Measuring Device Detecting Impact Forces on Impact Rollers

1. Introduction

When transporting bulk materials by belt conveyors, it is often necessary to transfer the transported material from one belt conveyor to another. This workspace, where material grains (carried on the surface of the conveyor belt) are thrown obliquely as they pass in front of the end drum [1] of the conveyor belt onto the conveyor belt of the following conveyor belt, is called the "transfer station", see Figure 1(a), and can be straight or angled (Figure 1(b)). The conveyed material can also be fed onto the working surface of the conveyor belt via a hopper, Figure 1(c).

Material grains of mass m [kg] with sharp edges falling from a height h [m] onto the working surface of the conveyor belt, at the point of the transfer or hopper, damage the conveyor belt due to their impact energy [2,3,4]. Repeated impacts of material grains can severely damage the covering rubber layer as well as the supporting frame of the conveyor belt and lead to its destruction [5,6,7]. One of the possible solutions, which is used in practice to limit the high values of the dynamic effects of falling material grains on the conveyor belt, is the use of so-called "impact rollers" at the filling points (the hopper) and the transfer points of conveyor belts.

In the article [8] K. Hicke et al. describe the acoustic monitoring of the rollers´ condition in industrial conveyor belt installations.

In the article [9] by the author Y. Liu et al. the monitoring of the sound of transport roller bearings is described.

Impact rollers are one of the auxiliary elements used for belt conveyors. In the load-bearing run of the conveyor belt, one (a straight conveyor idler bench) or more (a trough conveyor idler bench) conveyor idlers are used to support the conveyor belt. The specific function of the impact rollers is to provide optimum support for the conveyor belt at loading points and transfer points where the conveyor belt is subjected to significant impact forces.

In the article [10] the failures of a hundred bearings of conveyor belt rollers are analysed. This article specifies the possible causes of damage to the conveyor roller bearings and proposes measures to eliminate them.

The impact roller is generally similar in design to other types of transport rollers. It differs in that it is equipped with a central member, i.e. a reduced-diameter steel casing on which a grooved rubber hoop with the required thickness is fitted. The rubber hoop is usually designed as a set of concentric rings that form a grooved surface on the outer shell of the impact rollers. The grooved rubber hoop offers excellent impact resistance with the ability to absorb the forces induced by the impact of material grains on the working surface of the conveyor belt at the filling and transfer points of the conveyor belt, compared to conventional (steel or plastic) conveyor roller casings.

In the paper [11], a machine-learning method for diagnosing the failures of conveyor belt rollers is presented. The method consists of applying a wavelet transform to the measured vibration signals, extracting features from the processed signals and applying the Gradient Boosting method to classify the state of the idlers.

Impact rollers can be inserted into standard conveyor idlers (Figure 2(a)) or into the suspended carrying idlers (Figure 2(b)) of the conveyor belt. A selected number of impact rollers ( spacing and [m], see Figure 2(c)) is designed so that these rollers absorb as much of the impact force as possible at the transfer points and prevent accelerated wear of the conveyor belt. The spacing of the impact rollers is, at the filling and transfer points of the belt conveyors, smaller than the spacing of the conventional transport rollers mounted in the conveyor belt load-bearing run.

Impact rollers, like conveyor rollers, produce vibrations that become more intense as the circumferential speed of the rotating roller shell increases. Vibrations and the noise [12,13] of the conveyor rollers are an undesirable by-product of the continuous conveyor belt operation.

H. Shiri et al. in the article [14] define that due to the number of idlers to be monitored, the size of the conveyor, and the risk of accident when dealing with rotating elements and moving belts, monitoring of all idlers (i.e., using vibration sensors) is impractical regarding scale and connectivity. Hence, an inspection robot is proposed to capture acoustic signals instead of vibrations commonly used in condition monitoring.

The measurements of jacket’s vibrations of rollers installed on laboratory stand were made in the article [15] by G. Peruń. It also presents the results of the study, which have on aim non–invasive qualification of technical state of rollers in belt conveyor after certain time of exploitation.

In the article [16] F. Alharbi et al. presents a review of acoustic and vibration signal-based fault detection for belt conveyor idlers using ML models. It also discusses major steps in the approaches, such as data collection, signal processing, feature extraction and selection, and ML model construction.

In the article [17], the parameters that represent the technical condition of tension rollers for the purpose of condition monitoring are presented. This article describes a test device for monitoring the vibration and temperature of belt conveyor tension rollers.

Belt conveyors, especially of high lengths, are equipped with a large number of conveyor rollers, which must be monitored to prevent damage, especially to their bearings. Damage to the bearings leads to an increase in the motion resistance of the conveyor belt and also to the possibility of stopping the rotation of the roller casing. When the bearings of the conveyor roller are damaged and the rotation of the roller casing stops, the non-moving surface of the roller casing wears out due to friction in the contact surface of the moving conveyor belt. This can lead to mechanical damage, i.e. a longitudinal cutting of the cover or even the load-bearing layer, of the conveyor belt. It is therefore necessary to monitor the technical condition of the roller bearings, e.g. by machine vision [18], or by using sensors with measuring devices [19].

