CN103629297B - Equipment mounting base wideband dynamic damping vibration damping equipment - Google Patents
Equipment mounting base wideband dynamic damping vibration damping equipment Download PDFInfo
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- CN103629297B CN103629297B CN201310680859.7A CN201310680859A CN103629297B CN 103629297 B CN103629297 B CN 103629297B CN 201310680859 A CN201310680859 A CN 201310680859A CN 103629297 B CN103629297 B CN 103629297B
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Abstract
The invention belongs to industry equipment noise reduction technology field, relate generally to a kind of plant bottom case wideband dynamic damping vibration damping equipment.A kind of plant bottom case wideband dynamic damping vibration damping equipment proposed is " mass-spring-damper " subtense angle adding a multistage mode of vibration in the multistage main vibrating system of wanted vibration damping; Described " mass-spring-damper " subtense angle of multistage mode of vibration is made up of continuous structure equivalent mass element (5) and elastic damping element (6), and the base support beam (4) in described multistage main vibrating system forms one with continuous structure equivalent mass element (5) by elastic damping unit (6).The present invention can realize the damping effect of low frequency (0-1kHz) and high frequency (1k-8kHz) wide frequency ranges to main vibrating system in limited space, thus in wideband (0-8kHz) scope, effectively realize the vibration control of equipment.
Description
Technical field
The invention belongs to industry equipment noise reduction technology field, relate generally to a kind of equipment mounting base wideband (0-8kHz) dynamic damping vibration damping equipment.
Background technique
The basic principle of dynamic shock absorber is in the main vibrating system of wanted vibration damping, add " quality-spring " subtense angle.When the natural frequency of additional " quality-spring " subtense angle overlaps with the resonant frequency of main vibrating system, " quality-spring " subtense angle and main vibrating system generation antiphase resonance, the vibration of subtense angle opposing main system, thus reduce the vibration amplitude of main vibrating system.
The schematic diagram of main vibrating system is as Fig. 1: quality is
, rigidity is
, a frequency be
, amplitude is
simple harmonic quantity external force excitation under, system does forced vibration, vibration amplitude A
0for:
（1）
In formula
for the natural frequency of vibration system;
represent that mass block is in non-simple harmonic quantity external force
the lower Static Correction occurred of effect.
Composition graphs 2, on the master system an additional dynamic shock absorber:
The quality of dynamic shock absorber is
, rigidity is
, then:
（2）
（3）
In above formula, A is principal oscillation systems force amplitude, and B is the forced vibration amplitude of dynamic shock absorber annex quality block.In formula
for the natural frequency of dynamic shock absorber.If the frequency of the frequency of excitation force and vibration damper is more close, then the amplitude of principal oscillation mass block is less.
Damping vibration attenuation utilizes the damping characteristic of structural damping or material damping absorb and consume vibrational energy, such as, replace the structures such as plain carbon steel making equipment base with high damping steel; Structurally stick visco-elastic damping material; Adopt compound high damping structural material manufacturing structure.Damping material has metal mold and nonmetal type, nonmetallic damping material is widely used in engineering, visco-elastic damping material is one of the most frequently used in nonmetallic damping material, its damping capacity mainly comes from high molecular polymer and obtains in-fighting, when the vibration force of alternation acts on viscoelastic polymer, polymeric inner produces tension and compression deformation, bending deflection or shear deformation, is dissipated because its vibration deformation energy of viscous characteristics changes into heat energy, reduces the vibration amplitude of system.This consumption size of its vibration deformation energy of material damping characteristic that utilizes not only depends on structural damping size, also depend on amplitude and the frequency of malformation energy, the frequency of alternation is high, the energy that unit time consumes is many, and the damping function thus in general under same damping condition is higher to dither effect.
