Dynamic Characteristics Study for Surface Composite of AMMNCs Matrix Fabricated by Friction Stir Process

In the present work, Aluminum Metal Matrix Surface Nano Composites (AMMSNCs) were manufactured using Friction Stir Processing (FSP). Moreover, the fabricated surface composite matrix was exposed to a different number of tool passes with different processing parameters. The tensile test and microstructure examinations were used to study the mechanical properties of the composite surface. The dynamic properties were predicted using modal analysis and finite element methods. After this, dynamic characterization was achieved by combining the numerical and experimental methods to investigate the effects of changing the number of passes on the natural frequency and the damping capacity of the AMMSNCs manufactured using FSP. The results indicated that the damping capacity and dynamic behavior improved with an increased number of FSP passes.


Introduction
Applications that are subject to dynamic effects, especially in aircraft and vehicles, need materials with the highest possible damping coefficients and the best possible mechanical properties. In the last few years, Friction Stir Welding (FSW) and its development technique, Friction Stir Processing (FSP), have been widely used in industry. Furthermore, FSP is developed on the basic principles of FSW and aims to further improve the mechanical properties. In this method, a rotating tool with a pin and shoulder is fed to the workpiece, which causes intensive plastic deformation and mixes the material at higher temperatures. This leads to an increase in the homogeneity of the processed zone and refinement of the microstructure. The tool rotation speed, tool feed speed, and the number of tool passes are the main parameters that affect the mechanical behavior [1,2]. Furthermore, the addition of reinforcements in the form of nanoparticles, which come in different types and sizes, have enhanced the mechanical properties. Aluminum alloys have been developed and used in various industries due to their lower density and good strength with respect to weight and corrosion resistance. Metal matrix composites (MMCs) are new materials with excellent mechanical tribological properties [3].
The processing parameters, such as tool rotation speed, feed, and number of passes, play an important role in determining the surface composites. Moreover, the type and size of the nanoparticles used for reinforcement will affect the mechanical properties. The mechanical properties can be improved significantly by adding the reinforcement nanoparticles into the surface layer using an FSP technique. This investigation shows that a greater increase in the rotation speed has a greater effect on the surface layer thickness and grain size. Furthermore, this increase causes better dispersion and distribution of nanoparticles in the surface layer of aluminum alloys [4,5]. Nakata et al. [6] used multi-pass FSP and different types of reinforcement nanoparticles to increase the tensile strength of

Experimental Procedure
Multi-pass FSP allows us to refine the grain size of Al, which consequently improves the mechanical properties. AA 2024 alloy was used as the base alloy for performing FSP. Aluminum alloy plates were prepared and machined in order to have a suitable size for processing. The plates were grooved longitudinally by an end mill tool, with each groove having a diameter of 3 mm and a depth of 2 mm. These grooves were filled with Al 2 O 3 nano-particles with an average diameter of 30 nm in order to reinforce the Al metal matrix. The friction stir processing tool was manufactured from hardened K-110 tool steel. The FS tools were machined to have cylindrical geometry with a pin of (Ø8) mm and a shoulder of (Ø25) mm in diameter, while the tool pin length was 3.5 mm. The processing was performed using an automatic milling machine (Bridgeport, Elmira, NY, USA) as shown in Figure 1. The main processing parameters used in this study include different numbers of FSP passes, different tool rotation speeds from 1000 rpm to 2000 rpm, and three traverse speeds of 10, 15 and 20 mm/min. The tensile test was carried out according to ASTM B557 for aluminum alloys in order to calculate the engineering Young's modulus. All samples were cut in a direction that was parallel to FSP. The engineering Young's modulus and other mechanical properties were calculated. In order to study the shape of particles and microstructural characteristics of FSP, the specimens were examined using an optical metallurgical microscope and scanning electron microscopy (SEM, Quanta 250 FEG, Hillsboro, AL, USA).

Mechanical Properties
In the previous study [29], the tension test was performed in order to calculate the composite matrix mechanical properties, such as Ultimate Tensile Strength "UTS", Yield Strength "YS", and Young's modulus "E". Figure 2 shows the effect of pass number on Young's modulus under different processing conditions. The results revealed that the mechanical properties improved when the number of FSP passes increased.
From all the previous experimental data, a direct relationship was established to estimate the value of Young's modulus (Equation (1)). This new equation is expressed as a multi-variable power equation, which correlates Young's Modulus "E" to the number of passes "P", tool rotation speed "S" in rpm, and the tool traverse speed "V" in mm/min. A curve fitting was used to estimate the values of the power factor with an error of less than 10%.

