Development of a computational system to design a helical spring

Farah Kamil; Areej Ghazy Abdulshaheed; Mohannad Aziz Kadhom

doi:10.1556/1848.2024.00711

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International Review of Applied Sciences and Engineering

Volume/Issue:: Volume 15: Issue 3

Development of a computational system to design a helical spring

Authors:

Farah Kamil

Farah Kamil AL-Furat AL-Awsat Technical University (ATU), Technical Institute of Al-Diwaniyah, Iraq

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dw.frh@atu.edu.iq https://orcid.org/0000-0002-2178-4751

Areej Ghazy Abdulshaheed

Areej Ghazy Abdulshaheed AL-Furat AL-Awsat Technical University (ATU), Technical Institute of Al-Diwaniyah, Iraq

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, and

Mohannad Aziz Kadhom

Mohannad Aziz Kadhom AL-Furat AL-Awsat Technical University (ATU), Technical Institute of Al-Diwaniyah, Iraq

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Pages:: 287–295

Online Publication Date:: 06 Mar 2024

Publication Date:: 25 Oct 2024

Article Category:: Research Article

DOI:: https://doi.org/10.1556/1848.2024.00711

Keywords:: computer-aided design; helical spring; computational system; software

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Abstract

Springs are the most basic mechanical elements used in transmission mechanisms. The rapid development of the computer and cellular industry has encouraged spring manufacturers to develop the industry to produce very small springs. Most computer-aided design programs for mechanical parts provide the possibility of designing these parts, as these programs include different types of decisions. All these decisions require coordinates for geometric data as well as metadata. The paper aims to develop software programs to design and analyze springs as one of the most significant mechanical elements used. This paper aims to develop a design software of a helical spring system, where this software is built using a computer program in the language of Visual Basic Version 5. When the user enters data into the system, the system will perform a series of complex calculations in the system, then provide a detailed report on all the engineering dimensions of the spring, and test its efficiency. The output of the software shows the required spring wire parameters. The software was tested with test data from the open literature, and the required wire spring parameters were obtained.

Abstract

1 Introduction

According to [1], springs are mechanical components that deform when subjected to force. In addition to absorbing and storing energy, they release it when the force is removed. Furthermore, [2] springs can be grouped into flat, wire, or special-shaped springs. Within each of these subcategories, there are varieties of springs to choose from. To resist torsion, compressive, or tensile loads, wire springs are often constructed as helical springs using either square or round wire [3]. Although helical springs can have cross-section wires that are circular, rectangular, or square, the circular cross-section is the one that is most frequently utilized. When the springs are put under axial load, they will be subjected to shear stress in both the transverse and torsional directions. In addition, there is an additional effect of stress brought on by the curvature.

The design of a mechanical component has been characterized as a repeated process, which frequently calls for repeated analysis to achieve the best possible result from the design. Because of the system's sophisticated architecture, this procedure is laborious and takes a significant amount of time. This calls for using such an important tool as digital computers [4].

The use of computational systems in the design of engineering systems has significantly increased recently. Engineers will employ numerical modelling with a high level of accuracy to simulate, to a reasonable degree of precision, how a complex system will operate [5]. As a consequence of this, computer-aided design, often known as CAD, is frequently used in engineering practice, particularly for mechanical analysis, design, optimizing, and drawing. The application of CAD makes it possible to identify the automation design of both elements and machines [6].

There have been many different kinds of studies that have concentrated on the computational system used to design a spring. Ajay Ganesh Ram, V. et al. [7], evaluated the distribution of stresses in a helical that has an elliptical cross-section and a helix angle of fewer than 10° when it was exposed to an axial static force and took into consideration the influence of wire curvature. They provided both analytical and finite element (FE) analyses, and experimental research using an actual automobile valve spring was utilized to validate the analyses. A three-dimensional geometric modeling of a double helical spring was given in [8] using an FE method to analyze the mechanical behavior of the spring when subjected to axial tensile stress. Y. Peng et al. [9], stated that the model with three dimensions of a closed-end a stranded wire helical spring (SWHS), the parametric modeling method, and the spring formation concept were supplied. Using the commercial CAD program Pro/Engineering, a prototype of the machine tool is created and built using the motion control system as a personal computer plus Programmable Logic Controller (PC + PLC-based model), improving SWHS manufacturing.

