CN107413462A - Simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating - Google Patents
Simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating Download PDFInfo
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- CN107413462A CN107413462A CN201710534511.5A CN201710534511A CN107413462A CN 107413462 A CN107413462 A CN 107413462A CN 201710534511 A CN201710534511 A CN 201710534511A CN 107413462 A CN107413462 A CN 107413462A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
- B02C17/14—Mills in which the charge to be ground is turned over by movements of the container other than by rotating, e.g. by swinging, vibrating, tilting
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
- B02C17/18—Details
- B02C17/24—Driving mechanisms
Abstract
The present invention is that simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating, including main vibrating system and vibrating isolation system, the main vibrating system includes vibrating motor and mill tube, vibrating motor, mill tube and the upper plastid of upper plastid plate composition, one end of lower plastid is connected with main vibration spring group, and the lower plastid is connected by the main vibration spring group with vibrating isolation system；Vibrating isolation system includes the isolation spring being connected with the lower plastid other end, and the isolation spring is connected by base with ground, and the main vibration spring group is made up of several pitches not doubling-up helical springs, and each spring forms by a steel wire coil around structure.The present invention is due to that with main vibrating isolation system, on the one hand can bear bigger exciting force, on the other hand can effectively reduce vibration effect of the vibrating mill to ground, reach good energy-saving effect；Not doubling-up of the main vibration spring under possible maximum load so that system noise significantly reduces and dynamic stability greatly increases.
Description
Technical field
It is a kind of there are pitches not simultaneously the present invention relates to a kind of milling equipment prepared for the vibration of material fining powder
Coil spring, medium are the monotubular double-mass vibrating mill of hybrid density proportioning, belong to vibration using the interdisciplinary science with powder technology
Technology.
Background technology
Vibromill is the vibrating mechanical equipment that material fining grinding operation is completed using vibration principle, existing superfine powder
In technology of preparing, vibromill is with other preparation methods if any gas phase synthesis method, liquid phase synthesizing method, comminution by gas stream, roller mill method
Etc. comparing, there is the advantages such as mechanical mass activity is big, purification is convenient, cost is low, simple in construction, efficiency is high, existing vibromill branch
Support spring typically uses line style equal pitch helical spring；Its medium generally uses isodensity medium, and such as abrasion-resistant stee, zirconium oxide are single
One density medium；Body is mostly elemental body structure.
The elemental body structure of vibromill, show between the vibration plastid and base that are made up of cylinder and vibrator, be to pass through
Spiral compression spring is connected, and is vibrated caused by vibration plastid, ground can be directly acted on by spring pedestal, produced larger with making an uproar
Sound, therefore it is larger to consume energy.In recent years, or the research report that there is double-mass vibrating to grind, but due to double-mass vibrating mill be related to it is main every
Vibrating system designs, and its structure is relative complex, cost is higher, therefore practical application person is few.
In Practical Project, the parameter such as vibrational system quality, exciting force, damping force is mostly change person, such as vibromill
The mill that medium, the grinding charge material of system in itself are formed, which is situated between, to flow, and constantly throws, falls in motion process, and actually one
Nonlinear change can also occur wherein for the process of individual complicated mass change, damping, and the bias that the inclined block of vibrating motor is formed swashs
Power of shaking be with the change of corner and change it is non-linear, vibration grinding system be actually a typical nonlinear system, be
One has the strong nonlinear vibration system for determining excitation and uncertain response.
The load character curve for the equal pitch helical spring that existing vibrating machine generally uses for linear line, for etc. rigidity spiral shell
Spring is revolved, does not account for the actual condition of mission nonlinear, such as jigging conveyer, vibrating scalper, vibrating mill, due to motion
The system load moment is all changing under state, therefore the stiffness helix spring such as uses, though there are simple in construction, low cost and other advantages, so
Noise is big, power consumption is high, efficiency is low, the maintenance frequency is high, equipment life is low etc. be present.