Dynamic Characterization
In this section, dynamic characteristic was achieved by combining the numerical and experimental methods to study the effect of changing the number of passes on the natural frequency, mode shape, and the damping of the FSP and AMMSNCs.

Finite Element Model (FEM)
Finite element analysis was developed as a very efficient tool for solving complex problems in the field of design engineering. Many authors [24,[30][31][32] used FEM to model the cantilever beam. In this paper, a finite element model was developed to simulate both partially surface composite and fully surface composites. The mode shapes and frequency response function (FRF) have been determined. The AMMSNCs have already been modeled as a cantilever beam. Hence, the model was used to determine a structure's vibration characteristics, natural frequency, and mode shapes. In this model, the modal analysis module was selected to perform the dynamic study. Moreover, the

Mechanical Properties
In the previous study [29], the tension test was performed in order to calculate the composite matrix mechanical properties, such as Ultimate Tensile Strength "UTS", Yield Strength "YS", and Young's modulus "E". Figure 2 shows the effect of pass number on Young's modulus under different processing conditions. The results revealed that the mechanical properties improved when the number of FSP passes increased.
From all the previous experimental data, a direct relationship was established to estimate the value of Young's modulus (Equation (1)). This new equation is expressed as a multi-variable power equation, which correlates Young's Modulus "E" to the number of passes "P", tool rotation speed "S" in rpm, and the tool traverse speed "V" in mm/min. A curve fitting was used to estimate the values of the power factor with an error of less than 10%.

Mechanical Properties
In the previous study [29], the tension test was performed in order to calculate the composite matrix mechanical properties, such as Ultimate Tensile Strength "UTS", Yield Strength "YS", and Young's modulus "E". Figure 2 shows the effect of pass number on Young's modulus under different processing conditions. The results revealed that the mechanical properties improved when the number of FSP passes increased.
From all the previous experimental data, a direct relationship was established to estimate the value of Young's modulus (Equation (1)). This new equation is expressed as a multi-variable power equation, which correlates Young's Modulus "E" to the number of passes "P", tool rotation speed "S" in rpm, and the tool traverse speed "V" in mm/min. A curve fitting was used to estimate the values of the power factor with an error of less than 10%.

Dynamic Characterization
In this section, dynamic characteristic was achieved by combining the numerical and experimental methods to study the effect of changing the number of passes on the natural frequency, mode shape, and the damping of the FSP and AMMSNCs.

Finite Element Model (FEM)
Finite element analysis was developed as a very efficient tool for solving complex problems in the field of design engineering. Many authors [24,[30][31][32] used FEM to model the cantilever beam. In this paper, a finite element model was developed to simulate both partially surface composite and fully surface composites. The mode shapes and frequency response function (FRF) have been determined. The AMMSNCs have already been modeled as a cantilever beam. Hence, the model was used to determine a structure's vibration characteristics, natural frequency, and mode shapes. In this model, the modal analysis module was selected to perform the dynamic study. Moreover, the

Dynamic Characterization
In this section, dynamic characteristic was achieved by combining the numerical and experimental methods to study the effect of changing the number of passes on the natural frequency, mode shape, and the damping of the FSP and AMMSNCs.

