CN103028460A - Vibration jaw crushing machine - Google Patents
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- CN103028460A CN103028460A CN2011103033874A CN201110303387A CN103028460A CN 103028460 A CN103028460 A CN 103028460A CN 2011103033874 A CN2011103033874 A CN 2011103033874A CN 201110303387 A CN201110303387 A CN 201110303387A CN 103028460 A CN103028460 A CN 103028460A
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Abstract
The invention relates to a vibration jaw crushing machine. The crushing machine comprises a rack body, a fixed jaw lining plate, a movable jaw assembly, a vibration exciter mechanism, a non-linear elastic supporting assembly and a hydraulic clearance adjustment protection mechanism. According to the vibration jaw crushing machine, the actuation power of the movable jaw assembly can satisfy the requirements on crushing ores through utilizing inertia vibration, the crushing ratio and yield are increased, and energy consumption is reduced; and the movement track of the movable jaw assembly varies from top to bottom, so that the ores can be crushed, chopped and milled.
Description
Technical field
The invention relates to a kind of disintegrating machine, espespecially a kind of vibration jaw crusher, its natural building stones that will exploit gained carry out the machinery of broken processing by certain size, and are widely used in the industries such as metallurgy, mine, building materials, chemical industry, coal.
Background technology
Single toggle jaw crusher mainly is comprised of two jaws (sewing jaw and fixed jaw).Sewing jaw periodically moves back and forth fixed jaw, the time and close, the time and separate, make thus that the stone that is contained between two jaws is squeezed, splitting and flecition and fragmentation.Owing to the advantages such as simple in structure, easy to manufacture, reliable operation, easy maintenance are that engineering circles uses very widely.
The movable jaw of single toggle jaw crusher is directly to be suspended on the eccentric shaft, is subject to being partial to the direct driving of axle.The bottom of movable jaw is supported on the rear wall of frame with a thrust plate.So sewing jaw is made reciprocally swinging to deciding jaw on the one hand, can do simultaneously and swing up and down, the movement locus of every bit and different on the movable jaw, the swinging track of each point is to vary continuously to the ellipse of bottom by the top near circle on the jaw, the ellipse that more arrives the bottom is more flat, the horizontal throw of moving jaw is increasing variation the from lower to upper then, therefore not only can play crushing, split brokenly stone, can also play the broken effect of rolling.Because turning to of eccentric shaft is counterclockwise, the direction of motion of each point all is conducive to promote discharge on the moving jaw, so crushing effect is good, percentage of damage is higher, product granularity evenly and be cube more and be fit to hardness building stones in the fragmentation.Because during this class disintegrating machine work, the movement locus more complicated on the movable jaw each point therefore be called complicated oscillating-type jaw crusher, is called for short compound pendulum type jaw crusher (jaw is broken).
The crumbling method of present traditional single toggle jaw crusher all is limited to decide in the crusher chamber that working surface that jaw and moving jaw make up forms.
In other words crusher chamber is interior by the mode of deciding jaw and the formed closed volume of moving jaw and stereomutation, is the main key that produces shattering process.
With regard to modern theory of comminution, need in the process of material crushing constantly to change the orientation between the material particles, with extruding, the shear stress that bears alternation in crusher chamber.In the equal strength particle, those lattice defects are broken with the particle that the shearing force direction overlaps.Material crushing is indoor to be pushed mutually, if apply quantitative pressure to material bed this moment, can make material bed suitably compacting, and make material bear multi-faceted extruding, because the material particles interaction, thereby realize " bed of material pulverizing ".It is less that so-called bed of material pulverizing is based on material particles, and lattice defect is fewer, and intensity is larger, so the large granule of intensity can the broken adjacent little bulky grain of intensity.The so main and not broken crystal broken along the zone between lattice of material itself, the material after the fragmentation has the minimum pulverizing of crossing, thereby has realized " selective crushing " of material, can light broken compression strength between the material of 200～360Mpa.According to theory of comminution, for the broken material of hard difficulty, utilize frequent impact that material is applied huge impact energy and impulsive force, also can reach good crushing effect.