Normal spiral spring is linear characteristic wire spring, and its load is linear with deforming；Variable-pitch screw spring is then
For nonlinear characteristic wire spring, its load is in non-linear relation with deformation, has special performance, the load of all of which reaches
After to a certain degree, the stress in material section is changed along the length of material.Therefore, the size of material will be according to maximum
Stress determines；The height or length of spring will determine according to deformation required after stand under load.
Normal linear spring can not realize variation rigidity, then can not realize and the vibration coupling of above-mentioned complex vibration system or association
Vibration is adjusted, thus efficiency is low, energy consumption is big, noise is big.How so that the change of vibrational system rigidity and elastic force, with its in system
The active force that it varies goes to realize vibration coupling, to reach the purpose of efficient energy-saving, be one be worth inquire into the problem of, this hair
The introducing of bright variable-pitch spring, the needs of exactly this research.
Recent domestic experts and scholars are inquiring into the solution of above mentioned problem always, due to equal pitch, constant stiffness spiral shell
Rotation metal spring is easily designed, easily manufactured, good economy performance, therefore is widely used for a long time.In summary, while overcome above-mentioned
The new grinding machine with efficient energy-saving of problem is not yet suggested so far.
The content of the invention
The present invention provides a kind of pitches, and simultaneously coil spring, hybrid density medium monotubular double-mass vibrating are not ground, and have double matter
Body technique feature, main vibration spring are pitches not simultaneously coil spring, and isolation spring is rubber duck complex spring, master-isolation spring
It is variation rigidity；It is to improve to grind impact of Jie's ball in relative motion, extruding, shearing, the energy of collision in cylinder, it is close implements mixing
Spend medium size composition optimal design-aside, compared with existing widely used common single vibration grinding machine system, have obvious efficiency high,
The features such as noise is small, it is intended to effectively solve existing vibromill all the time, the technical bottlenecks such as pendent noise is big, efficiency is low
Problem.
The Novel monotubular double-mass vibrating mill of the present invention takes following technology to realize：
The present invention is that simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating, including main vibrating system and vibration isolation system
System,
The main vibrating system includes consolidating by the vibrating motor for being used as exciting source of Frequency Converter Control and with the vibrating motor
It is scheduled on mill tube together, the vibrating motor, the mill tube and the upper upper plastid of plastid plate composition, one end of lower plastid and master
Groups of springs of shaking is connected, and the lower plastid is connected by the main vibration spring group with vibrating isolation system；
The vibrating isolation system includes the isolation spring being connected with the lower plastid other end, and the isolation spring passes through base and ground
Base is connected；
The main vibration spring group is made up of several pitches not doubling-up helical springs, each spring by a steel wire coil around structure and
Into described steel wire is wound into variable-pitch screw structure according to design data, and steel wire is wound into variable-pitch screw structure, pitches
Not doubling-up helical spring at least 4 encloses the effective helix angle of the above, and the central diameter of effective helix angle is becomes central diameter spiral, central diameter is from centre
Typically it is distributed to both ends in Rearrangments.
Further improvement of the present invention is：The main vibration spring edge and vibrating motor main shaft vertical direction in vibromill
Put number row, placed several rows along with vibrating motor main axis parallel direction, form the uniform state of spring.
Further improvement of the present invention is：The isolation spring is composite as made of rubber duck composite
Isolation spring.
Further improvement of the present invention is：The mill tube medium is two or more different proportioning.
Double-mass vibrating mill of the present invention is mainly made up of main vibrating system with vibrating isolation system, vibrating motor in main vibrating system
As exciting source, the purpose for becoming exciting force can be reached by Frequency Converter Control, what is be fixed together with vibrating motor is mill tube,
Both form upper plastid together with upper plastid plate, and lower plastid one end is connected with main vibration spring group, passes through main vibration spring group and vibration isolation
System is connected；In vibrating isolation system, the other end is connected with isolation spring, and isolation spring is connected by base with ground.After energization, by
Frequency Converter Control vibrating motor, to change exciting force, vibrating motor makees approximate circle vibration with mill tube so that is ground in mill tube
Be situated between and produce mutually motion, so, in cylinder and be adhered to mill be situated between and barrel on powder reach grinding due to hitting, rubbing
Purpose.The double-mass vibrating mill passes through two groups of springs of main vibration spring group and isolation spring, can significantly reduce vibromill master
Body has reached the effect of energy-conservation to oscillation intensity caused by ground and noise.Isolation spring be installed on lower plastid and base it
Between, base, by bolt group concrete mutually, can prevent moving horizontally for vibrating mill with ground.
