CN113074204B - Anti-impact ultralow frequency vibration isolator - Google Patents
Anti-impact ultralow frequency vibration isolator Download PDFInfo
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- CN113074204B CN113074204B CN202110314108.8A CN202110314108A CN113074204B CN 113074204 B CN113074204 B CN 113074204B CN 202110314108 A CN202110314108 A CN 202110314108A CN 113074204 B CN113074204 B CN 113074204B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
- F16F7/082—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other and characterised by damping force adjustment means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
- F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/04—Friction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/066—Variable stiffness
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses an anti-impact ultralow frequency vibration isolator, and belongs to the technical field of ultralow frequency vibration isolators. The device comprises a shell, a bottom plate, a top plate, a lifting column and a device platform; a first lifting plate, an impact spiral spring, a second lifting plate and a tension and compression spiral spring are sequentially arranged in the shell from top to bottom; the tension and compression spiral spring is connected with the second lifting plate and the bottom plate; the first lifting plate is fixedly arranged at the lower end of the lifting column; the first compression springs and the second compression springs with the same rigidity are symmetrically arranged on the left side and the right side of the first lifting plate relative to the lifting column, and the first connecting rods and the second connecting rods with the same structures are symmetrically hinged on the left side and the right side of the bottom of the first lifting plate relative to the lifting column. The invention is a shock-resistant ultralow frequency vibration isolator which has simple and reasonable results, has the ultralow frequency characteristic of vibration isolation, can quickly absorb shock energy in an impact environment and does not have obvious impact and large deformation.
Description
Technical Field
The invention mainly relates to the technical field of ultralow frequency vibration isolators, in particular to an impact-resistant ultralow frequency vibration isolator.
Background
The lower the frequency of the vibration isolator system, the better the vibration isolation generally, and therefore ultra low frequency vibration isolators are receiving more and more extensive attention. However, the rigidity of the ultra-low frequency vibration isolator is very small, so that large displacement is easy to occur under the action of large exciting force, and the application occasions of the ultra-low frequency vibration isolator are limited. The ultra-low frequency vibration isolator in the prior art is easy to generate larger displacement in an impact environment, and even the vibration isolator is damaged due to too large displacement. Therefore, the design of the ultra-low frequency vibration isolator which can absorb impact energy and resist large deformation of impact has important significance.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: aiming at the technical problems in the prior art, the invention provides the anti-impact ultralow frequency vibration isolator which has simple and reasonable results, has the ultralow frequency characteristic of vibration isolation, can quickly absorb impact energy in an impact environment, effectively prevents large displacement and has higher vibration isolation safety performance.
In order to solve the problems, the solution proposed by the invention is as follows: the shock-resistant ultralow frequency vibration isolator comprises a shell, a bottom plate and a top plate which are respectively arranged at two ends of the shell, a lifting column which penetrates through the top plate and can freely lift, and an equipment platform which is arranged at the top of the lifting column and used for installing vibration-isolated equipment.
The first lifting plate, the impact spiral spring, the second lifting plate and the tension and compression spiral spring are sequentially arranged in the shell from top to bottom; the tension and compression spiral spring is connected with the second lifting plate and the bottom plate;
the first lifting plate is fixedly arranged at the lower end of the lifting column; first compression springs and second compression springs with the same rigidity are symmetrically arranged on the left side and the right side of the first lifting plate relative to the lifting column, and first connecting rods and second connecting rods with the same structures are symmetrically hinged on the left side and the right side of the bottom of the first lifting plate relative to the lifting column; the left end of the first compression-resistant spring is connected with the shell, the right end of the first compression-resistant spring is connected with the lifting plate, and the height of the left end of the first compression-resistant spring is lower than that of the right end of the first compression-resistant spring; the right end of the second compression spring is connected with the shell, the left end of the second compression spring is connected with the lifting plate, and the height of the right end of the second compression spring is lower than that of the left end of the second compression spring;
a first damping slide block and a second damping slide block which are symmetrical relative to the lifting column are arranged on the second lifting plate in a sliding manner; the first damping sliding block is hinged with the lower end of the first connecting rod, and the second damping sliding block is hinged with the lower end of the second connecting rod; two ends of the impact spiral spring are respectively connected with the first lifting plate and the second lifting plate;
the first connecting rod is inclined at a small angle with the horizontal direction, and the first compression-resistant spring is inclined with the horizontal direction.
Further, the compression rigidity of the impact coil spring is not less than five times the rigidity of the tension and compression coil spring.
Further, when the first compression-resistant spring is inclined to the horizontal direction, the tension-compression coil spring is in a compressed state.