Finite Element Model (FEM)
Finite element analysis was developed as a very efficient tool for solving complex problems in the field of design engineering. Many authors [24,[30][31][32] used FEM to model the cantilever beam. In this paper, a finite element model was developed to simulate both partially surface composite and fully surface composites. The mode shapes and frequency response function (FRF) have been determined. The AMMSNCs have already been modeled as a cantilever beam. Hence, the model was used to determine a structure's vibration characteristics, natural frequency, and mode shapes. In this model, the modal analysis module was selected to perform the dynamic study. Moreover, the harmonic response module was used along with modal analysis to predict the frequency response function (FRF).
A parametric study was performed on the beams with different geometry parameters. Variations in the length, width, and thickness were considered in the study. Furthermore, the AMMNSC properties were selected based on the previous test of mechanical properties. Increasing the number of FSP passes changes the mechanical properties. Therefore, Young's modulus and Poisson's ratio were calculated based on the mechanical properties obtained from experimental results in order to be used as a material input parameter for the model. The used geometries are shown in Figure 3A. The homogeneous rectangle beam represents the fully surface composite beam, which can be modelled as a base metal ( Figure 3). Furthermore, the partially surface composite beam with FSP surface is shown in the diagram. harmonic response module was used along with modal analysis to predict the frequency response function (FRF). A parametric study was performed on the beams with different geometry parameters. Variations in the length, width, and thickness were considered in the study. Furthermore, the AMMNSC properties were selected based on the previous test of mechanical properties. Increasing the number of FSP passes changes the mechanical properties. Therefore, Young's modulus and Poisson's ratio were calculated based on the mechanical properties obtained from experimental results in order to be used as a material input parameter for the model. The used geometries are shown in Figure 3A. The homogeneous rectangle beam represents the fully surface composite beam, which can be modelled as a base metal ( Figure 3). Furthermore, the partially surface composite beam with FSP surface is shown in the diagram. A mesh study was conducted to select the most appropriate size and type of mesh. After converging the output data error, the mesh size and type were determined. It was observed that the hexahedrons meshing type is the most suitable type as shown in Figure 4. Moreover, the mesh density was found to have a length of 180 elements and thickness of 4 elements. This hypothesis was created to allow for reasonable frequency calculations. After this, a modal shape analysis was performed to obtain the natural frequencies for the two models of the fully and partially (surface composite) FSP. Harmonic analysis was performed by entering the frequency range (0-7000 Hz) according to the frequency range calculated from the first step in modal analysis and mode shape frequency. After this, the boundary conditions were applied by providing a force at the other end of the cantilever beam. A nondestructive vibration hammer test technique was used as previously described by many researchers [33][34][35] in order to characterize the dynamic properties of the fabricated materials. A mesh study was conducted to select the most appropriate size and type of mesh. After converging the output data error, the mesh size and type were determined. It was observed that the hexahedrons meshing type is the most suitable type as shown in Figure 4. Moreover, the mesh density was found to have a length of 180 elements and thickness of 4 elements. This hypothesis was created to allow for reasonable frequency calculations. After this, a modal shape analysis was performed to obtain the natural frequencies for the two models of the fully and partially (surface composite) FSP. Harmonic analysis was performed by entering the frequency range (0-7000 Hz) according to the frequency range calculated from the first step in modal analysis and mode shape frequency. After this, the boundary conditions were applied by providing a force at the other end of the cantilever beam. A nondestructive vibration hammer test technique was used as previously described by many researchers [33][34][35] in order to characterize the dynamic properties of the fabricated materials.
obtain the natural frequencies for the two models of the fully and partially (surface composite) FSP. Harmonic analysis was performed by entering the frequency range (0-7000 Hz) according to the frequency range calculated from the first step in modal analysis and mode shape frequency. After this, the boundary conditions were applied by providing a force at the other end of the cantilever beam. A nondestructive vibration hammer test technique was used as previously described by many researchers [33][34][35] in order to characterize the dynamic properties of the fabricated materials.  In the present work, an experimental free vibration test was performed on the (AMMSNCs) beam to identify the damping factor and natural frequency. Rectangle beams with 90-mm length, 15-mm width, and 2-mm thickness were used in the test. The specimen was prepared as a cantilever beam with one free end. The time decay was measured using an accelerometer (B&K model 4507 B) mounted to the free end of the cantilever beam of AMMNSCs. The beam was excited by an impact hammer (B&K model 8206, Brüel & Kjaer, Naerum, Denmark). The vibration response was measured and analyzed using a pulse data analyzer (B&K module 3160-A-4/2 Brüel & Kjaer, Naerum, Denmark). Figure 5 shows the experimental test rig setup used in the study. The frequency response function (FRF), damping ratio and fundamental frequencies were calculated using modal analysis software (ME Scope) as shown in Figure 6. The free vibration test was carried out and repeated seven times in order to obtain an accurate value. In the present work, an experimental free vibration test was performed on the (AMMSNCs) beam to identify the damping factor and natural frequency. Rectangle beams with 90-mm length, 15mm width, and 2-mm thickness were used in the test. The specimen was prepared as a cantilever beam with one free end. The time decay was measured using an accelerometer (B&K model 4507 B) mounted to the free end of the cantilever beam of AMMNSCs. The beam was excited by an impact hammer (B&K model 8206, Brüel & Kjaer, Naerum, Denmark). The vibration response was measured and analyzed using a pulse data analyzer (B&K module 3160-A-4/2 Brüel & Kjaer, Naerum, Denmark). Figure 5 shows the experimental test rig setup used in the study. The frequency response function (FRF), damping ratio and fundamental frequencies were calculated using modal analysis software (ME Scope) as shown in Figure 6. The free vibration test was carried out and repeated seven times in order to obtain an accurate value.

