CN111981085B - Elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness - Google Patents
Elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness Download PDFInfo
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- CN111981085B CN111981085B CN202010897880.2A CN202010897880A CN111981085B CN 111981085 B CN111981085 B CN 111981085B CN 202010897880 A CN202010897880 A CN 202010897880A CN 111981085 B CN111981085 B CN 111981085B
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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
- 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
- F16F15/04—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 elastic means
- F16F15/046—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 elastic means using combinations of springs of different kinds
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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
- 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
- F16F15/03—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 magnetic or electromagnetic 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/063—Negative stiffness
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Abstract
The invention discloses an elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness.A upper platform and a lower platform are connected by each arched beam spring, so that the upper platform only moves relatively to the lower platform along the axial direction; the electromagnetic bistable mechanism is arranged on the lower platform, is formed by connecting an electromagnetic negative stiffness spring consisting of an inner magnetic ring, an outer magnetic ring and an electromagnetic coil in parallel with a second sheet spring and a third sheet spring to form a real-time adjustable electromagnetic bistable mechanism, and is connected with a first sheet spring fixedly connected on the upper platform in series; under the excitation of low-frequency large-displacement vibration, the electromagnetic bistable mechanism performs reciprocating snap between two balance points to consume energy to generate an elasticity-hysteresis phenomenon, so that high-efficiency vibration isolation is realized; the electromagnetic double-stable-state vibration isolation device is particularly suitable for working conditions of low-frequency large-displacement vibration isolation and buffering.
Description
Technical Field
The invention relates to the technical field of vibration isolation, in particular to an elastic-hysteresis low-frequency large-displacement vibration isolator which is designed by connecting a bistable mechanism based on electromagnetic negative stiffness and a linear sheet spring in series.
Background
Mechanical vibration is ubiquitous in production practice, and although the vibration phenomenon is often utilized in industry for screening, pile sinking and conveying, great convenience is provided for actual production; however, under most conditions, vibration will have many adverse effects on human production. Particularly, with the rapid development of aerospace high and new technologies, in order to meet the continuously improved on-orbit operation indexes, various aerospace equipment, such as antennas, solar sailboards and the like, develop towards a large scale and a flexible direction, and are easy to generate low-frequency large-displacement vibration responses under external interference, for example, a loop antenna with a certain caliber of 15m generates a low-frequency large-displacement vibration response with a first-order resonance frequency of only 0.22Hz and an amplitude of 5-6cm during posture adjustment; in the field of special military vehicles, 80% of vehicle-mounted precise electronic equipment is damaged and fails due to low-frequency large-displacement vibration response generated by running vehicles caused by uneven road surfaces, steering and the like. In view of the serious harm brought by the low-frequency large-displacement vibration response of various engineering structures, the vibration response needs to be effectively controlled to avoid the adverse effect.
In actual engineering, the low-frequency large-displacement vibration response source is complex and cannot be eliminated from the source, and the vibration isolation technology is the preferred control method. Aiming at the problem of low-frequency vibration response inhibition, researchers research various active vibration isolation methods based on intelligent materials, but the application of the active vibration isolation method is greatly limited due to the defects of high power consumption, low reliability, complex system and the like. In recent years, passive quasi-zero stiffness vibration isolators designed by connecting a negative stiffness mechanism and a positive stiffness element in parallel have attracted wide attention. The existing quasi-zero stiffness vibration isolators have good isolation effect on low-frequency micro-displacement vibration response, and the negative stiffness mechanism is accompanied with strong stiffness nonlinear characteristic under the excitation action of low-frequency large-displacement vibration, so that the low-frequency large-displacement vibration is difficult to realize high-efficiency isolation. Therefore, in order to effectively suppress the low-frequency large-displacement vibration response in the actual engineering, the negative stiffness mechanism and the positive stiffness element are connected in series to be applied to the low-frequency large-displacement vibration response control so as to increase the internal damping energy consumption performance of the vibration isolation system, but the vibration isolation system is still in the theoretical exploration stage, and no effective vibration damping device is available to cope with the low-frequency large-displacement vibration response in the actual engineering.
