Similarity Analysis between Scale Model and Prototype of Large Vibrating Screen

Abstract

In order to predict the physical characteristics of the large vibrating screen from its scale-down model, the similarity ratios of the frequency response functions, mode shapes, and dynamic stresses between the prototype and the scale model screen are built according to the similarity theory. The natural frequencies and modal shapes are extracted from the frequency response function by means of modal tests, in which the relative error of the natural frequencies is less than 9% and the modal shapes are consistent between the prototype and the model. The operating condition parameters including dynamic stress, displacement, velocity, and acceleration were also measured and conform to the similarity criteria. The results show that the inherent and operating condition parameters of the large vibrating screen can be obtained from the scale-down model conveniently, which provides an effective method for structural optimization and substructure coupling analysis of the large vibrating screen.

Academic Editor:Tai Thai

College of Electromechanical Engineering, Qingdao University of Science and Technology, Qingdao 266061, China

Received 6 February 2015; Revised 31 May 2015; Accepted 1 June 2015; 15 June 2015

This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

1. Introduction

Large vibrating screens are widely used for sieving and dewatering in mining, metallurgy, and chemical industry. The screen acceleration, frequency, and amplitude affect the separation efficiency and the fatigue life of the vibrating screen; thus, an optimization design should be done for the vibrating screen [1]. For novel large vibrating screen, making prototype will increase the research costs and the test cannot be performed easily and effectively because of the severe operating conditions [2]. Therefore, according to the principle of similarity using scale-down model is an essential method for structural dynamic analysis and optimal design [3]. Rezaeepazhand and Simitses [4] have established a scale model for predicting the free vibration and buckling of laminated shell. Wu et al. [5] have presented the scaling laws for the prediction of the vibration characteristics of a full size crane structure from those of a scale model by means of the similitude theory. Lin et al. [6] have analyzed the influence of pile modulus similarity ratio and geometry similarity ratio on the piles similarity of deflection behavior between model and prototype piles. De Rosa et al. [7] proposed a similitude for the analysis of the dynamic response of acoustoelastic assemblies. The objective of this paper is to predict the physical characteristics of a full size large linear vibrating screen by means of a scale-down model screen.

2. The Similarity Analysis of Modal Parameters between Scale Model and the Prototype

2.1. The Similarity Derivation of Modal Parameters of the Large Vibrating Screen

According to the similarity theory [8, 9], the prototype and scale model need to meet the following similarity criteria: geometry similarity, stress-strain similarity, mass and the gravity similarity, and the initial conditions and boundary conditions similarity. When only studying the inherent characteristics of the vibrating screen structure, the inertial force and the elastic restoring force need to obey the similitude rules. The gravity has less effect on the natural vibration characteristics; thus, its similar requirements could be ignored [10-12].

The free vibration equation of the prototype of the large vibrating screen is [figure omitted; refer to PDF]

The subscripts [figure omitted; refer to PDF] and [figure omitted; refer to PDF] represent the prototype and the scale model, respectively, and if we define [figure omitted; refer to PDF] , [figure omitted; refer to PDF] , [figure omitted; refer to PDF] , [figure omitted; refer to PDF] , [figure omitted; refer to PDF] , and [figure omitted; refer to PDF] as similarity ratio of mass, density, length, displacement, time, and modulus of elasticity between the vibrating screen prototype and model, respectively, then (1) can be rewritten as [figure omitted; refer to PDF]

Then, the similarity ratio of the natural frequency can be derived: [figure omitted; refer to PDF]

The similarity ratio of the frequency response function can be deduced as follows: [figure omitted; refer to PDF]

The similarity ratio of the mode shape is [figure omitted; refer to PDF]

The scale factor of the mode shape is a constant ratio when the material and size of the vibrating screen have been confirmed. Since the mode shape is the amplitude ratio of each point, if each of the mode shapes of the prototype and model is standardized at the same location, then [figure omitted; refer to PDF]

According to the expression of the frequency response function, [figure omitted; refer to PDF]

When [figure omitted; refer to PDF] , [figure omitted; refer to PDF] Then, we obtained [figure omitted; refer to PDF]

Thus, the similarity ratio of the modal mass can be derived: [figure omitted; refer to PDF] The similarity ratio of the modal stiffness can be deduced as follows: [figure omitted; refer to PDF] According to the viscous damping theory, [figure omitted; refer to PDF] With the similarity theory, (12) can be rewritten as [figure omitted; refer to PDF]

Then, the similarity ratio of the modal damping can be derived: [figure omitted; refer to PDF]

According to the similarity ratios of the modal parameters derived from the above, the similar relations of the modal parameters of the large vibrating screen were calculated and listed in Table 1 when the 1 : 5 similar test model and the prototype both are manufactured using the same material of mild carbon steel.

Table 1: The similarity ratios of the modal parameters of the large vibrating screen.