The load envnlope line of the pitches not doubling-up helical spring is cumulative type non-linear line, and be it is continuous or point
Section is continuous, and this is advantageous to the generation for preventing its resonance and flutter；Due to the change of central diameter, in identical steel wire diameter difference pitch
In the case of, decrement during adjacent two steel wires doubling-up, variable-pitch spring is big compared with common spring.It is special according to the structure of this spring
Point, consider the condition of not doubling-up, the not doubling-up of grinder system main vibration spring can be achieved, noise caused by spring doubling-up is zeroed.
Due to the pitch variation of the helical structure of composition pitches not doubling-up helical spring, there is the present invention obvious non-
Linear and required variation rigidity feature, i.e., the system stiffness that spring of the present invention is formed have the variation rigidity increased and decreased with loads increasing or decreasing
Feature, make the effective accumulation of energy of system, energy-conservation, steady running, the purpose for significantly reducing noise to reach.
The pitches not doubling-up helical spring group formula double-mass vibrating mill, spring edge in vibromill are hung down with electric machine main shaft
Nogata is multiple rows of to putting, and places some rows along with electric machine main shaft parallel direction, the uniform state of spring is formed, so that vibromill is more preferable
Work.
The spring design of vibrational system so far, the factor of not doubling-up was not almost accounted for, both due to traditional design
Limitation, existing again influences that not doubling-up associated technical parameters are more and calculate numerous and diverse, thus not only noise is big for system, and energy consumption
Height, efficiency are low.According to the design feature of this spring, the condition of not doubling-up is analyzed and studied in present invention research from working mechanism,
The not doubling-up of main vibration spring in the grinder system course of work can be achieved, noise caused by spring doubling-up is zeroed.
In the present invention, isolation spring can be made of rubber duck composite, and lower plastid passes through isolation spring and base
It is connected with ground, because isolation spring has hard nonlinear characteristic, its rigidity has the characteristics of changing with load change, therefore subtracts
Effect of shaking is good, can obtain preferable noise reduction, and the purpose of firm banking mainly prevents vibromill in the horizontal direction in face
Movement.
Vibromill is to utilize the vibration for vibrating mill tube generation certain frequency so that the medium such as ball or rod in cylinder produces inertia
Power has compact-sized, volume with comminuting matter, the acceleration of mill tube vibration to complete to impact typically up to 6g-12g
Small, in light weight, properties of powder performace concentration, process simplification, it is simple to operate, easy to maintenance, liner plate Medium Replacement is easy the advantages that, can be wide
It is general to be used for the industry powder such as metallurgy, building materials, mine, fire resisting, chemical industry, glass, ceramics, graphite.
The medium that existing vibromill technology uses, size can pass through experiment or numerical simulation according to different material
It is compared, to determine optimum gradation, it is substantially single density medium that its right density, which is chosen, typically using forged steel, wear-resisting
Steel, wear resistant cast iron, high chrome, middle chromium steel, zirconium oxide etc., its shape can be spherical or round bar shape, but mill tube to be further added by and
Acceleration during media impingement material, single density medium is almost helpless, and appropriate selection two or more not
With the medium size composition of density, such as wolfram steel, abrasion-resistant stee, in throwing, in collision process for grinding process, because its density of material differs
About 2 times, then cause that mill in cylinder is situated between involve, relative velocity and involve, the motion value such as relative acceleration increases severely, necessarily cause it
Impact energy greatly improves, and turns into the necessary condition for improving mill efficiency.
