CN116624548A - Vibration isolator and vibration isolation platform using same - Google Patents

Vibration isolator and vibration isolation platform using same Download PDF

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Publication number
CN116624548A
CN116624548A CN202310711788.6A CN202310711788A CN116624548A CN 116624548 A CN116624548 A CN 116624548A CN 202310711788 A CN202310711788 A CN 202310711788A CN 116624548 A CN116624548 A CN 116624548A
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CN
China
Prior art keywords
piston
vibration isolator
vibration
cavity
elastic diaphragm
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.)
Withdrawn
Application number
CN202310711788.6A
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Chinese (zh)
Inventor
龚屹东
张岚
曾志超
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Shanghai Fenchuang Information Technology Co ltd
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Shanghai Fenchuang Information Technology Co ltd
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Priority to CN202310711788.6A priority Critical patent/CN116624548A/en
Publication of CN116624548A publication Critical patent/CN116624548A/en
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/101—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by buffering features or stoppers
    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/103—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by method of assembly, production or treatment
    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
    • F16F13/107—Passage design between working chambers
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/0232—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means with at least one gas spring
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

The application provides a vibration isolator and a vibration isolation platform using the same, wherein the vibration isolator comprises a piston, an elastic diaphragm, a rigid shell and a bottom plate; the elastic diaphragm and the bottom plate are respectively matched with the rigid shell to form a load cavity and a damping cavity, and the piston is fixedly connected to the upper surface of the elastic diaphragm; a first throttling hole is arranged between the load cavity and the damping cavity, and a second throttling hole communicated with the outside is arranged in the load cavity; the elastic diaphragm is shaped into a structure which allows the piston to move vertically and horizontally relative to the annular gland simultaneously; the design of the vibration isolator in the application improves the effective isolation of the passive vibration isolator to low-frequency disturbance, not only can realize the attenuation of vertical vibration through the structure of the elastic membrane, but also can effectively attenuate the disturbance in the horizontal direction due to the elastic action of the deep U-shaped annular convex part.