Jaw crusher is by American's mine-laying gram E.W.Blake invention.Since the First jaw crusher comes out, had so far the history in more than 140 years.Its machine construction difficulty satisfies modern theory of comminution.Improve over the years and develop fluid pressure type, without grinding, impact type, direct drive, bicavate with decide jaw, the collaborative vibration jaw crusher of moving jaw.Comprehensive its motion principle roughly forms three macrotaxonomies:
The complicated oscillating motion track of moving jaw, the moving simple oscillating motion track of jaw and the comprehensive oscillating motion track of moving jaw.
Above-mentioned all kinds of jaw crusher all has following shortcoming:
1. because the complicated oscillating motion track of moving jaw, make the material effect that not only is squeezed, also be subject to the mill stripping effect of part, aggravate material and crossed crushing phenomenon, increase energy consumption, produce dust larger, the jaw ratio is easier to wear and tear.
2. the moving simple oscillating motion track of jaw, on the moving jaw every all the circular arc centered by axle is less near the central shaft circular arc, larger away from the central shaft circular arc.Have that crushing efficiency is low, the ratio of reduction is less than 6 shortcoming.
3. move the track that the comprehensive oscillating motion of jaw is followed simply, compound movement produces, the shortcoming of existing composite move: vertical stroke is greater than the level stroke, and lower aside-liner consumption is serious, generally very few use.
4. vibration jaw crusher is symmetrical (horizontal or vertical) arrangement forms of two moving jaws, under the vibratory impulse operating mode, the vibration that the vibration jaw crusher parts bear, impacts the most violently, and the energy of consumption is also large.In addition, strong vibratory impulse process is had relatively high expectations to spring, moving jaw kinetic swing and design bearing, also is the major issue that should solve in the vibration jaw crusher exploitation.
Summary of the invention
The inventor improves its not enough and disappearance, and then proposes a kind of vibration jaw crusher in view of the shortcoming that traditional jaw crusher exists substantially.
Vibration jaw crusher of the present invention, the main viewpoint that changes is kept the elemental body Near resonance oscillating system that the complicated oscillating motion track of existing moving jaw cooperates increase again, produce the comprehensive oscillating motion of moving jaw and improve moving jaw movement track, more be different from other vibration jaw crushers and be symmetrical (horizontal or vertical) arrangement form of two moving jaws, possess the characteristics of jaw crusher and increase single action jaw Near resonance oscillating system vibration, finish the improvement of motion start power.
For reaching above-mentioned purpose, make aforementioned vibration jaw crusher comprise:
One Rack Body is to be to be hollow, forms a frame on its rear end, and forms a holder on the front end, and Rack Body has two opposite side plates in addition, is provided with a bearing block at biside plate, is provided with an eccentric shaft at bearing block;
One fixed jaw liner plate is to be fixed on the frame of Rack Body;
One movable jaw assembly, be arranged on the eccentric shaft, the rotation that is subject to eccentric shaft also makes movable jaw swing, and and formation one crusher chamber between the fixed jaw liner plate, and have a movable jaw and a movable jaw liner plate, this movable jaw wears with its upper end and is hubbed on this eccentric shaft, and this movable jaw liner plate is fixed on the movable jaw;
One vibration exciter mechanism, be arranged on the movable jaw assembly, can excite the movable jaw assembly to vibrate, and have a base, a power transmission shaft and plural uneven piece, this base is fixed on movable jaw and back to crusher chamber, this power transmission shaft is horizontally installed on the base in a rotatable manner, and the uneven piece of this plural number is fixed on the power transmission shaft with eccentric manner and can not rotates relative to power transmission shaft;
At least one nonlinear flexible supports assembly is arranged between movable jaw and the eccentric shaft; And
Protection mechanism is adjusted in one fluid pressure type gap, is arranged between Rack Body holder and the movable jaw assembly.
Aforementioned hydraulic formula gap is adjusted protection mechanism and had: elasticity pushing and pressing plate is to be hubbed on the movable jaw lower end, and makes the movable jaw lower end near the fixed jaw liner plate, and is wealthy lower narrow so that this crusher chamber is presented; Saddle is adjusted in one gap, is to be hubbed on the end of the relative movable jaw of elasticity pushing and pressing plate; One adjusts hydraulic cylinder, is arranged on this gap and adjusts on the saddle, and can stretch to change length; And a hydraulic cylinder Connection Block, be arranged on and adjust the hydraulic cylinder relative gap and adjust on the end of saddle, and articulate with the holder of Rack Body.