Accordingly, F. M. Filotto and G. Kress [10] developed a planar nonlinear finite element model for calculating the reaction of helical bodies to homogeneous deformation, using axial torsion and elongation as an example. The results demonstrated that the situations of a simple round helix and many helices placed in a compliance matrix were identical. The outcomes match the responses obtained by a comparable three-dimensional FE mode. Whereas in H. Pawar and D. Desale [11], the helical compression spring developed for the front suspension of a three-wheeler has been revised and improved. ANSYS 16.0 is utilized to analyze the Computer-Aided-Design spring model with modified dimensions. HASE, Kazunori et al. [12], built a computational model of a flat spring to research the elastic distortion properties connected to the form of a prosthesis. The model assessed the connection with the floor in addition to the communication with the model of the human body. Evaluating the findings of the elastic characterization in comparison to the results of the FE analysis. Additionally, compared to those of the FE evaluation, the cost of computation and applicability of changes to parameters were significantly higher.

Navaneethasanthakumar, S. et al. [13], explored a novel way to enhance the helical compression springs design employing two objective functions, four control variables, and six and seven constraints, respectively, with LabVIEW. The spring is next modeled by AutoCAD (AutoLISP program) using the optimal design values determined in the previous step. Lastly, the transient structural environment by ANSYS is used to analyze the modelled spring. A. Venkatraman et al. [14], to make accurate projections on the functionality of micro springs, a surrogate model based on the Gaussian Process was developed. The overall computing cost was brought down thanks to the sequential design of the FE simulations. This methodology produced strong, accurate, and inexpensive performance estimates. The substitute model was utilized to optimize the performance of the micro-spring, resulting in an 80% improvement in performance. Neve, Abhishek G. et al. [15], the grasshopper enhancement process is utilized to improve the design of the snubber spring (through CATIA V5), which is then assessed using ANSYS 17.0. This approach simulates the natural behavior of grasshoppers and models the solution to an optimization issue.

Naresh, R. [16] modelled a novel leaf spring and performed transient and static analyses. Between the steel leaves of this spring is Ethylene Propylene Diene Monomer (EPDM) rubber, which is an artificial rubber with hyperplastic properties. NX 11.0 software was used to model both traditional and new leaf springs, while ANSYS 18.0 was used for static and dynamic assessments. In addition, L. M. Jugulkar et al. [17], described a variable rigidity system comprising a fluid damper with changeable stiffness and two helical springs. Four distinct degrees of fluid damper strength are modified to achieve the changeable rigidity of the prototype. MATLAB Simulink and Simscape were utilized to conduct numerical simulations. As a result, K. Evseev and A. Kartashov [18] investigated models that take into account the viscoelastic characteristics of springs made of poly composite elements. A MATLAB/Simulink model has been developed to enable the computation of composite springs. Preparing and validating a composite spring made it possible to compare its elastic properties derived through modelling and experimentation.

On the other hand, Y. M. Alsayed et al. [19], proposed a novel design and implementation method for modelling a helical spring actuator of a shape-memory alloy (SMA). The proposed method relies on a mechanism driven by shear strain. To manage the position of the SMA actuator under the strategy that was presented, a one-of-a-kind hybrid sliding-style adaptive relative integral controller was developed. The fuzzy logic system allows for the specified controller parameters to have automatic adjustments made to them. For a Baja car (an intercollegiate project competition organized by the Society of Automotive Engineers), Ajay Ganesh Ram, V. et al. [20], selected a helical compression spring. Baja cars are also renowned for their strength and longevity. As a result, the typical materials and specifications are optimized in the MATLAB program via a full factorial approach. ANSYS workbench was formerly utilized to conduct structural evaluation on the specified springs.

The following outline constitutes the framework of this study. The research technique is presented in sector 2. The discussion and the results are presented in Sector 3. In the final section, the results are discussed.

2 Materials and methods

2.1 Theoretical background and design considerations

2.1.1 Terms used in compression springs

The following phrases referring to compression springs are important to the whole discussion because of the way the topic is structured [21–23].

1-Solid length (LS)

It seems likely that the compression spring will be solid once the coils have been pressed to the point where they touch each other. When the spring is pulled, the coils touch each other.

