CN106021807B - Sizing Crusher Three-Dimensional Dynamic design method - Google Patents
Sizing Crusher Three-Dimensional Dynamic design method Download PDFInfo
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- CN106021807B CN106021807B CN201610395644.4A CN201610395644A CN106021807B CN 106021807 B CN106021807 B CN 106021807B CN 201610395644 A CN201610395644 A CN 201610395644A CN 106021807 B CN106021807 B CN 106021807B
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Abstract
The present invention relates to crusher design technical fields, specifically disclose a kind of Sizing Crusher Three-Dimensional Dynamic design method.The design method includes the following steps: discaling roll diameter, discaling roll length, broken odontoid and the installed power of 1) Preliminary design crusher；2) crushing teeth structural safety performance STATIC SIMULATION is carried out；3) crushing teeth structure static test is carried out；4) Modal Analysis and dynamic simulation are carried out；5) dynamic test of complete machine is carried out；6) Optimal Structure Designing is carried out based on orthogonal experiment.Design method more systematicization provided by the invention, more specification and efficiently, are greatly lowered research and development cost, accelerate research and development speed, while under the premise of guaranteeing crusher security performance and reliability, making equipment lightweight, further increasing cost performance.
Description
Technical field
The present invention relates to crusher design technical field, specifically a kind of Sizing Crusher Three-Dimensional Dynamic design method.
Background technique
Stagewise crusher belongs to a kind of novel crusher, mainly for underground coal mine Convergency fracturing coal, coal mine
There are the broken and Sizing Crusher of design of granularity requirements in the building Shang Mei and coal preparation plant, and the coal for being mainly used for high yield requirement is broken
It is broken, it is also applied for thick, the medium crushing in mine, metallurgical mineral.Because the research history of Sizing Crusher is shorter, therefore exist very much
Drawback.The design of crusher mainly according to the experience of technical staff, carries out scale-up, and using effect not can guarantee.System
The missing of design method directly affects the development of Sizing Crusher.It is necessary to develop a kind of Sizing Crusher of new system
Design method.
Summary of the invention
The object of the present invention is to provide a kind of Three-Dimensional Dynamic design methods of Sizing Crusher, solve systems approach and lack
The problem of mistake, crusher using effect not can guarantee.
To solve the above problems, the present invention is addressed by the following technical programs:
A kind of Sizing Crusher Three-Dimensional Dynamic design method, comprising the following steps:
1) according to the hardness of product to be broken, granularmetric composition and granularity requirements, rule of thumb and analogy, Preliminary design are broken
Discaling roll diameter, discaling roll length, broken odontoid and the installed power of machine.
2) crushing teeth structural safety performance STATIC SIMULATION is carried out, including crushing teeth model foundation, finite element unit are chosen, side
The determination and interpretation of result of boundary's condition.
3) crushing teeth structure static test is carried out.
4) Modal Analysis and dynamic simulation, including whole machine model foundation, unit selection, boundary condition determination are carried out,
Analysis of simulation result.
5) complete machine dynamic test, including complete machine manufacture, detection system design, Test-bed Design, installation sensor, inspection are carried out
Examining system debugging, test, interpretation of result.
6) Optimal Structure Designing is carried out based on orthogonal experiment.
The present invention by adopting the above technical scheme is compared with existing design method, and the unexpected technical effect of bring is such as
Under: Sizing Crusher Three-Dimensional Dynamic design method provided by the invention makes Sizing Crusher design method more systematicization, more
Specification and efficiently, is greatly lowered research and development cost, accelerates research and development speed, while guaranteeing crusher security performance and reliability
Under the premise of, make equipment lightweight, further increases cost performance.
The preferred technical solution of the present invention is as follows:
The STATIC SIMULATION of crushing teeth structural safety performance described in step 2 operating condition is successively are as follows: tangential load-bearing capacity analysis, method
It is analyzed to load-bearing capacity analysis and axial carrying capacity；If crushing teeth structural safety performance STATIC SIMULATION is unqualified, modification is just
Beginning design scheme, comprising: increase crushing teeth thickness, reduce broken tooth height, modify crushing teeth section, carry out again static imitative
Very, until reaching the requirement of the strength of materials.
Crushing teeth structure static test is carried out described in step 3), sequentially include the following steps: determine first tangential, normal direction and
Axial force size and loading position；Test is successively carried out by tangential carrying, normal direction carrying and axial carrying；Sentenced according to experimental result
The reasonability of disconnected broken gear mechanism；If experiment is unqualified, design scheme is changed according to experimental result, modifies simulation model, directly
To meeting the requirements.
