CN105665269A - Elastic device used for vibrating screen and vibrating screen - Google Patents
Elastic device used for vibrating screen and vibrating screen Download PDFInfo
- Publication number
- CN105665269A CN105665269A CN201410667584.8A CN201410667584A CN105665269A CN 105665269 A CN105665269 A CN 105665269A CN 201410667584 A CN201410667584 A CN 201410667584A CN 105665269 A CN105665269 A CN 105665269A
- Authority
- CN
- China
- Prior art keywords
- vibrosieve
- elastic device
- metal spring
- elastic
- spring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002184 metal Substances 0.000 claims abstract description 57
- 230000007246 mechanism Effects 0.000 claims abstract description 36
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 claims description 20
- 238000000034 method Methods 0.000 abstract description 7
- 230000008569 process Effects 0.000 abstract description 7
- 238000013016 damping Methods 0.000 abstract description 4
- 238000002955 isolation Methods 0.000 abstract description 3
- 229910000831 Steel Inorganic materials 0.000 description 7
- 239000010959 steel Substances 0.000 description 7
- UQMRAFJOBWOFNS-UHFFFAOYSA-N butyl 2-(2,4-dichlorophenoxy)acetate Chemical compound CCCCOC(=O)COC1=CC=C(Cl)C=C1Cl UQMRAFJOBWOFNS-UHFFFAOYSA-N 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000005284 excitation Effects 0.000 description 3
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000004570 mortar (masonry) Substances 0.000 description 2
- 239000004576 sand Substances 0.000 description 2
- 238000012216 screening Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 229920001967 Metal rubber Polymers 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000009527 percussion Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Landscapes
- Vibration Prevention Devices (AREA)
- Combined Means For Separation Of Solids (AREA)
Abstract
The invention provides an elastic device used for a vibrating screen and the vibrating screen. The elastic device is used for being connected between a screen body and a base of the vibrating screen and comprises a metal spring, a limiting mechanism used for variable parameters and an elastic mechanism, wherein the rigidity and the damping coefficient of the elastic mechanism are both larger than those of the metal spring. The limiting mechanism used for the variable parameters is fixed to the metal spring, and in addition, the limiting mechanism used for the variable parameters is arranged to repeatedly make contact with the elastic mechanism only when the amplitude of the metal spring exceeds a preset value. According to the technical scheme of the elastic device used for the vibrating screen and the vibrating screen, the vibrating screen can give play to good vibration isolation performance when being in a normal working state; when resonance occurs in the starting or stopping process of the vibrating screen, the rigidity and the damping coefficient of the vibrating screen are both improved remarkably, accordingly, the resonance is effectively inhibited, and impact on a machine frame, the screen body and other parts is reduced.
Description
Technical field
The present invention relates to screening plant field, in particular to a kind of elastic device for vibrosieve and vibrosieve.
Background technology
Vibrosieve is widely used in screening field, such as dry-mixed mortar plant, Machine-made Sand station etc. In vibrosieve, for coordinating the vibration displacement between sieve nest and the pedestal bottom sieve nest, reduce simultaneously and join the part active force to pedestal that shakes, be generally adopted support spring to connect sieve nest and pedestal. According to the requirement of dry-mixed mortar plant and Machine-made Sand station integral layout, vibrosieve is often arranged in steel structure frame, and the active force of pedestal is transferred to ground by steel structure frame by it. Being subject to the restriction of frame carrying, this mounting means is had higher requirement to supporting spring, it is necessary to reduce the vibrosieve active force to steel structure frame as far as possible.
Fig. 1 illustrates the structural representation of vibrosieve of the prior art, and wherein, the sieve nest 1 of vibrosieve is arranged on the pedestal 2 bottom vibrosieve by multiple support springs 3,4 and 5 etc. In the running of vibrosieve, motor driving eccentric block to rotate, thus exporting exciting force, excitation sieve nest 1 is by predetermined amplitude and frequency vibration, thus reaching the function of vibrosieve. Now, support spring 3,4 and 5 etc. except supporting sieve nest structure, also there is the function of vibration isolation. Support spring 3,4 and 5 and generally have two kinds of ways of realization, be the metal spring 6 shown in Fig. 2 and the rubber spring 7 shown in Fig. 3 respectively. But, in reducing the vibrosieve active force to steel structure frame, metal spring and rubber spring are respectively arranged with feature: metal spring is when vibrosieve steady operation, the vibrosieve active force to steel structure frame can be isolated preferably, but at startup and the stop phase of vibrosieve, particularly when shock electric machine is by system resonance point, it may appear that bigger vibration, namely covibration is produced, the impact of frame and sieve nest is bigger; The problem that when rubber spring can overcome resonance point, system vibration is excessive, but when vibrosieve steady operation, its vibration isolating effect is poor, and the active force of steel structure frame is significantly greater than situation when using metal spring by vibrosieve.Generally, can only accept or reject as the case may be when designing vibrosieve, select to use metal spring or rubber spring, be difficult to take into account each stage of vibrosieve simultaneously. Therefore, it is necessary to improve for the drawbacks described above existed in prior art.