Disclosure of Invention
The invention aims to solve the problems in the prior art, provides an elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness, is applied to working conditions such as low-frequency large-displacement vibration isolation and buffering, and realizes high-efficiency vibration isolation by using an electromagnetic bistable mechanism to generate elasticity-hysteresis phenomenon through energy consumption caused by reciprocating kick between two balance points under the excitation of low-frequency large-displacement vibration; the obvious attenuation of the low-frequency large-displacement vibration response is realized on the premise of no additional damping material.
The invention adopts the following technical scheme for realizing the purpose of the invention:
the structure of the elasticity-hysteresis low-frequency large-displacement vibration isolator based on the electromagnetic negative stiffness is characterized in that: the upper platform and the lower platform are connected by all arch beam springs which are distributed on the periphery at equal intervals, and the arch beam springs restrict the upper platform to move relatively relative to the lower platform only along the axial direction; an electromagnetic negative stiffness spring composed of an inner magnetic ring, an outer magnetic ring and an electromagnetic coil is fixedly arranged on the lower platform, the electromagnetic negative stiffness spring, a second sheet spring and a third sheet spring are connected in parallel to form a real-time adjustable electromagnetic bistable mechanism, and the electromagnetic bistable mechanism is connected in series with a first sheet spring fixedly connected to the upper platform through a central shaft.
The elasticity-hysteresis low-frequency large-displacement vibration isolation based on the electromagnetic negative stiffness is also characterized in that: the outer ring of the first leaf spring is fixed on the first boss of the upper platform, and a first central hole of the first leaf spring is sleeved at the upper end of the central shaft and is matched and fixed with the upper thread section of the central shaft by a first nut; the second leaf spring and the third leaf spring are fixedly connected with the lower platform, and a third screw sequentially penetrates through a second peripheral through hole in an outer ring of the second leaf spring, a third peripheral through hole in a fixing piece of the outer magnetic ring, a fourth peripheral through hole in a clamp of the outer magnetic ring, a fifth peripheral through hole in an outer ring of the third leaf spring and is fixedly connected with a third thread through hole in the lower platform; a second central hole of the second sheet spring is sleeved in the middle section of the central shaft and is matched and fixed with the middle thread section of the central shaft by a second nut; the third central hole of the third sheet spring is sleeved on the lower section of the central shaft and is matched and fixed with the lower thread section of the central shaft and the second boss by a third nut.
The elasticity-hysteresis low-frequency large-displacement vibration isolation based on the electromagnetic negative stiffness is also characterized in that: in the electromagnetic bistable mechanism, an outer magnetic ring is clamped and fixed on a lower platform by an outer magnetic ring clamp and an outer magnetic ring fixing piece, a sleeve, an end cover, an inner magnetic ring and an inner magnetic ring clamp are sequentially arranged between a second sheet spring and a third sheet spring along a central shaft and are fastened between a middle thread section and a second boss by a second nut, the inner magnetic ring is fixed in the inner magnetic ring clamp by the end cover, and an electromagnetic coil is arranged on the periphery of the inner magnetic ring clamp.
The elasticity-hysteresis low-frequency large-displacement vibration isolation based on the electromagnetic negative stiffness is also characterized in that:
the assembling structure of the arched beam spring comprises the following components:
the upper end of the arched beam spring is horizontally an upper fixed edge and is provided with a first through hole in the upper fixed edge;
the lower end of the arched beam spring is a horizontal lower fixed edge; and a second through hole in the lower fixing edge;
the bottom surface of the upper platform is provided with a horizontal groove which is matched with the upper fixing edge and is provided with a first threaded through hole;
the bottom surface of the lower platform is provided with a horizontal groove which is matched with the lower fixing edge and is provided with a second threaded through hole;
the upper fixing edge of the arched beam spring is embedded with the horizontal groove in the upper platform and is connected by a first screw;
the lower fixed edge of the arched beam spring is embedded with the horizontal groove in the lower platform and is connected by a fourth screw.