Visual and acoustic methods are commonly used to identify faulty or defective guide bearings is shown in [20]. The article describes the use of an accelerometer that moves with the belt and at the same time monitors the condition of all bearings.

The article [21] presents the detection of damage to rollers based on the transverse vibration signal measured on the conveyor belt. A solution was proposed for a wireless measuring device that moves with the conveyor belt along of the route, which records the signal of transverse vibrations of the belt.

2. Materials and Methods

2.1. Laboratory device detecting the forces of grains impacting on the impact roller

The laboratory apparatus, see Figure 3, was designed for a practical verification of the theoretical assumption that the vibrations transmitted to the conveyor belt load bearing run, as well as the dynamic effects of falling material grains from a height of h [m] on the working surface of the conveyor belt at the point of transfer, will be of a lower magnitude when using plastic brackets placed in the trestles of the fixed conveyor idler into which the flattened end parts of the axle of the impact roller are fitted.

The laboratory equipment consists of a frame 1, made of aluminium profiles with a cross dimension of 30x30 mm, with a manufacturing designation MI 30x30 B8 [22]. The fixed conveyor idler bench 2 of the conventional or special design was mounted on two strain gauge force transducers AST-250 kg 4 [23], which are attached to the lower part of the aluminium frame 1. A weight 6 is lowered by free fall from a height H [m] onto the impact roller 3, which is guided onto the impact roller by a rod 5 with a circular cross-section.

The end flattened parts of the axis of the impact roller 1 are inserted into the trestles notches of the fixed conveyor idler 2, see Figure 4(a), with a traditional design. In the case of a special fixed conveyor idler, plastic brackets 4 are inserted into the structurally modified trestles 3 into which the end parts of the impact roller axle 1 are inserted, see Figure 4(b).

The aim of the experimental measurements carried out on the laboratory equipment (see Figure 3) was to verify whether the plastic brackets, mounted in the structurally modified trestles of the fixed conveyor idler (see Figure 4(b)) can limit the magnitude of the dynamic force exerted by the impact of two bodies (the weight and the rubberized shell of the impact roller) transmitted to the conveyor belt load bearing run. The dynamic force is generated by an incident weight 6 f mass m_z [kg] from height H [m] on the rubber coating of the casing of the impact roller 3.

A verification of the damping assumption was carried out by laboratory tests as follows: weights 1 with the mass m_z [kg] were freely dropped from a known height H [m] onto the rubberised casing of the impact roller 2, see Figure 5. At the moment of the impact of the weight, moving with velocity v_z = (2·g·H)^1/2 [m·s^-1], on the rubber surface of the impact roller, the potential energy of the weight was transferred through the end parts of the axis of the impact roller to the fixed conveyor idler 3. The dynamic forces acting in the end parts of the fixed conveyor idler (as the response to the impact of the falling weight at v_z [m·s^-1] on the surface of the impacting roller) were detected by strain gauge force transducers 4. Excited signals in the “mV“ of deformed strain gauges of strain gauge force transducers 4 were recorded by the strain gauge DS NET 5 [24] and graphically displayed on the PC monitor 6 (ASUS K72JR-TY131) in the DEWESoft X2 SP5 software environment.

2.2. Laboratory device for detecting the vibration of a rotating impact roller

On the laboratory device, see Figure 6, the vibrations (in three planes perpendicular to each other) of a rotating rubberized impact roller casing mounted in a conventional (Figure 4(a)) or special (Figure 4(b)) trestle conveyor idler were tested.

The laboratory device designed to measure the vibration of the rotating casing of an impact roller, see Figure 6, consists of a welded steel frame 1, to which a fixed conveyor idler is attached by screw connections 2. A split V-belt pulley 4 is clamped against the outer surface of the rubberised casing of the impact roller 3. The V-belt 5 (type SPZ 2500 Lw 9.7x2513 La L=L), guided through the groove of the drive pulley mounted on the shaft of the electric motor 6, spins the impact roller 3 to reach the desired speed of n_r [s^-1]. Speed n_e [s^-1] of the electromotor 6 is controlled by a frequency converter (type YASKAWA VS-606 V7) [25]. Applying the necessary pressure to the V-belt 5 to the driven and driving V-belt pulley is done using a tensioning device 7.

The objective was to achieve rotation at the desired circumferential velocity v_r [m·s^-1] of the impact roller during the experimental measurements of the vibration of the rotating shell of the impact roller on a laboratory device (Figure 6), and it was carried out in the Laboratory of Research and Testing, Department of Machine and Industrial Design, Faculty of Mechanical Engineering, VSB-Technical University of Ostrava. Due to the inaccuracy of the outer dimension of the rubber coating, it was not possible to mount a pulley on the impact roller similarly to the use of conveyor rollers with a steel or plastic casing [26,27]. For impact rollers of 108 mm and 89 mm diameter, pulleys for V-belts with an outer diameter of 174 mm and 154 mm and a width of 16 mm were purchased from Pikron s.r.o. [28]. These pulleys were cut into two equal parts 1, see Figure 7(a). Four holes with a diameter of 4.2 mm were drilled in the face of each part of the cut pulley. Using bolted connections 2, brackets 3 were attached to the front faces of parts 1, see Figure 7(b).