Be provided with at least one spring on the aforementioned elasticity pushing and pressing plate.
Be provided with plural number spring arranged side by side on the aforementioned elasticity pushing and pressing plate.
Aforementioned vibration exciter mechanism vibrations frequency ratio less than or equal 2.
Aforementioned this nonlinear flexible supports assembly has an interior ring, an outer shroud and plural tabular spring, and this inner ring sleeve is located on the eccentric shaft; This outer shroud is connected with the movable jaw upper end and is set on the interior ring; The tabular spring of this plural number is arranged between outer shroud and the interior ring, and the distance that provides radical elasticity so that outer shroud and interior ring are separated by diametrically.
The tabular spring of aforementioned nonlinear flexible supports assembly is L-shaped.
Have following advantages by above-mentioned technological means the present invention:
1. because of operation principle and design feature, the production capacity of vibration jaw crusher is improved.
Because the vibration jaw crusher associated component in assembling and structural change, as follows in the advantage of using and make: a. is because of constructional change, causes in jaw crusher overall weight minimizing nearly 2%.B. movable jaw 31 uses nonlinear flexible supports assembly 50 to replace bearing, need not lubricating system and reduces production costs.C. the fluid pressure type gap is adjusted protection mechanism 60 and is used buffering such as increase such as spring 610 flexible members such as grade and overload protection function.
3. utilize Near resonance oscillating nonlinear system principle, appropriate frequency than the time can reduce energy consumption.
Description of drawings
Fig. 1 is front view of the present invention.
Fig. 2 is the lateral plan that the present invention omits side plate.
Fig. 3 is the lateral plan of Rack Body of the present invention and fixed jaw liner plate.
Fig. 4 is that the protection mechanism lateral plan is adjusted in movable jaw assembly of the present invention and fluid pressure type gap.
Fig. 5 is that movable jaw assembly motion structure of the present invention is analyzed schematic diagram.
Fig. 6 is the present invention's one vibration exciter mechanism lateral plan.
Fig. 7 is that protection mechanism amplification lateral plan is adjusted in fluid pressure type of the present invention gap.
The specific embodiment
Below cooperate graphic and of the present invention preferred embodiment, further setting forth the present invention is to reach the technological means that predetermined purpose is taked.
Please refer to Fig. 1 to Fig. 7, vibration jaw crusher of the present invention includes: protection mechanism 60 is adjusted in a Rack Body 10, a fixed jaw liner plate 20, a movable jaw assembly 30, a vibration exciter mechanism 40, at least one nonlinear flexible supports assembly 50 and a fluid pressure type gap.
This Rack Body 10 is to be the tetragonal body configuration, and be hollow, form a frame 12 on its rear end, and form a holder 13 on the front end 11, Rack Body 10 has two opposite side plates 15 in addition, be respectively arranged with a bearing block 14 at biside plate 15, on bearing block 14, be provided with in a rotatable manner an eccentric shaft 16.Eccentric section 160 on the eccentric shaft 16 is eccentric state so that eccentric shaft 16 when rotating eccentric section 160 carry out beat.
This fixed jaw liner plate 20 is to utilize bolt and flexible member to be fixed on the frame 12 of Rack Body 10.
This movable jaw assembly 30 is arranged on the eccentric shaft 16, the rotation that is subject to eccentric shaft 16 also makes movable jaw 30 swing, and form a crusher chamber 300 between the fixed jaw liner plate 20, and have a movable jaw 31, a movable jaw backplate 32, a movable jaw liner plate 33, a briquetting 34, a fastening bolt 341, a flexible member 342.
This movable jaw 31 wears with its upper end and is hubbed on this eccentric shaft 16.
This movable jaw backplate 33 is arranged on the movable jaw 31 and towards crusher chamber 300.
This movable jaw liner plate 33 is fixed on the movable jaw 31 and towards crusher chamber 300.
This briquetting 34 is arranged on the movable jaw 31 and towards crusher chamber 300.
This fastening bolt 341 runs through briquetting 34 and movable jaw 31.
This flexible member 342 is set on the fastening bolt 341 and is positioned at movable jaw 31 on a side of crusher chamber 300, and fastening bolt 341 is packed in briquetting 34 on the movable jaw 31.