L_{S} = n^{'} \times d

(1)

Where n' = Coils total number, and

d = Wire diameter.

2-Free length (LF)

It is the spring length in the free or unloaded situation, as shown in Fig. 1.

Fig. 1.

Compression spring terminology (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

Spring free length,

L_{F} = n^{'} \times d + δ_{\max} + 0.15 δ_{\max}

(2)

where

δ_{\max}

= Maximum compression

0.15 $δ_{\max} =$ Clearance between adjacent coils.

The spring free length can also be determined using the relationship shown below.

L_{F} = n^{'} \times d + δ_{\max} + (n^{'} - 1) \times 1 m m

(3)

3-Spring index (C)

It is the proportion of wire diameter to coil mean diameter. In terms of mathematics,

Spring index (C), = C = D / d

(4)

Where: – “D = Coil mean diameter, and”

“d = Wire diameter”.

4-Spring rate (к)

It is the amount of force needed to bend a spring one unit. In terms of mathematics,

Spring rate (к), k = W / δ

(5)

Where: - W = Load,

δ = Spring deformation.

Note: Compression springs are not usually made to close under their highest working force when they are used for what they are meant for. This is because there is a risk of breaking the spring. As a consequence, there is a gap supplied between the adjacent coils so that the coils do not close throughout the service. It might be as much as 15% of the maximum deflection.

5-Pitch (p)

It is the axial space between neighboring helixes in the uncompressed situation. In mathematical terms,

Coil pitch (p) = $L_{F} / {(n}^{'} - 1)$

The following formula can also be used to determine the coil pitch:

p = (L_{F} - L_{S}) / n^{'}

(6)

Note:

1-The number of turns (n) between the locations of the beginning and finishing turns of loops and similar loops should be equal to the total amount of turns on the tension helical spring. According to the findings of certain trials, the author should double the number of turns for each loop. As a result, the sum of the number of turns that are active for a spring's two end loops is,

$n^{;}$ = n +1

2-Experimental research has shown that a spring acts as a column and might break by bending at a relatively low load when its free length (LF) exceeds four times the mean or pitch diameter (D). in other word, if (L_F) is above four times (D), then the spring is under the curvature.

$L_{F} > 4 D$ spring is exposed to curvature

2.1.2 Stresses in circular wires of helical springs

Take, for example, the circular wire that can be found in a helical compression spring. This wire is depicted in Fig. 2 as being subjected to the axial load (W).

1-The wire's torsional shear stress (τt).

T = W \times D / 2 = π / 16 \times τ_{1} \times d_{3}

(8 . F . D) / π d_{3}

(7)

2-Direct shear stress owing to the load (τd).

τ_{d} = W / ((π \times d) \div 4) = 4 W / π d^{2}

(8)

3-The wire's maximum shear stress (τ).

τ = τ_{t} + τ_{d} = (8 . W . D) / π d_{3} + 4 W / π d^{2}

τ = (8 . W . D) / π d_{3} (1 + d / 2 D)

τ = K_{S} (8 . W . D) / π d_{3}

(9)

Where: - K_S = factor of shear stress.

K_{S} = 1 + (1 / 2 C)

(10)

K = (4 C - 1) / (4 C - 4) + (0.615 / C)

(11)

Where: - K = Wahl's factor of correction.

Fig. 2.

Stresses in circular wires of helical springs (a) axial load and (b) torsional and direct shear (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

“Maximum shear stress (τ).”

$τ = K_{S} (8 . W . D) / π d_{3}$ Neglect the effect of curvature.

τ = K (8 . W . D) / π d_{3}

Consider the effect of curvature.

C = D / d \to τ = K (8 . W . C) / π d^{2}

(12)

It is possible to determine the values of (K) that are associated with a certain spring index (C) by referring to the graph that is presented in Fig. 3.

Fig. 3.

Wahl's stress factor for helical springs (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

As a result of looking at Fig. 3, the author has concluded that the factor of Wahl's stress will rapidly grow whenever the spring index would decrease. The spring that is typically utilized in machinery has a spring index that is more than 3.

Note that the two sub-factors (KC) and (KS) can be considered components of Wahl's stress factor (K), which means

K = K_{S} \times K_{C}

In which KS represents the shear stress component and KC represents the kinematic stress concentration.

