzzy logic system (IT2FLS), bound from above and below by two Type-1 fuzzy sets (T1FSs), also called the footprint of uncertainty (FOU), is an extension of the concept of T1FSs. Hence, IT2FLSs can deal with uncertain parameters, modeling vagueness, linguistic uncertainties, and unreliability of information. However, Type-2 fuzzy logic system require a large computational cost (CC). Up to now, many iterative approaches for implementing TR for interval Type-2 fuzzy sets (IT2FSs) have been proposed [21,22]. Much research has been dedicated to providing non-iterative methods to make the effective implementation of the IT2FLS easier, such as the uncertainty bound (UB) method [23], the Nagar–Bardini (NB) method [24], and Begian–Melek–Mendel (BMM) algorithms [25]. A novel and non-iterative TR method using the Moradi–Zirkohi–Lin (MZL) algorithms [26] was created to simultaneously reduce the computational burden and ensure accuracy.

In this paper, an intelligent contact force regulator incorporating MZL algorithms is presented to deal with oscillations produced from uncertain stiffness and to govern the contact force to a pre-specified reference value. Meanwhile, comparative simulations were used to confirm that the proposed TR method outperforms other TR methods.

The rest of this paper is organized as follows: Section 2 describes the simplified PCS model and problem formulation. Section 3 develops the intelligent contact force regulation with the MZL TR method. Section 4 provides the comparative simulation results. Section 5 gives the conclusion is given.

2. A Brief Description of the PCS Mathematical Model and Problem Formulation

The dynamics of a PCS are expressed in two common type models: multi-body and lumped-mass. The former is complex and high-computation-time; the latter is relatively simple, standard, and composed of a kinematical chain with elastic joints. Moreover, the lumped-parameters model is discussed in much research to test the performance of the controller [13,18,19,27]. Therefore, this paper focuses on the linear lumped-mass model with two degrees of freedom; the motion equation of the PCS model is shown in Figure 1 [18,19].

m_{f} {\ddot{x}}_{f} (t) + c_{f} ({\dot{x}}_{f} (t)) + c_{h} ({\dot{x}}_{f} (t) - {\dot{x}}_{h} (t)) + k_{h} (x_{f} (t) - x_{h} (t)) = F_{u p}

(1)

m_{h} {\ddot{x}}_{h} (t) + c_{h} ({\dot{x}}_{h} (t) - {\dot{x}}_{f} (t)) + k_{h} (x_{h} (t) - x_{f} (t)) + k_{p a n} (x_{h} (t) - x_{c a t} (t)) = 0

(2)

k_{p a n} (x_{c a t} (t) - x_{h} (t)) + k_{c a t} x_{c a t} (t) = 0

(3)

where

F_{u p} (t)

and

F_{c} (t)

are the dynamic uplift force (input) and the contact force (output) of the PCS, respectively. The PCS parameters are listed in Table 1.

If state variables are defined as

x_{1} = x_{h}

x_{2} = {\dot{x}}_{1}

x_{3} = x_{f}

, and

x_{4} = {\dot{x}}_{3}

, the state-space representation of the PCS model can be given as

\dot{x} (t) = [\begin{matrix} 0 & 1 & 0 & 0 \\ \frac{1}{m_{h}} (\frac{- k_{p a n} k_{c a t}}{k_{p a n} + k_{c a t}} - k_{h}) & - \frac{c_{h}}{m_{h}} & \frac{k_{h}}{m_{h}} & \frac{c_{h}}{m_{h}} \\ 0 & 0 & 0 & 1 \\ \frac{k_{h}}{m_{f}} & \frac{c_{h}}{m_{f}} & - \frac{k_{h}}{m_{f}} & - \frac{c_{f} + c_{h}}{m_{f}} \end{matrix}] x (t) + [\begin{matrix} 0 \\ 0 \\ 0 \\ \frac{1}{m_{f}} \end{matrix}] F_{u p} (t)

(4)

F_{c} (t) = [\begin{matrix} \frac{k_{p a n} k_{c a t}}{k_{p a n} + k_{c a t}} & 0 & 0 & 0 \end{matrix}] x (t) = \frac{k_{p a n} k_{c a t}}{k_{p a n} + k_{c a t}} x_{1} (t)

(5)

where

x (t) = {[x_{1} (t), x_{2} (t), x_{3} (t), x_{4} (t)]}^{T}

. The main objective is to design the dynamic uplift force

F_{u p} (t)

to regulate the contact force

F_{c} (t)

to the prescribed constant value

F_{c d} (t) = 100

N. If the time-varying stiffness of the catenary influenced by the stiffness-variation coefficient

α

, the operational speed of train

V

, and the length in a span

L

are considered, the contact force (5) will be rewritten as

F_{c} (t) = \frac{k_{p a n} k_{c a t}}{k_{p a n} + k_{c a t}} (1 + α \cos (\frac{2 π V}{L} t)) x_{1} (t)

(6)

In this paper, using the novel MZL TR algorithm [26] to lower CC and to fully handle or accommodate linguistic and numerical uncertainties, the interval Type-2 adaptive fuzzy logic control (IT2AFLC) incorporating with the identifier is developed to suppress the vibration resulting from the stiffness-variation coefficient

α

, the operational speed of train

V

, and the length in a span

L

Remark: It is well known that stiffness variation and wave propagation in catenaries are the main sources of contact loss between the pantograph and catenary [28]. Particularly, wave reflection becomes a major cause for the loss of contact when the speed of the rail vehicle is above 250 km/h. However, the maximum speed of the rail vehicle in our model is 70 km/h and the wave propagation effect can be neglected.