The spinning of the impact rollers, fixed in the fixed conveyor idler of the laboratory device (Figure 6), was done by mounting both parts of the pulley 1 (see Figure 7) on the outer diameter of the rubber coating of the impact roller. Both parts of the pulley 1 were mechanically connected using bolted connections 4.

For a 154 mm (174 mm) outer diameter pulley mounted on an 89 mm (108 mm) diameter impact roller, the calculated diameter is D_w = 150 mm (170 mm).

The vibrations of the impact rollers with outer diameters Dr = 89 mm, 108 mm and 133 mm were measured on the laboratory device (Figure 6) at the circumferential speeds of the impact roller casings v_r = 3.15, 2.5 and 1.25 m·s^-1.

Due to the different calculated diameters of the pulleys D_w [m], it was necessary to correct the speed n_r [s^-1] of the impact roller casings by changing the speed of the driving electric motor n_e [s^-1] using a Yaskawa VS-606 V7 frequency converter [25]. The torque is transferred from the drive pulley of the calculated diameter d_w = 85 mm (which is mounted on the shaft of the drive electric motor) to the driven pulley of the calculated diameter D_w [m], which is mounted on the impact roller casing, using a V-belt.

According to relation (1), it is possible to determine the theoretical magnitude of the frequency f_i [Hz], see Table 1, which is set on the frequency converter at the moment when the impact roller casing is rotating at the circumferential velocity v_r [m·s^-1], assuming that i_w = D_w/d_w [m].

(1)

Table 1. Frequency f_i [Hz] set on the frequency converter for the required circumferential velocity of the impact roller v_r [m·s^-1].

Dr [mm]	89			108
vr [m·s-1]	fi [Hz]	nr [s-1]	nr [min-1]	fi [Hz]	nr [s-1]	nr [min-1]
3.15	41.28	11.27	675.96	38.55	9.28	557.04
2.50	32.76	8.94	536.48	30.59	7.37	442.10
1.25	16.38	4.47	268.24	15.30	3.68	221.05

Table 1. Frequency f_i [Hz] set on the frequency converter for the required circumferential velocity of the impact roller v_r [m·s^-1].

Dr [mm]	89			108
vr [m·s-1]	fi [Hz]	nr [s-1]	nr [min-1]	fi [Hz]	nr [s-1]	nr [min-1]
3.15	41.28	11.27	675.96	38.55	9.28	557.04
2.50	32.76	8.94	536.48	30.59	7.37	442.10
1.25	16.38	4.47	268.24	15.30	3.68	221.05

The rotational speed n_r [s^-1] of the impact roller with a casing moving at a circumferential velocity v_r [m·s^-1] was determined according to relation (2).

(2)

This section may be divided by subheadings. It should provide a concise and precise description of the experimental results, their interpretation, as well as the experimental conclusions that can be drawn.

The aim of the experimental measurements carried out on the laboratory equipment (see Figure 6) was to verify whether the plastic brackets, fixed in the structurally modified trestles of the fixed conveyor idler (see Figure 4(b)) are able to limit the magnitude of the vibrations excited by the rotation of the rubberized casing of the impact roller by the speed of n_r [s^-1].

Verification of the vibration magnitude limitation assumption was carried out by laboratory tests as follows: vibration (in three mutually perpendicular planes) caused by the rubberized impact roller casing 1 rotating at circumferential speed v_r [m·s^-1], see Figure 8, were detected by two acceleration sensors 2 PCE KS903.10 [29]. The speed of the impact roller 1 was taken by an optical laser sensor 3 DS-TACHO-3 [30]. The signals from the acceleration sensor 2 were recorded during the experimental measurements with the Dewesoft SIRIUSi-HS 6xACC, 2xACC+ 4 [31]. The time records of the measured values were transformed by the measuring apparatus into the effective values of the broadband velocity value v_(*) [mm·s^-1] (where * defines the direction of the "x", "y", or "z" axis of the coordinate system) in the range of 10÷1·10⁴ Hz (this frequency range is applied to the ISO 10816-3 standard) [32]). The effective speed values v_(*)RMS(fi) [m·s^-1] periodic waveforms were displayed on a PC monitor using DEWESoft X measurement software.

2.1. Impact rollers

For the impact roller with outer diameter D_r = 108 mm, supplied to the market by DUBA-DP s.r.o., used for experimental measurements on laboratory equipment, a 9.5 mm thick rubber layer is installed on the 89 mm diameter steel casing, see Figure 9(a).

For the 89 mm outer diameter impact roller (Figure 10(a)) a 19 mm thick rubber layer is applied on the 51 mm diameter steel casing.