Results of Finite Element Model
A parametric study is considered to be an effective tool to obtain a set of variables and parameters without changing the model setup. Four major parameters are used in this investigation in order to study the influence of material geometry and properties on the dynamic behavior, including: effect of length, width, thickness and Young's modulus of the resultant frequencies. There is an inverse relationship between length and the natural frequency as shown in Figure 7. We used a fully composite beam in the simulated model. Different values for Young's modulus was used in order to simulate the fabricated samples. The parametric study demonstrated that the natural frequency has direct relationship with the width and thickness. The surface composite beam was modeled in a similar way to the previous study. Figure 8 shows the effect of composite volume parameters on the natural frequency when using different Young's moduli. In addition, the base metal has a constant Young's modulus of 60 GPa. An increased volume of the composite matrix

Results of Finite Element Model
A parametric study is considered to be an effective tool to obtain a set of variables and parameters without changing the model setup. Four major parameters are used in this investigation in order to study the influence of material geometry and properties on the dynamic behavior, including: effect of length, width, thickness and Young's modulus of the resultant frequencies. There is an inverse relationship between length and the natural frequency as shown in Figure 7. We used a fully composite beam in the simulated model. Different values for Young's modulus was used in order to simulate the fabricated samples. The parametric study demonstrated that the natural frequency has direct relationship with the width and thickness. The surface composite beam was modeled in a similar way to the previous study. Figure 8 shows the effect of composite volume parameters on the natural frequency when using different Young's moduli. In addition, the base metal has a constant Young's modulus of 60 GPa. An increased volume of the composite matrix results in an increased natural frequency of the overall surface composite structure. In this model, when the composite surface layer has poorer mechanical properties than the base material, there is an inverse relationship between the width of the composite layer and dynamic frequency response. When the composite layers have better mechanical properties than the base metal, there is a direct relationship between Young's modulus and natural frequency.

Modal Analysis Results
In this study, the different mode shapes and their corresponding natural frequencies were simulated. Referring to the data given in the previous sections, the three models were simulated in order to obtain the fundamental frequencies in each case. The results are summarized in Table 1. The results reveal that there is no significant difference in the values of natural frequency. In particular, this lack of significant differences occurs in the first three-mode shape and their corresponding frequencies. The frequency response function (FRF) for both the simulated model and experimental free vibration test are illustrated in Figure 9.

Modal Analysis Results
In this study, the different mode shapes and their corresponding natural frequencies were simulated. Referring to the data given in the previous sections, the three models were simulated in order to obtain the fundamental frequencies in each case. The results are summarized in Table 1. The results reveal that there is no significant difference in the values of natural frequency. In particular, this lack of significant differences occurs in the first three-mode shape and their corresponding frequencies. The frequency response function (FRF) for both the simulated model and experimental free vibration test are illustrated in Figure 9.

Results of Dynamic Properties.
In the current work, the free experimental vibration tests were performed on the surface composite beam. The pulse impact method was applied to identify the resonant frequency in each sample. The modal analysis software (Structural Vibration Solutions, Aalborg East, Denmark) computes the dynamic parameters obtained from the time domain curves.

Results of Dynamic Properties
In the current work, the free experimental vibration tests were performed on the surface composite beam. The pulse impact method was applied to identify the resonant frequency in each sample. The modal analysis software (Structural Vibration Solutions, Aalborg East, Denmark) computes the dynamic parameters obtained from the time domain curves.
The decay curve method and Fast Fourier Transformation (FFT) analysis were used to calculate the damping ratio (ζ) and frequency response function, respectively. The damping ratio was measured by the vibration accelerometer (Brüel & Kjaer, Naerum, Denmark) as a function of time. The damping ratio was obtained by Equations (2) or (3) [34] or by using the modal analysis software. The storage modulus, complex modulus of elasticity and loss factor were calculated according to Equations (4)-(6) [35][36][37]. The results, which are shown in Table 2, demonstrate the dynamic properties of the surface composite beam with respect to the base aluminum alloy. In addition, we observed variation in the dynamic characteristics between the as-received alloy (AA2024) and the composite surface fabricated by multi-pass FSP.
where M is the mass of the AMMNSCs cantilever beam (kg), m is the mass of the accelerometer, L is the free beam length (m), I is the area moment of inertia (m4), fn is the first mode natural frequency, δ is the logarithmic decrement, E* is the complex modulus of elasticity, E is the elastic (or storage) modulus, E" is the damping (or loss) modulus, and [j] = √ −1.