In practical engineering application, the complex system that industry equipment and installation system are made up of multiple component, each parts are at least multistage mode of vibration continuous members, such as continuous beam, its mode of vibration kind comprises the tension and compression mode, torsion mode, mode of flexural vibration etc. of beam, for often kind of vibration mode can divide single order, second order.。。。。。Etc., for the complex system of multi-modes, the vibration frequency range of response of structure is the superposition of the multi-peak vibration of wideband multi-modes, and principal vibration energy comprises multi-frequency response component.Such as multicylinder compressor mounting base, base forms complicated multi-modes system by irregular section beam and installation connecting element and support etc., the vibration that its structure produces under equipment runs external force excitation is a superposition for complicated wideband multimodal response, if adopt single " quality-spring " subtense angle mode to the multimodal vibration control of equipment complexity, more difficult, especially for equipment working environment and installing space position limited when, this shortcoming is particularly outstanding, on the other hand, for damping vibration attenuation process, because its effectiveness in vibration suppression depends on the damping loss factor of material and the size of energy of deformation thereof, for low-frequency vibration mode relative high frequency mode, often effectiveness in vibration suppression is poor even to no effect.
Summary of the invention
The present invention is based on the theoretical and damping vibration attenuation mechanism of multi-freedom vibration systems and application technology, a kind of the multi-freedom degree dynamic damping vibration damping equipment and the wideband dynamic damping vibration damping equipment that are applied to equipment mounting base are proposed, the damping effect of low frequency (0-1kHz) and high frequency (1k-8kHz) wide frequency ranges can be realized main vibrating system in limited space, thus in wideband (0-8kHz) scope, effectively realize the vibration control of equipment.
The present invention realizes its goal of the invention and takes following technological scheme:
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described plant bottom case wideband dynamic damping vibration damping equipment is " mass-spring-damper " subtense angle adding a multistage mode of vibration in the multistage main vibrating system of wanted vibration damping; Described " mass-spring-damper " subtense angle of multistage mode of vibration is made up of continuous structure equivalent mass element and elastic damping element; Described continuous structure equivalent mass element has multiple mode of vibration, and described elastic damping element has multiple mode of vibration; Continuous structure equivalent mass element provides the quality in " mass-spring-damper " subtense angle, not only provide spring function in " mass-spring-damper " subtense angle by possessing elastic damping element that high damping and flexible material form simultaneously, the damping in " mass-spring-damper " subtense angle is provided simultaneously and forms " mass-spring-damper " subtense angle of multistage mode of vibration; Continuous structure equivalent mass element and elastic damping unit provide the multistage vibration modal frequency corresponding with main vibrating system; Described " mass-spring-damper " subtense angle is arranged in the base support beam in multistage main vibrating system; For ensureing vibrating fatigue effect, base support beam in described " mass-spring-damper " subtense angle and multistage main vibrating system forms one by elastic damping unit, and the base support beam in described multistage main vibrating system and continuous structure equivalent mass element pass through elastic damping unit and formed integrally.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described base support beam is: " mouth " type beam, " work " word beam, trough girder, tubulose.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described continuous structure equivalent mass element is " mouth " tee section beam, trough girder, " L " tee section beam, tubulose; Described continuous structure equivalent mass element is positioned at described base support beam.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, the material of described continuous structure equivalent mass element is identical with the material of base support beam, or the heavy metal different from the material of base support beam, alloy or composite material.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described elastic damping unit is made up of visco-elastic damping material, and described elastic damping unit is plate or band.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described elastic damping unit is combined into one by adhesive or sulfuration process and continuous structure equivalent mass element and base support beam; Or connect mechanically.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described elastic damping unit is paint pattern, is combined into one by pouring into curing mode and continuous structure equivalent mass element and base support beam.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, in described main vibrating system base support beam or " mass-spring-damper " subtense angle in continuous structure equivalent mass element on additional damping structure, in order to increase the damping effect of main vibrating system, thus other vibration peak caused because of forced excitation outside control master oscillator frequenc, this excitation comprises the excitation of equipment ground propagation or the unsteady state excitation of equipment operation.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described damping structure is the free damping structure that individual layer damping layer is formed, base support beam in the one side of described individual layer damping layer and main vibrating system or continuous structure equivalent mass element bonding, and another side is in free state without constraint.
A kind of plant bottom case wideband dynamic damping vibration damping equipment, described damping structure is the constrained damping structure be made up of damping layer and restraint layer, and described restraint layer is positioned at the skin of described damping layer; Described constrained damping structure is one deck, two-layer or multilayer.
