In order to gain a consistent aggregate quality, quantity and uniformity and achieve a balanced circuit, employees should operate cone crusher at a consistent closed side discharge setting. It will result in less production and more over-sized aggregate, if the crusher is operated at a wider-than-optimum setting, even if done only temporarily. In addition, over-sized product almost always causes issues in the circuit flow.
An example regarding the effect that crusher setting has on the product gradation is as follows, if the target crusher setting is 3/8 in. (10mm) yet the setting is not checked and it wears open to 1/2 in. (13mm), then the end result is a 15 percent decrease in the minus 3/8-in. (10mm) material size. There is a significant decrease in cone crusher productivity. If crushers are not being operated at consistent close side settings, many aggregate producers lose some of their revenue and the size of the amount could really surprise them. Therefore, it is good to check the crushers setting on a per shift basis.
The product will have an inconsistent shape and the production rate will be inconsistent, if the crusher is being operated at different cavity levels during the shift. When operating at a low cavity level, also known as half cavity, the product gradation will be much coarser. This level makes the product particles flatter and more elongated. A proper choke-fed cavity level should be pursued as it will increase crusher throughput tonnage and result in a more cubical product especially with tertiary (short head) crushers that make the most of the producers salable products.
Try not to trickle feed a cone crusher. In addition to causing poor cone crusher productivity and product shape, trickle feeding has an impact on bearing alignment within said crusher. A crusher should be operated above 40% but below 100% rated horsepower in order to maximize cone crusher productivity and to have a proper loaded bearing alignment. An optimal power range is to operate between 75%-95%. Operating a crusher above 110% rated power can cause premature crusher failure.
Try to direct the incoming feed material so that it is distributed vertically into the center of the crusher. This will ensure that all sides of the crushing cavity remain evenly filled. If the feed is directed somewhere else other than the center, it will cause over-sized product, more flat and elongated product particles and a low crusher throughput tonnage.
In this situation, the operator will typically tighten the crusher setting in an attempt to produce a smaller product size, which can cause an over-load in the form of adjustment ring movement on the side that is heavily loaded. Over time, in this condition the adjustment ring can become tilted on the main frame and it can cause a bigger loss in productivity. With correct feed distribution, maximum crusher capacity, more consistent product uniformity, significant reduction of the adjustment ring action, minimum pressure on the bearings, reduction in energy consumption and even wear of the liner can be reached.
The feed material entering the crushing cavity should not be segregated but should be well mixed and homogenous. The feed can become segregated when bigger stones are directed to one side and smaller ones to the opposite side of the crushing cavity. In this case, the smaller stones will have a higher bulk density which can cause a condition called packing or pancaking.
Packing makes the adjustment ring move on the side of the crusher where smaller stones are, and this movement forces the operator to open the crusher setting. Opening the crusher setting eliminates the over-load condition but it will cause oversized product because of the setting increase. Also, if the feed becomes segregated and if the adjustment ring is jumping or bumping, the ring can become tilted which leads to even a larger loss in cone crushers productivity.
Surge loading has a bad effect on the production of any crusher. Surge piles or feed hoppers along with variable speed feeding devices can be used to provide a better and more consistent feed control to the crusher. This makes it possible for the operator to run the crusher at a very consistent and stable cavity level. Cone crusher productivity can be easily increased by a minimum of 10 % by having better feed control. It can be achieved by using surge piles, hoppers and variable speed feeding devices such as belt conveyors or vibrating pan feeders.
Regarding the volume limit, each crushing cavity has a volumetric limit that determines maximum throughput and a choke-fed crusher is operating at its volumetric limit. The volume limit is exceeded when feed material overflows the top of the crusher.
As for the horsepower limit, each crusher has been designed to operate at a maximum power draw, and power draw will increase as the feed rate increases and as the feed material is crushed finer. The horsepower limit has been exceeded when the crusher draws more power than it is rated for.
Lastly, we must not forget about the crushing force limit of the crusher and as with the horsepower limit, crushing forces being applied between the mantle and bowl liner increase as the feed rate increases and as the feed material is crushed finer. The crushing force limit of the crusher has been crossed when the adjustment ring jumps, bumps, bounces, wiggles or moves on top of the main frame.