Modal Analysis described in step 4) and dynamic simulation, if crushing teeth structural safety performance STATIC SIMULATION does not conform to
Lattice then modify preliminary design scheme, comprising: increase crushing teeth thickness, reduce broken tooth height, modify crushing teeth section, again
STATIC SIMULATION is carried out, until reaching the requirement of the strength of materials.
The dynamic test that complete machine is carried out described in step 5), if dynamic test structural safety performance is undesirable,
Change its design and modification simulation model, comprising: increase the sectional dimension of rack and main shaft, increase weldment plate thickness, again into
Mobile state test, until completing crusher structure modular in design.
Structure optimization is carried out based on orthogonal test described in step 6), is that perimeter strip is turned to crusher handling capacity maximum
Part optimizes complete machine structure with overall mass most gently for target.
The step 1) to step 6) each step, can according to practical industrial and mineral require carry out step selection, each step it
Between can intersect progress.
Detailed description of the invention
Fig. 1 is Sizing Crusher Three-Dimensional Dynamic design method flow chart of the present invention.
Fig. 2 is the toothed plate type crushing teeth geometrical model figure of the embodiment of the present invention 1.
Fig. 3 is the crushing teeth grid chart of the embodiment of the present invention 1.
Stress envelope when Fig. 4 is the top surface load of the embodiment of the present invention 1.
Fig. 5 is stress envelope when loading before the crushing teeth of the embodiment of the present invention 1.
Stress envelope when Fig. 6 is the side loaded of the embodiment of the present invention 1.
Fig. 7 is the tooth head model figure of the embodiment of the present invention 2.
Fig. 8 is that the model meshes of the embodiment of the present invention 2 divide figure.
Stress envelope when Fig. 9 is the top surface load of the embodiment of the present invention 2.
Stress envelope when Figure 10 is the tangential force load of the embodiment of the present invention 2.
Stress envelope when Figure 11 is the axial force load of the embodiment of the present invention 2.
Figure 12 is that figure is compared in the tooth head model modification design front and back of the embodiment of the present invention 2.
Figure 13 is the grid dividing figure after the modification design of the embodiment of the present invention 2.
Figure 14 is the tooth head normal direction loading stress analysis chart after the modification design of the embodiment of the present invention 2.
Figure 15 is that the tangential force after the modification design of the embodiment of the present invention 2 loads analysis chart.
Figure 16 is that the axial force after the modification design of the embodiment of the present invention 2 loads analysis chart.
Specific embodiment
Those skilled in the art can use for reference present disclosure, be suitably modified realization of process parameters.In particular, it should be pointed out that
All similar substitutions and modifications are apparent to those skilled in the art, they are considered as being included in this hair
It is bright.
Embodiment 1
1) initial designs:
Material to be broken: raw coal (amount containing cash is 58%), compression strength 40Mpa；
Material size :≤500mm, containing grain 5% is surpassed, the visible amount containing cash of maximum particle size 500mm ,+50mm is 58%；
Discharging-material size :≤150mm；
Processing capacity: 1200t/h；
Rule of thumb and analogy, the discaling roll diameter of Preliminary design crusher, are crushed odontoid and installed power at discaling roll length
It is as follows:
First fixed tooth roller diameter 900mm, using fluted disc structure, discaling roll length 2500mm, installed power: 2x200kW.
Step 2 crushing teeth structural safety performance STATIC SIMULATION:
1, the foundation of geometrical model
Sizing Crusher crushing teeth and fluted disc are integrated, fluted disc rigidity with higher, guarantee to be crushed in shattering process
Biggish deformation and displacement will not occur for root portion.In material shattering process, crushing teeth itself can bear size, space, when
Between upper random distribution load effect, it is more complicated than the stress condition of fluted disc very much.Also indicate that crushing teeth damages in actual use
Bad probability is significantly larger than the probability of broken tooth plate damage.Therefore, crushing teeth can be isolated from broken tooth plate, it is individually right
Its intensity is analyzed.Toothed plate type crushing teeth is separated from tooth plate, and the geometrical model established is as shown in Figure 2.
2, grid dividing transitivity parameter setting
When application software carries out finite element analysis, grid dividing and physical parameter setting are impact analysis result accuracys
Two key factors.In the research of this paper, maximum distance on crushing teeth between two o'clock is 89.2mm, the size of crushing teeth compared with
It is small, static analysis only is carried out to crushing teeth, lattice number and calculation amount are relatively small.Meanwhile the edge chamfer of crushing teeth is more,
In this case, lattice number and calculation amount will not be made excessive with free grid, the workload of grid dividing can also be reduced.Therefore it adopts
Gridding is carried out to crushing teeth with tetrahedral grid, sees that Fig. 3, grid sum are 270364.