Further, the included angle between the first connecting rod and the horizontal direction is theta, and the range of theta is 0-20 degrees.
Further, after the vibration-isolated equipment is installed on the equipment platform, the axes of the first compression springs and the second compression springs are collinear along the horizontal direction.
Furthermore, the end faces, close to the shell, of the first damping slide block and the second damping slide block are provided with rough surfaces.
Furthermore, after the vibration-isolated equipment is installed on the equipment platform, clearance fit is formed between the first damping slide block and the shell and between the second damping slide block and the shell.
Compared with the prior art, the invention has the following advantages and beneficial effects: according to the shock-resistant ultralow frequency vibration isolator, when the first compression spring and the second compression spring are horizontally collinear, the static balance state is achieved after vibration isolation equipment is installed on an equipment platform, and therefore the shock-resistant ultralow frequency vibration isolator has the characteristics of ultralow rigidity and ultralow frequency under the action of small exciting force; in addition, the invention is also provided with a high-rigidity impact spiral spring, and the first damping slide block and the second damping slide block are driven to generate corresponding friction damping force under the action of larger exciting force, so that the vertical displacement of the second lifting plate and the second lifting plate is effectively prevented, and the effect of quickly absorbing impact energy by friction damping is realized. Therefore, the shock-resistant ultralow frequency vibration isolator has a simple and reasonable structure, has the ultralow frequency characteristic of vibration isolation, can quickly absorb shock energy in an impact environment, and does not generate obvious large deformation.
Drawings
Fig. 1 is a structural schematic diagram of the shock-resistant ultralow frequency vibration isolator after being loaded.
Fig. 2 is a schematic structural diagram of the shock-resistant ultralow frequency vibration isolator after being unloaded.
In the figure, 1 — equipment platform; 10-equipment to be isolated by vibration; 11-a lifting column; 21-a bottom plate; 22-a housing; 23-a top plate; 24-an elastic cylinder; 3-a first lifter plate; 41, pulling and pressing a spiral spring; 42-a first compression spring; 43 — a second compression spring; 51-impact coil spring; 52-a second lifter plate; 53-first link; 54 — a first damping slide; 55-a second link; 56-second dampening shoe.
Detailed Description
The invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1 and 2, the anti-impact ultralow frequency vibration isolator of the present invention comprises a housing 22, a bottom plate 21 and a top plate 23 respectively installed at both ends of the housing 22, a lifting column 11 freely liftable through the top plate 23, and an equipment platform 1 installed at the top of the lifting column 11 for installing an equipment 10 to be vibration isolated.
Referring to fig. 1 and 2, the first lifting plate 3, the impact coil spring 51, the second lifting plate 52 and the tension and compression coil spring 41 are sequentially arranged in the housing 22 from top to bottom; the tension/compression coil spring 41 is connected to the second elevating plate 52 and the base plate 21.
Referring to fig. 1 and 2, a first lifting plate 3 is fixedly installed at the lower end of a lifting column 11; the first compression spring 42 and the second compression spring 43 with the same rigidity are symmetrically arranged on the left side and the right side of the first lifting plate 3 relative to the lifting column 11, and the first connecting rod 53 and the second connecting rod 55 with the same structure are symmetrically hinged on the left side and the right side of the bottom of the first lifting plate 3 relative to the lifting column 11; the left end of the first compression-resistant spring 42 is connected with the shell 22, the right end thereof is connected with the lifting plate 3, and the left end of the first compression-resistant spring 42 is lower than the right end thereof; the right end of the second compression spring 43 is connected to the housing 22, the left end thereof is connected to the rising and lowering plate 3, and the right end of the second compression spring 43 is lower in height than the left end thereof. After the equipment platform 1 is placed on the vibration isolation equipment 10, the first lifting plate 3 descends, so that the first pressure resisting spring 42 and the second pressure resisting spring 43 are in a horizontal collinear state and are both subjected to compression deformation.
Referring to fig. 1 and 2, the second lifting plate 52 is slidably provided with a first damping slider 54 and a second damping slider 56 which are symmetrical with respect to the lifting column 11; the first damping sliding block 54 is hinged with the lower end of the first connecting rod 53, and the second damping sliding block 56 is hinged with the lower end of the second connecting rod 55; both ends of the impact coil spring 51 are connected to the first lifter plate 3 and the second lifter plate 52, respectively.
The first link 53 is inclined at a small angle to the horizontal direction, and the first pressure-resisting spring 42 is inclined to the horizontal direction.