An ideal operational condition would exist when the crusher is operating at its volumetric limit while still being slightly below both the horsepower limit and crushing force limit. Operating any crusher outside of its designed parameters with either excessive power draw or with excessive crushing force results in a very serious crusher over-load. These over-loads create something known as fatigue damage which is permanent, irreversible and cumulative. Without a doubt, frequent over-loads will shorten the life cycle of any cone crusher.
If you find the crusher operating in a crushing force over-load condition (ring movement) or a power over-load condition (excessive power), open the crusher setting slightly, but try to stay choke fed. The benefit of staying choke fed is that there will still be rock-on-rock crushing and grinding taking place in the crushing cavity. This helps to maintain good cubical product shape even though the setting is slightly larger than optimum.
The other option of course would be to decrease the feed rate to the crusher. The disadvantage of this option is that product shape would typically suffer. Most common reasons for adjustment ring movement or excessive power draw are tramp events, poor feed distribution, segregation of the feed, too many fines in the feed, high moisture content, wrong mantle and bowl liner being used. It is also possible that the operator is simply trying to operate at an unrealistically small closed side setting.
The crusher will slow down and the belts will slip when proper drive belt tension is not maintained. This will cause unbelievably high power peaks at a very low crusher throughput tonnage. Improper or neglected drive maintenance will result in a high-horsepower consumption at a low crusher throughput tonnage. This inefficient use of connected horsepower will cause a higher than normal energy cost per ton of material crushed.
A speed sensor can be used to monitor the crusher countershaft speed and will send a warning signal of a slowing crusher to the PLC or it could be wired to simply turn on a warning lamp. When a warning is detected, the maintenance department can be dispatched to re-tighten the drive belts. When a speed sensor is used, drive belt life is extended, and proper production levels can be maintained.
"Fines in the crusher feed" is defined as material entering the top of the crusher which is already equal to or smaller than the crusher's closed-side discharge setting. As a rule of thumb, the maximum number of fines in the crusher feed should not exceed 25 percent for secondary crushers or 10 percent for tertiary crushers. When there is an excessive quantity of fines in the feed, it is typically the result of a vibrating screen problem. This problem could be because the screen is insufficient in size or a screen which is properly sized but is inefficient in operation.
Re-crushing and re-handling product size material due to vibrating screen, inefficiencies due to the way the screen is originally set up or due to improper vibrating screen maintenance will lead to an excessive quantity of fines in the crusher feed. This in-turn will lead to inefficient use of connected crusher horsepower and a higher energy cost per ton of material crushed.
Three feet, or one meter, is the maximum distance from which the feed material should fall from into the top of a small to mid-size cone crusher. When the feed material drops from a much greater distance than it should, the stones tend to slam into the V shaped crushing cavity with such velocity that it subjects the crusher to shock loads and extremely high stress levels. This situation is called high-velocity wedging. High-velocity wedging can result in power over-loads or force over-loads, or both. This action puts undue stress and strain on the crusher components and results in increased maintenance repair costs and poor crusher productivity.
Also, controlling the speed of the material that reaches the crusher is very important. When the material falls from a high height, some material can pass through the open side of the crushing chamber and others only crush in the end of the chamber, reducing the efficiency and causing adjustment ring movement, resulting in severe damages in the bronze liner on the main frame seating surface and the main frame pin bushings. Additionally, it can result in premature damage of the tramp release cylinders. In order to avoid those problems, the feeding material speed should be reduced, with steps in the chutes or stone box, reducing the fall height.
A vibrating screen positioned before the crusher is used to remove the fines or sticky material from the feed stream before it reaches the crushing chamber. This will help to avoid the packing or pancaking of the feed material within the crushing chamber, which also causes the jumping or bumping of the adjustment ring and inefficient operation. Keep in mind that the vibratingscreen needs to be sufficient in size and efficient in operation for it to work successfully.