Description

Vibration isolator and vibration isolation platform using same
Technical Field
The application relates to the technical field of precise vibration reduction, in particular to a vibration isolator and a vibration isolation platform using the vibration isolator.
Background
The vibration isolator is a core component forming a vibration isolation system, and the characteristics of the vibration isolator have a decisive influence on the final performance of the vibration isolation system; common vibration isolation means can be divided into passive vibration isolation and active vibration isolation, and the passive vibration isolation system effectively attenuates high-frequency disturbance by the passive vibration isolation unit connected between the working unit and the foundation support. The system has a simple structure, is stable and reliable, does not need to introduce external energy input in the working process, and cannot effectively isolate low-frequency disturbance. The active vibration isolation system actively introduces external energy input, and in the process that the working unit is excited to vibrate, control force is instantaneously applied or the dynamic characteristics of the working unit are changed, so that the vibration of the unit is rapidly attenuated and controlled. The active vibration isolation system has obvious advantages for the disturbance in low frequency and ultra-low frequency ranges, especially the excitation of factors such as air flow, inertia and the like directly acting on the working unit, so that the active vibration isolation system is widely paid attention to the field of ultra-precise equipment. However, the cost of active vibration isolation technology is relatively high, and is usually targeted for low-frequency vibration isolation, while passive vibration isolation technology is usually adopted for high-frequency disturbance. The application aims to provide an isolator and an isolation platform using the isolator, which improve the isolation effect of a passive isolation system on low-frequency disturbance, and further achieve the effect of active isolation as much as possible by a low-cost passive isolation technology.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, an object of the present application is to provide a vibration isolator and a vibration isolation platform using the same, which are used for solving the problem that the passive vibration isolator in the prior art cannot effectively isolate low-frequency disturbance.
To achieve the above and other related objects, a first aspect of the present application provides a vibration isolator comprising: the device comprises a piston, an elastic diaphragm, a rigid shell and a bottom plate; the elastic diaphragm and the upper part of the rigid shell are matched to form a load cavity for containing air, the lower part of the rigid shell is matched with the bottom plate to form a damping cavity, and the volume of the damping cavity is larger than that of the load cavity; the piston is fixedly connected to the middle part of the upper surface of the elastic membrane; a first throttling hole for allowing gas to pass through and generating damping force is communicated between the load cavity and the damping cavity, and a second throttling hole communicated with the outside is arranged in the load cavity; an adjustable throttle valve for adjusting the opening area at the second throttle hole is arranged at the outer side opening of the second throttle hole;
the edge of the elastic diaphragm is fixedly and hermetically connected with the upper end of the rigid shell through an annular gland, and the piston is embedded in the center of the annular gland and is in clearance fit with the annular gland; the elastic diaphragm is shaped to allow simultaneous vertical and horizontal movement of the piston relative to the annular gland.
In the design, the air spring is adopted, and the function of buffering and shock absorption (vibration isolation) mainly comes from the compressibility of filling air in the rigid shell; when the piston of the vibration isolator is vibrated, the rubber film deforms to cause pressure change in the load cavity, so that pressure difference between the piston and the damping cavity is formed, gas flows back and forth in the two cavities under the action of the pressure difference, a throttling effect is caused when the gas flows through the throttling hole, damping force is generated, and vibration damping is accelerated. The damping cavity can reduce the rigidity characteristic of the vibration isolator which is disturbed in the low frequency range, and meanwhile, the vibration eliminating performance is enhanced; in the high-frequency stage, the vibration frequency of the load cavity is very high, the pressure change is very fast, the air flow speed is limited under the action of the orifice, and the air can change again without passing through the orifice, so that the orifice is completely closed, the damping cavity is disabled, and the vibration isolator is only operated by the load cavity; when in the low-frequency stage, the vibration frequency of the load cavity is low, the pressure change is very slow, the gas causes a throttling effect when flowing through the first throttling hole, a damping force is generated, the vibration attenuation is accelerated, and the low-frequency vibration isolation effect is achieved. In this design, the volume of damping chamber is greater than the volume of load chamber, can further improve the isolation of isolator to the low frequency disturbance, and is further, through adjustable choke valve adjustable second orifice's opening size, and then adjustment isolator is to different frequency disturbance adaptability.