This vibration exciter mechanism 40 is arranged on the movable jaw assembly 30, can excite movable jaw assembly 30 to vibrate, and has a base 41, a power transmission shaft 42 and plural uneven piece 43.
This base 41 is fixed on movable jaw 31 on a side of crusher chamber 300.
This power transmission shaft 42 is horizontally installed on the base 41 in a rotatable manner, and can fix a belt pulley 421 on power transmission shaft 42 1 ends and be attached to an external power supply for driving belt is installed.
The uneven piece 43 of this plural number is to be fixed on the power transmission shaft 42 and can not to rotate relative to power transmission shaft 42 with eccentric manner.Each uneven piece 43 has a framework 431, a balancing weight 432 and plural spring 433.This framework 431 and balancing weight 432 are mutually assemblings and around being fixed on the power transmission shaft 42.This plural number spring 433 is arranged between framework 431 and the balancing weight 432, make relatively framework 431 radially moving back and forth along power transmission shaft 42 of balancing weight 432, when power transmission shaft 42 rotates, uneven piece 43 produces inertia force, this inertia force is through base 41 and be delivered to movable jaw assembly 30, so that movable jaw assembly 30 produces vibration, strengthen the crushing effect of vibration jaw crusher.
In addition, the vibration ratio of vibration exciter mechanism 40
Less than or equal 2.ω 0 is the intrinsic frequency of vibration exciter mechanism 40, and ω then is operating frequency.
This nonlinear flexible supports assembly 50 is to be ring type structure, has an interior ring 51, an outer shroud 52 and plural tabular spring 53.
Should be sheathed on the eccentric shaft 16 by interior ring 51.
This outer shroud 52 is connected with this movable jaw upper end and is set on the interior ring 51.
The tabular spring 53 of this plural number can be L-shaped haply elastic plate body; be arranged between outer shroud 52 and the interior ring 51; and the even distance that provides radical elasticity so that outer shroud 52 and interior ring 51 are separated by diametrically reaches the function that buffer protection function has the contained property of circular motion and protecting against shock.
This fluid pressure type gap is adjusted protection mechanism 60 and is arranged between Rack Body 10 holders 13 and the movable jaw assembly 30, and has elasticity pushing and pressing plate 61, gap adjustment saddle 62, adjustment hydraulic cylinder 63 and a hydraulic cylinder Connection Block 64.
This elasticity pushing and pressing plate 61 is to be hubbed on movable jaw 31 lower ends, utilizes elasticity pushing and pressing plate 61 to make movable jaw 31 lower ends near fixed jaw liner plate 20, forms wealthy lower narrow crusher chamber 30 on this, carries out the fragmentation of material.Elasticity pushing and pressing plate 61 can be provided with at least one spring 610 on the elasticity pushing and pressing plate 61 so that itself can stretch and compression; provide by this movable jaw assembly 30 bufferings and overload protection effect, avoid movable jaw assembly 30 stuck and infringement by excessive or too hard material institute.In addition, elasticity pushing and pressing plate 61 can have plural number spring 610 arranged side by side.
This gap adjustment saddle 62 is hubbed on the end of elasticity pushing and pressing plate 61 relative movable jaws 31.
This adjustment hydraulic cylinder 63 is arranged on this gap and adjusts on the saddle 62, and can stretch to change length.
This hydraulic cylinder Connection Block 64 is arranged on to be adjusted hydraulic cylinder 63 relative gaps and adjusts on the end of saddle 62, and articulates with the holder 13 of Rack Body 10.