Fengbiao Wu, Lifeng Ma, Guanghui Zhao, Zhijian Wang, "Chamber Optimization for Comprehensive Improvement of Cone Crusher Productivity and Product Quality", Mathematical Problems in Engineering, vol. 2021, Article ID 5516813, 13 pages, 2021. https://doi.org/10.1155/2021/5516813
This study aims to analyze the impact of key structural parameters such as the bottom angle of the mantle, the length of the parallel zone, and the eccentric angle on the productivity and product quality of the cone crusher and optimize the crushing chamber to improve the crusher performance. The amount of ore in the blockage layer was calculated by analyzing the movement state of the ore in the crushing chamber. Considering the amount of ore uplift further, the traditional mathematical model of crusher productivity was revised. Then, a mathematical model for dual-objective optimization of productivity and product quality of cone crusher was established. Furthermore, taking the existing C900 cone crusher as the research object, the influence of key parameters on the performance of the crusher was researched. And the optimal values of key structural parameters were obtained. Finally, based on the iron ore coarsely crushed by the gyratory crusher, the dynamic characteristics of the C900 cone crusher were simulated by using the discrete element method (DEM), and the simulation results are basically consistent with the numerical analysis results. Results show that considering the amount of ore uplift in the blockage layer, the revised mathematical model of crusher productivity can better characterize the actual productivity. The bottom angle of the mantle and the length of the parallel zone are within the range of 5060and 140mm190mm, respectively. The productivity shows a positive correlation with the bottom angle and a negative correlation with the length of the parallel zone. But the dependence of product quality on the angle and the length is just the opposite. The eccentric angle is within the range of 1.42 and its decrease has a negative effect on the productivity and product quality.
As one of the key equipment in the bulk materials crushing system, the cone crusher is mainly used for the medium and fine crushing of bulk materials. With the continuous promotion of breaking instead of grinding, the application of cone crusher is more extensive. The crushing chamber is the key factor that determines the performance of the cone crusher. At present, Bengtsson, Grndah, Lee et al. , Zhang et al. , Huang et al. , Khalid et al. , Bengtsson et al. , and Franks et al.  have studied the interparticle breakage behavior of bulk materials through the ore mechanics test system and established a productivity model, and the influence of the engagement angle, different close side settings (CSS), the mantle shaft speed, and particle shape of the cone crusher on the performance of the crusher is studied. However, the productivity model does not consider the effect of ore uplift in the blockage layer, and the bottom angle of the mantle, the length of the parallel zone, and the eccentric angle have a great influence on the chamber structure, and the chamber structure is related to the number of broken ores. Therefore, it is necessary to further study the influence of these parameters on the crushing performance. In addition, the DEM has been proved to be a very good virtual simulation environment by Cleary, Delaney et al. [11, 12], Quist et al. , and Chen et al. . The virtual simulation environment can be used to gain a fundamental understanding regarding internal processes and operational responses. A virtual crushing platform can not only be used for understanding but also for the development of new crushers and for optimization purposes.
Therefore, the working process of the cone crusher is taken as the specific analysis object, and considering the amount of ore uplift, the traditional mathematical model of crusher productivity was revised. Then, a mathematical model for dual-objective optimization of productivity and product particle size distribution of cone crusher was established. Furthermore, the influence of the bottom angle of the mantle, the length of the parallel zone, and the eccentric angle on cone crusher performances is analyzed by the optimal numerical calculation method. Finally, the reliability of the optimization model and optimization algorithm of cone crusher is verified by the DEM based on the characteristics of coarse crushing ores.
The crushing chamber is composed of the mantle and concave, as shown in Figures 1(a) and 1(b). The drive turns the horizontal countershaft. The pinion gear on the countershaft rotates the eccentric gear. The eccentric bushing rotation causes the mantle to wobble. The functional principle of a cone crusher is to compress particles between two surfaces. The compressive action is realised by inflicting a nutational motion on the mantle while the concave remains fixed. The ore is squeezed and crushed several times along the crushing chamber from the feeding port to the discharging port, especially in the parallel section, which does the final crushing. Larger ore needs longer time between squeezes.
The crushing of ore is directly related to the compression ratio, and the bottom angle and eccentric angle determine the compression stroke of the mantle. The length of the parallel zone determines the number of ore fractures. Therefore, the productivity and particle quality of the cone crusher are affected by these structural parameters of the crushing chamber.