3. Results

The experimental measurements under identical technical conditions on laboratory equipment were carried out on a fixed conveyor idler of a conventional or special design and for two impact rollers with diameters of 89 mm and 108 mm.

The first laboratory device was used to measure the dynamic forces generated by the impact of a weight hitting the rubberized hoop of the impact roller casing. The second laboratory device was used to measure vibrations in three mutually perpendicular planes of the impact roller rotating casing.

3.1. Measurement of the force in the supports of a conveyor idler for a weight falling on the casing of an impact roller. Placement of the roller axle in the plastic brackets

Measurements of the magnitude of the forces were carried out on laboratory equipment at the points of the mechanical attachment of the supports for the special design conveyor idler fixed roller table to the aluminium frame, with impacting the weight hitting the rubberised hoop of the impact roller, see Figure 11.

Table 2 presents measured force waveforms F_(Dr)j,i [N], generated by the impact of a weight with mass m_z = 1 kg, falling from the height of H = 787 mm on the rubberised casing of the impact roller with the outer diameter of D_r = 89 mm. The two flattened end parts (Figure 9(a)) of the impact roller were mounted in plastic brackets, embedded in the structurally modified trestles of the fixed conveyor idler (Figure 4(b)).

Table 1 shows the calculated arithmetic mean of all i = 5 measured force values F_d(Dr)j [N], including the limit measurement error κ_α,j [N], for the selected risk Student's distribution α = 5% and Student's coefficient t_α,i = 2.78 [33,34].

Figure 12 presents a graphical time record of two measured forces detected by strain gauge force transducers at measuring points A and B of a fixed conveyor idler, on laboratory equipment used to measure impact forces, see Figure 11. Figure 12(a) presents the measured forces F_0(Dr)j,i [N], these forces define the weight of the relative part of the impact roller and the fixed conveyor idler at the moment when the weight is not in contact with the impact roller. Figure 12(b) presents the measured forces F_(Dr)j,i [N]. These forces define the maximum values of the forces that were detected at the moment of the impact of the weight on the rubberised hoop of the impact roller casing.

Table 2 presents measured force waveforms F_(Dr)j,i [N], generated by the impact of a weight with mass m_z = 1 kg, falling from the height of H = 778 mm on the rubberised casing of the impact roller with the outer diameter of D_r = 108 mm.

Table 3. Impact roller with D_r = 108 mm diameter, plastic roller axle bracket.

Dr [mm]	108
F0(Dr)j,i [N]	Measurement point “j”			F(Dr)j,i [N]			Measurement point “j”		F(Dr)j,i - F0(Dr)j,i
	“A“	“B“					“A“	“B“	“A“	“B“
	124.0	127.9					188.4	192.5	64.4	64.6
	123.8	127.9					186.3	192.8	62.5	64.9
	123.5	127.7					174.5	178.8	51.0	51.1
	123.8 1	127.9 1					193.5 2	198.9 2	69.7	71.0
	123.5	127.9					179.6	187.5	56.1	59.6
							Fd(Dr)j [N]		60.7	62.2
							κα,j [N]		10.0	9.6

¹ see Figure 13(a), ² see Figure 13(b).

Table 3. Impact roller with D_r = 108 mm diameter, plastic roller axle bracket.

Dr [mm]	108
F0(Dr)j,i [N]	Measurement point “j”			F(Dr)j,i [N]			Measurement point “j”		F(Dr)j,i - F0(Dr)j,i
	“A“	“B“					“A“	“B“	“A“	“B“
	124.0	127.9					188.4	192.5	64.4	64.6
	123.8	127.9					186.3	192.8	62.5	64.9
	123.5	127.7					174.5	178.8	51.0	51.1
	123.8 1	127.9 1					193.5 2	198.9 2	69.7	71.0
	123.5	127.9					179.6	187.5	56.1	59.6
							Fd(Dr)j [N]		60.7	62.2
							κα,j [N]		10.0	9.6

¹ see Figure 13(a), ² see Figure 13(b).

Figure 13 shows a graphical time record of two measured forces detected by strain gauge force transducers at measuring points A and B of a fixed conveyor idler, on a laboratory device used to measure impact forces, which was fitted with a 108 mm diameter impact roller.

3.2. Measurement of the force in the supports of a fixed conveyor idler of a weight falling on the conveyor roller casing. Placement of the roller axle in the steel trestles.

Table 3 presents the measured force waveforms generated by the impact of a weight of mass m_z = 1 kg from a height of H = 787 mm on the rubber hoop of the impact roller casing with the outer diameter of D_r = 89 mm. Both flattened end parts (Figure 9(a)) of the impact roller were placed in the grooves of the steel trestles on the fixed conveyor idler (Figure 4(b)).

Table 4. Impact roller with D_r = 89 mm diameter, steel roller axle bracket.