Operating principle explanation of the present invention below will be described:
Vibrating machine generally is comprised of vibrator, work body, damper and flexible member, and vibrator is the key point of vibrating machine success or failure, and vibrator can produce unidirectional or multidirectional, the exciting force of simple harmonic quantity or non-simple harmonic quantity.If with regard to the system of a single shaft inertial vibration machine simple motion on the x-y plane, the power that acts on the vibration plastid comprises body inertia force, damping force, elastic force and exciting force, in each moment of vibration, always make a concerted effort is zero (force balance principle), therefore center of mass point can be write as at x, y direction of principal axis moving equilibrium equation on the x-y plane
Jθ+C
Yθ+K
Yθ＝T
θ＝J
0θ+F
Y(t)-F
x(t)
M is mass body, the m of movable jaw assembly 30 in the formula
0Quality, F for uneven piece 43
Y(t)=m
0R ω
2Be exciting force, the F of the mass centre by movable jaw assembly 30 along Y direction
X(t)=m
0R ω
2Be exciting force, the C of the mass centre by movable jaw assembly 30 along X-direction
YBe damping force, the C of the mass centre by movable jaw assembly 30 along Y direction
XBe damping force, the K of the mass centre by movable jaw assembly 30 along X-direction
YBe elastic force, the K of the mass centre by movable jaw assembly 30 along Y direction
XBe the elastic force of the mass centre by movable jaw assembly 30 along X-direction.
If damping force, elastic force are ignored, Rack Body 10 inertia force m ω then
2A and uneven piece 43 inertia force m
0R ω
2Mutual balance, movable jaw assembly 30 moving equilibrium equations then, can be write as (with reference to figure 5):
Resolve amplitude and torsional oscillation angular amplitude result, the amplitude of movable jaw assembly 30
The equation of motion of any point P is on movable jaw assembly 30:
Y
P＝Y
0-θL
PX＝(A
Y-A
θXL
PX)sinωt-A
θYL
PXcosωt
X
P＝X
0+θL
PY＝(A
X+A
θYL
PY)cosωt+A
θXL
PYsinωt
Changing from X through coordinate
V, Y
VAxle system changes X into, Y-axis is the moving jaw feeding mouth end M that (with reference to figure 5) then can ask
1, discharge port end M
2Displacement.Because exciting inertia force does not pass through movable jaw 31 barycenter, the coupling effect of vibrational system can make jaw feeding mouth end, the discharge port end displacement amount of moving in the horizontal direction increase and go into elliptical orbit, again because of K
1＞＞K
2Make the horizontal direction amount of movement of discharge port end greater than the feeding mouth end, the horizontal throw that satisfies the moving jaw of jaw crusher is from lower to upper increasing actual demand then.
Establishing OA in such as Fig. 5 aspect jaw crusher movable jaw 31 movement locus is eccentric shaft 16 eccentric throw E, O
1B is movable jaw 31 bracket length T, OO
1Be X ' direction, OO
1Be frame setting height(from bottom) H, AB length P, AB
2Be movable jaw 31 effect extension lines, B
1B
2For movable jaw liner plate 33 is loaded on movable jaw 31 length N
2, AB
1Length N
2, M
1B
1Length N
1, M
2B
2Length N
4, AO
1Be S, ∠ AOO
1=θ, ∠ OO
1A=φ, ∠ AO
1B=ψ, ∠ ABO
1=γ, ∠ YOY '=θ
0, cross the A point and make OO
1Parallel lines and line segment
Angle theta
2The coordinate that can get movable jaw 31 feeding mouth ends (upper end), discharge port end (lower end) according to the law of motion during take X ' Y ' as axes of coordinates close be as:
Moving jaw feeding mouth end: Y '
M1=Ecos θ+N
1Cos θ
2-N
2Sin θ
2, X '
M1=Esin θ+N
1Sin θ
2+ N
2Cos θ
2
Moving jaw discharge port end: Y '
M2=Ecos θ+N
3Cos θ
2-N
4Sin θ
2, X '
M2=Esin θ+N
3Sin θ
2+ N
4Cos θ
2
That General Oscillation machinery all has is simple in structure, cost is little and the characteristics of less energy consumption, and unstable, the steady-state amplitude of amplitude is adjusted complicated shortcoming when certainly also having the Near resonance oscillating frequency.So suitable vibration ratio is the main key of success or failure of the present invention.
Have following advantages by above-mentioned technological means the present invention:
1. because of operation principle and design feature, the production capacity of vibration jaw crusher is improved.
2. assembling and structural change because of the vibration jaw crusher associated component, as follows in the advantage of using and make:
A. because of constructional change, cause nearly reducing 2% in the jaw crusher overall weight.
B. movable jaw 31 uses nonlinear flexible supports assembly 50 to replace bearing, need not lubricating system and reduces production costs.
C. the fluid pressure type gap is adjusted protection mechanism 60 and is used buffering such as increase such as spring 610 flexible members such as grade and overload protection function.