3. Intelligent Controller Design

The objective of the controller is to design an adequate uplift force to effectively regulate the uncertain fluctuation of the contact force

F_{c} (t)

to the desired constant value

F_{c d} (t) = 100

N, thereby achieving stable current collection. Based on the IT2AFLC incorporating the interval Type-2 adaptive fuzzy neural network identifier (IT2AFNNI) to predict the contact force used to tune the design parameters of the IT2AFLC by a back propagation (BP) algorithm, the intelligent control scheme with output feedback including uncertain stiffness is as shown in Figure 2.

To begin with, the proposed control configuration includes two structures, IT2AFNNI and IT2AFLC; the details of the procedures are illustrated as follows.

3.1. Training Algorithm for IT2AFNNI

The structure of IT2AFNNI is as shown in Figure 2 and the two inputs are

F_{u p} (k)

and

F_{c} (k - 1)

. The output is the predicted contact force

F_{c I} (k)

used to replace

F_{c} (k)

in the regulation phase. In order to train the IT2AFNNI, the performance index (PI) is defined as

J_{I} (k) = \frac{1}{2} {(e_{I} (k))}^{2} = \frac{1}{2} {(F_{c} (k) - F_{c I} (k))}^{2}

(7)

The BP algorithm used to adjust the weights of the IT2AFNNI by minimizing the PI is briefly described as

W_{I} (k + 1) = W_{I} (k) + Δ W_{I} (k) = W_{I} (k) + η_{I} (- \frac{\partial J_{I} (k)}{\partial W_{I}})

(8)

By using the chain rule, (8) can be rewritten as

W_{I} (k + 1) = W_{I} (k) + η_{I} (- \frac{\partial J_{I} (k)}{\partial e_{I} (k)} \frac{\partial e_{I} (k)}{\partial F_{c I} (k)} \frac{\partial F_{c I} (k)}{\partial W_{I}})

(9)

where

e_{I} (k) = F_{c} (k) - F_{c I} (k)

is the training error,

η_{I}

is the learning rate, and

W_{I}

is the output weight. Subscript I symbolizes the identifier.

3.2. Training Algorithm for IT2AFLC

e_{C} (k)

and

{\dot{e}}_{C} (k)

are two inputs of the IT2AFLC, as shown in Figure 2. The output is contact force

F_{c} (k)

. The PI used to train the IT2AFLC to regulate the contact force is defined as

J_{C} (k) = \frac{1}{2} {(e_{C} (k))}^{2} = \frac{1}{2} {(F_{c d} (k) - F_{c} (k))}^{2}

(10)

To update the weights of the IT2AFLC by attenuating the PI, the BP algorithm is briefly described as

W_{C} (k + 1) = W_{C} (k) + Δ W_{C} (k) = W_{C} (k) + η_{C} (- \frac{\partial J_{C} (k)}{\partial W_{C}})

(11)

Based on the chain rule, (11) can be rewritten as

W_{C} (k + 1) = W_{C} (k) + η_{C} (- \frac{\partial J_{C} (k)}{\partial e_{C} (k)} \frac{\partial e_{C} (k)}{\partial F_{c} (k)} \frac{\partial F_{c} (k)}{\partial F_{u p} (k)} \frac{\partial F_{u p} (k)}{\partial W_{C}})

(12)

where

e_{C} (k) = F_{c d} (k) - F_{c} (k)

is the regulation error,

η_{C}

is the learning rate, and

W_{C}

is the output weight. Subscript C denotes the controller. The system sensitivity

\frac{\partial F_{c} (k)}{\partial F_{u p} (k)}

must be known in order to update the output weights in (12) to guarantee the convergence of the IT2FLC. The IT2AFNNI can achieve this goal by replacing

\frac{\partial F_{c} (k)}{\partial F_{u p} (k)}

with

\frac{\partial F_{c I} (k)}{\partial F_{u p} (k)}

and (12) can be rewritten as

W_{C} (k + 1) = W_{C} (k) + η_{C} (- \frac{\partial J_{C} (k)}{\partial e_{C} (k)} \frac{\partial e_{C} (k)}{\partial F_{c} (k)} \frac{\partial F_{c I} (k)}{\partial F_{u p} (k)} \frac{\partial F_{u p} (k)}{\partial W_{C}})

(13)

3.3. Main Results

The IT2AFLC with the MZL TR method is presented to suppress the vibration between the pantograph and the catenary and to deal with the uncertainties resulted from the noisy training data, noisy measurements, and linguistic uncertainties. It is a non-iterative algorithm which can reduce CC and ensure accuracy without computing the center of IT2FLS by sorting weights.