The plant bottom case wideband dynamic damping vibration damping equipment that the present invention proposes, the damping effect of low frequency (0-1kHz) and high frequency (1k-8kHz) wide frequency ranges can be realized main vibrating system in limited space, thus in wideband (0-8kHz) scope, effectively realize the vibration control of equipment.
Accompanying drawing explanation
Fig. 1 is main vibrating system schematic diagram.
Fig. 2 adds a dynamic shock absorber schematic diagram on the master system.
Fig. 3 is an equipment mounting base schematic diagram.
Fig. 4 is plant bottom case wideband dynamic damping vibration damping equipment schematic diagram.
Fig. 5 ~ Figure 13 is the schematic cross-section of plant bottom case wideband dynamic damping vibration damping equipment.
Figure 14 ~ Figure 17 is the schematic diagram of additional damping structure.
Wherein: 1, equipment; 2, yielding support; 3, installed base; 4, base support beam; 5, continuous structure equivalent mass element; 6, elastic damping unit; 7, damping layer; 8, restraint layer.
Embodiment
With embodiment, the present invention is illustrated by reference to the accompanying drawings:
Fig. 3 is an equipment mounting base schematic diagram, and base support beam 4 is supported by yielding support 2 below, is provided with installed base 3 and equipment 1 above.
Figure 4 shows that plant bottom case wideband dynamic damping vibration damping equipment, be made up of base support beam 4, continuous structure equivalent mass element 5, elastic damping unit 6; Wherein, bonding or cold adhesive means forms one by elastic damping unit 6 for base support beam 4 and continuous structure equivalent mass element 5.
Implement modal test and theory pattern to base support beam 4, find out front 20 rank model frequency and condition shapes, the boundary conditions of test and analysis is identical with actual operating mode or close, and system comprises equipment 1 and yielding support 2 and installed base 3 etc.The frequency range analyzed contains main vibrating response peak value scope, and primary modal comprises Vertical direction, horizontal and longitudinal mode of flexural vibration, torsion mode etc., and often planting vibrational mode to each direction has single order, second order, three rank etc. multi-modes.Table 1 provides four cylinder compressor base support beams 4 of a kind of load-carrying about 1 ton, at two ends vertical stiffness be 3kN/mm yielding support 2 on finite element modal frequency analysis result (front 17 rank, covering frequence scope is to 2500Hz).
Table 1 model frequency analysis result
| Order | Frequency |
| 1 | 8.8 |
| 2 | 61.2 |
| 3 | 97.8 |
| 4 | 899.8 |
| 5 | 928.6 |
| 6 | 953.3 |
| 7 | 1048.8 |
| 8 | 1254.7 |
| 9 | 1527.1 |
| 10 | 1576.8 |
| 11 | 1581.3 |
| 12 | 1680.1 |
| 13 | 1758.0 |
| 14 | 1768.6 |
| 15 | 1925.9 |
| 16 | 1981.1 |
| 17 | 2116.9 |
Composition graphs 5 ~ Figure 13, adds " mass-spring-damper " subtense angle of a multistage mode of vibration in the multistage main vibrating system of wanted vibration damping; Described " mass-spring-damper " subtense angle of multistage mode of vibration is made up of continuous structure equivalent mass element 5 and elastic damping element 6; Described continuous structure equivalent mass element 5 has multiple mode of vibration, and described elastic damping element 6 has multiple mode of vibration; Continuous structure equivalent mass element 5 provides the quality in " mass-spring-damper " subtense angle, provides spring function in " mass-spring-damper " subtense angle and damping by possessing elastic damping element 6 that high damping and flexible material form simultaneously; Continuous structure equivalent mass element 5 and elastic damping unit 6 provide the multistage vibration modal frequency corresponding with main vibrating system; Described " mass-spring-damper " subtense angle is arranged in the base support beam 4 in multistage main vibrating system; Base support beam 4 in described " mass-spring-damper " subtense angle and multistage main vibrating system forms one by elastic damping unit 6, and the base support beam 4 in described multistage main vibrating system is formed integrally by elastic damping unit 6 with continuous structure equivalent mass element 5.Base support beam 4 is: " mouth " type beam, " work " word beam, trough girder, tubulose; Continuous structure equivalent mass element 5 is " mouth " tee section beam, trough girder, " L " tee section beam, tubulose; Continuous structure equivalent mass element 5 is positioned at described base support beam 4; The material of continuous structure equivalent mass element 5 is identical with the material of base support beam 4, or the heavy metal different from the material of base support beam, alloy or composite material.Elastic damping unit 6 is made up of visco-elastic damping material, model SA-3 damping plate (the << visco-elastic damping material >> that Luoyang boat Material Insitute specifically can be adopted to develop, National Defense Industry Press, in October, 2012,165 pages), described elastic damping unit 6 is plate or band, is combined into one by adhesive or sulfuration process and continuous structure equivalent mass element 5 and base support beam 4; Or connect mechanically.Elastic damping unit 6 also can be paint pattern, model PD-1 pouring type damping material (the << visco-elastic damping material >> that Luoyang boat Material Insitute specifically can be adopted to develop, National Defense Industry Press, in October, 2012,139 pages), be combined into one by pouring into curing mode and continuous structure equivalent mass element 5 and base support beam 4.