The elasticity-hysteresis low-frequency large-displacement vibration isolation based on the electromagnetic negative stiffness is also characterized in that: the inner magnetic ring and the outer magnetic ring are made of neodymium iron boron materials magnetized along the axial direction, and except the inner magnetic ring, the outer magnetic ring and the electromagnetic coil, other components of the vibration isolator are made of non-magnetic materials or weak magnetic materials.
Compared with the prior art, the invention has the beneficial effects that:
1. the invention introduces an internal degree of freedom by connecting the electromagnetic bistable mechanism and the linear sheet spring in series, then connects the electromagnetic bistable mechanism and the arched beam spring in parallel, consumes energy by the reciprocating jump of the electromagnetic bistable mechanism between two balance points under the excitation of low-frequency large-displacement vibration, generates an elasticity-hysteresis phenomenon, and realizes the high-efficiency isolation of low-frequency large-displacement vibration response.
2. The electromagnetic negative stiffness mechanism is composed of an inner magnetic ring, an outer magnetic ring and an electromagnetic coil, and when the electromagnetic coil is not electrified, the permanent magnetic negative stiffness is provided by the inner magnetic ring and the outer magnetic ring; when the electromagnetic coil is electrified, the real-time control of the electromagnetic negative rigidity performance can be realized by adjusting the electrified current, so that an ideal electromagnetic bistable characteristic is obtained, and active and passive integrated vibration isolation is realized;
3. the loss factor of the invention is irrelevant to the excitation frequency and the inherent damping characteristic of the device, has high amplitude dependence and is beneficial to the high-performance inhibition of low-frequency large-displacement vibration response.
4. The invention utilizes the arched beam springs to restrain the upper platform to only generate relative motion along the axial direction relative to the lower platform, thereby avoiding the friction effect caused by using the linear bearing with the guiding function.
5. The invention adopts non-magnetic conductive or weak magnetic conductive materials for other components except the inner magnetic ring, the outer magnetic ring and the electromagnetic coil, thereby effectively avoiding the interference to the magnetic field of the electromagnetic mechanism;
6. the electromagnetic mechanism is applied, the response is quick, the contact is avoided, the size is small, the cleaning is realized, and no external damping material is required to be added; the structure is simple, the use is convenient, the cost is low, and the bearing capacity is strong.
Drawings
FIG. 1 is a schematic structural view of the vibration isolator of the present invention;
FIG. 2a is a schematic view of the upper platform of the vibration isolator of the present invention;
FIG. 2b is a schematic view of the lower platform of the vibration isolator of the present invention;
figure 3a is a schematic view of a first leaf spring in the vibration isolator of the present invention;
figure 3b is a schematic view of a second leaf spring in the vibration isolator of the present invention;
figure 3c is a schematic view of a third leaf spring in the vibration isolator of the present invention;
FIG. 4 is a schematic view of the arched beam springs of the isolator of the present invention;
figure 5 is a schematic center axis view of the vibration isolator of the present invention;
FIG. 6 is a schematic view of the outer magnetic ring fixture of the vibration isolator of the present invention;
FIG. 7 is a schematic view of an outer magnetic ring clamp in the vibration isolator of the present invention;
FIG. 8 is a schematic view of an inner magnetic ring clamp in the vibration isolator of the present invention;
figure 9 is a potential energy diagram of the electromagnetic bistable mechanism in the vibration isolator of the present invention;
figure 10 is a graph of the spring-hysteresis restoring force of the vibration isolator of the present invention.