Summary of the invention
Present invention is primarily targeted at a kind of elastic device for vibrosieve of offer and vibrosieve so that this vibrosieve starting and the stop phase reduction impact to the parts such as frame and sieve nest, can play again good vibration isolation function when steady operation.
To achieve these goals, according to an aspect of the present invention, provide a kind of elastic device for vibrosieve, described elastic device is for being connected between sieve nest and the pedestal of described vibrosieve, and described elastic device includes metal spring, variable element position-limit mechanism and rigidity and damped coefficient is all higher than the elastic mechanism of described metal spring; Wherein, described variable element position-limit mechanism is fixedly installed on described metal spring, and, described variable element position-limit mechanism is set to only just repeatedly contact with described elastic mechanism when the amplitude of described metal spring exceedes preset value.
Further, described elastic device also includes being arranged on the top installed surface of described metal spring upper end and being arranged on the bottom installed surface of described metal spring lower end, described top installed surface is connected with the sieve nest of described vibrosieve, and described bottom installed surface is connected with described pedestal.
Further, described elastic device also includes protection shell, and the bottom surface of described protection shell is connected to described bottom installed surface, and described protection shell has the inner chamber for holding described metal spring, described variable element position-limit mechanism and described elastic mechanism.
Further, described elastic mechanism is arranged on the inwall of described inner chamber.
Further, described variable element position-limit mechanism is the limited block being fixedly connected on described metal spring.
Further, described elastic mechanism is rubber spring.
Further, described rubber spring is one, and is arranged on above or below described limited block.
Further, described rubber spring is multiple, and is separately positioned on above and below described limited block.
Further, described rubber spring is multiple, and arranges in parallel to each other.
According to a further aspect in the invention, it is provided that a kind of vibrosieve, including sieve nest, pedestal and connect described sieve nest and the resilient supporting unit of described pedestal, described resilient supporting unit is the elastic device for vibrosieve according to any one of aforementioned aspect.
Application technical scheme, when vibrosieve is in normal operating conditions, it is possible to play good anti-vibration performance; When vibrosieve occurs to resonate in starting or stoping process, its rigidity and damped coefficient all can significantly rise, thus effectively suppressing resonance, reduce the impact to the parts such as sieve nest and frame.
Accompanying drawing explanation
The Figure of description constituting the part of the application is used for providing a further understanding of the present invention, and the schematic description and description of the present invention is used for explaining the present invention, is not intended that inappropriate limitation of the present invention. In the accompanying drawings:
Fig. 1 illustrates the structural representation of vibrosieve of the prior art;
Fig. 2 illustrates the structural representation of metal spring of the prior art;
Fig. 3 illustrates the structural representation of rubber spring of the prior art;
Fig. 4 illustrates the change curve of vibration transmissibility T under different damping coefficient;
Fig. 5 illustrates the rigidity comparison diagram of metal spring and rubber spring;
Fig. 6 illustrates the damped coefficient comparison diagram of metal spring and rubber spring;
Fig. 7 illustrates the schematic diagram of the elastic device for vibrosieve according to embodiments of the present invention;
Fig. 8 illustrates the stiffness characteristics figure of the elastic device for vibrosieve according to embodiments of the present invention.
Detailed description of the invention
It should be noted that when not conflicting, the embodiment in the application and the feature in embodiment can be mutually combined. Describe the present invention below with reference to the accompanying drawings and in conjunction with the embodiments in detail.
Generally, it is considered that in the running of vibrosieve, for reducing the requirement to frame steel construction, be transferred to the dynamic loading on the pedestal bottom vibrosieve more low more good. In long-term engineering practice, applicant finds with verification experimental verification repeatedly through careful observing: can describe dynamic loading with vibration transmissibility T and be transferred to the degree of pedestal; It is to say, vibration transmissibility T is more low, then it is transferred to the dynamic loading on pedestal more few.