Ratio of natural frequency [figure omitted; refer to PDF]	Ratio of modal shape [figure omitted; refer to PDF]	Ratio of modal mass [figure omitted; refer to PDF]	Ratio of modal stiffness [figure omitted; refer to PDF]	Ratio of modal damping [figure omitted; refer to PDF]
0.2	1	125	5	25

2.2. The Similarity Experiment of Modal Parameters of the Large Vibrating Screen

The prototype of the 27 m² large linear vibrating screen with width of 3.6 m and length of 7.5 m is shown in Figure 1(a). The single-point excitation and multipoint response method was used to test the modal parameters and the HP5423A structure dynamic analyzer was used to get frequency response function from test data [13]. The scale-down test model screen is shown in Figure 1(b), which used multipoint excitation and single-point response method to test. The structure was excited by impact hammer and the output signal was measured by accelerometer [14, 15].

Figure 1: The prototype and model of the vibrating screen. (a) The prototype of 27 m² linear vibrating screen. (b) The 1 : 5 scale model screen.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

In order to analyze the similarity of frequency response function between the prototype and model screen, the imaginary parts of the frequency response function curve are shown in Figure 2, the frequency of prototype ranging from 0 to 60 Hz and the frequency of model ranging from 0 to 300 Hz accordingly. The frequency response function curves and the natural frequencies of the model are consistent with the prototype according to the similarity ratio of 1/5. Equation (10) shows that the modal mass is inversely proportional to the frequency response function value and the square of the circular frequency, which has been verified by the frequency response function curve shown in Figure 2. For instance, when the natural frequency is 50 Hz of the prototype corresponding to 250 Hz of the model, the value of the imaginary part of the frequency response function is -0.016 m·s^-2 ·N^-1 of the prototype corresponding to -0.08 m·s^-2 ·N^-1 of the model, which is consistent with the similarity ratio.

Figure 2: The imaginary part of the frequency response function curve. (a) The frequency response function of the prototype. (b) The frequency response function of the model.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

According to the natural frequencies extracted from the frequency response function, the mode shapes can be seen clearly in the form of animation by signal processing software, in which the sixth-order mode shapes of the prototype and model screen are shown in Figure 3. In the first ten order modes, the side panel bending deformation is more obviously revealed by the mode shapes. The main reason is that the side panel thickness of the 27 m² vibrating screen is relatively thin, owing to shell structure; thus, the overall stiffness is low and easy for deformation. In order to improve its dynamic characteristics and prolong its fatigue life, the stiffness of the side panel can be increased by adding the number of beams or reasonable decorated stiffener on the side panel. At the same time, the deformation of the beam is larger, indicting the stiffness of the beams is not adapted to the working characteristic of the vibrating screen, which can use rectangular hollow beam to make it conform to the requirement of the vibrating screen.

Figure 3: The sixth mode shape of the prototype compared to the model screen. (a) The bending mode shape of the prototype. (b) The bending mode shape of the model.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

The first seven order natural frequencies, modal masses, and modal stiffness of the 27 m² linear vibrating screen prototype and the model are listed in Table 2. Through comparing the scale-down model and the prototype screen, the maximum relative error is 8.7% of the natural frequencies, the maximum relative error is 8.9% of the modal masses, and the maximum relative error is 9.7% of the stiffness. The reasons for errors are mainly that the scale-down model has a certain degree of simplification compared to the prototype and measurement errors. But according to the similarity theory, the test results of the model and prototype screen are consistent within the engineering permissible errors.

Table 2: The similar relations of the natural frequency, modal mass, and modal stiffness.

Mode number	Natural frequency of the prototype [figure omitted; refer to PDF] /Hz	Natural frequency of the model [figure omitted; refer to PDF] /Hz	Modal mass of the prototype [figure omitted; refer to PDF] (Kg)	Modal mass of the model [figure omitted; refer to PDF] (Kg)	Modal stiffness of the prototype [figure omitted; refer to PDF] (N/m)	Modal stiffness of the model [figure omitted; refer to PDF] (N/m)
1	1.16	5.97	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
2	4.36	23.71	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
3	6.98	30.17	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
4	12.47	60.18	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
5	23.41	112.84	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
6	26.95	130.84	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]
7	29.96	152.07	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]	[figure omitted; refer to PDF]

3. The Similarity Analysis of Operating Condition Parameters between the Scale Model and the Prototype

3.1. The Similarity Derivation of Operating Condition Parameters of the Large Vibrating Screen

In operating condition, the large vibrating screen is excited by harmonic force and its differential equation of motion is [16] [figure omitted; refer to PDF] The similarity ratios are substituted into (15) to obtain [figure omitted; refer to PDF] According to the similarity theory, (16) can be deduced: [figure omitted; refer to PDF]

Equating the exponents of the two sides of (17) gives the following relationships: [figure omitted; refer to PDF] In addition, other similarity ratios can be derived [17]: [figure omitted; refer to PDF]

According to the similarity ratios of the operating condition parameters derived from the above, the similar relations of the operating condition parameters of the large vibrating screen were calculated and listed in Table 3 when the 1 : 5 similar test model and the prototype both are manufactured using the same material of mild carbon steel.

Table 3: The similar relations of the operating condition parameters of large vibrating screen.