Dr [mm]	89
F0(Dr)j,i [N]	Measurement point “j”			F(Dr)j,i [N]			Measurement point “j”		F(Dr)j,i - F0(Dr)j,i
	“A“	“B“					“A“	“B“	“A“	“B“
	114.9	122.5					201.6	219.6	86.7	90.1
	114.8	129.5					200.5	218.4	85.7	88.9
	114.8	129.6					203.2	219.9	88.4	90.3
	115.3 1	130.3 1					201.7 2	218.5 2	86.4	88.2
	117.0	131.4					202.4	218.8	85.4	87.4
							Fd(Dr)j [N]		86.5	89.0
							κα,j [N]		1.4	1.7

¹ see Figure 14(a), ² see Figure 14(b).

Table 4. Impact roller with D_r = 89 mm diameter, steel roller axle bracket.

Dr [mm]	89
F0(Dr)j,i [N]	Measurement point “j”			F(Dr)j,i [N]			Measurement point “j”		F(Dr)j,i - F0(Dr)j,i
	“A“	“B“					“A“	“B“	“A“	“B“
	114.9	122.5					201.6	219.6	86.7	90.1
	114.8	129.5					200.5	218.4	85.7	88.9
	114.8	129.6					203.2	219.9	88.4	90.3
	115.3 1	130.3 1					201.7 2	218.5 2	86.4	88.2
	117.0	131.4					202.4	218.8	85.4	87.4
							Fd(Dr)j [N]		86.5	89.0
							κα,j [N]		1.4	1.7

¹ see Figure 14(a), ² see Figure 14(b).

Figure 14 shows a graphical time record of two measured forces detected by strain gauge force transducers at measuring points A and B of a fixed conveyor idler, on a laboratory device used to measure impact forces, which was fitted with and 89 mm diameter impact roller.

Table 5 presents measured force waveforms F_(Dr)j,i [N], generated by the impact of a weight with mass m_z = 1 kg, falling from the height of H = 778 mm on the rubberised casing of the impact roller with the outer diameter of D_r = 108 mm.

Figure 15 shows a graphical time record of two measured forces detected by strain gauge force transducers at measuring points A and B of a fixed conveyor idler, on a laboratory device used to measure impact forces, which was fitted with a 108 mm diameter impact roller.

3.3. Vibration measurement of the rotating rubberized impact roller casing, steel roller axle bracket.

The experimental measurement of vibration speeds v_(*)RMS(fi) [mm·s^-1] for the rotating impact roller of diameter D_r [mm], was carried out on a laboratory machine, see Figure 16, under the same technical conditions on two types of fixed conveyor idler (basic dimensions correspond to CSN ISO 1537 standard [30]), see Figure 4.

The experimental measurement of vibration speeds v_(*)RMS(fi) [mm·s^-1] was performed on a middle roller (horizontally mounted roller in a fixed conveyor idler), see Figure 4, laboratory device (Figure 6). An impact roller of a given diameter D_r [mm] fitted with a V-belt pulley, see Figure 7, was rotated by an SPZ V-belt type to the speed of n_r [min^-1] (see Table 5). Two acceleration sensors [7] detected the vibration of the rotating impact roller on the trestle (B or D) of the fixed conveyor idler, see Figure 16(b), or on the top surface of the laboratory equipment frame (see point A or C).

Table 6 gives the effective vibration velocity values v_(*)RMS(fi) [mm·s^-1], as read from the DEWESoft X, measuring software, for the measured vibration values of an 89 mm diameter impact roller at measuring points A and B of a fixed roller table with steel trestles (Figure 4(a)) of the laboratory device (Figure 16(a)).

Figure 17 indicates the measured effective vibration velocity values v_(*)RMS(31.5) [mm·s^-1] in the "x", "y" and "z" axes of the selected coordinate system at the circumferential velocity v_r = 2.5 m·s^-1 impact roller with a diameter of 89 mm, placed in the steel trestle of the fixed conveyor idler.

Figure 17. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point A, (b) measuring point B.

Figure 17. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point A, (b) measuring point B.

Table 7. Axle placement of the impact roller with diameter Dr = 89 mm - steel trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
39.82	677	3.15	0.44	0.21	0.10	0.54	0.11	0.62
31.48	535	2.49	0.79 1	0.20 1	0.09 1	0.57 2	0.13 2	0.43 2
15.78	268	1.25	0.15	0.09	0.07	0.17	0.08	0.16

¹ viz Figure 18(a), ² viz Figure 18(b).

Table 7. Axle placement of the impact roller with diameter Dr = 89 mm - steel trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
39.82	677	3.15	0.44	0.21	0.10	0.54	0.11	0.62
31.48	535	2.49	0.79 1	0.20 1	0.09 1	0.57 2	0.13 2	0.43 2
15.78	268	1.25	0.15	0.09	0.07	0.17	0.08	0.16

¹ viz Figure 18(a), ² viz Figure 18(b).

Figure 18. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point C, (b) measuring point D.

Figure 18. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point C, (b) measuring point D.

Table 8. Axle placement of the impact roller with diameter Dr = 108 mm - steel trestle.

fi	nr	vr	Measurement point “A“			Measurement point “B“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.72	559	3.16	0.38	0.32	0.18	0.56	0.20	0.92
29.98	444	2.51	0.33 1	0.30 1	0.15 1	0.41 2	0.16 2	0.85 2
14.96	222	1.25	0.10	0.15	0.08	0.16	0.10	0.36

¹ see Figure 19(a), ² see Figure 19(b).