To start with, consider a Type-2 FLS having n inputs

x_{1} \in X_{1}

\dots

x_{n} \in X_{n}

and one output

y \in Y

. The Type-2 fuzzy rule base consists of a collection of IF-THEN rules. The rule of a Type-2 relation between the input space

X_{1} \times X_{2} \times \dots \times X_{n}

and the output space Y can be expressed as

R^{l} : IF x_{1} is {\tilde{F}}_{1}^{l} and \dots and x_{n} is {\tilde{F}}_{n}^{l}, THEN y is {\tilde{W}}^{l}, l = 1, 2, \dots, M

(14)

where

{\tilde{F}}_{j}^{l}

are antecedent Type-2 sets (

j = 1, 2, \dots, n

) and

{\tilde{W}}^{l}

are consequent Type-2 sets. Let

f^{i} \in {\tilde{F}}^{i} \equiv [{\underline{f}}^{i}, {\bar{f}}^{i}]

{\underline{f}}^{i}

and

{\bar{f}}^{i}

are the lower and upper bounds of the firing strength of the

i th

rule of the IT2FLSs, and

y^{i} \in Y^{i} \equiv [{\underline{y}}^{i}, {\bar{y}}^{i}]

{\underline{y}}^{i}

and

{\bar{y}}^{i}

are the lower and upper bounds of the interval sets considered for the consequent part of the

i th

rule of the IT2FLSs.

The MZL TR algorithm is described in Table 2.

To summarize the above analysis, intelligent contact force regulation of PCS based on the MZL TR algorithm is proposed as follows.

Procedure:

Step (1): Specify the membership functions

μ_{F_{u p}}

and

μ_{F_{c}}

, and adjust the output weights of the IT2AFNNI by BP algorithm (9) to predict the contact force

F_{c I} (k)

of the PCS.

Step (2): Specify the membership functions

μ_{e}

μ_{d e}

, and set up the rule table of the IT2AFLC.

Step (3) Incorporate the IT2AFLC with IT2AFNNI based on the MZL algorithm by replacing

\frac{\partial F_{c} (k)}{\partial F_{u p} (k)}

with

\frac{\partial F_{c I} (k)}{\partial F_{u p} (k)}

and using the BP algorithm (13) to tune the output weights of the IT2AFLC to regulate the contact force to the prescribed level, 100N.

4. Simulation Results

In order to verify the regulation performance, the control algorithm proposed in this paper was and compared with T1AFLC and passive control. Furthermore, a comparative study with other TR methods is provided. Simulation results show that the advocated control schemes can not only robustly attenuate the uncertain fluctuation of the contact force, but that the CC can also be efficiently reduced.

The parameters of the PCS used in the following simulation [18] are as specified:

m_{h} = 9.1

kg,

c_{h} = 130

Ns/m,

k_{h} = 7 \times 10^{3}

N/m,

m_{f} = 17.2

kg,

c_{f} = 30

Ns/m,

k_{c a t} = 1.535 \times 10^{6}

N/m,

k_{p a n} = 8.23 \times 10^{4}

N/m. According to the design procedure, the design is given in the following steps.

Step (1): The membership functions

μ_{F_{u p}}

and

μ_{F_{c}}

for IT2AFNNI are selected as follows and as shown in Figure 3.

μ_{F_{u p_{1}}} = {\begin{matrix} \frac{1}{1 + e^{0.5 (F_{u p} (k) - 60)}} & u p p e r b o u n d \\ \frac{1}{1 + e^{0.5 (F_{u p} (k) - 40)}} & l o w e r b o u n d \end{matrix}, μ_{F_{u p_{2}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 75)}^{2}}{30^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 75)}^{2}}{10^{2}}} & l o w e r b o u n d \end{matrix}

μ_{F_{u p_{3}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 100)}^{2}}{30^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 100)}^{2}}{10^{2}}} & l o w e r b o u n d \end{matrix}, μ_{F_{u p_{4}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 125)}^{2}}{30^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{u p} (k) - 125)}^{2}}{10^{2}}} & l o w e r b o u n d \end{matrix}

μ_{F_{u p_{5}}} = {\begin{matrix} \frac{1}{1 + e^{- 0.5 (F_{u p} (k) - 140)}} & u p p e r b o u n d \\ \frac{1}{1 + e^{- 0.5 (F_{u p} (k) - 160)}} & l o w e r b o u n d \end{matrix}, μ_{F_{c_{1}}} = {\begin{matrix} \frac{1}{1 + e^{0.5 (F_{c} (k) - 60)}} & u p p e r b o u n d \\ \frac{1}{1 + e^{0.5 (F_{c} (k) - 40)}} & l o w e r b o u n d \end{matrix}