The realization of hybrid density media technology main points, it is a variety of to can reach generation impact, shearing, extruding etc. in grinding operation
The Practical Project effect of the combining ability effect of power, some work barrier for overcoming vibrating machine, it is special to solve vibrating machine
It is some key technologies of vibromill or restricts the bottleneck problem developed, does not refine, easily rolls into a ball as solved ultramicro powder in vibromill
Poly-, powder product is distributed the problems such as band is big compared with wide and energy consumption, mill efficiency is low, capacity usage ratio is low, and then realizes material
Ultra-fine or ultramicro grinding, reduce energy consumption, improve efficiency, there is significant engineering effort, economic and social benefit, due to high density
Medium is using the financial cost that grinding machine exciting power is slightly lifted is caused, compared with economic benefit caused by the present invention, for chasing after
The target of high-quality powder is asked to can be ignored substantially.
The beneficial effects of the invention are as follows：Vibrating mill of the present invention is compared with common elemental body grinding machine, due to master
Vibrating isolation system, bigger exciting force on the one hand can be born, on the other hand can effectively reduce vibration effect of the vibrating mill to ground,
Reach good energy-saving effect；The rigidity of the variable-pitch spring and rubber spring can be with the change of grinder system maximum load
And change, can not only have accumulation of energy, the effect of energy-conservation, and necessary condition is provided for the coupled vibrations of main vibration isolation, main vibration spring
Not doubling-up under possible maximum load so that system noise significantly reduces and dynamic stability greatly increases, and overall efficiency is bright
Aobvious lifting；In the case of hybrid density medium size composition optimal design-aside, compared with existing grinder system, from this angle of Media density
Degree examination, it is even more apparent to improve the advantages such as high, the reduction energy consumption of system effectiveness.
The effect of the present invention is positive, obvious and unique, and it has ultramicro powder refinement, de-agglomerated, powder product point
Strap narrows, energy consumption is low, mill efficiency is high, capacity usage ratio is high and effective accumulation of energy, energy-conservation, steady running, significantly reduces and makes an uproar
The features such as sound, vibration isolating effect are good.The above-mentioned technology of the present invention, is effectively solving existing vibromill pendent energy all the time
In the technical bottleneck problems such as consumption is big, efficiency is low, a step of leap will be realized.
Brief description of the drawings
Fig. 1 is vibromill structural representation of the embodiment of the present invention.
Fig. 2 is the moulding figure of main vibration spring of the embodiment of the present invention.
Fig. 3 is that two spring characteristic curves compare before and after amendment of the embodiment of the present invention.
Fig. 4 is main vibration spring of embodiment of the present invention rigidity and load matched curve figure.
Fig. 5 is main vibration spring component Butut of the embodiment of the present invention.
Wherein：1- mill tubes；The upper plastid plates of 2-；Plastid under 3-；4- bases；5- isolation springs；6- main vibration spring groups；
7- vibrating motors.
Embodiment
In order to deepen the understanding of the present invention, present invention work is further retouched in detail below in conjunction with drawings and examples
State, the embodiment is only used for explaining the present invention, and protection scope of the present invention is not formed and limited.
It is vibration milling machine structure sketch of the present invention shown in Fig. 1, grinding Jie's packing factor in cylinder is set to 65%, and mill tube medium is
Abrasion-proof steel ball, wolfram steel ball, two kinds of mill betweenness amount ratios are 6:4, a diameter of 2 mm of mill Jie, 3.5 mm, 5 mm, 6.5mm, material is super
Hard fine powder body, grinding machine vibration frequency is 1450 rpm, surveys amplitude<22mm, shake strong<20.
It is mainly old to left avertence block portion point because the structure of vibrating motor or so block portion point partially is full symmetric on central plane
State, right avertence block portion point is identical with left avertence block some embodiments；Due to symmetry, during motion or so partially block portion point easily realize it is same
Step, occasionally there is nonsynchronous situation in short-term, because rotor axis of electric has enough rigidity and intensity, therefore the caused axial moment of couple
Completely in system tolerance range.The present invention to be mainly characterized by exciting force, amplitude, frequency, the parameter variation range such as strong that shakes big,
Its size, action time can be control effectively by frequency converter.