Preferably, the compression rigidity of the impact coil spring 51 is not less than five times the rigidity of the tension and compression coil spring 41. Because the rigidity of the impact spiral spring 51 is much higher than that of the tension and compression spiral spring 41, the equipment platform 1 is in a static equilibrium state after being installed with the vibration isolation equipment 10, and the rigidity of the whole system is almost independent of the rigidity of the impact spiral spring 51.
Preferably, the tension/compression coil spring 41 is in a compressed state when the first compression spring 42 is in an inclined state with respect to the horizontal direction. After the vibration isolation device 10 is installed on the device platform 1, because the first compression spring 42 and the second compression spring 43 are horizontally collinear and in a compressed state, the balance formed by the first lifting plate 3 and the second lifting plate 52, which are formed by the tension and compression coil spring 41, the first compression spring 42 and the second compression spring 43, is very unstable, that is, a small external force breaks the balance, so that the total stiffness of the whole system in a static balance state is remarkably reduced and is almost zero.
Preferably, the first link 53 forms an angle θ with the horizontal direction, and θ is in the range of 0 to 20 °. When the impact force applied to the first lifter plate 3 is larger than the force required for the impact coil spring 51 to undergo compression deformation in a significant millimeter level, the smaller the angle θ, the larger the positive pressure and the frictional force of the first damper slider 54 and the second damper slider 56 to the housing 22.
As shown in fig. 2, preferably, after the vibration-isolated equipment 10 is mounted on the equipment platform 1, the axes of the first compression springs 42 and the second compression springs 43 are collinear in the horizontal direction. Since the collinear state of the axes of the first compression spring 42 and the second compression spring 43 in the horizontal direction is very unstable, the stiffness of the whole system will be significantly less than that of the tension and compression coil spring 41.
Preferably, the end faces of the first dampening slider 54 and the second dampening slider 56 adjacent the housing 22 are provided with a roughened surface.
Preferably, after the vibration-isolated equipment 10 is installed on the equipment platform 1, the first damping slide 54 and the second damping slide 56 form a clearance fit with the housing 22, and a clearance less than one millimeter can be reserved between the first damping slide 54 and the second damping slide 56.
Ultra-low frequency working principle: when vibration occurs, the vibration exciting force is generally smaller, and the vibration isolator of the invention has the characteristic of ultralow frequency vibration isolation. After the equipment platform 1 is installed with the vibration isolation equipment 10, the first compression springs 42 and the second compression springs 43 are just collinear, and the tension and compression coil springs 41 are in a compressed state. Therefore, regardless of whether the direction of the vibration exciting force is upward or downward, the second lifting plate 52 is inevitably displaced significantly, so that the first and second pressure springs 42 and 43 are again inclined. Therefore, the whole system presents the characteristic of ultra-low rigidity, and the vibration isolator of the invention presents the characteristic of ultra-low frequency. Since the above-mentioned force is small and the impact coil spring 51 of insufficient rigidity undergoes a significant compression deformation, the first and second damping slides 54 and 56 do not generate a frictional damping force with the housing 22.
The principle of impact resistance: when an impact occurs, the impact force is very large, which will give a very large downward force to the equipment platform 1, which is then transmitted to the impact coil spring 51 through the first lifting plate 3. Since the magnitude of this impact force is large enough, the impact coil spring 51 undergoes significant compression deformation, so that the first damping slider 54 and the second damping slider 56 are moved away from each other and pressed against the inner wall of the housing 22. At this time, although the stiffness of the whole system is as small as that in the ultra-low frequency operating state, the first damping slider 54 and the second damping slider 56 provide a large frictional damping force, so that the displacement amount of the second lifting plate 52 is significantly reduced, and the impact frictional damping force absorbs the impact energy. In the present invention, the greater the impact force, the greater the frictional damping force provided by the first and second damping sliders 54 and 56, and thus the vibration isolator of the present invention can achieve good impact resistance characteristics.
The above is only a specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that are not thought of through creative efforts should fall within the scope of the present invention.