The expression formula of vibration transmissibility T is:
Wherein, ξ is damped coefficient, and f is excitation force frequency, fnFor system frequency.
Further, fnMeet:
Wherein, k is the rigidity supporting spring, and m is the quality of vibrosieve.
In order to more clearly observe the variation tendency of vibration transmissibility T, it is possible to the expression formula of vibration transmissibility T is drawn and becomes the change curve of vibration transmissibility T under different damping coefficient, as shown in Figure 4. Wherein, the vertical coordinate of Fig. 4 is vibration transmissibility T, and abscissa is frequency ratio f/fn5 curves being numbered 01 to 05 represent that (the damped coefficient ξ that damped coefficient ξ is 0.2,03 line that damped coefficient ξ is 0.5,02 line of 01 line is 0.1 to different damped coefficient ξ, the damped coefficient ξ that damped coefficient ξ is 0.05,05 line of 04 line is 0.01).
Observe Fig. 4 it can be seen that allow in interval Q in the design supporting spring, frequency ratio f/fnMore high, damped coefficient ξ is more low, then vibration transmissibility T is also more low. Considering for the vibrosieve determined, its excitation force frequency f is fixing, by aforementioned fnExpression formula it can be seen that support spring k rigidity more low, system frequency fnAlso more low, then frequency ratio f/fnWill be more high, therefore vibration transmissibility T is also more low. In other words, for supporting spring, rigidity k and damped coefficient ξ is more low, and vibration transmissibility T is also more low, and vibration isolating effect is more good.
According to above-mentioned discovery, as shown in Figure 5 and Figure 6, the rigidity of metal spring and rubber spring and damped coefficient have been contrasted by applicant again. Fig. 5 illustrates the rigidity comparison diagram of metal spring and rubber spring, and wherein abscissa is displacement D, and vertical coordinate is rigidity k. Fig. 6 illustrates the damped coefficient comparison diagram of metal spring and rubber spring, and wherein abscissa is displacement D, and vertical coordinate is damped coefficient ξ.
As shown in Figure 5, the rigidity k of metal spring S2mRigidity k lower than rubber spring S1r. It will be appreciated from fig. 6 that the damped coefficient ξ of metal spring S2mDamped coefficient ξ lower than rubber spring S1r. Therefore, metal spring has good anti-vibration performance. But, startup and stop phase in vibrosieve, owing to the rigidity k and damped coefficient ξ of metal spring are relatively low, this is easily caused vibrosieve and covibration occurs, there is violent vibration, thus bringing very big shock loading to the parts such as frame and sieve nest, now according to rubber spring, owing to its rigidity k and damped coefficient ξ is higher, therefore can effectively suppress vibrosieve in the covibration started and during stop phase, but its during normal use vibration isolating effect (when namely vibrosieve is in steady operation) is poorer than metal spring.
In sum, applicant is found by above-mentioned analysis, owing to rigidity and the damped coefficient of rubber spring are above metal spring, startup and stop phase in vibrosieve, rubber spring suppresses resonance, prevents the ability impacted to be better than metal-rubber, but at the serviceability limit stage of vibrosieve, owing to rigidity and the damped coefficient of metal spring are below rubber spring, thus vibration transmissibility T is relatively low, therefore the anti-vibration performance of metal spring is better than rubber spring.
In order to solve problems of the prior art, the invention provides a kind of elastic device for vibrosieve, described elastic device is for being connected between sieve nest and the pedestal of described vibrosieve, and described elastic device includes metal spring, variable element position-limit mechanism and rigidity and damped coefficient is all higher than the elastic mechanism of described metal spring; Wherein, described variable element position-limit mechanism is fixedly installed on described metal spring, and, described variable element position-limit mechanism is set to only just repeatedly contact with described elastic mechanism when the amplitude of described metal spring exceedes preset value.
According to technical scheme, when vibrosieve is in normal operating conditions, rigidity and the damped coefficient of this elastic device are functionally identical to metal spring, therefore, it is possible to play good anti-vibration performance; When vibrosieve occurs to resonate in starting or stoping process, the rigidity of the elastic device of the present embodiment and damped coefficient all can significantly rise, and reach the level of approximate rubber spring, thus effectively suppressing resonance, reduce the impact to the parts such as frame and sieve nest.
Fig. 7 illustrates the schematic diagram of the elastic device for vibrosieve according to embodiments of the present invention. As it is shown in fig. 7, the described elastic device for vibrosieve includes metal spring 10, limited block 20, rubber spring 30, protection shell 40, upper installed surface 50 and lower installed surface 60.