Productivity refers to the amount of ore processed by the crusher per unit time under the conditions of certain feed size and discharge size, which is a key indicator reflecting the performance of the crusher. The calculation results of the existing cone crusher productivity are compared with the actual production results. The calculation results are always greater than the actual production results. After analysis, because the crusher has a blockage layer in actual work, the mantle far away from the concave will fall. The ore on the side of the mantle close to the concave will arch up and cannot be discharged from the discharge port. Therefore, it is necessary to theoretically derive the amount of ore in the blockage layer and revise the existing theoretical calculation model of cone crusher productivity.
The existing theoretical calculation model of productivity is calculated based on the volume of the ore discharged from the crushing chamber once the mantle swings , as shown in Figure 2. The following equation represents the mathematical model:where is the volume of the ore discharged from the crushing chamber once the mantle swings, is the thickness of the ore layer when the ore is compressed, is the ore displacement when the mantle swings, and is the average diameter of the ore compression layer, considered to be approximately equal to the bottom diameter of the mantle .
Considering the ore hardness and feed size, the following equation represents the productivity per minute:where is productivity, is ore bulk density, is the mantle swing times per minute, is loose factor, , is ore hardness coefficient (hard ore: ; medium hard or soft ore: ), is feed size factor, and is feed opening width, as shown in Table 1.
As shown in Figure 3, the crushing chamber formed by the mantle and the concave is divided into four areas, and the mantle rotates counterclockwise. When the mantle closes to the concave and extrudes the ore, the ore in the A and D areas will arch upward. That is, when the mantle is close to the concave, the ore cannot be discharged naturally and upward movement occurs.
At this time, the ore speed is consistent with the moving speed of the mantle, and the ore throughput is obtained by double-integrating the ore velocity and area in the A and D areas. In Figure 3, plane is the cross section of the blockage layer, is the center of the concave section, and is the center of the mantle section.
Therefore, the ore quantity in this area is calculated, and then the traditional productivity theory is used to subtract the ore quantity in this part, so a more accurate calculation method of productivity can be obtained. Ore velocity in the upper arch area is shown as follows:where is 1/2 cycle, (the rotating speed of the mantle is ) and is the moving distance of the mantle. Take a microelement for the upper arch area of the blockage layer, and the integral function of the upper arch zone can be expressed as follows:where is the angle enclosed by the upper arch boundary and the coordinate axis, is the distance from the center of the concave to the boundary of the mantle, is the radius of the concave, and is the speed of the ore in the upper arch area.
The good performance of the cone crusher is mainly reflected in the high productivity and neat particle size distribution of crushed products. There is a strong coupling relationship between productivity optimization and product quality optimization models. Based on the principle of interparticle breakage, the kinematic characteristics of bulk materials, and the population balance modeling (PBM), a dual-objective programming model of the cone crusher is established.
In the case of ensuring the particle size of the crushed product, the productivity of the crusher should be improved as much as possible. Taking productivity as the first objective function of optimizing crusher chamber, the objective function as shown in the following equation is obtained according to equation (5):
The mass proportion of the bulk materials whose diameter is smaller than the CSS is the main technical index to measure the particle size distribution of the crushed product. Therefore, the following equation is used as the second objective function for optimizing the chamber shape of the crusher:
Equation (7) is based on the model proposed and perfected by Broadbent et al.  and Lynch  in the study of coal crushing process. After the continuous improvement of most scholars, equation (8) of the product particle size distribution model of the material is gradually summarized:where is selection function, is crushing function, is the number of crushing times the material has been subjected to, , is the unit matrix of feeding granularity.
For the selection function and crushing function mentioned in the above equation, Professor Evertsson of Chalmers University of Technology in Sweden [20, 21] has obtained the relevant mathematical model by simulating lamination crushing through experiments, as shown in the following equations:where is the compression height of the bulk materials before lamination and crushing, is the amount of feed compression, is the particle size of the Nth layer of the lamination and crushing materials, is the smallest particle size in the product, is the largest particle size in the feed, and is the equivalent particle size of the Nth layer of laminated crushed materials.