As shown in figure 1, caused vibration directly drives upper plastid and mill tube, mill tube during each rotation of block partially on vibrating motor
Built with medium and powder, vibrate the mills such as the steel ball made in mill tube Jie and collision, impact produced to material, shears, extrude and rubs with the hands and grind,
Reach and material is crushed and the purpose of fine grinding, pass through and adjust the angle of the inclined block of major-minor, change the grading that mill is situated between and select, implement
The measures such as VFC, required certain frequency high amplitude, Gao Zhenqiang vibration crushing effect can be produced.
Grinding machine of the present invention is made up of upper and lower plastid and main vibrating isolation system, formed double mass, upper plastid mainly by upper plastid plate,
Vibrating motor, mill tube consolidation form, and have mill Jie and powder in cylinder, are connected between upper and lower plastid with main vibration spring group；Lower plastid
It is connected between base with isolation spring, base is with ground with bolt group concrete mutually.Under working condition, shaken by Frequency Converter Control
Dynamic motor, changes exciting force by changing transient state rotational frequency, so change amplitude, shake strong change curve, reach efficient powder
The purpose of mill.
The present invention is from the medium size composition of two kinds of different densities, i.e. wolfram steel, abrasion-resistant stee, in the throwing of grinding process, collides
During, because its density of material differs about 2 times, then cause that mill in cylinder is situated between involves, relative velocity and involves, relative acceleration
Increase severely Deng motion value, due to greatly improving for impact energy, then generate improve mill efficiency, reduce smashing fineness,
Reduce the multi-effect of noise.
As shown in Fig. 2 pitches not doubling-up helical spring by a steel wire coil around forming, described steel wire coil by design around
Into variable-pitch screw structure, the Parameters variation such as the design visible system quality of variable-pitch spring, exciting force is improved.Pitches
Not doubling-up helical spring at least 4 enclose the above effective helix angle, and the effective pitch of effective helix angle be equal pitch spiral, spiral
Central diameter is from centre to both ends Rearrangments.
The load envnlope line of the spring is cumulative type non-linear line, and is continuous or zonal cooling：This is advantageous to
Prevent the generation of its resonance and flutter；The big I of pitch takes different pitches between each circle, or a few circles are one group
Take into several different pitches；Pitch can ascending unidirectional array, also can be by bi-directional arrangement broad in the middle small in ends.
The pitch of pitches not doubling-up helical spring is identical, and spiral central diameter is from centre to both ends Rearrangments.Pitches are not
Doubling-up helical spring plays support framework, has good nonlinear characteristic and a damping and amortization, is particularly carried in system during work
Lotus increase, it is mutated or can be played when overloading and doubling-up occurs and improve bearing capacity, increase system stiffness and noise reduction, noise reduction, vibration damping
Effect.
Set in embodiment the nonlinear characteristic line equation of main vibration spring as：
(1)
In formula：A system transient load in office and corresponding deformation,For undetermined coefficient.
According to system loading conditions, if the number of main vibration spring is n, the static load plastid quality that is determined by system can must be
Single spring institute is loaded during static load of uniting is
N
During system motion, maximum dynamic loading is suffered by single spring
N （2）
Above formula will consider at 2 points：
(1) minimum load situation is static load scenario, and now single spring stress is。
(2) additional load caused by each spring Dynamic And Static Loads and its uneven effect, takes each spring stand under load nonuniformity coefficient
For 1.4, Dynamic And Static Loads consider the experimental test situation of the not doubling-up of vibromill minimum rigidity coil spring, chooseMost
Big dead load, cause maximum inertia force plus vibrating motor exciting, as maximum dynamic loading.