In an embodiment of the application, the middle part of the elastic membrane is recessed inwards to form a recessed part matched with the bottom of the piston, the edge of the elastic membrane is turned outwards to form an annular protruding part with a deep U-shaped section, and the ratio of the depth to the width of the section is greater than 2:1; the annular protrusion is sandwiched between a contoured surface of the piston and an inner contoured surface of the annular gland. The elastic membrane can be made of rubber membrane or other existing materials with the same properties.
In the design, the structure of the elastic membrane not only can realize the attenuation of vertical vibration, but also can effectively attenuate the disturbance in the horizontal direction due to the elastic action of the deep U-shaped annular convex part.
In an embodiment of the application, an annular sealing portion for improving the tightness of the load cavity is integrally formed at the outer edge of the annular protruding portion of the elastic diaphragm, and an annular groove for accommodating the annular sealing portion is correspondingly formed on the joint surface of the annular gland and the rigid shell.
In the design, the annular sealing part can effectively improve the sealing performance of the load cavity.
In an embodiment of the present application, the piston is fixedly connected with the elastic membrane through a plurality of bolts, a balance plate is disposed on the lower surface of the elastic membrane, the balance plate is made of metal, and the plurality of bolts sequentially penetrate through the balance plate and the elastic membrane from bottom to top and are in threaded connection with the piston.
In the design, the balance plate is arranged at the bottom of the piston, so that the center of the piston moves downwards, and the stability is improved.
In an embodiment of the present application, the piston top end is integrally formed with a limiting plate, and the limiting plate and the annular gland top end are matched and limited.
In the design, the limiting plate can limit the piston in the vertical moving direction, so that the vibration isolator structure is prevented from being damaged when the piston is subjected to excessive pressure.
In an embodiment of the present application, the first orifice and the second orifice are detachably installed with a variable-diameter restrictor for increasing air damping, the variable-diameter restrictor includes a cylindrical cavity formed inside, two ends of the cavity are respectively communicated with the outside through a first through hole and a second through hole, and diameters of the first through hole and the second through hole are smaller than diameters of the cylindrical cavity; the diameter of the second through hole is smaller than that of the first through hole.
In the design, the reducing throttler can effectively improve the damping effect on the air flow, and the model size of the reducing throttler can be designed according to specific implementation requirements.
In one embodiment of the application, the variable diameter restrictor is threadably coupled to the first orifice or the second orifice.
In the design, the threaded connection mode is convenient for replacing and disassembling the reducer throttler.
In an embodiment of the application, the bottom plate is fixedly connected with the lower end of the rigid shell, and a sealing ring is arranged at the joint of the bottom plate and the lower end of the rigid shell.
In the design, the sealing ring is arranged at the joint of the bottom plate and the lower end of the rigid shell, so that the sealing performance of the damping cavity can be effectively improved.
The second aspect of the application provides a vibration isolation platform, which comprises a platform body, a platform bracket and a plurality of vibration isolators according to any one of the technical schemes, wherein the lower surface of the platform body is connected with the platform bracket through the plurality of vibration isolators.
In the design, the vibration isolator combination is applied to the vibration isolation platform, so that the low-frequency disturbance isolation performance of the vibration isolation platform can be effectively improved.
In an embodiment of the present application, the bottom plate of the vibration isolator is fixedly connected to the platform bracket, and the lower surface of the platform body is connected to the top end of the piston.
As described above, the vibration isolator and the vibration isolation platform using the vibration isolator have the following beneficial effects: the effective isolation of the passive vibration isolator for low-frequency disturbance is improved, the vertical vibration can be attenuated through the structure of the elastic membrane, and meanwhile, the disturbance in the horizontal direction can be effectively attenuated due to the elastic action of the deep U-shaped annular convex part; the vibration isolator combination is applied to the vibration isolation platform, so that the low-frequency disturbance isolation performance of the vibration isolation platform can be effectively improved; the size of the opening of the second orifice can be adjusted through the adjustable throttle valve, so that the adaptive capacity of the vibration isolator to different disturbance can be adjusted.
Drawings
FIG. 1 is a perspective view of a shock absorber according to an embodiment of the present application;
FIG. 2 is a schematic diagram of a isolator in a semi-section according to an embodiment of the present application;
FIG. 3 is an enlarged view of FIG. 2 at A;
FIG. 4 is a schematic diagram of an elastic membrane according to an embodiment of the application;
FIG. 5 is an enlarged view of FIG. 2 at B;
FIG. 6 is a graph showing Z-direction-phase/transmissibility/acceleration/coherence and a table of relevant data statistics;
FIG. 7 is a graph showing X-direction-phase/transmissibility/acceleration/coherence and a table of relevant data statistics;
fig. 8 shows a graph of Y-direction-phase/transmissivity/acceleration/coherence and a table of relevant data statistics.
Description of element reference numerals