μ_{F_{c_{2}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{c} (k) - 75)}^{2}}{40^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{c} (k) - 75)}^{2}}{20^{2}}} & l o w e r b o u n d \end{matrix}, μ_{F_{c_{3}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{c} (k) - 100)}^{2}}{40^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{c} (k) - 100)}^{2}}{20^{2}}} & l o w e r b o u n d \end{matrix}

μ_{F_{c_{4}}} = {\begin{matrix} e^{- \frac{1}{2} \frac{{(F_{c} (k) - 125)}^{2}}{40^{2}}} & u p p e r b o u n d \\ e^{- \frac{1}{2} \frac{{(F_{c} (k) - 125)}^{2}}{20^{2}}} & l o w e r b o u n d \end{matrix}, μ_{F_{c_{5}}} = {\begin{matrix} \frac{1}{1 + e^{- 0.5 (F_{c} (k) - 140)}} & u p p e r b o u n d \\ \frac{1}{1 + e^{- 0.5 (F_{c} (k) - 160)}} & l o w e r b o u n d \end{matrix}

The identification performance is shown in Figure 4 and we can see that the IT2AFNNI can predict the contact force very quickly by (9).

Step (2) The membership functions

μ_{e}

and

μ_{d e}

for IT2AFLC are selected as shown in Figure 5.

Table 3 gives the rule table of the IT2AFLC with

M = 49

fuzzy IF-THEN linguistic rules based on the input membership functions

μ_{e}

and

μ_{d e}

, and output membership function

[{\underline{y}}^{i}, {\bar{y}}^{i}] = [{\underline{w}}_{C}^{i}, {\bar{w}}_{C}^{i}]

, with the interval weights corresponding rule consequents presented.

Step (3) In order to obtain the appropriate uplift force

F_{u p} (t)

, which is the output of the IT2AFLC to force the contact force to the reference level 100 N, the non-iterative MZL algorithm was used to calculate the center of the IT2FLS to reduce the CC and to ensure accuracy. In accordance with the fuzzy IF-THEN linguistic rule table, the MZL employed to achieve the regulation objective is demonstrated as follows. The most-left uplift force

F_{u p_{l}}

and the most-right uplift force

F_{u p_{r}}

will be derived from the following process.

(1): Set average $W_{a v g}$ by

$W_{a v g} = \frac{\sum_{i = 1}^{49} {\bar{f}}^{i} + \sum_{i = 1}^{49} {\underline{f}}^{i}}{2}$

(15)
(2): Determine weights and then match firing strengths of rules

${\bar{p}}_{i} = {\begin{matrix} 0 & {\bar{w}}_{C}^{i} \leq 0 \\ {\bar{w}}_{C}^{i} & {\bar{w}}_{C}^{i} > 0 \end{matrix}, {\underline{p}}_{i} = {\begin{matrix} 0 & {\underline{w}}_{C}^{i} \leq 0 \\ {\underline{w}}_{C}^{i} & {\underline{w}}_{C}^{i} > 0 \end{matrix} {\bar{q}}_{c_{i}} = {\begin{matrix} {\bar{w}}_{C}^{i} & {\bar{w}}_{C}^{i} < 0 \\ 0 & {\bar{w}}_{C}^{i} \geq 0 \end{matrix}, {\underline{q}}_{i} = {\begin{matrix} {\underline{w}}_{C}^{i} & {\underline{w}}_{C}^{i} < 0 \\ 0 & {\underline{w}}_{C}^{i} \geq 0 \end{matrix} [\begin{matrix} {\bar{A}}_{1} & {\bar{A}}_{2} \\ {\underline{A}}_{1} & {\underline{A}}_{2} \end{matrix}] = [\begin{matrix} \sum_{i = 1}^{49} {\underline{f}}^{i} {\bar{p}}^{i} & \sum_{i = 1}^{49} {\bar{f}}^{i} {\bar{p}}^{i} \\ \sum_{i = 1}^{49} {\underline{f}}^{i} {\underline{p}}^{i} & \sum_{i = 1}^{49} {\bar{f}}^{i} {\underline{p}}^{i} \end{matrix}], [\begin{matrix} {\bar{B}}_{1} & {\bar{B}}_{2} \\ {\underline{B}}_{1} & {\underline{B}}_{2} \end{matrix}] = [\begin{matrix} \sum_{i = 1}^{49} {\underline{f}}^{i} {\bar{q}}^{i} & \sum_{i = 1}^{49} {\bar{f}}^{i} {\bar{q}}^{i} \\ \sum_{i = 1}^{49} {\underline{f}}^{i} {\underline{q}}^{i} & \sum_{i = 1}^{49} {\bar{f}}^{i} {\underline{q}}^{i} \end{matrix}]$

(16)
(3): Compute all possible combinations

$A_{l} = [\begin{matrix} {\bar{A}}_{1} + {\bar{B}}_{1} & {\bar{A}}_{1} + {\bar{B}}_{2} & {\bar{A}}_{2} + {\bar{B}}_{1} & {\bar{A}}_{2} + {\bar{B}}_{2} \end{matrix}] A_{r} = [\begin{matrix} {\underline{A}}_{1} + {\underline{B}}_{1} & {\underline{A}}_{1} + {\underline{B}}_{2} & {\underline{A}}_{2} + {\underline{B}}_{1} & {\underline{A}}_{2} + {\underline{B}}_{2} \end{matrix}]$