Table 8. Axle placement of the impact roller with diameter Dr = 108 mm - steel trestle.

fi	nr	vr	Measurement point “A“			Measurement point “B“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.72	559	3.16	0.38	0.32	0.18	0.56	0.20	0.92
29.98	444	2.51	0.33 1	0.30 1	0.15 1	0.41 2	0.16 2	0.85 2
14.96	222	1.25	0.10	0.15	0.08	0.16	0.10	0.36

¹ see Figure 19(a), ² see Figure 19(b).

Figure 19. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ1089 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point A, (b) measuring point B.

Figure 19. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ1089 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point A, (b) measuring point B.

Table 9. Axle placement of the impact roller with diameter Dr = 108 mm - steel trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.73	559	3.16	0.35	0.33	0.13	0.72	0.21	1.06
30.00	444	2.51	0.37	0.30	0.13	0.66	0.17	1.06
14.97	222	1.25	0.12	0.14	0.08	0.20	0.10	0.37

¹ see Figure 20(a), ² see Figure 20(b).

Table 9. Axle placement of the impact roller with diameter Dr = 108 mm - steel trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.73	559	3.16	0.35	0.33	0.13	0.72	0.21	1.06
30.00	444	2.51	0.37	0.30	0.13	0.66	0.17	1.06
14.97	222	1.25	0.12	0.14	0.08	0.20	0.10	0.37

¹ see Figure 20(a), ² see Figure 20(b).

Figure 20. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ108 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point C, (b) measuring point D.

Figure 20. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ108 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, steel brackets, (a) measuring point C, (b) measuring point D.

3.4. Vibration measurement of the rotating rubberized impact roller casing, plastic roller axle bracket.

Table 10 gives the effective vibration velocity values v_(*)RMS(fi) [mm·s^-1], read from the DEWESoft X measuring software, for the measured vibration values of an 89 mm diameter impact roller at measuring points A and B of a fixed conveyor idler of special design (Figure 4(b)) on the laboratory machine (Figure 16(a)).

Figure 21 shows the measured effective vibration velocity values v_(*)RMS(31.5) [mm·s^-1 in the "x", "y" and "z" axes of the selected coordinate system at the circumferential velocity v_r = 2.5 m·s^-1 of an impact roller with a diameter of 89 mm, mounted in the plastic brackets of engineered steel trestles in a fixed conveyor idler.

Figure 21. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point A, (b) measuring point B.

Figure 21. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point A, (b) measuring point B.

Table 11. Axle placement of the impact roller with diameter Dr = 89 mm - plastic trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
39.56	672	3.13	0.32	0.49	0.10	0.44	0.19	1.98
31.36	533	2.48	0.53 1	0.30 1	0.10 1	0.42 2	0.17 2	1.18 2
15.70	267	1.24	0.19	0.14	0.06	0.20	0.10	0.43

¹ see Figure 22(a), ² see Figure 22(b).

Table 11. Axle placement of the impact roller with diameter Dr = 89 mm - plastic trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
39.56	672	3.13	0.32	0.49	0.10	0.44	0.19	1.98
31.36	533	2.48	0.53 1	0.30 1	0.10 1	0.42 2	0.17 2	1.18 2
15.70	267	1.24	0.19	0.14	0.06	0.20	0.10	0.43

¹ see Figure 22(a), ² see Figure 22(b).

Figure 22. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point C, (b) measuring point D.

Figure 22. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ89 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point C, (b) measuring point D.

Table 12. Axle placement of the impact roller with diameter Dr = 108 mm - plastic trestle.

fi	nr	vr	Measurement point “A“			Measurement point “B“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.62	557	3.15	0.73	0.57	0.22	0.71	0.48	1.20
29.84	442	2.50	0.26 1	0.42 1	0.10 1	0.33 2	0.20 2	1.14 2
14.87	220	1.25	0.11	0.18	0.07	0.20	0.10	0.46

¹ see Figure 23(a), ² see Figure 23(b).

Table 12. Axle placement of the impact roller with diameter Dr = 108 mm - plastic trestle.

fi	nr	vr	Measurement point “A“			Measurement point “B“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.62	557	3.15	0.73	0.57	0.22	0.71	0.48	1.20
29.84	442	2.50	0.26 1	0.42 1	0.10 1	0.33 2	0.20 2	1.14 2
14.87	220	1.25	0.11	0.18	0.07	0.20	0.10	0.46

¹ see Figure 23(a), ² see Figure 23(b).

Figure 23. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ8 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point A, (b) measuring point B.

Figure 23. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ8 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point A, (b) measuring point B.

Table 13. Axle placement of the impact roller with diameter Dr = 108 mm - plastic trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.62	557	3.15	0.77	0.43	0.10	0.66	0.65	1.22
29.83	442	2.50	0.24	0.27	0.08	0.34	0.20	1.13
14.86	220	1.24	0.11	0.12	0.05	0.21	0.13	0.46

¹ see Figure 24(a), ² see Figure 24(b).