3. utilize Near resonance oscillating nonlinear system principle, appropriate frequency than the time can reduce energy consumption.
4. can under heavy load, start.
Main points of view of the present invention is to cooperate elemental body Near resonance oscillating system by the complicated oscillating motion track of keeping existing movable jaw 31 again, produce movable jaw 31 comprehensive oscillating motions and improve movable jaw 31 movement locus, more be different from other traditional vibration jaw crushers and be symmetrical (horizontal or vertical) arrangement form of two moving jaws, the characteristics of possessing jaw crusher are single movable jaw Near resonance oscillating system vibration only, finishes the improvement of motion start power.
In addition, the transmission that the present invention changes movable jaw 31 is closed and to be, makes the swinging track of movable jaw 31 complicated, can increase the production capacity of vibration jaw crusher.
Moreover; movable jaw 31 of the present invention uses nonlinear flexible supports assembly 50 to replace bearing; restrain movable jaw 31 feeding ends and produce excessive coupling effect; slow down simultaneously the impact of 31 pairs of eccentric shafts 16 of movable jaw; the elastic thrust plate 61 that is installed on movable jaw 31 bottoms utilizes compression helical spring arranged side by side 610; impose pre-power adjustment helical spring 610 is fixed in two fixed blocks, the flexible defencive function when except possessing originally thrust plate effect, having simultaneously foreign matter intrusion crusher chamber.Vibration exciter mechanism 40 is installed on power transmission shaft 42 by the uneven piece 43 of this plural number as shown in Figure 6 and produces inertia force via driving the 30 generation vibrations of movable jaw assembly with movable jaw 31 fastening bases 41.
In brief, vibration jaw crusher of the present invention has the following advantages compared to traditional jaw crusher:
1. the vibro-crusher gross weight alleviates.
2. the discharge end horizontal displacement increases, and can reduce the material excessive wear.
3. the feeding end horizontal displacement increases, and can increase production capacity.
The above only is preferred embodiment of the present invention, be not that the present invention is done any pro forma restriction, although the present invention discloses as above with preferred embodiment, yet be not to limit the present invention, any those skilled in the art, in the scope that does not break away from technical solution of the present invention, when the technology contents that can utilize above-mentioned announcement is made a little change or is modified to the equivalent embodiment of equivalent variations, in every case be the content that does not break away from technical solution of the present invention, any simple modification that foundation technical spirit of the present invention is done above embodiment, equivalent variations and modification all still belong in the scope of technical solution of the present invention.
Claims (7)
1. a vibration jaw crusher is characterized in that, comprises:
One Rack Body is to be to be hollow, forms a frame on its rear end, and forms a holder on the front end, and Rack Body has two opposite side plates in addition, is provided with a bearing block at biside plate, is provided with an eccentric shaft at bearing block;
One fixed jaw liner plate is to be fixed on the frame of Rack Body;
One movable jaw assembly, be arranged on the eccentric shaft, the rotation that is subject to eccentric shaft also makes movable jaw swing, and and formation one crusher chamber between the fixed jaw liner plate, and have a movable jaw and a movable jaw liner plate, this movable jaw wears with its upper end and is hubbed on this eccentric shaft, and this movable jaw liner plate is fixed on the movable jaw;
One vibration exciter mechanism, be arranged on the movable jaw assembly, can excite the movable jaw assembly to vibrate, and have a base, a power transmission shaft and plural uneven piece, this base is fixed on movable jaw and back to crusher chamber, this power transmission shaft is horizontally installed on the base in a rotatable manner, and the uneven piece of this plural number is fixed on the power transmission shaft with eccentric manner and can not rotates relative to power transmission shaft;
At least one nonlinear flexible supports assembly is arranged between movable jaw and the eccentric shaft; And
Protection mechanism is adjusted in one fluid pressure type gap, is arranged between Rack Body holder and the movable jaw assembly.