Effect of Linear Travel Speed on the Damping Capacity
The results show that the linear travel speed has a significant effect on the damping capacity when fabricating the surface composite using FSP. Figure 10A shows the microstructure of the as-received AA2024 alloy, which has a larger grain size with intermetallic components. After having applied FSP to the surface of the matrix, the grains become finer and the Al 2 O 3 nanoparticles are distributed homogenously around the boundary of the grains as shown in Figure 10B. Adding alumina nanoparticles to the mixture enhances the damping capacity of the fabricated composite.

Effect of Linear Travel Speed on the Damping Capacity
The results show that the linear travel speed has a significant effect on the damping capacity when fabricating the surface composite using FSP. Figure 10A shows the microstructure of the asreceived AA2024 alloy, which has a larger grain size with intermetallic components. After having applied FSP to the surface of the matrix, the grains become finer and the Al2O3 nanoparticles are distributed homogenously around the boundary of the grains as shown in Figure 10B. Adding alumina nanoparticles to the mixture enhances the damping capacity of the fabricated composite.
A low feed rate increases the heat generated during the process, which allows Al2O3 nanoparticles to redistribute around the grain boundary of the base metal microstructure. Furthermore, it decreases the microstructure grain size as shown in Figure 11. These results are consistent with previous studies [38,39].
The damping capacity was enhanced at a relatively lower rotation speed, while higher travel speeds and tool rotation speeds did not improve the damping values.

Effect of the Number of FSP Passes on the Damping Capacity
Multi-pass FSP is considered to be one of the most important processing parameters as it can improve both the mechanical properties and dynamic properties. A better distribution of the Al2O3 nanoparticles and improved microstructure of the grains can improve the damping capacity of the processed metal matrix nanocomposites. Figure 12 shows the effect of the number of FSP passes as three FSP passes were applied in this present study. The first pass was excluded due to the incomplete fabrication of the surface composite matrix. Thus, the combination matrix of aluminum alloy and dry A low feed rate increases the heat generated during the process, which allows Al 2 O 3 nanoparticles to redistribute around the grain boundary of the base metal microstructure. Furthermore, it decreases the microstructure grain size as shown in Figure 11. These results are consistent with previous studies [38,39].

Effect of Linear Travel Speed on the Damping Capacity
The results show that the linear travel speed has a significant effect on the damping capacity when fabricating the surface composite using FSP. Figure 10A shows the microstructure of the asreceived AA2024 alloy, which has a larger grain size with intermetallic components. After having applied FSP to the surface of the matrix, the grains become finer and the Al2O3 nanoparticles are distributed homogenously around the boundary of the grains as shown in Figure 10B. Adding alumina nanoparticles to the mixture enhances the damping capacity of the fabricated composite.
A low feed rate increases the heat generated during the process, which allows Al2O3 nanoparticles to redistribute around the grain boundary of the base metal microstructure. Furthermore, it decreases the microstructure grain size as shown in Figure 11. These results are consistent with previous studies [38,39].
The damping capacity was enhanced at a relatively lower rotation speed, while higher travel speeds and tool rotation speeds did not improve the damping values.

Effect of the Number of FSP Passes on the Damping Capacity
Multi-pass FSP is considered to be one of the most important processing parameters as it can improve both the mechanical properties and dynamic properties. A better distribution of the Al2O3 nanoparticles and improved microstructure of the grains can improve the damping capacity of the processed metal matrix nanocomposites. Figure 12 shows the effect of the number of FSP passes as three FSP passes were applied in this present study. The first pass was excluded due to the incomplete fabrication of the surface composite matrix. Thus, the combination matrix of aluminum alloy and dry The damping capacity was enhanced at a relatively lower rotation speed, while higher travel speeds and tool rotation speeds did not improve the damping values.

Effect of the Number of FSP Passes on the Damping Capacity
Multi-pass FSP is considered to be one of the most important processing parameters as it can improve both the mechanical properties and dynamic properties. A better distribution of the Al 2 O 3 nanoparticles and improved microstructure of the grains can improve the damping capacity of the processed metal matrix nanocomposites. Figure 12 shows the effect of the number of FSP passes as three FSP passes were applied in this present study. The first pass was excluded due to the incomplete fabrication of the surface composite matrix. Thus, the combination matrix of aluminum alloy and dry Al 2 O 3 nanoparticles need more than one pass of FSP to obtain the required fabricated surface composite metal matrix. The as-received alloy demonstrated a lower damping capacity after the second and third FSP passes. Al2O3 nanoparticles need more than one pass of FSP to obtain the required fabricated surface composite metal matrix. The as-received alloy demonstrated a lower damping capacity after the second and third FSP passes.   Al2O3 nanoparticles need more than one pass of FSP to obtain the required fabricated surface composite metal matrix. The as-received alloy demonstrated a lower damping capacity after the second and third FSP passes.