Ratio of time [figure omitted; refer to PDF]	Ratio of excited force [figure omitted; refer to PDF]	Ratio of dynamic stress [figure omitted; refer to PDF]	Ratio of displacement [figure omitted; refer to PDF]	Ratio of velocity [figure omitted; refer to PDF]	Ratio of acceleration [figure omitted; refer to PDF]	Ratio of stiffness [figure omitted; refer to PDF]	Ratio of dynamic strain [figure omitted; refer to PDF]
5	25	1	5	1	0.2	5	1

3.2. The Similarity Experiment of Operating Condition Parameters of the Large Vibrating Screen

According to the similar relations of the operating condition parameters of the large vibrating screen shown in Table 3, the excited force for the scale model is 1/25 of the prototype, namely, 9.6 kN; the support stiffness of the spring is 1/5 of the prototype screen, which is 120 N/m. The damping performance of model similar to the prototype is very difficult, which does not produce great influence on the similarity analysis [18-20].

First, the similarity of the dynamic strain in operating condition was tested, using resistance strain gauge, 45° strain rosettes, and multichannel experimental apparatus to measure dynamic strain of the beam and side panel. The experimental picture of the dynamic strain test of the model screen is shown in Figure 4. The time history of strain for the midpoint of the 5 # floor beam is shown in Figure 5; Figure 5(a) is for the prototype and Figure 5(b) is for the scale-down model. The maximum of the strains of the prototype screen and the scale model are 21.5 μ[straight epsilon] and 19 μ[straight epsilon] , respectively. The maximum relative error of the dynamic strain is 11.6%. The reasons for error are mainly some details of configuration of the model screen simplified and the size effect, but the time history of strain basically conforms to the similarity criterion between the prototype and the scale model of the vibrating screen.

Figure 4: The strain test photo for the model screen.

[figure omitted; refer to PDF]

Figure 5: The time history of strain for the midpoint of the 5 # floor beam. (a) The time history of strain for the midpoint of the 5 # floor beam of the prototype. (b) The time history of strain for the midpoint of the 5 # floor beam of the scale model.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

The displacement similarity of prototype screen compared with model screen is shown in Figure 6 and Figure 6(a) is the prototype screen displacement curve; Figure 6(b) is the scale-down model screen displacement curve. The amplitude of the prototype screen is 4.19 mm and the amplitude of the model screen is 0.9 mm; the relative error is 7.4% according to the similarity criterion. The reason for error is that the real operating condition for the prototype is severe and unsteady but the displacement of the model is measured under laboratory conditions.

Figure 6: The displacement similarity of the vibrating screen. (a) The displacement of the prototype screen. (b) The displacement of the model screen.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

The velocity similarity of prototype screen compared with model screen is shown in Figure 7 and Figure 7(a) is the prototype screen velocity curve; Figure 7(b) is the scale-down model screen velocity curve. The maximum velocity of the prototype screen is 407.97 mm/s, the maximum velocity of the model screen is 428.53 mm/s, and the relative error is 5.0% according to the similarity criterion. The level of the velocity similarity is high between the prototype and the scale model of the vibrating screen. The velocity of the prototype screen can be predicted precisely by the scale model according to the associated scaling laws.

Figure 7: The velocity similarity of the vibrating screen. (a) The velocity of the prototype screen. (b) The velocity of the model screen.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

The acceleration similarity of prototype screen compared with model screen is shown in Figure 8 and Figure 8(a) is the prototype screen acceleration curve; Figure 8(b) is the scale-down model screen acceleration curve. The maximum acceleration of the prototype screen is 41.6 m/s² , the maximum acceleration of the model screen is 218.76 m/s² , and the relative error is 5.2% according to the similarity criterion. It is apparent that the time histories of accelerations between the prototype and the model are also in good agreement according to the similarity ratio. The acceleration of prototype screen can also be accurately predicted by means of the scale-down model.

Figure 8: The acceleration similarity of the vibrating screen. (a) The acceleration of the prototype screen. (b) The acceleration of the model screen.

(a) [figure omitted; refer to PDF]

(b) [figure omitted; refer to PDF]

4. Conclusions

According to the similarity theory, the equation analysis method was used to analyze the similarity criterions of the modal parameters for the scale-down model and the prototype of the vibrating screen. The modal parameters of the scale-down model and the prototype were tested by the impact hammer method; the experimental results show that the frequency response functions, natural frequencies, and mode shapes conform to the similarity criteria. Experiments prove that a reasonable scale-down model vibrating screen can replace the prototype vibrating screen for modal testing analysis, which can provide a shortcut to structural modification and substructure coupling analysis of the prototype of the large vibrating screen.

The similarity criterions of the operating condition parameters between scale-down model and the prototype were deduced with equation analysis method. The operating condition parameters including the dynamic strains, displacements, velocities, and accelerations were tested. The operating condition parameters of the scale-down model are consistent with the prototype according to the similarity criterions. Therefore, testing scale-down model can replace the prototype of the large vibrating screen for theoretical and experimental modal analysis.

Acknowledgments

This project is supported by the National Hi-Tech Research and Development Program of China (Grant no. 2006AA04Z408-2) and Shandong Provincial Natural Science Foundation of China (Grant no. ZR2014EEM003).

Conflict of Interests

The authors declare that there is no conflict of interests regarding the publication of this paper.

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