2. vibration jaw crusher according to claim 1 is characterized in that, described fluid pressure type gap is adjusted protection mechanism and had:
One elasticity pushing and pressing plate is to be hubbed on the movable jaw lower end, and makes the movable jaw lower end near the fixed jaw liner plate, and is wealthy lower narrow so that this crusher chamber is presented;
Saddle is adjusted in one gap, is to be hubbed on the end of the relative movable jaw of elasticity pushing and pressing plate;
One adjusts hydraulic cylinder, is arranged on this gap and adjusts on the saddle, and can stretch to change length; And
One hydraulic cylinder Connection Block is arranged on and adjusts the hydraulic cylinder relative gap and adjust on the end of saddle, and articulates with the holder of Rack Body.
3. vibration jaw crusher according to claim 2 is characterized in that, is provided with at least one spring on the described elasticity pushing and pressing plate.
4. vibration jaw crusher according to claim 2 is characterized in that, is provided with plural number spring arranged side by side on the described elasticity pushing and pressing plate.
5. vibration jaw crusher according to claim 1 is characterized in that, described vibration exciter mechanism vibrations frequency ratio less than or equal 2.
6. vibration jaw crusher according to claim 1 is characterized in that, described nonlinear flexible supports assembly has an interior ring, an outer shroud and plural tabular spring, and this inner ring sleeve is located on the eccentric shaft; This outer shroud is connected with the movable jaw upper end and is set on the interior ring; The tabular spring of this plural number is arranged between outer shroud and the interior ring, and the distance that provides radical elasticity so that outer shroud and interior ring are separated by diametrically.
7. vibration jaw crusher according to claim 6 is characterized in that, the tabular spring of described nonlinear flexible supports assembly is L-shaped.
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|---|---|---|---|
| CN2011103033874A CN103028460A (en) | 2011-10-09 | 2011-10-09 | Vibration jaw crushing machine |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104668024A (en) * | 2013-11-30 | 2015-06-03 | 大连隆星新材料有限公司 | Petroleum wax crusher |
| CN105521864A (en) * | 2016-02-15 | 2016-04-27 | 海安欣凯富机械科技有限公司 | Crusher |
| CN105689046A (en) * | 2016-02-23 | 2016-06-22 | 海安欣凯富机械科技有限公司 | Crushing machine |
| CN107413423A (en) * | 2017-05-11 | 2017-12-01 | 能诚集团有限公司 | A kind of jaw crusher |
| CN108339594A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of new bio experiment soil crushing apparatus |
| CN108344606A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of Bioexperiment soil crushing apparatus |
| CN108344605A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of modified Bioexperiment soil crushing apparatus |
| CN108722539A (en) * | 2018-05-31 | 2018-11-02 | 南京秦驰机械制造有限公司 | A kind of Furan Resin-Bonded Sand line vibration crushing regenerating machine |
| CN112547169A (en) * | 2020-12-24 | 2021-03-26 | 董国勤 | Stone crusher for open-air quarries |
| CN113275068A (en) * | 2020-07-02 | 2021-08-20 | 杭州大嘴兽科技有限公司 | Jaw crusher for solid waste treatment |
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| CN104668024A (en) * | 2013-11-30 | 2015-06-03 | 大连隆星新材料有限公司 | Petroleum wax crusher |
| CN105521864A (en) * | 2016-02-15 | 2016-04-27 | 海安欣凯富机械科技有限公司 | Crusher |
| CN105689046A (en) * | 2016-02-23 | 2016-06-22 | 海安欣凯富机械科技有限公司 | Crushing machine |
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| CN108339594A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of new bio experiment soil crushing apparatus |
| CN108344606A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of Bioexperiment soil crushing apparatus |
| CN108344605A (en) * | 2017-12-20 | 2018-07-31 | 广州正顺机械技术开发有限公司 | A kind of modified Bioexperiment soil crushing apparatus |
| CN108722539A (en) * | 2018-05-31 | 2018-11-02 | 南京秦驰机械制造有限公司 | A kind of Furan Resin-Bonded Sand line vibration crushing regenerating machine |
| CN113275068A (en) * | 2020-07-02 | 2021-08-20 | 杭州大嘴兽科技有限公司 | Jaw crusher for solid waste treatment |
| CN113275067A (en) * | 2020-07-02 | 2021-08-20 | 杭州大嘴兽科技有限公司 | Jaw crusher for solid waste treatment |
| CN112547169A (en) * | 2020-12-24 | 2021-03-26 | 董国勤 | Stone crusher for open-air quarries |
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Application publication date: 20130410 |