Wherein, upper installed surface 50 is arranged on the upper end of metal spring 10, and lower installed surface 60 is arranged on the lower end of metal spring 10. Upper installed surface 50 and lower installed surface 60 are conducive to convenient and are stably installed this elastic device. Thus, by upper installed surface 50 and lower installed surface 60, the elastic device of this embodiment may be mounted between vibrosieve and pedestal, and this is similar with the mounting means supporting spring in prior art.
Referring to Fig. 7, the bottom surface of protection shell 40 is connected to lower installed surface 60, namely descends the upper surface of installed surface 60 to link together with the bottom surface of protection shell 40. Protection shell 40 has inner chamber, and the parts such as metal spring 10, limited block 20 and rubber spring 30 are arranged in this inner chamber, therefore protection shell 40 serves the effect protecting these parts. Preferably, rubber spring 30 can be conveniently placed on the inwall of this inner chamber.
The cross section of limited block 20 is not limit, and is fixedly connected on metal spring 10. Preferably, limited block 20 is fixedly connected on the superposed inoperative section of metal spring 10, to reduce the impact of the normal operation on metal spring 10 as far as possible.
Further, in fig. 7 it is shown that polylith rubber spring 30, they are arranged on the inwall of the inner chamber of protection shell 40 in parallel to each other, and are distributed in the upper and lower both sides of limited block 20. In upside or the downside of limited block 20, arrange evenly and at intervals between each rubber spring 30.
During use, when vibrosieve is in normal operating conditions, its amplitude is less, and therefore limited block 20 will not touch rubber spring 30, and now vibrosieve is provided resiliency supported by metal spring 10 completely, has played good anti-vibration performance;When vibrosieve occurs to resonate in starting or stoping process, its amplitude increases, limited block 20 is contacted with rubber spring 30 repeatedly, thus adding rigidity and the damped coefficient of whole resilient supporting unit, reach the support effect of rubber like spring, inhibit the resonance of vibrosieve, reduce the percussion of the sieve nest to vibrosieve and frame etc.
Certainly, rubber spring 30 can also only arrange one piece, it is possible to is positioned at above or below limited block 20, such that it is able to flexible arrangement rubber spring simplify the structure of elastic mechanism. Rubber spring 30 is it can also be provided that many block gaps are arranged, and lay respectively at above or below limited block 20, further, can be parallel to each other between them, thus, when the amplitude of metal spring 10 reaches to a certain degree, the number of the rubber spring 30 that limited block 20 touches is different, rigidity and damped coefficient that now whole elastic device shows also there occurs change, better adapted to the vibrosieve vibrational state in the different operating stage.
Fig. 8 illustrates the stiffness characteristics figure of the elastic device for vibrosieve according to embodiments of the present invention, can explain the operating characteristic of the elastic device of the present embodiment principle better, and wherein abscissa D represents displacement, and vertical coordinate S represents elastic force.
As shown in Figure 8, when vibrosieve is in normal operating conditions, its amplitude is within screen(ing) machine working amplitude X0, and now limited block 20 will not touch variable element rubber spring 30, therefore vibrosieve is provided support by metal spring 10 completely, and support stiffness is the stiffness K 0 of metal spring. When vibrosieve occurs to resonate in starting or stoping process, its amplitude increases, apparently higher than screen(ing) machine working amplitude X0, limited block 20 is contacted with variable element rubber spring 30 repeatedly, thus adding the rigidity of whole resilient supporting unit to K2 so that whole resilient supporting unit has an overall equivalent stiffness K1.
In like manner, when vibrosieve is in normal operating conditions, the damped coefficient of the elastic device that the present embodiment provides is equal to the damped coefficient of metal spring, and when vibrosieve occurs to resonate in starting or stoping process, the damped coefficient of this elastic device also can dramatically increase, reach approximately the damped coefficient level of rubber spring, thus, whole elastic device is equivalent to the damped coefficient with two changes.
To sum up, when vibrosieve is in normal operating conditions, rigidity and the damped coefficient of the elastic device of the present embodiment are equal to metal spring, therefore, it is possible to play good anti-vibration performance; When vibrosieve occurs to resonate in starting or stoping process, the rigidity of the elastic device of the present embodiment and damped coefficient all can significantly rise, reach the level of approximate rubber spring, thus effectively suppressing resonance, reduce the impact to the parts such as frame and sieve nest, therefore, the elastic device of the present embodiment can take into account the vibrosieve feature in different phase.