Three point coordinates of nonlinear characteristic line can be obtained accordingly, and then determine constant, obtain nonlinear characteristic line bullet
Spring deformation under load equation.According to vibrating mill engineering site situation and design experiences, shear modulus is takenG, allowable shear stress can be obtained, mean diameter of coil D, spring filament diameter d are chosen, looks into spring design manual, according to curling up ratio, curvature correction factor K is taken, then is calculated
Spring can be obtained and respectively enclose rigidity, spring rate before and after each circle doubling-up、, respectively enclose load during doubling-up, pitchDeng calculating knot
Fruit.Calculating process is carried out MATLAB programing operations, by changing mean diameter of coilDAnd spring filament diameterd, different springs can be obtained
Natural length H, spring-mass and displacement, it is ensured that spring not doubling-up under maximum load effect, the reasonability of assay.
From the foregoing, because pitch from both ends to centre is two-way incremental arrangement, therefore the 2nd, 6 circles have met maximum functional
Not doubling-up requirement under load, to ensure with certain safe clearance and pitches requirement, the spacing value ratio of the 3rd, 4,5 three circle
2nd, 6 circles are big, each circle deformation of springThere is following relation with the spacing of each circle：
（3）
Data above is substituted into the formula (1) for having determined that undetermined coefficient, revised spring load deformation characteristic equation can be obtained, thus
Two front and rear spring non-linear hard characteristic wire spring load of amendment and deformation curve can be made, as shown in Fig. 2 as seen from Figure 2,
Revised curve has more preferable variation rigidity characteristic.Wherein, curve 1 is curve after amendment, and curve 2 is curve before amendment.
Analyzed from Fig. 4, system variant increases and increased with system load under varions type load；Increase when load is mutated
During to certain value, always due to not reaching maximum dynamic loading, therefore spring will not doubling-up, now system variant increase and several with load
It is unchanged, obvious hardware features nonlinear characteristic is presented, this is beneficial to increase amplitude stability.
Rigidity before each circle doubling-up is plotted into curve as shown in Figure 4 with the rule of load change, as can be seen from Figure：It is single
Spring load from minimum load to maximum load in the range of the rigidity curve of load be approximately a straight line, i.e., now system stiffness with
Load is substantially linear.
Accordingly, the stability of hardware features nonlinear system amplitude can be further illustrated.By the natural frequency of vibration of spring
(4)
Analysis is understood, in variable mass system, when rigidity and load are linear change, thenωIt is still a constant, because the system is
Worked under Near resonance oscillating situation, and its amplitude near Near resonance oscillating area, known by (4) formulaIt is substantially constant, rFor
The damped coefficient of system, change is also little, if now exciting forceFIt is substantially constant,ThenFor constant, therefore shaken under Near resonance oscillating state
Substantially constant, this just illustrates now system amplitude stability, and working condition is steady.
From the experiment of prototype design, under the high vibration intensity effect that system occurs, irregular pitch helical spring
Pitch variation by it is ascending be incremented by unidirectional array when, and the number of turns is more and noise is larger, and causes load to the inclined block system of two level
The Spline smoothing reaction of lotus is unstable；Pitch variation is by two-way incremental arrangement broad in the middle small in ends, and without the simultaneously number of turns, doubling-up is made an uproar
Sound is zero, and causes the Spline smoothing of load to react relatively stable to the inclined block system of two level；In view of the influence of high vibration intensity
And the stability of system vibration, therefore the design uses the latter.
Non-linear variable-pitch spring makes system stiffness change with load change, not only the feature with efficient energy-saving, together
When system amplitude can be made basicly stable.Therefore it is changed to fit as the normal spiral compression spring of main vibration spring during conventional vibration is ground
Suitable non-linear variable-pitch screw compression spring, can reach systems stabilisation amplitude, realizes the purpose of system high efficiency energy-conservation.
As shown in figure 5, the distribution situation of pitches not doubling-up helical spring group, pitches not doubling-up helical spring is in vibromill
Two rows are put along with electric machine main shaft vertical direction, position 1-6 is placement location of the spring in vibromill, along side parallel with electric machine main shaft
To 3 rows are placed, 6 uniform states of spring are formed, so that mill tube can normally complete vibratory milling work.