Verification of the Dynamic Properties
The finite element model was verified with the experimental natural frequency obtained from the free vibration test. Figure 14 shows a significant convergence between the experimental natural frequency and simulated frequency with an average error of 5%. The natural frequency calculated from the experimental free vibration test was used in Equation 4 in order to calculate the dynamic or (complex) modulus. The static engineering Young's modulus was obtained from a tension test according to ASTM B557. The samples were cut in a direction that was parallel to FSP. The engineering Young's modulus was calculated from the applied tension load and sample elongation value. The results revealed that there is a significant convergence between the experimental engineering Young's modulus and that obtained from the nondestructive experimental test for dynamic moduli with an average error of 3.5%. These values are close, especially at a lower tool rotation speed ( Figure 15).

Verification of the Dynamic Properties
The finite element model was verified with the experimental natural frequency obtained from the free vibration test. Figure 14 shows a significant convergence between the experimental natural frequency and simulated frequency with an average error of 5%. The natural frequency calculated from the experimental free vibration test was used in Equation 4 in order to calculate the dynamic or (complex) modulus. The static engineering Young's modulus was obtained from a tension test according to ASTM B557. The samples were cut in a direction that was parallel to FSP. The engineering Young's modulus was calculated from the applied tension load and sample elongation value. The results revealed that there is a significant convergence between the experimental engineering Young's modulus and that obtained from the nondestructive experimental test for dynamic moduli with an average error of 3.5%. These values are close, especially at a lower tool rotation speed ( Figure 15).

Verification of the Dynamic Properties
The finite element model was verified with the experimental natural frequency obtained from the free vibration test. Figure 14 shows a significant convergence between the experimental natural frequency and simulated frequency with an average error of 5%. The natural frequency calculated from the experimental free vibration test was used in Equation 4 in order to calculate the dynamic or (complex) modulus. The static engineering Young's modulus was obtained from a tension test according to ASTM B557. The samples were cut in a direction that was parallel to FSP. The engineering Young's modulus was calculated from the applied tension load and sample elongation value. The results revealed that there is a significant convergence between the experimental engineering Young's modulus and that obtained from the nondestructive experimental test for dynamic moduli with an average error of 3.5%. These values are close, especially at a lower tool rotation speed ( Figure 15).  Figure 14.

C
Measured natural frequency values against predicted frequency using modal analysis simulation.

Conclusions
From the current investigation, the following conclusions are drawn:


The natural frequencies obtained by the simulation model were close to the values obtained from the experimental free vibration test.  The damping capacity for the surface composite beam was enhanced with respect to the base alloy by 44% as it acts as a self-damping material. This is due to the presence of Al2O3 nanoparticles, which are homogenously dispersed in the metal matrix. Furthermore, this damping capacity can be improved by using an increased number of FSP passes.  A significant improvement in the damping ratio was obtained from the third pass of FSP.  The dynamic properties were enhanced at a lower feed rate speed, with the optimum values observed at a travel speed of 10 mm/min. This can be explained by the fact that a lower travel speed allows for adequate heating time and homogenous distribution of nanoparticles in the surface composite matrix.  The results revealed that there is consistency between the dynamic and static engineering Young's moduli.

Conclusions
From the current investigation, the following conclusions are drawn: • The natural frequencies obtained by the simulation model were close to the values obtained from the experimental free vibration test.

•
The damping capacity for the surface composite beam was enhanced with respect to the base alloy by 44% as it acts as a self-damping material. This is due to the presence of Al 2 O 3 nanoparticles, which are homogenously dispersed in the metal matrix. Furthermore, this damping capacity can be improved by using an increased number of FSP passes. • A significant improvement in the damping ratio was obtained from the third pass of FSP.

•
The dynamic properties were enhanced at a lower feed rate speed, with the optimum values observed at a travel speed of 10 mm/min. This can be explained by the fact that a lower travel speed allows for adequate heating time and homogenous distribution of nanoparticles in the surface composite matrix.

•
The results revealed that there is consistency between the dynamic and static engineering Young's moduli.