(17)
(4): Compute

${y^{'}}_{l 1} = \frac{\min (A_{l})}{W_{a v g}}, {y^{'}}_{l 2} = \frac{\max (A_{l})}{W_{a v g}}, {y^{'}}_{r 1} = \frac{\min (A_{r})}{W_{a v g}}, {y^{'}}_{r 2} = \frac{\max (A_{r})}{W_{a v g}}$

(18)
(5): Compute crisp output, uplift force $F_{u p}$

$y_{l} = \frac{{y^{'}}_{l 1} + {y^{'}}_{l 2}}{2}, y_{r} = \frac{{y^{'}}_{r 1} + {y^{'}}_{r 2}}{2} and F_{u p} = \frac{y_{l} + y_{r}}{2}$

(19)

The following two case simulations will be analyzed and discussed:

Case 1:

To check robustness, the comparison between the T1AFLC with interference from a white Gaussian noise with SNR 20 dB, the traditional passive control (

F_{u p} (t) = 100

N), and the proposed IT2AFLC will be considered. Due to the inclusion of linguistic uncertainty and data noise, the IT2AFLC can more efficiently regulate the contact force than Type-1 adaptive fuzzy logic control (T1AFLC) and the traditional passive control, as shown in Figure 6. The dynamic uplift force is severely unsteady, i.e., much more control effort must be consumed for T1AFLC, resulting in implementation difficultly as shown in Figure 7. In contrast, the control force is stable for IT2AFLC.

Case 2:

To consider the influence resulting from the time-varying stiffness of the catenary, the feedback signal of contact force

F_{c} (t)

blended with the stiffness-variation coefficient

α

, the operational speed of train

V

, and the length in a span

L

as (6), the vibration suppression efficiency (VSE) [29] will be analyzed and compared between the proposed MZL algorithm, the Karnik–Mendel (KM) algorithm [30,31,32,33], and simplified interval Type-2 Takagi–Sugeno–Kang fuzzy systems (IT2 TSK FS) [34,35,36].

First of all, the VSE is defined as

VSE ≜ (1 - \frac{Φ}{Φ_{0}}) \cdot 100 %

(20)

where

Φ

is the amplitude of the steady contact force value and

Φ_{0} = 2 α F_{c d} (t)

is the amplitude of the contact force by traditional passive control, as shown in Figure 8.

Two different sets of the different

(α = 0.3, V = 70, L = 40)

and

(α = 0.6, V = 70

, L = 80)

are simulated and analyzed as follows. The contact force regulation performance for IT2AFLC with different three TR methods are almost the same, as shown in Figure 9. Similarly, the vertical position, speed, and acceleration of the pantograph head and frame are definitely the same as those demonstrated in Figure 10 and Figure 11, respectively. Finally, the simplified IT2 algorithm uses larger dynamic uplift force than the proposed MZL algorithm and the KM algorithm, as illustrated in Figure 12.

Furthermore, comparative results of the VSE and the CC for

α = 0.3

α = 0.4

α = 0.5

, and

α = 0.6

, with speed

V = 60

and

V = 70

km/hr and

L

, are reported in Table 4 and Table 5, respectively. To provide a better comparison, the bar-line chart of the data reported in Table 4 and Table 5 is also shown in Figure 13. It can be clearly seen that the VSE are very similar for the three different TR algorithms. However, for real-time applications, the computation time is a major factor; therefore, we can notice that the proposed MZL TR algorithm is more operant than the KM algorithm and the simplified IT2 algorithm in terms of contact force regulation accuracy and computational cost.

In order to test the effect of parameter variations on the performance of vibration suppression and contact force regulation, the stiffness of the pantograph shoe suspension

k_{p a n}

, the pan-head suspension

k_{h}

, the catenary suspension

k_{c a t}

, the viscous damping of the pan-head suspension

c_{h}

, and the frame suspension

c_{f}

were changed from 80% to 120% of their nominal values given in the above simulation. Table 6 summarizes the performance changes when there were

\pm 20 %

parameter perturbations in the spring and damping coefficients. The results show excellent contact force regulation and vibration suppression performance robust with our proposed control scheme.

5. Conclusions

In this paper, based on the MZL TR method, an intelligent control scheme is presented to suppress the vibration between the pantograph and the catenary by regulating the contact force to a reference value. The simple MZL algorithm is used to reduce the computational time cost and to deal with model uncertainties, linguistic uncertainties, and exterior interference; stable current collection can then be achieved. Comparative simulation results show that the vibration of the contact force resulting from the time-varying stiffness of the catenary can be effectively suppressed and the proposed MZL TR algorithm is more efficient than the simplified IT2 structure algorithm, a hybrid structure of four Type-1 fuzzy systems, and the KM TR algorithm, all common iterative algorithms, in regards to accuracy and computational burden. Furthermore, the proposed control scheme will be applied in real life in future experimental implementations.