The chamber structure parameters of the cone crusher are the key parameters that affect the performance of the crusher. The bottom angle of the mantle , the length of the parallel zone , the eccentric angle , and the rotating speed are determined as the design variables of the dual-objective programming model, as shown in the following equation:
The value range of the crushing optimization constraints was set by referring to the parameters of the C900 cone crusher. The parameters of C900 are shown in Table 2 where is open side size, is eccentricity, and is engagement angle.(1)According to the calculation of the critical speed and the actual parameters r/min, speed was defined as .(2)According to the suspension height of the cone crusher, the eccentric angle was defined as . The swing stroke and eccentricity of the mantle are affected by the eccentric angle.(3)According to the original parameters and actual design experience, the value range of the bottom angle of the mantle was defined as .(4)The product quality can be effectively improved by increasing the length of the parallel zone, and the length of the parallel zone was defined as .
The objective function was determined by studying the performance of the cone crusher. The design variables were determined by analyzing the structure parameters and process parameters of the cone crusher. The constraint conditions were set by combining the parameters of the cone crusher C900. Comprehensive analysis of the objective optimization problem of the cone crusher was performed using the main objective method, taking productivity as the main objective of crusher optimization and transforming the product quality optimization into nonlinear constraints. According to equations (6), (7), (12), and (13), the dual-objective programming model of cone crusher is established, and the forms are shown in the following equations:
The dual-objective programming model of the cone crusher is solved by using K-T  nonlinear sequential quadratic programming method, and the optimization results are shown in Table 3. Figures 46 show the effects of changing the bottom angle of the mantle , the length of the parallel zone , and the eccentric angle on productivity and particle size distribution of crushed products.
As shown in Figures 4(a) and 4(b), crusher productivity is increased from 1008t/h to 1238t/h at the rate of 23%, as the bottom angle of the mantle increases from 50 to 60. However, the particle size and quality of crushed products decrease, which is less than the closed side setting of broken product percentage from 85% to 78%. This is due to the decrease of the effective crushing times in the crushing chamber when the bottom angle of the mantle increases.
As shown in Figures 5(a) and 5(b), crusher productivity is decreased from 998t/h to 850t/h at the rate of 15%,, as the length of the parallel zone increases from 140mm to 190mm. However, the particle size and quality of crushed products increase, which is less than the closed side setting of broken product percentage which increases by about 9.6%. This is because as the parallel zone increases, ores were more fully broken, but the broken time results in a decline in productivity growth.
As shown in Figures 6(a) and 6(b), crusher productivity and the particle size and quality are increased, as the eccentric angle increases from 1.4 to 2. This is because the eccentricity of the crusher and swing stroke of the mantle increase with the increase of eccentric angle.
The above research shows that the influence of the structure parameters of the crusher on the productivity and product quality is mutually restricted, and there is a strong coupling relationship. Therefore, both productivity optimization and product quality optimization are taken into account, the optimal performance parameters of the crusher C900 were obtained, the mantle bottom angle is in the range of 50 to 60, the length of the parallel zone is in the range of 140mm190mm, and the eccentric angle is in the range of 1.42. The optimal structural parameters of the C900 crusher chamber was obtained: the swing speed of the mantle, the length of the parallel zone, the bottom angle of the mantle, the eccentric angle, the eccentricity, and the engagement angle are 285r/min, 150mm, 55, 2, 44.8mm, and 23, respectively.
The DEM provides a bonding and energy accumulation crushing model, which can accurately describe the crushing process of ores under the action of equipment. Hasankhoei et al.  and Cleary et al.  have proved to be a powerful tool for studying the flow of bulk materials and ore crushing behavior. In this paper, based on the coarse broken iron ores in the rotary crusher, the ore particle model was established by using DEM software. The dynamic characteristics of the model were simulated by combining with the three-dimensional cone crusher model in order to study the influence of relevant parameters on the performance of the crusher.