The piston 1, the elastic diaphragm 2, the rigid shell 3, the bottom plate 4, the load cavity 5, the damping cavity 6, the first throttling hole 7, the second throttling hole 8, the adjustable throttle valve 9, the annular gland 10, the concave part 11, the annular convex part 12, the annular sealing part 13, the annular groove 14, the balance plate 15, the reducing throttle 16, the sealing ring 17, the first through hole 18, the second through hole 19, the cylindrical cavity 20 and the limiting plate 21.
Detailed Description
Further advantages and effects of the present application will become apparent to those skilled in the art from the disclosure of the present application, which is described by the following specific examples.
Please refer to fig. 1 to 5. It should be understood that the structures, proportions, sizes, etc. shown in the drawings are for illustration purposes only and should not be construed as limiting the application to the extent that it can be practiced, since modifications, changes in the proportions, or otherwise, used in the practice of the application, are not intended to be critical to the essential characteristics of the application, but are intended to fall within the spirit and scope of the application. Also, the terms such as "upper," "lower," "left," "right," "middle," and "a" and the like recited in the present specification are merely for descriptive purposes and are not intended to limit the scope of the application, but are intended to provide relative positional changes or modifications without materially altering the technical context in which the application may be practiced.
Example 1
Referring to fig. 1-2, the present embodiment provides a vibration isolator, including: a piston 1, an elastic membrane 2, a rigid housing 3 and a bottom plate 4; the elastic diaphragm 2 and the upper part of the rigid shell 3 are matched to form a load cavity 5 for containing air, the lower part of the rigid shell 3 is matched with the bottom plate 4 to form a damping cavity 6, and the volume of the damping cavity 6 is larger than that of the load cavity 5; the piston 1 is fixedly connected to the middle part of the upper surface of the elastic membrane 2.
A first orifice 7 for allowing gas to pass through and generating damping force is communicated between the load cavity 5 and the damping cavity 6, and the load cavity 5 is provided with a second orifice 8 communicated with the outside; an adjustable throttle valve 9 for adjusting the opening area at the second throttle hole 8 is arranged at the opening at the outer side of the second throttle hole 8.
The edge of the elastic diaphragm 2 is fixedly and hermetically connected with the upper end of the rigid shell 3 through an annular gland 10, the piston 1 is embedded in the center of the annular gland 10 and is in clearance fit with the annular gland 10, and in the embodiment, the clearance between the annular gland 10 and the piston 1 is 3mm; the elastic diaphragm 2 is shaped in a structure allowing simultaneous vertical and horizontal movement of the piston 1 with respect to the annular gland 10.
Referring to fig. 4, specifically, in this embodiment, the middle portion of the elastic membrane 2 is recessed inwards to form a recess 11 matched with the bottom of the piston 1, the edge is turned outwards to form an annular protrusion 12 with a deep U-shaped cross section, the ratio of the U-shaped depth to the width at the cross section is greater than 2:1, in this embodiment, the thickness of the elastic membrane 2 is 0.5mm, the cross-sectional depth of the deep U-shaped annular protrusion 12 is 11.5, and the annular protrusion 12 is sandwiched between the contour surface of the piston 1 and the inner contour surface of the annular gland 10. The structure of the elastic membrane 2 not only can realize the damping of vertical vibration, but also can effectively damp the disturbance in the horizontal direction due to the elastic action of the deep U-shaped annular convex part 12.
In the present embodiment, the elastic membrane 2 is a rubber membrane.
The vibration isolator of the embodiment adopts a structural form of an air spring, and the function of buffering and absorbing (vibration isolation) mainly comes from the compressibility of the rigid shell 3 after being filled with air; when the piston 1 of the vibration isolator is vibrated, the rubber diaphragm deforms to cause pressure change in the load cavity 5, so that pressure difference between the piston and the damping cavity 6 is formed, gas flows back and forth in the two cavities under the action of the pressure difference, a throttling effect is caused when the gas flows through the first throttling hole 7, damping force is generated, and vibration damping is accelerated. The damping cavity 6 can reduce the rigidity characteristic of the vibration isolator which is disturbed in the low frequency range, and meanwhile, the vibration eliminating performance is enhanced; in the high frequency stage, the vibration frequency of the negative pressure is high, the pressure change is quick, the air flow speed is limited under the action of the orifice, and the air flow is changed again without passing through the orifice, so that the orifice is completely closed, the damping cavity 6 is disabled, and the vibration isolator is only operated in the load cavity 5. In this design, the volume of damping chamber 6 is greater than the volume of load chamber 5, can effectively improve the isolator and to the isolation of low frequency disturbance, and is further, through adjustable throttle valve 9 adjustable second orifice 8 everywhere the flow size of air current, and then the adjustment isolator is to different disturbance adaptability.
In this embodiment, the outer edge of the annular protrusion 12 of the elastic diaphragm 2 is integrally formed with an annular sealing portion 13 for improving the sealing performance of the load chamber 5, and the joint surface of the annular gland 10 and the rigid housing 3 is correspondingly provided with a ring groove 14 for accommodating the annular sealing portion 13.