Author Contributions

Conceptualization, T.-C.L.; Data curation, M.M.Z.; Formal analysis, T.-C.L., C.-W.S. and M.M.Z.; Funding acquisition, Y.-C.L.; Investigation, T.-C.L.; Methodology, T.-C.L.; Project administration, Y.-C.L.; Resources, Y.-C.L.; Software, C.-W.S.; Supervision, T.-C.L.; Validation, T.-C.L. and C.-W.S.; Visualization, C.-W.S. and M.M.Z.; Writing–original draft, T.-C.L. and C.-W.S. All authors have read and agreed to the published version of the manuscript.

Funding

This research received no external funding.

Data Availability Statement

The original contributions presented in the study are included in the article, and further inquiries can be directed to the corresponding author.

Conflicts of Interest

The authors declare no conflict of interest.

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Figure 2. Block diagram of the proposed intelligent IT2AFLC scheme.

Figure 3. The membership functions for

μ_{F_{u p}}

and

μ_{F_{c}}

. (a) The membership function

μ_{F_{u p}}

. (b) The membership function

μ_{F_{c}}

Figure 3. The membership functions for

μ_{F_{u p}}

and

μ_{F_{c}}

. (a) The membership function

μ_{F_{u p}}

. (b) The membership function

μ_{F_{c}}

Figure 4. The IT2AFNNI simulation performance.

Figure 5. The membership functions for

μ_{e}

and

μ_{d e}

. (a) The membership function

μ_{e}

. (b) The membership function

μ_{d e}

Figure 5. The membership functions for

μ_{e}

and

μ_{d e}

. (a) The membership function

μ_{e}

. (b) The membership function

μ_{d e}

Figure 6. The contact force regulation performance. (a) The contact force for T1AFLC and the proposed IT2AFLC. (b) The contact force for passive control and the proposed IT2AFLC.

Figure 7. The dynamic uplift force. (a) The dynamic uplift force for T1AFLC. (b) The dynamic uplift force for proposed IT2AFLC.

Figure 8. The definition of the

Φ

and

Φ_{0}

for VSE.

Figure 8. The definition of the

Φ

and

Φ_{0}

for VSE.

Figure 9. The contact force regulation performance for IT2AFLC with three different type reduction methods.

Figure 10. The resulting vertical position, velocity, and acceleration of the pantograph head.

Figure 11. The resulting vertical position, velocity, and acceleration of the pantograph frame.

Figure 12. The dynamic uplift force.

Figure 13. Bar-line chart showing the comparative results (bar—CC, line—VSE).

Table 1. Pantograph–catenary system parameter values.

Parameters	Displacement	Speed	Mass	Viscous Damping Coefficient	Stiffness of Suspension
Pantograph head	$x_{h}$	${\dot{x}}_{h}$	$m_{h}$	$c_{h}$	$k_{h}$
Pantograph frame	$x_{f}$	${\dot{x}}_{f}$	$m_{f}$	$c_{f}$
Pantograph shoe					$k_{p a n}$
Catenary	$x_{c a t}$				$k_{c a t}$

Table 2. The Moradi–Zirhohi–Lin type reduction algorithm.