2.1.3 Helical spring deflection

The entire active wire's length (l) = One coil's length × active coils' No. = π D × n

Spring axial deformation δ = θ \times (D / 2)

(13)

Where: – θ = the angular deformation of the wire when the torque (T) is applied.

The author additionally acknowledges

T / J = τ / (D / 2) = (G . θ) / l

θ = (T . l) / (J . G) “ [Taking into account T / J = (G . θ) / l] ”

Where: J is the spring wire's polar moment of inertia.

J = (π / 32) \times d^{4}

“d = spring wire diameter”.

And “G = Modulus of rigidity for the spring wire material”.

Now, in the preceding formula, the author has replaced the values of (l) and (J) with the following:

θ = (T . l) / (J . G) = [(W \times D / 2) \times π D n] / (π / 32) \times d^{4} G

θ = (16 W . D^{2} . n) / G . d^{4}

(14)

Replacing this value of (θ) in formula (13), the author has

δ = [(16 W . D^{2} . n) / G . d^{4}] \times (D / 2) = (8 W . D^{3} . n) / G . d^{4}

δ = (8 W . C^{3} . n) / G . d

(15)

And the spring rate (k) = (G . d) / (8 C^{3} . n)

(16)

2.2 System design

2.2.1 Information preparation

The essential information that must be stored in our system is illustrated in Fig. 4, and it is as follows: (Load, deflection, spring index, shear stress and stiffness modulus).

Fig. 4.

System architecture (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.2.2 The development of the system

To accurately perform spring design calculations, the technology has been thoroughly constructed. In addition, the system that was designed can perform a wide variety of functions, as illustrated in Fig. 4. Every function in the system is intertwined with the other functions of the system.

2.2.3 User interface

The principal module of the user interface is what makes it possible for users to access any part of the system. This module also plays an important part in some other system processes. The user and other components of the system communicate with one another through a medium known as the user interface. After the relevant inputs have been submitted by the user via the user interface, a series of system activities is carried out to compute the required spring design information and generate an exhaustive output report.

2.2.4 Spring design module

The spring design function is the procedure that determines the spring design's mathematical computations. Likewise, this module included multiple design steps. Hence, based on the type of data entered by the user, a system has been built and designed to calculate the necessary information for the spring design, as depicted in Figs 5 and 6.

Fig. 5.

Display in detail the steps and procedures for designing the spring (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

Fig. 6.

Flowchart of the spring design procedures (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3 Designing the computational system interfaces for the spring design using the Visual Basic program

The system's interfaces are established sequentially and clearly to make easy understanding as follows:

2.3.1

When the required inputs are entered through the user interface, the first interface is used to compute the diameter of the spring wire. The user interface receives the inputs needed to calculate the diameter of the wire. The next step is for the user to determine whether or not the spring is experiencing the curvature effect. The program will calculate Wahl's correction factor if it is under the effect of curvature. If it is not affected by the curvature effect, the system will first determine the shear stress modulus. Then it will determine the spring wire diameter, as depicted in Fig. 7.

Fig. 7.

Interface for calculating spring wire diameter (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3.2

The second interface is used to calculate the spring coil diameter on average. The system will compute the average spring coil diameter based on the outputs of the first interface, which are the spring index and the spring wire diameter. This calculation can be seen in Fig. 8.

Fig. 8.

Interface for calculating the mean diameter of the spring coil (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3.3

After computing the actual number of spring turns, the next step is to use the third interface to get the total number of spring turns. This step follows the first step. After the number of spring rotations has been counted, this number is calculated (calculated from the deflection equation). In addition to the outputs of the first and second interfaces, how this is performed is dependent on a set of inputs; this is represented in Fig. 9.

Fig. 9

Interface for calculating the number of coils turns (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3.4

The purpose of the fourth interface is to compute the spring free length by drawing on the outputs of the three interfaces that came before it as well as some inputs. To do this, it relies on the outputs of the three interfaces that came before it. See Fig. 10.

Fig. 10.

Interface for calculating spring free length (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3.5

As can be seen in Fig. 11, the fifth interface is intended to compute the coil pitch by taking into account the outputs of the four interfaces that came before it, together with a few inputs.