In this embodiment, the piston 1 is fixedly connected with the elastic membrane 2 through a plurality of bolts, the lower surface of the elastic membrane 2 is provided with a balance plate 15, the balance plate 15 is made of metal, and the plurality of bolts sequentially penetrate through the balance plate 15 and the elastic membrane 2 from bottom to top to be in threaded connection with the piston 1. The balance plate 15 is arranged at the bottom of the piston 1, so that the center of the piston 1 can be moved downwards, and the stability is improved.
In this embodiment, the top end of the piston 1 is integrally formed with a limiting plate 21, and the limiting plate 21 is matched with a limiting groove at the top end of the annular gland 10 for limiting. The limiting plate can limit the piston 1 in the vertical moving direction, so that the vibration isolator structure is prevented from being damaged when the piston 1 is subjected to excessive pressure.
Referring to fig. 3, in the present embodiment, the first orifice 7 and the second orifice 8 are detachably mounted with a reducer restrictor 16 for increasing air damping, the reducer restrictor 16 includes a cylindrical cavity 20 formed therein, two ends of the cavity are respectively communicated with the outside through a first through hole 18 and a second through hole 19, and diameters of the first through hole 18 and the second through hole 19 are smaller than diameters of the cylindrical cavity 20; the diameter of the second through hole 19 is smaller than the diameter of the first through hole 18. The reducing restrictor 16 can effectively improve the damping effect on the air flow, and the model size of the reducing restrictor 16 can be designed according to specific implementation requirements.
Specifically, in the present embodiment, the diameter of the first through hole 18 is 2.8mm, the diameter of the second through hole 19 is 0.7mm, and the diameter of the circumferential cavity is 3.6mm.
In the present embodiment, the variable diameter restrictor 16 is screwed to the first orifice 7 or the second orifice 8. The threaded connection facilitates replacement and removal of the reducer restrictor 16.
Referring to fig. 5, in the present embodiment, the bottom plate 4 is fixedly connected to the lower end of the rigid housing 3, and a sealing ring 17 is disposed at the joint between the bottom plate 4 and the lower end of the rigid housing 3. The sealing ring 17 is arranged at the joint of the bottom plate 4 and the lower end of the rigid shell 3, so that the sealing performance of the damping cavity 6 can be effectively improved.
In order to evaluate the performance of the vibration isolator in this embodiment, a detection report is provided, in the detection process, the vibration isolator in this embodiment is placed between the marble base and the load table, and the natural frequency of the vibration isolator in this embodiment is 2.5Hz by detecting the vibration acceleration of the marble base and the load table and obtaining the vibration transfer rate curves of the two, and by analyzing the phase, transfer rate, acceleration and coherence curves in the Z direction, the X direction and the Y direction, test data are obtained, see fig. 6-8. The test result of the vibration isolator in the embodiment shows that the peak value of the vibration transmission rate measured in each direction of Z/X/Y is in the range of the design reference value, and meets the design requirement (the vibration removal efficiency of the 5Hz section is more than or equal to 30%, the vibration removal efficiency of the 10Hz section is more than or equal to 75%, and the vibration removal efficiency of the 20Hz section is more than or equal to 90%).
Example 2
The embodiment provides a vibration isolation platform, which comprises a platform body, a platform bracket (not shown in the attached drawing), and a plurality of vibration isolators, wherein the lower surface of the platform body is connected with the platform bracket through four vibration isolators. By applying the vibration isolator combination to the vibration isolation platform, the isolation performance of the vibration isolation platform to low-frequency disturbance and high-frequency disturbance (micro vibration) can be effectively improved.
In this embodiment, the bottom plate 4 of the vibration isolator is fixedly connected to the platform bracket, and the lower surface of the platform body is connected to the top end of the piston 1.
In summary, the application improves the effective isolation of the passive vibration isolator for low-frequency disturbance, not only can realize the attenuation of vertical vibration through the structure of the elastic membrane, but also can effectively attenuate the disturbance in the horizontal direction due to the elastic action of the deep U-shaped annular convex part; the vibration isolator combination is applied to the vibration isolation platform, so that the low-frequency disturbance isolation performance of the vibration isolation platform can be effectively improved; the size of the opening of the second orifice can be adjusted through the adjustable throttle valve, so that the adaptive capacity of the vibration isolator to different disturbance can be adjusted. Therefore, the application effectively overcomes various defects in the prior art and has high industrial utilization value.
The above embodiments are merely illustrative of the principles of the present application and its effectiveness, and are not intended to limit the application. Modifications and variations may be made to the above-described embodiments by those skilled in the art without departing from the spirit and scope of the application. Accordingly, it is intended that all equivalent modifications and variations of the application be covered by the claims, which are within the ordinary skill of the art, be within the spirit and scope of the present disclosure.