Before the ore modeling with DEM software, the basic physical and mechanical properties of iron ore were explored through rock uniaxial compression [25, 26], fracture toughness, rock material damage, and other experiments. The grain size, structure size, internal porosity, pore radius, coordination number, and other factors of the ore were analyzed by computed tomography (CT) nondestructive testing technology. The DEM virtual ore model can more truly reflect the physical characteristics and crushing characteristics from the experimental results. Figure 7 shows the cutting and sampling from the crude ore after the rotary crusher. The equipment used is a cutting machine and a drilling prototype to make the iron ore into regular cylindrical specimens for the mechanical properties experiment.
For the collected specimens, the internal structure and characteristics of the ore were observed through nondestructive testing with CT. The internal structure of the ore is visually characterized through three-dimensional technology [27, 28]. Finally, the relationship between structure and performance was established based on the experimental data. Figures 8(a) and 8(b) show the technical scheme of CT nondestructive testing and CT.
The test conditions were voltage 100kV, current 50A, and resolution 1.12m. A full-diameter CT scan test was performed on ore samples, and the internal three-dimensional (3D) structure data volume of the sample was obtained for three-dimensional display. After that, different internal substances were extracted by using the gray difference for three-dimensional rendering. The internal structure of the ore was observed to understand the structural characteristics of the internal pores and fractures of the ore. Figures 9(a) and 9(b) show the three-dimensional display and rendering of iron ore. The red area shows the cracks. The cracks were extracted by threshold segmentation. The volume percentage of the study area (i.e., porosity) occupied by the cracks is 10.18%.
Figures 10(a) and 10(b) show the three-dimensional rendering of iron ore porosity. The extracted pores were marked with different colors for each isolated pore. At the same time, the pores were marked and sieved. The pore equivalent diameter (EqD) sieve is shown in Figures 11(a)11(h). The number of equivalent diameters of different pores and the percentage of the total pore volume are shown in Table 4.
The characteristic parameters such as porosity, coordination number, pore radius, and pore volume were obtained through the experimental exploration of the ore after coarse crushed by the gyratory crusher. The number of pore equivalent diameters in the range of 9
In order to characterize the ore particle model well, bonded particle model (BPM) was selected. The BPM model was published by Potyondy et al.  and A. R. Hasankhoei for the purpose of simulating ore breakage. The approach has been applied and further developed by Cho et al. and Johansson et al. [30, 31]. The concept is based on bonding or gluing a packed distribution of spheres together forming a breakable body.
When setting the crushed ore particles, firstly, a certain amount of particles were combined to form ore particles through the bonding bond at a given time. When subjected to crushing force, the particles formed by the bonding bond will be dispersed to show the broken state. At this time, the bonding bond is broken. The larger the number of broken bonds, the better the crushing effect and the higher the product quality. This paper mainly analyzes the impact of different parameters on the crushing effect. Because of the large amount of crushed iron ore, the influence of the shape of the ore was not considered, and the iron ore model was equivalent to a spherical shape. Figure 12 shows a schematic diagram of ore model generation and crushing.
Since the particle size of the ore feed cannot be less than 100mm, the design iron ore model diameter is 100mm. According to the physical properties of the iron ore obtained by experiments, such as the porosity and coordination number, the diameter of the fraction used to fill the iron ore particles was determined to be 5mm. The empirical equation (17) for determining the number of filling particles given in the DEM was used to calculate the number of filling fractions:where is particle filling coefficient, is the volume of feed particle, is the number of filled fractions, and is the volume of filled fractions.
Firstly, import the crusher chamber model drawn by SolidWorks into the geometry module, and set the motion characteristics for each part. The movement of the mantle includes two: one is its own rotation movement, the speed is very low, generally 1015r/min, and the other is the eccentric movement around the axis of the concave. The eccentric movement speed is specifically set according to the optimization result, and the movement time is set to 5s.
Secondly, set the basic property parameters of iron ore and liner materials in the globals module, including density, Poissons ratio, and shear modulus. Define the properties of fraction particles and whole particles in the particle panel, including particle radius, volume, and mass. The fraction particle radius is 5mm. Because of the soft ball contact model, the actual contact radius is slightly larger than 5mm, which is defined as 5.5mm here, and the whole particle is 50mm.
During the operation of the crusher, the ore and the ore, and the ore and the liner are squeezed into each other. Therefore, it is necessary to separately set the coefficient of restitution between the ore and the ore, the coefficient of static friction, the coefficient of dynamic friction, and the three coefficients between the ore and the liner.