Static force analysis method is analysis Sizing Crusher crushing teeth in the various various forms of maximum loads that may be subject to
The effective ways of stress when under effect.In crushing teeth stress analysis, physical parameter is as shown in table 1.
1 crushing teeth physical parameter of table
| Elasticity modulus (N/mm2) | Poisson's ratio | Mass density (kg/m3) | Yield strength (MPa/m2) |
| 213000 | 0.286 | 7870 | 1215 |
Normal direction load-bearing capacity analysis:
=3.24× N
Stress distribution when Fig. 4 is top surface load, it can be seen that stress maximum value is present in the tooth root center of front,
Maximum stress value is 325MPa, is lower than material allowable stress value.
Tangential load-bearing capacity analysis:
Torque: T=9549 × P/n=9549 × 200/74=25808N.m
Fig. 5 is stress envelope when loading before crushing teeth, and maximum stress value 827Mpa appears in broken sword and bottom
At the tooth root of face connection.As it can be seen that crushing teeth maximum stress is lower than allowable stress.
Axial carrying capacity analysis:
=0.8=4.588×N
Stress envelope when Fig. 6 is side loaded, as seen from the figure, maximum stress value is present in loading surface tooth root, especially
It is proximate on the dedendum angle before crushing teeth, and stress concentration becomes apparent, and maximum stress value 642MPa is lower than allowable stress
Value.
Step 3) carries out force analysis to the broken fluted disc of production, respectively by tangential carrying, normal direction carrying and axial carrying
It is successively tested, observes the deformation of crushing teeth.
Normal direction loads position in broken tooth top, loading force for 3.24 ×N；Tangential load adds in the front edge of crushing teeth
Carrying power is；The axially loaded side in crushing teeth, loading force are, crushing teeth do not have obviously
Deformation or damage.
Step 4) establishes complete machine Three-Dimensional Dynamic model using finite element software, carries out model analysis to it and calculates intrinsic frequency
Rate and the vibration shape are to prevent it from resonating.Successively progress whole machine model foundation, unit selection, boundary condition determine, simulation result
Analysis, ess-strain are less than the working strength of material.
Step 5)
After device fabrication assembles, strain transducer is installed in ess-strain larger part, connects electric test running, through detecting,
The projects such as equipment noise, vibration, temperature rise all meet testing requirements, the larger ess-strain of complete machine analyzed with step 4 it is identical,
Less than the working strength of material.
Embodiment 2
Step 1) initial designs:
Material to be broken: raw coal；
Material size :≤700mm；
Discharging-material size :≤300mm；
Processing capacity: 2000t/h；
Rule of thumb and analogy, the discaling roll diameter of Preliminary design crusher, are crushed odontoid and installed power at discaling roll length
It is as follows:
First fixed tooth roller diameter 830mm, using fluted disc structure, discaling roll length 2500mm, installed power: 2x315kW, material
It can be same as Example 1.
Step 2 crushing teeth STATIC SIMULATION
1, the foundation of geometrical model
Tooth head model figure is shown in Fig. 7.
Model meshes division figure is shown in Fig. 8.
2, grid dividing
The details of grid dividing is as follows:
Number of nodes: 10954；
Cell size: 6.85606mm；
Tolerance: 0.342803 mm；
Unit sum: 7178.
3, normal direction load-bearing capacity analysis:
Normal direction stress=6240 N；
Fig. 9 be top surface load when stress envelope, it can be seen that maximum stress value be 19.5MPa, stress very little,
It can ignore.
4, tangential load-bearing capacity analysis:
Torque: T=9549 × P/n=9549 × 315/74=40648N.m；
；
Stress distribution when Figure 10 is tangential force load, maximum stress value 1155.1Mpa appear in broken sword and bottom surface
At the tooth root of connection, maximum stress exceeds the allowable stress of material.
5, axial carrying capacity is analyzed:
=0.8=78358N；
Stress envelope when Figure 11 is axial force load, maximum stress value especially lean on present in loading surface tooth root
On dedendum angle before nearly crushing teeth, maximum stress value 503MPa is lower than allowable stress value.
6, modification design:
Tangential force load is analyzed, stress 1155.1MPa at tooth root, and the allowable stress for having exceeded material needs to modify design,
Under the premise of not changing breakage parameter, thickness direction at tooth root is increased 20mm, 80 mm are revised as by 60mm.Length direction
23mm is increased, 112 mm are revised as by 89mm.Tooth height is constant, and tooth top size is also constant, referring specifically to Figure 12.
After modification design, step 1~5 need to be repeated, model is remake, carries out force analysis, all directions load and modification
It is preceding identical.
Figure 13 is the tooth head grid dividing figure after modification design, number of nodes 10909, unit sum 7117.