Reference numbers in the figures: 1 upper platform, 1.1 first threaded through hole, 1.2 first boss, 1.3 counterbore, 2 first screw, 3 second screw, 4 first leaf spring, 4.1 first center hole, 4.2 first peripheral through hole, 5 center shaft, 5.1 upper threaded section, 5.2 middle threaded section, 5.3 second boss, 5.4 lower threaded section, 6 first nut, 7 arched beam spring, 7.1 upper fixed edge, 7.2 lower fixed edge, 7.3 first through hole, 7.4 second through hole, 8 second leaf spring, 8.1 second center hole, 8.2 second peripheral through hole, 9 third screw, 10 second nut, 11 sleeve, 12 outer magnetic ring fixing piece, 12.1 third peripheral through hole, 13 outer magnetic ring clamp, 13.1 fourth peripheral through hole, 13.2 bottom boss, 14 inner magnetic ring, 15 outer magnetic ring, 16 end cap, 17 ring clamp, 17.1 upper boss, 17.2 lower boss, 17.3.2 lower boss, 17.18 bottom boss, 19.18 third through hole, 17.2 inner ring boss, 19.1 third centre hole, 19.2 fifth periphery through-hole, 20 third nut, 21 lower platform, 21.1 second screw through-hole, 21.2 third screw through-hole, 21.3 supporting legs, 22 fourth screw.
Detailed Description
Referring to fig. 1, the structural form of the elastic-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness in the present embodiment is as follows:
the upper platform 1 and the lower platform 21 are connected by 6 arc beam springs 7 with the same structure which are distributed at the periphery at equal intervals, and the arc beam springs 7 restrict the relative movement of the upper platform 1 relative to the lower platform 21 only along the axial direction.
An electromagnetic negative stiffness spring composed of an inner magnetic ring 14, an outer magnetic ring 15 and an electromagnetic coil 18 is fixedly arranged on the lower platform 21, the electromagnetic negative stiffness spring, a second sheet spring 8 and a third sheet spring 19 are connected in parallel to form a real-time adjustable electromagnetic bistable mechanism, and the electromagnetic bistable mechanism is connected in series with a first sheet spring 4 fixedly connected on the upper platform 1 through a central shaft 5.
In specific implementation, the corresponding structural form also includes:
as shown in fig. 1, fig. 2a and fig. 3a, the outer ring of the first leaf spring 4 is fixed on the first boss 1.2 of the upper platform 1, and the first central hole 4.1 of the first leaf spring 4 is sleeved on the upper end of the central shaft 5 and is fixed by the first nut 6 in cooperation with the upper thread section 5.1 of the central shaft 5; specifically, a first peripheral through hole 4.2 is arranged on an outer ring of a first sheet spring 4, a first central hole 4.1 is arranged in the center of the first sheet spring 4, and a counter bore 1.3 is arranged on a first boss 1.2 in an upper platform 1; the second screw 3 is screwed in the counter bore 1.3 through the first peripheral through hole 4.2.
As shown in fig. 1, 2b, 3c and 5, the second leaf spring 8 and the third leaf spring 19 are fixedly connected with the lower platform 21 by a third screw 9 sequentially passing through a second peripheral through hole 8.2 in an outer ring of the second leaf spring 8, a third peripheral through hole 12.1 in the outer magnetic ring fixing member 12, a fourth peripheral through hole 13.1 in the outer magnetic ring clamp 13, and a fifth peripheral through hole 19.2 in an outer ring of the third leaf spring 19, and fixedly connected with a third threaded through hole 21.2 on the lower platform 21, and a supporting foot 21.3 is arranged at the bottom of the lower platform 21; a second central hole 8.1 of the second sheet spring 8 is sleeved in the middle section of the central shaft 5 and is matched and fixed with a second nut 10 and a middle thread section 5.2 of the central shaft 5; the third central hole 19.1 of the third leaf spring 19 is sleeved on the lower section of the central shaft 5 and is fixed by the third nut 20 in cooperation with the lower thread section 5.4 of the central shaft 5 and the second boss 5.3.