$Computing y_{l}$	$Computing y_{r}$
$W_{a v g} = \frac{\sum_{i = 1}^{M} {\bar{f}}^{i} + \sum_{i = 1}^{M} {\underline{f}}^{i}}{2}$
${\underline{p}}_{l}^{i} = {\begin{cases} {\underline{y}}^{i} i f {\underline{y}}^{i} > 0 \\ 0 i f {\underline{y}}^{i} \leq 0 \end{cases}$ , ${\underline{q}}_{l}^{i} = {\begin{cases} {\underline{y}}^{i} i f {\underline{y}}^{i} < 0 \\ 0 i f {\underline{y}}^{i} \geq 0 \end{cases}$	${\bar{p}}_{r}^{i} = {\begin{cases} {\bar{y}}^{i} i f {\bar{y}}^{i} > 0 \\ 0 i f {\bar{y}}^{i} \leq 0 \end{cases}$ , ${\bar{q}}_{r}^{i} = {\begin{cases} {\bar{y}}^{i} i f {\bar{y}}^{i} < 0 \\ 0 i f {\bar{y}}^{i} \geq 0 \end{cases}$
Match the firing strength $f^{i}$ with their respective weights ${\underline{y}}^{i}$	Match the firing strength $f^{i}$ with their respective weights ${\bar{y}}^{i}$
${\underline{b}}_{l}^{i} = {\begin{cases} {\underline{f}}^{i} i f {\underline{y}}^{i} > 0 \\ 0 i f {\underline{y}}^{i} \leq 0 \end{cases}$ , ${\bar{b}}_{l}^{i} = {\begin{cases} {\bar{f}}^{i} i f {\underline{y}}^{i} > 0 \\ 0 i f {\underline{y}}^{i} \leq 0 \end{cases}$ ${\underline{h}}_{l}^{i} = {\begin{cases} {\underline{f}}^{i} i f {\underline{y}}^{i} < 0 \\ 0 i f {\underline{y}}^{i} \geq 0 \end{cases}$ , ${\bar{h}}_{l}^{i} = {\begin{cases} {\bar{f}}^{i} i f {\underline{y}}^{i} < 0 \\ 0 i f {\underline{y}}^{i} \geq 0 \end{cases}$	${\underline{b}}_{r}^{i} = {\begin{cases} {\underline{f}}^{i} i f {\bar{y}}^{i} > 0 \\ 0 i f {\bar{y}}^{i} \leq 0 \end{cases}$ , ${\bar{b}}_{r}^{i} = {\begin{cases} {\bar{f}}^{i} i f {\bar{y}}^{i} > 0 \\ 0 i f {\bar{y}}^{i} \leq 0 \end{cases}$ ${\underline{h}}_{r}^{i} = {\begin{cases} {\underline{f}}^{i} i f {\bar{y}}^{i} < 0 \\ 0 i f {\bar{y}}^{i} \geq 0 \end{cases}$ , ${\bar{h}}_{r}^{i} = {\begin{cases} {\bar{f}}^{i} i f {\bar{y}}^{i} < 0 \\ 0 i f {\bar{y}}^{i} \geq 0 \end{cases}$
$[A_{l}^{1} A_{l}^{2}] = [\sum_{i = 1}^{M} {\underline{p}}_{l}^{i} {\underline{b}}_{l}^{i} \sum_{i = 1}^{M} {\underline{p}}_{l}^{i} {\bar{b}}_{l}^{i}]$ $[B_{l}^{1} B_{l}^{2}] = [\sum_{i = 1}^{M} {\underline{q}}_{l}^{i} {\underline{h}}_{l}^{i} \sum_{i = 1}^{M} {\underline{q}}_{l}^{i} {\bar{h}}_{l}^{i}]$	$[A_{r}^{1} A_{r}^{2}] = [\sum_{i = 1}^{M} {\bar{p}}_{r}^{i} {\underline{b}}_{r}^{i} \sum_{i = 1}^{M} {\bar{p}}_{r}^{i} {\bar{b}}_{r}^{i}]$ $[B_{r}^{1} B_{r}^{2}] = [\sum_{i = 1}^{M} {\bar{q}}_{r}^{i} {\underline{h}}_{r}^{i} \sum_{i = 1}^{M} {\bar{q}}_{r}^{i} {\bar{h}}_{r}^{i}]$
$A_{l} = [A_{l}^{1} + B_{l}^{1} A_{l}^{1} + B_{l}^{2} A_{l}^{2} + B_{l}^{1} A_{l}^{2} + B_{l}^{2}]$	$A_{r} = [A_{r}^{1} + B_{r}^{1} A_{r}^{1} + B_{r}^{2} A_{r}^{2} + B_{r}^{1} A_{r}^{2} + B_{r}^{2}]$
${y^{'}}_{l 1} = \frac{\min (A_{l})}{W_{a v g}}$ , ${y^{'}}_{l 2} = \frac{\max (A_{l})}{W_{a v g}}$	${y^{'}}_{r 1} = \frac{\min (A_{r})}{W_{a v g}}$ , ${y^{'}}_{r 2} = \frac{\max (A_{r})}{W_{a v g}}$
$y_{l} = \frac{{y^{'}}_{l 1} + {y^{'}}_{l 2}}{2}$	$y_{r} = \frac{{y^{'}}_{r 1} + {y^{'}}_{r 2}}{2}$
Output $y = \frac{y_{l} + y_{r}}{2}$

Table 3. Interval Type-2 fuzzy rule table.

	$μ_{d e_{1}}$	$μ_{d e_{2}}$	$μ_{d e_{3}}$	$μ_{d e_{4}}$	$μ_{d e_{5}}$	$μ_{d e_{6}}$	$μ_{d e_{7}}$
	$μ_{d e_{1}}$	$μ_{d e_{2}}$	$μ_{d e_{3}}$	$μ_{d e_{4}}$	$μ_{d e_{5}}$	$μ_{d e_{6}}$	$μ_{d e_{7}}$
$μ_{e_{1}}$	$(85, 93)$	$(85, 93)$	$(90, 95)$	$(90, 95)$	$(93, 97)$	$(95, 99)$	$(97, 101)$
$μ_{e_{2}}$	$(85, 93)$	$(90, 95)$	$(90, 95)$	$(93, 97)$	$(95, 99)$	$(97, 101)$	$(100, 102)$
$μ_{e_{3}}$	$(90, 95)$	$(90, 95)$	$(93, 97)$	$(95, 99)$	$(97, 101)$	$(100, 102)$	$(101, 103)$
$μ_{e_{4}}$	$(90, 95)$	$(93, 97)$	$(95, 99)$	$(97, 101)$	$(100, 102)$	$(101, 103)$	$(102, 107)$
$μ_{e_{5}}$	$(93, 97)$	$(95, 99)$	$(97, 101)$	$(100, 102)$	$(101, 103)$	$(102, 107)$	$(102, 107)$
$μ_{e_{6}}$	$(95, 99)$	$(97, 101)$	$(100, 102)$	$(101, 103)$	$(102, 107)$	$(102, 107)$	$(105, 125)$
$μ_{e_{7}}$	$(97, 101)$	$(100, 102)$	$(101, 103)$	$(102, 107)$	$(102, 107)$	$(105, 125)$	$(105, 125)$