Fig. 11.

Interface for calculating the coil pitch (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

2.3.6

The sixth and final interface is the thorough report that displays the findings on the most essential information required for the design of the spring Fig. 12.

Fig. 12.

Interface of spring design results (Own source)

Citation: International Review of Applied Sciences and Engineering 15, 3; 10.1556/1848.2024.00711

3 Results and discussion results

3.1 System evaluation

An explanatory case study is presented here to evaluate the validity and completeness of the developed system:

The following data of a helical compression spring:

The largest shear stress that can be applied is 420 MPa, and the stiffness about 84 kN/mm2. 1,000 N is the maximum force, while 5 is the approximate spring index, the deflection is 25 mm, and the spring index is approximately 5.

Use Wahl ’ s factor, K = [(4 C - 1) / (4 C - 4)] + (0.615 / C)

Now the author designs the spring depending on the mathematical equations:

Given that W = 1000 N, C = D/d = 5, δ = 25 mm, G = 84 kN/mm² = 84 × 103 N/mm², τ = 420 MPa = 420 N/mm², the following solution is provided.

1-“Spring wire Diameter”.

K = \frac{4 C - 1}{4 C - 4} + \frac{0.615}{C}

K = \frac{(4 \times 5) - 1}{(4 \times 5) - 4} + \frac{0.615}{5}

K = 1.31

τ = K (8 . W . C) / π d^{2} \to 420 = 1.31 (8.1000.5) / π d^{2} \to d = 6.3 mm

2-“Spring coil mean diameter”.

C = D / d \to D = C \times d = 5 \times 6.3 = 31.5 mm

3-The number of times the coil turns ( $n^{'}$ ).

n = the number of turns on the active coils.

δ = (8 W . C^{3} . n) / G . d \to 25 = (8 . 1000 . 5^{3} . n) / 84 . 10^{3} . 6.3

⸫n = 13.23 Say 14

The total turns number for squared and ground ends,

n^{'} = 14 + 2 = 16

4-Spring free length.

L_{F} = n^{'} \times d + δ_{\max} + 0.15 δ_{\max} = 16 \times 6.3 + 25 + 0.15 \times 25

L_{F} = 129.55 m m

5-Coil pitch.

p = L_{F} / {(n}^{'} - 1) = 129.55 / (16 - 1) = 8.63 m m

Now, the author applies the program based on the data given in above to ensure that the results match and the system is effective as follows:

3.2 Results discussion

Through the previous interfaces and results, the author can see the effectiveness of the system in obtaining the same theoretical results in a shorter time, compared to complex calculations using the manual method of calculation. The computational system makes it possible to swiftly and precisely perform calculations and processing that frequently involve a large number of variables. The variable data can be changed in some way to enable additional analysis of any change's ramifications. Implementing computational systems offers a framework that makes it possible to personify the essential data, that must be taken into account when choosing a suitable technology. Coil springs are used in a wide range of applications, hence the goal of this research was to develop a computational method for their design. The developed system, which was built in Visual Basic, calculated the necessary information to manufacture a spring. The software's user interface was created using Visual Basic 5.0. It is the major part of the program and consists of forms for data entry and methods for producing the results. Despite being easy to use, it is a useful tool for calculating the necessary data and analyzing the results. Because of the wide range of applications it has, it is expected that any organization and design engineers will find this system to be a potent tool that helps data analysis, understanding of the necessary dimensions, and their evaluation.

You may encourage sustainability in your field and in your industry by using CAD software. Making design decisions based on environmental standards and criteria including life cycle analysis, carbon footprint, and eco-labeling is possible with the use of CAD software [24]. Using renewable materials, biodegradable parts, or circular design concepts are just a few examples of creative solutions that can lessen the environmental effect of your products that you can investigate using CAD software. For instance, CAD software can be used to design items that are easily repairable, reusable, or recyclable, or it can be used to develop things that can harness renewable energy sources like solar, wind, or hydro power [25].