Figure 14 is the tooth head normal direction loading stress analysis chart after modification design, and maximum stress 19.8MPa and does not have before modification
Big variation.
Figure 15 is the tangential force load analysis chart after modification design, phase before the position of produce maximum stress is designed with modification
Together, maximum stress 891.3MPa, lower than the allowable stress of material.
Figure 16 is the axial force load analysis chart after modification design, phase before the position of produce maximum stress is designed with modification
Together, it also decreases before maximum stress 305MPa, with modification.
The above analytic explanation, the tooth head for modifying design load in normal direction, tangential and axial three directions respectively, and stress is all low
In allowable stress.
Step 3) crushing teeth static test
Test specimen is made by modified parameter, makees slow test in three direction loads respectively, it is radial obvious deformation occur
And damage, step 2 is repeated, until crushing teeth intensity meets design requirement.
Step 4) establishes complete machine Three-Dimensional Dynamic model using finite element software, carries out model analysis to it and calculates intrinsic frequency
Rate and the vibration shape are to prevent it from resonating.Successively progress whole machine model foundation, unit selection, boundary condition determine, simulation result
Analysis: when working frequency and intrinsic frequency are close, change drive arrangement form or change discaling roll diameter and length, to avoid altogether
Vibration；Stress raiser suitably increases fillet or increasing section size.
Step 5)
After device fabrication assembles, strain transducer is installed in ess-strain larger part, connects electric test running, through detecting,
The projects such as equipment noise, vibration, temperature rise all meet testing requirements, and the larger ess-strain of complete machine is identical as step 4) analysis,
The respectively less than working strength of material.
Above-described embodiment provided by the invention, make Sizing Crusher design method more systematicization, more specification and efficiently,
Research and development cost is greatly lowered, accelerates research and development speed, while under the premise of guaranteeing crusher security performance and reliability, making to set
Standby lightweight, further increases cost performance.
It is only the preferred embodiment of the present invention described in upper, it is noted that for those skilled in the art
For, various improvements and modifications may be made without departing from the principle of the present invention, these improvements and modifications should also regard
For protection scope of the present invention.
Claims (1)
1. a kind of Sizing Crusher Three-Dimensional Dynamic design method carries out as follows:
1) according to the hardness of product to be broken, granularmetric composition and granularity requirements, discaling roll diameter, the discaling roll of Preliminary design crusher are long
Degree, broken odontoid and installed power；
2) crushing teeth structural safety performance STATIC SIMULATION is carried out, including crushing teeth model foundation, finite element unit are chosen, perimeter strip
The determination and interpretation of result of part；The crushing teeth structural safety performance STATIC SIMULATION operating condition is successively are as follows: tangential load-bearing capacity analysis,
Normal direction load-bearing capacity analysis and axial carrying capacity analysis；If crushing teeth structural safety performance STATIC SIMULATION is unqualified, modify
Preliminary design scheme, comprising: increase crushing teeth thickness, reduce broken tooth height, modify crushing teeth section, carry out again static imitative
Very, until reaching the requirement of the strength of materials；
3) crushing teeth structure static test is carried out；It sequentially includes the following steps: and determines tangential, normal direction and axial force size first and add
Carry position；Test is successively carried out by tangential carrying, normal direction carrying and axial carrying；Broken gear mechanism is judged according to experimental result
Reasonability；If experiment is unqualified, design scheme is changed according to experimental result, modifies simulation model, until meeting the requirements；
4) Modal Analysis and dynamic simulation, including whole machine model foundation, unit selection, boundary condition determination, emulation are carried out
Interpretation of result；The Modal Analysis and dynamic simulation are modified if crushing teeth structural safety performance STATIC SIMULATION is unqualified
Preliminary design scheme, comprising: increase crushing teeth thickness, reduce broken tooth height, modify crushing teeth section, carry out again static imitative
Very, until reaching the requirement of the strength of materials；
5) complete machine dynamic test, including complete machine manufacture, detection system design, Test-bed Design, installation sensor, detection system are carried out
System debugging, test, interpretation of result；The dynamic test for carrying out complete machine, if dynamic test structural safety performance is undesirable,
Change its design and modification simulation model, comprising: increase the sectional dimension of rack and main shaft, increase weldment plate thickness, again into
Mobile state test, until completing crusher structure modular in design；
6) Optimal Structure Designing is carried out based on orthogonal experiment；Structure optimization is carried out based on orthogonal test, is passed through with crusher
Ability maximum turns to boundary condition, with overall mass most gently for target, optimizes to complete machine structure.
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| 基于PROE技术的分级破碎机设计与分析;刘玉刚;《选煤技术》;20120831(第4期);第79-81、84页 |
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