Above describe the elastic device for vibrosieve of the present invention according to embodiment, but this mounting structure is not limited in the parts described in this embodiment and/or annexation. Such as, variable element position-limit mechanism is not limited to the limited block shown in embodiment, it is possible to be any mechanism/parts that can play position-limiting action; Elastic mechanism is also not necessarily limited to the rubber spring shown in embodiment, it is possible to be the various mechanism/parts that can provide elastic force; Additionally, the quantity of rubber spring and arrangement are also not necessarily limited to shown in this embodiment, it is possible to need according to the change of rigidity and damped coefficient and arrange.
Present invention also offers a kind of vibrosieve, including sieve nest, pedestal and connect described sieve nest and the resilient supporting unit of described pedestal, described resilient supporting unit is the elastic device for vibrosieve described in previous embodiment and modification thereof.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations. All within the spirit and principles in the present invention, any amendment of making, equivalent replacement, improvement etc., should be included within protection scope of the present invention.
Claims (10)
1. the elastic device for vibrosieve, described elastic device is for being connected between sieve nest and the pedestal of described vibrosieve, it is characterized in that, described elastic device includes metal spring, variable element position-limit mechanism and rigidity and damped coefficient is all higher than the elastic mechanism of described metal spring; Wherein, described variable element position-limit mechanism is fixedly installed on described metal spring, and, described variable element position-limit mechanism is set to only just repeatedly contact with described elastic mechanism when the amplitude of described metal spring exceedes preset value.
2. the elastic device for vibrosieve according to claim 1, it is characterized in that, described elastic device also includes being arranged on the top installed surface of described metal spring upper end and being arranged on the bottom installed surface of described metal spring lower end, described top installed surface is connected with the sieve nest of described vibrosieve, and described bottom installed surface is connected with described pedestal.
3. the elastic device for vibrosieve according to claim 2; it is characterized in that; described elastic device also includes protection shell; the bottom surface of described protection shell is connected to described bottom installed surface, and described protection shell has the inner chamber for holding described metal spring, described variable element position-limit mechanism and described elastic mechanism.
4. the elastic device for vibrosieve according to claim 3, it is characterised in that described elastic mechanism is arranged on the inwall of described inner chamber.
5. the elastic device for vibrosieve according to any one of claim 1 to 4, it is characterised in that described variable element position-limit mechanism is the limited block being fixedly connected on described metal spring.
6. the elastic device for vibrosieve according to claim 5, it is characterised in that described elastic mechanism is rubber spring.
7. the elastic device for vibrosieve according to claim 6, it is characterised in that described rubber spring is, and is arranged on above or below described limited block.
8. the elastic device for vibrosieve according to claim 6, it is characterised in that described rubber spring is multiple, and is separately positioned on above and below described limited block.
9. the elastic device for vibrosieve according to claim 6, it is characterised in that described rubber spring is multiple, and arranges in parallel to each other.
10. a vibrosieve, including sieve nest, pedestal and connect described sieve nest and the resilient supporting unit of described pedestal, it is characterised in that described resilient supporting unit is the elastic device for vibrosieve according to any one of claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410667584.8A CN105665269B (en) | 2014-11-20 | 2014-11-20 | Elastic device and vibrating screen for vibrating screen |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410667584.8A CN105665269B (en) | 2014-11-20 | 2014-11-20 | Elastic device and vibrating screen for vibrating screen |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105665269A true CN105665269A (en) | 2016-06-15 |
| CN105665269B CN105665269B (en) | 2019-08-06 |
Family
ID=56957907