4 Conclusions

With the help of the Computational system, it is possible to perform calculations and processing that commonly include a huge number of variables quickly, while keeping a high level of precision. Altering the variable data in some way allows for further investigation into the implications of any change. Implementing computational systems provides a framework that enables the crucial information that must be considered, when selecting an appropriate technology to be personified. The objective of this research was to design a computational method for the design of coil springs, which are utilized in a wide variety of applications. To create a spring, the developed system, which was constructed using Visual Basic, computed the relevant information that was required. The user interface of the software is built with Visual Basic 5.0. It comprises data entering forms and procedures for outputting the results, and it is the main component of the program. It is an effective tool for computing the required information and interpreting the results, despite being simple to use. It is anticipated that any organization and design engineers would find this system to be a powerful instrument that facilitates data analysis, knowledge of the necessary dimensions, and their evaluation as a result of the vast field of application that it covers.

Disclosure statement

The author of this article does not receive any monetary research support from a company or institution. The author has not disclosed any possible conflicts of interest.

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International Review of Applied Sciences and Engineering

Print ISSN:: 2062-0810

Online ISSN:: 2063-4269

Editorial Board

Mohammad Nazir AHMAD, Institute of Visual Informatics, Universiti Kebangsaan Malaysia, Malaysia

Murat BAKIROV, Center for Materials and Lifetime Management Ltd., Moscow, Russia

Nicolae BALC, Technical University of Cluj-Napoca, Cluj-Napoca, Romania

Umberto BERARDI, Toronto Metropolitan University, Toronto, Canada

Ildikó BODNÁR, University of Debrecen, Debrecen, Hungary

Sándor BODZÁS, University of Debrecen, Debrecen, Hungary

Fatih Mehmet BOTSALI, Selçuk University, Konya, Turkey

Samuel BRUNNER, Empa Swiss Federal Laboratories for Materials Science and Technology, Dübendorf, Switzerland

István BUDAI, University of Debrecen, Debrecen, Hungary

Constantin BUNGAU, University of Oradea, Oradea, Romania

Shanshan CAI, Huazhong University of Science and Technology, Wuhan, China

Michele De CARLI, University of Padua, Padua, Italy

Robert CERNY, Czech Technical University in Prague, Prague, Czech Republic

Erdem CUCE, Recep Tayyip Erdogan University, Rize, Turkey

György CSOMÓS, University of Debrecen, Debrecen, Hungary

Tamás CSOKNYAI, Budapest University of Technology and Economics, Budapest, Hungary

Anna FORMICA, IASI National Research Council, Rome, Italy

Alexandru GACSADI, University of Oradea, Oradea, Romania

Eugen Ioan GERGELY, University of Oradea, Oradea, Romania

Janez GRUM, University of Ljubljana, Ljubljana, Slovenia

Géza HUSI, University of Debrecen, Debrecen, Hungary

Ghaleb A. HUSSEINI, American University of Sharjah, Sharjah, United Arab Emirates

Nikolay IVANOV, Peter the Great St. Petersburg Polytechnic University, St. Petersburg, Russia

Antal JÁRAI, Eötvös Loránd University, Budapest, Hungary

Gudni JÓHANNESSON, The National Energy Authority of Iceland, Reykjavik, Iceland

László KAJTÁR, Budapest University of Technology and Economics, Budapest, Hungary

Ferenc KALMÁR, University of Debrecen, Debrecen, Hungary

Tünde KALMÁR, University of Debrecen, Debrecen, Hungary

Milos KALOUSEK, Brno University of Technology, Brno, Czech Republik

Jan KOCI, Czech Technical University in Prague, Prague, Czech Republic

Vaclav KOCI, Czech Technical University in Prague, Prague, Czech Republic

Imre KOCSIS, University of Debrecen, Debrecen, Hungary

Imre KOVÁCS, University of Debrecen, Debrecen, Hungary

Angela Daniela LA ROSA, Norwegian University of Science and Technology, Trondheim, Norway