Table 13. Axle placement of the impact roller with diameter Dr = 108 mm - plastic trestle.

fi	nr	vr	Measurement point “C“			Measurement point “D“
			v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)	v(x)RMS(fi)	v(y)RMS(fi)	v(z)RMS(fi)
[Hz]	[min-1]	[m·s-1]	[mm·s-1]			[mm·s-1]
37.62	557	3.15	0.77	0.43	0.10	0.66	0.65	1.22
29.83	442	2.50	0.24	0.27	0.08	0.34	0.20	1.13
14.86	220	1.24	0.11	0.12	0.05	0.21	0.13	0.46

¹ see Figure 24(a), ² see Figure 24(b).

Figure 24. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ108 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point C, (b) measuring point D.

Figure 24. Effective vibration speed values v_(*)RMS(fi) [mm·s^-1], the impact roller of ϕ108 mm, circumferential speed of the roller v_r = 2.5 m·s^-1, plastic brackets, (a) measuring point C, (b) measuring point D.

4. Discussion

The evaluated measurements of the forces, given in Chapter “3. Results“, generated by the impact of the weight hitting the impact roller with ϕ89 mm diameter show that (for i = 5 repeated measurements under the same technical conditions) the mean value of the measured force F_(Dr)j,i [N] at measuring point A, and also at measuring point B, (see Figure 11(b)) is lower when the axle of the impact roller is placed in the plastic brackets.

Table 2 shows for measuring points A and B, on a fixed conveyor idler with rubber impact roller axle brackets ϕ89 mm, the magnitude of the calculated dynamic force F_(89)A,p = 83.8 ± 1.5 N and F_(89)B,p = 85.5 ± 2.3 N.

According to Table 4, for the measuring points A and B, the dynamic force F_(89)A,s = 86.5 ± 1.4 N and F_(89)B,s = 89.0 ± 1.7 N were calculated for the fixed conveyor idler with steel impact roller axle brackets of ϕ89 mm.

For the ϕ89 mm impact roller, the size of the force F_(89)A,p [N] reaches 98.0% of the force F_(89)A,s [N] and the size of F_(89)B,p [N] force reaches a magnitude of 97.2% of the force F_(89)B,p [N].

At both measuring point C and measuring point D (see Figure 11(b)) the magnitudes of the forces generated by the impact of the weight hitting the impact roller ϕ89 mm are also lower when the axle of the impact roller is mounted in plastic brackets.

By evaluating the measurements of the forces generated by the impact of the weights hitting the impact roller ϕ108 mm, see section “3. Results” (for i = 5 repeated measurements under the same technical conditions) it can be concluded that the mean values of the measured forces F_(Dr)j,i [N] at measuring point A, and at measuring point B, (see Figure 11(b)) are also lower in the case of the placement of the axle of the impact roller placed in the plastic brackets.

Table 4 shows for measuring points A and B, on a fixed conveyor idler with rubber brackets for the axle of the impact roller ϕ89 mm, the magnitude of the calculated dynamic force F_(108)A,p = 60.7 ± 10.0 N a F_(108)B,p = 62.2 ± 9.6 N.

According to Table 5, there are the calculated dynamic forces F_(108)A,s = 72.4 ± 6.5 N and F_(108)B,s = 72.9 ± 4.6 N for measuring points A and B on a fixed conveyor idler with steel brackets for the axle of this impact roller ϕ89.

For the ϕ108 mm impact roller the magnitude of the force F_(108)A,p [N] reaches 83.8% of the force F_(108)A,s [N] and the magnitude of the force F_(108)B,p [N] reaches 85.3% of the force F_(108)B,s [N].

It is advantageous to install plastic holders in engineered steel trestles that are welded to the circular cross-section tube of fixed conveyor idlers, as they can dampen the magnitude of impact forces generated at the transfer points of the conveyor belt. The impact of material grains thrown diagonally over the edge of the drum from the first conveyor belt onto the belt of the second conveyor causes impact forces of high magnitudes. The magnitude of the force impulse depends on the magnitude of the force and the time over which the force was applied. It is known that the impulse of the force is equal to the change in momentum of the body, therefore, if the weight of the falling grain acts for a longer time (a deformation of the rubber brackets to which the ends of the impact roller axle are attached is higher than the deformation of the steel trestles), the impact force has a lower magnitude.

The realised vibration measurements, see Chapter 3.3 and Chapter 3.4 of the rotating rubberised casing (ϕ89 mm and ϕ108 mm) impact roller on laboratory device, see Figure 16, have not demonstrated, as stated in [1,2], that the plastic brackets limit the amount of vibration (excited by the rotating casing of the conveyor roller) transferred by the support beam of a fixed conveyor idler to the steel frame of a laboratory device that simulates the conveyor belt run.