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410667584.8A Active CN105665269B (en) | 2014-11-20 | 2014-11-20 | Elastic device and vibrating screen for vibrating screen |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105665269B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106523567A (en) * | 2016-12-26 | 2017-03-22 | 徐工集团工程机械有限公司 | Vibration reducing device, vibration screen and asphalt mixing station |
| CN108397510A (en) * | 2018-03-28 | 2018-08-14 | 深圳市德达康健股份有限公司 | A kind of vibration absorber of oxygenerator compressor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2021679C1 (en) * | 1991-03-11 | 1994-10-30 | Красноярский государственный аграрный университет | Support of grain-cleaning machine |
| CN2491135Y (en) * | 2001-08-28 | 2002-05-15 | 罗嘉洵 | Rhombus ladder type vibrating screen |
| CN201261011Y (en) * | 2008-07-25 | 2009-06-24 | 东北大学 | Anti-resonance vibrating screen |
| CN201739410U (en) * | 2010-08-03 | 2011-02-09 | 鞍山重型矿山机器股份有限公司 | Vibration-reducing spring for vibrating screen |
| CN102878240A (en) * | 2012-10-15 | 2013-01-16 | 扬州龙鑫机械有限公司 | Intelligent hydraulic frictional damping device |
| CN102873024A (en) * | 2012-09-17 | 2013-01-16 | 东北大学 | Elliptic or circular motion antiresonance vibrating screen |
| CN202700802U (en) * | 2012-07-17 | 2013-01-30 | 鞍山重型矿山机器股份有限公司 | Spiral spring device with damping and sound attenuation functions |
-
2014
- 2014-11-20 CN CN201410667584.8A patent/CN105665269B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2021679C1 (en) * | 1991-03-11 | 1994-10-30 | Красноярский государственный аграрный университет | Support of grain-cleaning machine |
| CN2491135Y (en) * | 2001-08-28 | 2002-05-15 | 罗嘉洵 | Rhombus ladder type vibrating screen |
| CN201261011Y (en) * | 2008-07-25 | 2009-06-24 | 东北大学 | Anti-resonance vibrating screen |
| CN201739410U (en) * | 2010-08-03 | 2011-02-09 | 鞍山重型矿山机器股份有限公司 | Vibration-reducing spring for vibrating screen |
| CN202700802U (en) * | 2012-07-17 | 2013-01-30 | 鞍山重型矿山机器股份有限公司 | Spiral spring device with damping and sound attenuation functions |
| CN102873024A (en) * | 2012-09-17 | 2013-01-16 | 东北大学 | Elliptic or circular motion antiresonance vibrating screen |
| CN102878240A (en) * | 2012-10-15 | 2013-01-16 | 扬州龙鑫机械有限公司 | Intelligent hydraulic frictional damping device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106523567A (en) * | 2016-12-26 | 2017-03-22 | 徐工集团工程机械有限公司 | Vibration reducing device, vibration screen and asphalt mixing station |
| CN106523567B (en) * | 2016-12-26 | 2019-01-25 | 徐工集团工程机械有限公司 | Vibration absorber, vibrating screen and asphalt blending station |
| CN108397510A (en) * | 2018-03-28 | 2018-08-14 | 深圳市德达康健股份有限公司 | A kind of vibration absorber of oxygenerator compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105665269B (en) | 2019-08-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| RU2288388C1 (en) | Net beaded insulator | |
| KR101303562B1 (en) | Air damping mount | |
| JPS6054537B2 (en) | Rubber bearing device with air damping | |
| US20060117812A1 (en) | Washing machine having dynamic vibration absorber | |
| JPH04358916A (en) | Upper installation structure for strut-type suspension | |
| JP2003106370A (en) | Damping device | |
| JPH086778B2 (en) | Hydraulic buffer type cylindrical anti-vibration rubber seat | |
| US8398060B2 (en) | Vibration absorber for a vehicle suspension spring | |
| JP2007100929A (en) | Vibration reducing device | |
| US8151954B2 (en) | Vibration damping apparatus | |
| CN105665269A (en) | Elastic device used for vibrating screen and vibrating screen | |
| JPS62101937A (en) | Improvement of hydraulic type shock-absorbing supporter | |
| JP2017113310A (en) | Washing machine | |
| RU2618350C1 (en) | Vibro-isolating system of kochetov for machine tools | |
| JP7072543B2 (en) | Anti-vibration unit mounting structure | |
| US10914356B2 (en) | Hydraulically damping mount | |
| JP2015098267A (en) | Spare tire supporter | |
| JP3107321B2 (en) | Operator cabin elastic support structure for construction machinery | |
| JPH0434245A (en) | Vibration removing device | |
| JPH04230477A (en) | Torsional vibration damper | |
| CN106678236A (en) | Spring shock absorber | |
| RU2301919C1 (en) | Vibration isolating rubber base | |
| JP2004116654A (en) | Dynamic damper | |
| JP2008202608A (en) | Vibration damping device | |
| CN211145223U (en) | Damping device of petrochemical instrument |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Application publication date: 20160615 Assignee: HUNAN ZOOMLION CONCRETE MACHINERY STATION EQUIPMENT CO.,LTD. Assignor: ZOOMLION HEAVY INDUSTRY SCIENCE AND TECHNOLOGY Co.,Ltd. Contract record no.: X2023980042761 Denomination of invention: Elastic device and vibrating screen for vibrating screen Granted publication date: 20190806 License type: Common License Record date: 20231010 |
|
| EE01 | Entry into force of recordation of patent licensing contract |