Éva LOVRA, Univeqrsity of Debrecen, Debrecen, Hungary

Elena LUCCHI, Eurac Research, Institute for Renewable Energy, Bolzano, Italy

Tamás MANKOVITS, University of Debrecen, Debrecen, Hungary

Igor MEDVED, Slovak Technical University in Bratislava, Bratislava, Slovakia

Ligia MOGA, Technical University of Cluj-Napoca, Cluj-Napoca, Romania

Marco MOLINARI, Royal Institute of Technology, Stockholm, Sweden

Henrieta MORAVCIKOVA, Slovak Academy of Sciences, Bratislava, Slovakia

Phalguni MUKHOPHADYAYA, University of Victoria, Victoria, Canada

Balázs NAGY, Budapest University of Technology and Economics, Budapest, Hungary

Husam S. NAJM, Rutgers University, New Brunswick, USA

Jozsef NYERS, Subotica Tech College of Applied Sciences, Subotica, Serbia

Bjarne W. OLESEN, Technical University of Denmark, Lyngby, Denmark

Stefan ONIGA, North University of Baia Mare, Baia Mare, Romania

Joaquim Norberto PIRES, Universidade de Coimbra, Coimbra, Portugal

László POKORÁDI, Óbuda University, Budapest, Hungary

Roman RABENSEIFER, Slovak University of Technology in Bratislava, Bratislava, Slovak Republik

Mohammad H. A. SALAH, Hashemite University, Zarqua, Jordan

Dietrich SCHMIDT, Fraunhofer Institute for Wind Energy and Energy System Technology IWES, Kassel, Germany

Lorand SZABÓ, Technical University of Cluj-Napoca, Cluj-Napoca, Romania

Csaba SZÁSZ, Technical University of Cluj-Napoca, Cluj-Napoca, Romania

Ioan SZÁVA, Transylvania University of Brasov, Brasov, Romania

Péter SZEMES, University of Debrecen, Debrecen, Hungary

Edit SZŰCS, University of Debrecen, Debrecen, Hungary

Radu TARCA, University of Oradea, Oradea, Romania

Zsolt TIBA, University of Debrecen, Debrecen, Hungary

László TÓTH, University of Debrecen, Debrecen, Hungary

László TÖRÖK, University of Debrecen, Debrecen, Hungary

Anton TRNIK, Constantine the Philosopher University in Nitra, Nitra, Slovakia

Ibrahim UZMAY, Erciyes University, Kayseri, Turkey

Andrea VALLATI, Sapienza University, Rome, Italy

Tibor VESSELÉNYI, University of Oradea, Oradea, Romania

Nalinaksh S. VYAS, Indian Institute of Technology, Kanpur, India

Deborah WHITE, The University of Adelaide, Adelaide, Australia

International Review of Applied Sciences and Engineering
Address of the institute: Faculty of Engineering, University of Debrecen
H-4028 Debrecen, Ótemető u. 2-4. Hungary
Email: irase@eng.unideb.hu

Indexing and Abstracting Services:

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2023
Scimago
Scimago H-index	11
Scimago Journal Rank	0.249
Scimago Quartile Score	Architecture (Q2) Engineering (miscellaneous) (Q3) Environmental Engineering (Q3) Information Systems (Q4) Management Science and Operations Research (Q4) Materials Science (miscellaneous) (Q3)
Scopus
Scopus Cite Score	2.3
Scopus CIte Score Rank	Architecture (Q1) General Engineering (Q2) Materials Science (miscellaneous) (Q3) Environmental Engineering (Q3) Management Science and Operations Research (Q3) Information Systems (Q3)
Scopus SNIP	0.751

International Review of Applied Sciences and Engineering
Publication Model	Gold Open Access Online only
Submission Fee	none
Article Processing Charge	1100 EUR/article
Regional discounts on country of the funding agency	World Bank Lower-middle-income economies: 50% World Bank Low-income economies: 100%
Further Discounts	Limited number of full waivers available. Editorial Board / Advisory Board members: 50% Corresponding authors, affiliated to an EISZ member institution subscribing to the journal package of Akadémiai Kiadó: 100%
Subscription Information	Gold Open Access

International Review of Applied Sciences and Engineering
Language	English
Size	A4
Year of Foundation	2010
Volumes per Year	1
Issues per Year	3
Founder	Debreceni Egyetem
Founder's Address	H-4032 Debrecen, Hungary Egyetem tér 1
Publisher	Akadémiai Kiadó
Publisher's Address	H-1117 Budapest, Hungary 1516 Budapest, PO Box 245.
Responsible Publisher	Chief Executive Officer, Akadémiai Kiadó
ISSN	2062-0810 (Print)
ISSN	2063-4269 (Online)