Claims (10)

1. A vibration isolator, comprising: the device comprises a piston, an elastic diaphragm, a rigid shell and a bottom plate; the elastic diaphragm and the upper part of the rigid shell are matched to form a load cavity for containing air, the lower part of the rigid shell is matched with the bottom plate to form a damping cavity, and the volume of the damping cavity is larger than that of the load cavity; the piston is fixedly connected to the middle part of the upper surface of the elastic membrane;
a first throttling hole for allowing gas to pass through and generating damping force is communicated between the load cavity and the damping cavity, and a second throttling hole communicated with the outside is arranged in the load cavity; an adjustable throttle valve for adjusting the opening area at the second throttle hole is arranged at the outer side opening of the second throttle hole;
the edge of the elastic diaphragm is fixedly and hermetically connected with the upper end of the rigid shell through an annular gland, and the piston is embedded in the center of the annular gland and is in clearance fit with the annular gland; the elastic diaphragm is shaped to allow simultaneous vertical and horizontal movement of the piston relative to the annular gland.
2. The vibration isolator according to claim 1, wherein: the middle part of the elastic diaphragm is inwards recessed to form a recessed part matched with the bottom of the piston, the edge of the elastic diaphragm is outwards turned into an annular convex part with a deep U-shaped section, the ratio of the depth to the width of the section is greater than 2:1, and the annular convex part is clamped between the contour surface of the piston and the inner contour surface of the annular gland.
3. The vibration isolator according to claim 2, wherein: the annular sealing part for improving the tightness of the load cavity is integrally formed at the outer edge of the annular convex part of the elastic diaphragm, and an annular groove for accommodating the annular sealing part is correspondingly formed on the joint surface of the annular gland and the rigid shell.
4. The vibration isolator according to claim 1, wherein: the piston is fixedly connected with the elastic diaphragm through a plurality of bolts, a balance plate is arranged on the lower surface of the elastic diaphragm, and a plurality of bolts sequentially penetrate through the balance plate, the elastic diaphragm and the piston from bottom to top.
5. The vibration isolator according to claim 1, wherein: the piston top integrated into one piece has the limiting plate, the limiting plate with the spacing groove cooperation spacing on annular gland top.
6. The vibration isolator according to claim 1, wherein: the two ends of the cavity are respectively communicated with the outside through a first through hole and a second through hole, and the diameters of the first through hole and the second through hole are smaller than the diameter of the cylindrical cavity; the diameter of the second through hole is smaller than that of the first through hole.
7. The vibration isolator according to claim 6, wherein: the variable-diameter restrictor is in threaded connection with the first orifice or the second orifice.
8. The vibration isolator according to claim 1, wherein: the bottom plate is fixedly connected with the lower end of the rigid shell, and a sealing ring is arranged at the joint of the bottom plate and the lower end of the rigid shell.
9. A vibration isolation platform comprises a platform body and a platform bracket; the vibration isolator of any one of claims 1-8, wherein the lower surface of the platform body is connected to the platform bracket by a plurality of vibration isolators.
10. The vibration isolation platform of claim 9, wherein: the bottom plate of the vibration isolator is fixedly connected with the platform bracket, and the lower surface of the platform body is connected with the top end of the piston.
CN202310711788.6A 2023-06-15 2023-06-15 Vibration isolator and vibration isolation platform using same Withdrawn CN116624548A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310711788.6A CN116624548A (en) 2023-06-15 2023-06-15 Vibration isolator and vibration isolation platform using same

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310711788.6A CN116624548A (en) 2023-06-15 2023-06-15 Vibration isolator and vibration isolation platform using same

Publications (1)

Publication Number Publication Date
CN116624548A true CN116624548A (en) 2023-08-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310711788.6A Withdrawn CN116624548A (en) 2023-06-15 2023-06-15 Vibration isolator and vibration isolation platform using same

Country Status (1)

Country Link
CN (1) CN116624548A (en)

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