Similarly as in [1] higher effective vibration velocity values in each of the "x", "y" and "z" coordinate axes were measured on the laboratory equipment for higher impact roller casing speeds, see Table 6 to Table 13.

The measured effective vibration velocity values in the vertical direction (z-axis of the coordinate system) at measuring points B and D (see Figure 25) are higher if the axle of the impact roller ϕ89 mm and the impact roller ϕ108 mm are placed in plastic brackets.

It can be seen from Table 6 and Table 10 that the vibration v_{(z)RMS(31.38)} = 1.26 mm·s^-1 (Figure 25) in the case of mounting the impact roller axle in plastic brackets (Figure 4(b)) is 2.8 times (by 280%) higher at measuring point B than the vibration v_{(z)RMS(31.55)} = 0.45 mm·s^-1 corresponding to mounting the impact roller axle at measuring point B in a steel bracket (Figure 4(a)).

From Table 7 and Table 11, it can be expressed that the vibration v_{(z)RMS(31.36)} = 1.18 mm·s^-1 (Figure 25) in the case of mounting the axle of the impact roller in plastic brackets (Figure 4(b)) is 2.7 times (by 274%) higher at measuring point D than the vibration v_{(z)RMS(31.48)} = 0.43 mm·s^-1 corresponding to mounting the axle of the impact roller at measuring point D in a steel bracket (Figure 4(a)).

Figure 25. Effective vibration velocity values for the impact roller ϕ89mm (a) steel trestle, (b) plastic trestle.

Figure 25. Effective vibration velocity values for the impact roller ϕ89mm (a) steel trestle, (b) plastic trestle.

From Table 8 and Table 12, it can be expressed that the vibration v_{(z)RMS(29.84)} = 1.14 mm·s^-1 (Figure 26) in the case of mounting the axle of the impact roller ϕ108 mm in plastic brackets (Figure 4(b)) is 1.3 times (by 134%) higher than the vibration at measurement point B v_{(z)RMS(29.98)} = 0.85 mm·s^-1 for the corresponding location of the axle of the impact roller at measuring point B in the steel bracket (Figure 4(a)).

Table 9 and Table 13 prove that the vibrations v_{(z)RMS(29.83)} = 1.13 mm·s^-1 (Figure 26) in the case of the axle of the impact roller ϕ108 mm placed in the plastic brackets (Figure 4(b)) is 1.1 times (by 107%) higher at measuring point D than the vibrations v_{(z)RMS(30.00)} = 1.06 mm·s^-1 for the corresponding location of the axle of the impact roller at measuring point D in the steel bracket (Figure 4(a)).

Figure 26. Effective vibration velocity values for the impact roller ϕ89mm (a) steel trestle, (b) plastic trestle.

Figure 26. Effective vibration velocity values for the impact roller ϕ89mm (a) steel trestle, (b) plastic trestle.

The different results of the calculated effective vibration values (in the "z" axis of the coordinate system) of the impact rollers, with outer diameters of rubber hoops D_r [m] for circumferential velocities v = 1.25÷3.15 m·s^-1, from conveyor rollers of identical diameters with plastic or steel casings [2] can be expressed by the fact that the rubber hoops applied on a steel casing are not of an identical outer diameter. The difference in the outer diameters of the partial rubber hoops (6 pcs for the impact roller ϕ89 mm, 16 pcs for the impact roller ϕ108 mm) can already be seen visually. For experimental vibration measurements of the impact rollers on laboratory equipment (Figure 16), it was not possible to use "pulley assemblies" [2], which have been used in the experimental vibration measurements of the conveyor rollers with plastic or steel casings. The impossibility of sliding the "pulley assembly" to the required distance on the outer diameter of the rubberized hoops on the side of the impact rollers led to the necessity of designing split pulleys, see Figure 7.

5. Conclusions

The current trend of the digitization of industry called Industry 4.0, which aims to automate and digitize production processes, uses methods and tools to save time, and money and adapt to the situation and operations of companies. The process of automation brings with it the introduction of new technologies, equipping machines with chips and sensors and controlling computers to remotely monitor and control production processes. Through IoT technologies, data from various sensors and gauges can be collected and shared for further use.

The plastic brackets embedded in the designed roller axle brackets can dampen vibrations transmitted to the conveyor belt structure. It is preferable to use these special fixed conveyor idlers along the length of the conveyor belt run, and less suitable to use them at transfer points and hoppers.

The individual rubber hoops of unequal outer diameters cause oscillations and vibrations due to the unbalanced mass during the rotation of the impact rollers. The vibrations are more intense at higher impact roller speeds, as the centrifugal force of the rotating unbalanced mass is known to be proportional to the square of the angular velocity.

Experimental measurements carried out on both laboratory devices showed that the implemented plastic brackets for the axle of the conveyor rollers in the structurally modified steel trestles of the fixed conveyor idler have the ability to dampen the vibrations excited by the rotating casing of the conveyor roller. The plastic brackets fitted into the trestles of the fixed conveyor idler also allow to absorb of a part of the impact force of the falling material grains at the transfer points or on the hoppers of the conveyor belts.