Claims (7)
1. An anti-impact ultralow frequency vibration isolator comprises a shell (22), a bottom plate (21) and a top plate (23) which are respectively arranged at two ends of the shell (22), a lifting column (11) which can freely lift and fall through the top plate (23), and an equipment platform (1) which is arranged at the top of the lifting column (11) and is used for installing vibration-isolated equipment (10); the method is characterized in that:
the first lifting plate (3), the impact spiral spring (51), the second lifting plate (52) and the tension and compression spiral spring (41) are sequentially arranged in the shell (22) from top to bottom; the tension and compression spiral spring (41) is connected with the second lifting plate (52) and the bottom plate (21);
the first lifting plate (3) is fixedly arranged at the lower end of the lifting column (11); a first compression spring (42) and a second compression spring (43) with the same rigidity are symmetrically arranged on the left side and the right side of the first lifting plate (3) relative to the lifting column (11), and a first connecting rod (53) and a second connecting rod (55) with the same structure are symmetrically hinged on the left side and the right side of the bottom of the first lifting plate (3) relative to the lifting column (11); the left end of the first compression-resistant spring (42) is connected with the shell (22), the right end of the first compression-resistant spring is connected with the lifting plate (3), and the height of the left end of the first compression-resistant spring (42) is lower than that of the right end of the first compression-resistant spring; the right end of the second compression spring (43) is connected with the shell (22), the left end of the second compression spring is connected with the lifting plate (3), and the height of the right end of the second compression spring (43) is lower than that of the left end of the second compression spring;
a first damping slide block (54) and a second damping slide block (56) which are symmetrical relative to the lifting column (11) are arranged on the second lifting plate (52) in a sliding way; the first damping slide block (54) is hinged with the lower end of the first connecting rod (53), and the second damping slide block (56) is hinged with the lower end of the second connecting rod (55); both ends of the impact spiral spring (51) are respectively connected with the first lifting plate (3) and the second lifting plate (52);
the first connecting rod (53) is inclined at a small angle with the horizontal direction, and the first pressure-resistant spring (42) is inclined with the horizontal direction.
2. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: the compression rigidity of the impact coil spring (51) is not less than five times the rigidity of the tension and compression coil spring (41).
3. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: when the first compression-resistant spring (42) is inclined to the horizontal direction, the tension-compression coil spring (41) is in a compressed state.
4. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: the included angle between the first connecting rod (53) and the horizontal direction is theta, and the range of theta is 0-20 degrees.
5. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: after the vibration-isolated equipment (10) is installed on the equipment platform (1), the axes of the first compression spring (42) and the second compression spring (43) are collinear along the horizontal direction.
6. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: the end surfaces of the first damping sliding block (54) and the second damping sliding block (56) close to the shell (22) are provided with rough surfaces.
7. The anti-impact ultralow frequency vibration isolator according to claim 1, wherein: after the vibration isolation equipment (10) is installed on the equipment platform (1), clearance fit is formed between the first damping slide block (54) and the second damping slide block (56) and the shell (22).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110314108.8A CN113074204B (en) | 2021-03-24 | 2021-03-24 | Anti-impact ultralow frequency vibration isolator |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110314108.8A CN113074204B (en) | 2021-03-24 | 2021-03-24 | Anti-impact ultralow frequency vibration isolator |
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| CN113074204A CN113074204A (en) | 2021-07-06 |
| CN113074204B true CN113074204B (en) | 2022-02-25 |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113494559B (en) * | 2021-07-27 | 2022-09-16 | 常州大学 | Metal vibration isolator with damping force proportional to vibration displacement |
| CN113464597B (en) * | 2021-08-02 | 2022-09-16 | 常州大学 | Variable damping force metal vibration isolator with rigidity decoupling function and damping decoupling function |
| CN115747409B (en) * | 2022-11-25 | 2023-12-01 | 中国十七冶集团有限公司 | Self-adaptive sliding support of vaporization cooling flue of steelmaking converter and mounting and using method |
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| GB1411611A (en) * | 1971-12-07 | 1975-10-29 | Graubremse Gmbh | Device for damping shock and oscillations |
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| CN210178810U (en) * | 2019-06-21 | 2020-03-24 | 无锡市江大隔振器有限公司 | Little volume isolator that shocks resistance |
| CN110925345A (en) * | 2019-12-25 | 2020-03-27 | 潍柴动力股份有限公司 | Vibration isolator |
| CN111765197A (en) * | 2020-06-18 | 2020-10-13 | 常州大学 | Shock-resistant large-damping vibration isolator |
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2021
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Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1411611A (en) * | 1971-12-07 | 1975-10-29 | Graubremse Gmbh | Device for damping shock and oscillations |
| CN208089849U (en) * | 2018-01-10 | 2018-11-13 | 丰宁金龙黄金工业有限公司 | A kind of mine electromechanical equipment damping device |
| CN108253084A (en) * | 2018-01-29 | 2018-07-06 | 哈尔滨工业大学 | Six degree of freedom superlow frequency vibration isolating device and its control system of the one kind based on zero stiffness system |
| CN108825697A (en) * | 2018-07-09 | 2018-11-16 | 葛成侠 | A kind of new-energy automobile shock absorber |
| CN209725077U (en) * | 2019-03-25 | 2019-12-03 | 江阴诺明精密五金有限公司 | A kind of controllable unidirectional frcition damper of double reinforcements |
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