In described main vibrating system base support beam 4 or " mass-spring-damper " subtense angle in continuous structure equivalent mass element 5 on additional damping structure, in order to increase the damping effect of main vibrating system, thus other vibration peak caused because of forced excitation outside control master oscillator frequenc, this excitation comprises the excitation of equipment ground propagation or the unsteady state excitation of equipment operation.In conjunction with Figure 14, Figure 17, described damping structure is the free damping structure that individual layer damping layer 7 is formed, and one side and the continuous structure equivalent mass element 5 of described damping layer 7 are bonding, and another side is in free state without constraint.Described damping layer 7 is solid-state high viscoelastic damping materials, the model SA-3 damping plate of such as Luoyang boat Material Insitute's development, or pouring type damping material solidify to form, the model PD-1 pouring type damping material of such as Luoyang boat Material Insitute's development; In conjunction with Figure 15, Figure 16, described damping structure is the constrained damping structure be made up of damping layer 7 and restraint layer 8, and described restraint layer 8 is positioned at the skin of described damping layer 7; Described constrained damping structure is one deck, two-layer or multilayer; The thickness of every layer of damping layer 7 and restraint layer 8 designs as required respectively.Described restraint layer 8 is made up of the material that rigidity is high, the such as composite material of the metallic material such as aluminium alloy plate or steel plate or high rigidity.It is one deck, two-layer structural representation that Figure 15, Figure 16 provide constrained damping structure respectively.
Claims (10)
1. a plant bottom case wideband dynamic damping vibration damping equipment, is characterized in that: described plant bottom case wideband dynamic damping vibration damping equipment is " mass-spring-damper " subtense angle adding a multistage mode of vibration in the multistage main vibrating system of wanted vibration damping; Described " mass-spring-damper " subtense angle of multistage mode of vibration is made up of continuous structure equivalent mass element (5) and elastic damping unit (6); Described continuous structure equivalent mass element (5) has multiple mode of vibration, and described elastic damping unit (6) has multiple mode of vibration; Continuous structure equivalent mass element (5) provides the quality in " mass-spring-damper " subtense angle, not only provide spring function in " mass-spring-damper " subtense angle by possessing elastic damping unit (6) that high damping and flexible material form simultaneously, the damping in " mass-spring-damper " subtense angle is provided simultaneously and forms " mass-spring-damper " subtense angle of multistage mode of vibration; Continuous structure equivalent mass element (5) and elastic damping unit (6) provide the multistage vibration modal frequency corresponding with main vibrating system; Described " mass-spring-damper " subtense angle is arranged in the base support beam (4) in multistage main vibrating system; Base support beam (4) in described " mass-spring-damper " subtense angle and multistage main vibrating system forms one by elastic damping unit (6), and the base support beam (4) in described multistage main vibrating system is formed integrally by elastic damping unit (6) with continuous structure equivalent mass element (5).
2. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: described base support beam (4) is: " mouth " type beam, " work " word beam, trough girder, tubulose.
3. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: described continuous structure equivalent mass element (5) is " mouth " tee section beam, trough girder, " L " tee section beam, tubulose; Described continuous structure equivalent mass element (5) is positioned at described base support beam (4).
4. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: the material of described continuous structure equivalent mass element (5) is identical with the material of base support beam (4), or heavy metal, alloy or the composite material different from the material of base support beam (4).
5. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: described elastic damping unit (6) is made up of visco-elastic damping material, described elastic damping unit (6) is tabular or band shape.
6. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: described elastic damping unit (6) is combined into one by adhesive or sulfuration process and continuous structure equivalent mass element (5) and base support beam (4); Or connect mechanically.
7. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 1, it is characterized in that: described elastic damping unit (6) is paint pattern, being combined into one by pouring into curing mode and continuous structure equivalent mass element (5) and base support beam (4).
8. according to the plant bottom case wideband dynamic damping vibration damping equipment described in claim 1 or 2 or 3 or 4, it is characterized in that: in described main vibrating system base support beam (4) or " mass-spring-damper " subtense angle in the upper additional damping structure of continuous structure equivalent mass element (5), in order to increase the damping effect of main vibrating system, thus other vibration peak caused because of forced excitation outside control master oscillator frequenc, this excitation comprises the excitation of equipment ground propagation or the unsteady state excitation of equipment operation.
9. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 8, it is characterized in that: described damping structure is the free damping structure that individual layer damping layer (7) is formed, base support beam (4) in the one side of described individual layer damping layer (7) and main vibrating system or continuous structure equivalent mass element (5) bonding, and another side is in free state without constraint.
10. according to plant bottom case wideband dynamic damping vibration damping equipment according to claim 8, it is characterized in that: described damping structure is the constrained damping structure be made up of damping layer (7) and restraint layer (8), and described restraint layer (8) is positioned at the skin of described damping layer (7); Described constrained damping structure is one or more layers.
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| CN105443649B (en) * | 2016-01-15 | 2017-08-25 | 重庆大学 | High resistant damping magnesium alloy vibration-proof structure and its application |
| CN105840711B (en) * | 2016-05-27 | 2017-11-21 | 哈尔滨工程大学 | A kind of metal isolator for supporting underwater sound insulation baffle |
| CN109631172B (en) * | 2018-10-30 | 2021-06-22 | 青岛海尔空调电子有限公司 | Air conditioner vibration reduction method and system |
| CN110441401B (en) * | 2019-08-22 | 2022-03-15 | 陈方 | Method and device for testing damping coefficient of additive manufacturing material structure |
| CN110714372A (en) * | 2019-11-15 | 2020-01-21 | 中铁二院工程集团有限责任公司 | Dynamic vibration absorption and energy consumption device for delaying development of rail corrugation |
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| CN201973166U (en) * | 2011-03-10 | 2011-09-14 | 哈尔滨工程大学 | Damping structure with small mass ratio |
| CN202468833U (en) * | 2012-02-28 | 2012-10-03 | 长春东方水泵有限公司 | Vibration damping device of mechanical equipment |
| CN103343414A (en) * | 2013-07-22 | 2013-10-09 | 江苏万工科技集团有限公司 | Heald frame bending mode control device |
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| JP4503493B2 (en) * | 2005-06-08 | 2010-07-14 | ヤクモ株式会社 | Thin vibration damping device and vibration damping system |
| TW201115047A (en) * | 2009-05-07 | 2011-05-01 | Nikon Corp | Vibration control apparatus, vibration control method, exposure apparatus, and device manufacturing method |
| JP5584913B2 (en) * | 2010-03-19 | 2014-09-10 | 公益財団法人鉄道総合技術研究所 | Floor structure |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201973166U (en) * | 2011-03-10 | 2011-09-14 | 哈尔滨工程大学 | Damping structure with small mass ratio |
| CN202468833U (en) * | 2012-02-28 | 2012-10-03 | 长春东方水泵有限公司 | Vibration damping device of mechanical equipment |
| CN103343414A (en) * | 2013-07-22 | 2013-10-09 | 江苏万工科技集团有限公司 | Heald frame bending mode control device |
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