Isolation spring the present embodiment selects the crate tire of rubber duck composite, and experiment proves and General Purpose Rubber bullet
Spring, metal spring are compared, and its vibration isolating effect is considerably better, and not only vibration absorbing performance is good, noise is low, and simple in construction, good economy performance,
With very high cost performance.
Claims (4)
1. simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating, including main vibrating system and vibrating isolation system, it is special
Sign is：
The main vibrating system includes consolidating by the vibrating motor for being used as exciting source of Frequency Converter Control and with the vibrating motor
It is scheduled on mill tube together, the vibrating motor, the mill tube and the upper upper plastid of plastid plate composition, one end of lower plastid and master
Groups of springs of shaking is connected, and the lower plastid is connected by the main vibration spring group with vibrating isolation system；
The vibrating isolation system includes the isolation spring being connected with the lower plastid other end, and the isolation spring passes through base and ground
Base is connected；
The main vibration spring group is made up of several pitches not doubling-up helical springs, each spring by a steel wire coil around structure and
Into steel wire is wound into variable-pitch screw structure, and pitches not doubling-up helical spring at least 4 encloses the effective helix angle of the above, and has
The central diameter of spiral is imitated to become central diameter spiral, central diameter is typically distributed in Rearrangments from the middle to both ends.
2. simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating according to claim 1, it is characterised in that：
The main vibration spring puts number row, edge and vibrating motor main axis parallel direction in vibromill along with vibrating motor main shaft vertical direction
Place several rows, form the uniform state of spring.
3. simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating according to claim 1, it is characterised in that：
The isolation spring is isolation spring made of composite.
4. simultaneously coil spring is not ground pitches with hybrid density medium double-mass vibrating according to claim 1, it is characterised in that：
The mill tube medium is two or more different proportioning.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3404942A1 (en) * | 1984-02-11 | 1985-08-14 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Grinding apparatus |
| CN101191524A (en) * | 2006-11-29 | 2008-06-04 | 上海通运汽车科技有限公司 | Pitch variable spiral compression spring |
| CN101480629A (en) * | 2009-02-10 | 2009-07-15 | 南京工程学院 | Vibrating motor direct drive type double-mass monotubular vibrating grinding mill |
| CN101773865A (en) * | 2010-03-08 | 2010-07-14 | 南京工程学院 | Multistage eccentric block single barrel vibrating mill |
| CN201802792U (en) * | 2010-08-26 | 2011-04-20 | 芜湖天佑汽车技术有限公司 | Variable-stiffness coil spring for automotive suspension |
| CN201851570U (en) * | 2010-10-08 | 2011-06-01 | 南京工程学院 | Variable-pitch spiral metal composite spring with rubber coating |
-
2017
- 2017-07-03 CN CN201710534511.5A patent/CN107413462A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3404942A1 (en) * | 1984-02-11 | 1985-08-14 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Grinding apparatus |
| CN101191524A (en) * | 2006-11-29 | 2008-06-04 | 上海通运汽车科技有限公司 | Pitch variable spiral compression spring |
| CN101480629A (en) * | 2009-02-10 | 2009-07-15 | 南京工程学院 | Vibrating motor direct drive type double-mass monotubular vibrating grinding mill |
| CN101773865A (en) * | 2010-03-08 | 2010-07-14 | 南京工程学院 | Multistage eccentric block single barrel vibrating mill |
| CN201802792U (en) * | 2010-08-26 | 2011-04-20 | 芜湖天佑汽车技术有限公司 | Variable-stiffness coil spring for automotive suspension |
| CN201851570U (en) * | 2010-10-08 | 2011-06-01 | 南京工程学院 | Variable-pitch spiral metal composite spring with rubber coating |
Non-Patent Citations (1)
| Title |
|---|
| 田中达夫: "采用介质的超微粉碎机的最佳介质粒径的确定", 《中国建材科技》 * |
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Application publication date: 20171201 |