Finally, determine the simulation time step and divide the mesh. Generally, 2-3 times the radius of the smallest particle element is selected as the basis for meshing. In this simulation, 2 times the radius of the smallest particle element 5mm is selected as the ideal side length of the mesh element.
The time step is determined by the Rayleigh  wave method. For a system composed of different particles, the time step was calculated as follows:where is particle velocity, is particle density, is shear modulus, and is particle radius.
Simulation was carried out according to the parameters in Table 3, and the total number of ore bonding bonds N was set as 144,298. Figures 13(a)13(d) show the DEM simulation of the crushing process of the cone crusher at different moments and the velocity cloud diagram of the particles in the crushing chamber.
In Table 5, is the total number of ore bonding bonds and is the number of ore fracture bonds. The bottom angle of the mantle , the length of the parallel zone , and the eccentric angle are changed respectively for simulation. For different variable values, the corresponding number of ore fracture bonds and are shown in Table 5. The breaking rule of ore bonding bond with crushing time is shown in Figures 14(a)14(c).
It can be seen from the above that when the bottom angle of the mantle increases from 50 to 60, the number of bond breaks decreases from 130,589 to 118,901, and the broken percentage decreases from 90.5% to 82.4%. And when the length of the parallel zone increases from 140mm to 190mm, the number of bond breakages increases from 126838 to 136650 and the broken percentage increases from 87.9% to 94.7%. While when the eccentric angle increased from 1.4 to 2, the number of bond breaks increased from 115,149 to 122,941, and the broken percentage increased from 79.8% to 85.2%. The simulation value is slightly higher than the numerical calculation value, but the trend of the broken percentage with the change of the bottom angle of the mantle, the length of the parallel zone, and the eccentric angle is consistent.
By analyzing the movement state of the ore in the crushing chamber, the cone crusher productivity and product quality are used as the objective functions to study the influence of the chamber structure parameters on the crusher performance with the method of optimized numerical calculation. The main conclusions of this paper are as follows:(1)In order to obtain a more accurate productivity model, it is necessary to remove the blockage ore uplift in the traditional model. For this reason, considering the influence of the ore arching of the blockage layer in the A and D areas, the traditional productivity model was revised to improve the calculation accuracy of the crushers productivity. For the C900 cone crusher, the relative error of the revised productivity model calculation value is reduced by 16%.(2)Taking the parameters such as mantle bottom angle, parallel zone length, and the eccentric angle of the chamber structure as optimization variables, a dual-objective programming model about the productivity and product quality for the cone crusher was established. The optimal parameter matching scheme of C900 cone crusher performance was obtained: The swing speed of the mantle, the length of the parallel zone, the bottom angle of the mantle, the eccentric angle, the eccentricity, and the engagement angle are 285r/min,1 50mm, 55, 2, 44.8mm, and 23, respectively. After optimization, the productivity and the percentage of crushed products of the C900 cone crusher can be increased by about 2% and 2.1%, respectively.(3)Based on the physical characteristics of the iron ore after coarse crushing by the gyratory crusher, the discrete element method is used to simulate the crushing process. The simulation results are consistent with the trend of the numerical calculation results, verifying the feasibility and reliability of the dual-objective programming model of the cone crusher as well as the optimization numerical method.
Copyright 2021 Fengbiao Wu et al. 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.
Cone crushers are used in the aggregate and mining industries to crush blasted rock. In order to design the latest cone crushers, using equations of motion and population balance models, new designs of cone crusher chamber geometry are introduced to achieve chamber optimization. Several models are investigated by analyzing the internal relationships between the main machine parameters (including speed of eccentric shaft, eccentricity, length of parallel strip, base angle of cone) and the chamber, output and size reduction. Multi-objective models of the crushing chamber, output and size reduction based on new output calculation methods, population balance models and interparticle breakage is accomplished, which provide the theoretical basis for developing the latest cone crusher models. Optimization results are also applied to improve the existing PYB1750 cone crusher, and the validity and reliability of these models are verified by the manufacturers full-scale prototype test.Get in Touch with Mechanic