Table 4. The comparative results of the vibration suppression efficiency and the computational cost for

α = 0.3, 0.5

Table 4. The comparative results of the vibration suppression efficiency and the computational cost for

α = 0.3, 0.5

Time- Varying Stiffness	$α$	0.3						0.5
	$V$	60			70			60			70
	$L$	40	60	80	40	60	80	40	60	80	40	60	80
Simplified	CC (sec)	45.58	45.81	52.01	44.86	45.38	45.25	50.74	43.68	46.43	52.36	44.11	52.29
Simplified	VSE (%)	79.22	82.13	84.92	76.30	81.14	83.35	76.68	81.69	86.42	74.06	79.19	84.43
KM	CC (sec)	81.60	80.59	81.05	70.58	80.42	72.11	70.05	77.22	69.91	71.38	70.48	74.40
KM	VSE (%)	80.44	83.51	85.90	77.36	82.69	84.82	79.48	84.63	88.19	77.16	82.29	87.00
MZL	CC (sec)	24.35	22.54	21.06	25.52	24.43	22.96	23.34	20.84	23.55	27.28	26.31	26.08
MZL	VSE (%)	78.93	82.31	84.85	75.95	81.22	83.59	78.43	82.38	86.21	75.66	80.33	84.51

Table 5. The comparative results of the vibration suppression efficiency and the computational cost for

α = 0.4, 0.6

Table 5. The comparative results of the vibration suppression efficiency and the computational cost for

α = 0.4, 0.6

Time- Varying Stiffness	$α$	0.4						0.6
	$V$	60			70			60			70
	$L$	40	60	80	40	60	80	40	60	80	40	60	80
Simplified	CC (sec)	46.72	50.39	51.71	52.36	44.11	52.29	54.49	53.71	45.24	45.67	53.94	54.99
Simplified	VSE (%)	78.34	83.40	85.77	75.13	81.84	84.56	75.95	78.36	85.18	73.33	76.16	81.62
KM	CC (sec)	66.30	73.87	66.45	71.38	70.48	74.40	68.82	68.64	77.52	67.03	75.86	77.45
KM	VSE (%)	80.26	85.65	87.32	77.19	84.04	86.76	79.92	82.14	87.48	78.34	80.44	84.86
MZL	CC (sec)	24.50	19.21	27.16	27.28	26.31	26.08	21.81	23.67	21.20	24.50	23.67	27.16
MZL	VSE (%)	78.84	83.53	85.98	75.62	81.99	84.84	78.34	80.33	85.56	76.91	79.18	82.65

Table 6. Test of performance robustness.

Item		Contact Force	Variance (%)	$VSE (α = 0.6, V = 70, L = 40)$	Variance (%)
Nominal		99.9120	0	76.9096	0
Viscous damping coefficient $c_{h}, c_{f}$	+20%	99.9202	0.0082	76.6405	0.3499
Viscous damping coefficient $c_{h}, c_{f}$	−20%	99.9106	0.0014	76.9648	0.0718
Stiffness of suspension $k_{h}, k_{p a n} k_{c a t}$	+20%	99.9105	0.0015	76.0437	1.1259
Stiffness of suspension $k_{h}, k_{p a n} k_{c a t}$	−20%	99.9155	0.0035	76.7688	0.1831

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Lin, T.-C.; Sun, C.-W.; Lin, Y.-C.; Zirkohi, M.M. Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology. Electronics 2022, 11, 132. https://doi.org/10.3390/electronics11010132

AMA Style

Lin T-C, Sun C-W, Lin Y-C, Zirkohi MM. Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology. Electronics. 2022; 11(1):132. https://doi.org/10.3390/electronics11010132

Chicago/Turabian Style

Lin, Tsung-Chih, Chien-Wen Sun, Yu-Chen Lin, and Majid Moradi Zirkohi. 2022. "Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology" Electronics 11, no. 1: 132. https://doi.org/10.3390/electronics11010132

APA Style

Lin, T.-C., Sun, C.-W., Lin, Y.-C., & Zirkohi, M. M. (2022). Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology. Electronics, 11(1), 132. https://doi.org/10.3390/electronics11010132

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Intelligent Contact Force Regulation of Pantograph–Catenary Based on Novel Type-Reduction Technology

Abstract

1. Introduction

2. A Brief Description of the PCS Mathematical Model and Problem Formulation

3. Intelligent Controller Design

3.1. Training Algorithm for IT2AFNNI

3.2. Training Algorithm for IT2AFLC

3.3. Main Results

4. Simulation Results

5. Conclusions

Author Contributions

Funding

Data Availability Statement

Conflicts of Interest

References

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