As shown in fig. 1, 6, 7 and 8, in the electromagnetic bistable mechanism, the outer magnetic ring 15 is clamped and fixed on the lower platform 21 by the bottom edge boss 13.2 and the outer magnetic ring fixing piece 12 in the outer magnetic ring clamp 13, a sleeve 11, an end cover 16, an inner magnetic ring 14 and an inner magnetic ring clamp 17 are sequentially arranged between the second sheet spring 8 and the third sheet spring 19 along the central shaft 5, and are fastened between the middle thread section 5.2 and the second boss 5.3 by the second nut 10, the inner magnetic ring 14 is fixed in the inner magnetic ring clamp 17 by the end cover 16, the electromagnetic coil 18 is arranged on the periphery of the inner magnetic ring clamp 17, the upper boss 17.1 and the lower boss 17.2 are respectively arranged on the outer circumferential surface of the inner magnetic ring clamp 17, and a coil framework of the electromagnetic coil 18 is formed; the inner magnetic ring clamp 17 shown in fig. 8 is provided with a bottom through hole 17.3 at the center of the bottom surface, and the central shaft 5 passes through the bottom through hole 17.3 of the inner magnetic ring clamp 17; an inner ring groove 17.4 is arranged on the upper ring inner ring of the inner magnetic ring clamp 17, and the end cover 16 is arranged on the inner ring groove 17.4.
As shown in fig. 1, 2a, 2b and 4, the assembling structure of the arched beam spring 7 is as follows: the upper end of the arched beam spring 7 is horizontally provided with an upper fixed edge 7.1 and a first through hole 7.3 in the upper fixed edge; the lower end of the arched beam spring 7 is horizontally provided with a lower fixed edge 7.2 and a second through hole 7.4 in the lower fixed edge; the bottom surface of the upper platform 1 is provided with a horizontal groove which is matched with the upper fixing edge 7.1 and is provided with a first threaded through hole 1.1; the bottom surface of the lower platform 21 is provided with a horizontal groove which is matched with the lower fixing edge 7.2 and is provided with a second threaded through hole 21.1; an upper fixed edge 7.1 of the arched beam spring 7 is embedded with a horizontal groove in the upper platform 1, and a first screw 2 penetrates through a first through hole 7.3 in the upper fixed edge 7.1 and is in threaded connection with a first threaded through hole 1.1 in the horizontal groove in the upper platform 1; the lower fixed edge 7.2 of the arched beam spring 7 is embedded with a horizontal groove in the lower platform 21, and a fourth screw 22 passes through a second through hole 7.4 in the lower fixed edge 7.2 and is in threaded connection with a second threaded through hole 21.1 in the horizontal groove in the lower platform 21.
The inner magnetic ring 14 and the outer magnetic ring 15 are made of neodymium iron boron materials magnetized along the axial direction, and except for the inner magnetic ring 14, the outer magnetic ring 15 and the electromagnetic coil 18, other components of the vibration isolator are made of non-magnetic materials or weak magnetic materials.
When the upper platform 1 relatively moves with respect to the lower platform 21 along the axial direction, the first leaf spring 4 is connected in series with the electromagnetic bistable mechanism composed of the second leaf spring 8, the third leaf spring 19, the inner magnetic ring 14, the outer magnetic ring 15 and the electromagnetic coil 18 through the central shaft 5 to introduce an internal degree of freedom into the vibration isolator, and under the action of low-frequency large-displacement vibration excitation, the vibration isolator performs reciprocating jump between two balance points of the electromagnetic bistable mechanism to generate an elasticity-hysteresis phenomenon with remarkable energy consumption characteristics.
The inner magnetic ring 14, the outer magnetic ring 15 and the electromagnetic coil 18 form an adjustable electromagnetic negative stiffness mechanism, and when the electromagnetic coil 18 is not electrified, the inner magnetic ring 14 and the outer magnetic ring 15 provide permanent magnetic negative stiffness; when the electromagnetic coil 18 is electrified, the real-time control of the electromagnetic negative rigidity performance can be realized by adjusting the current, and the required electromagnetic bistable characteristic is obtained.
In the invention, the second leaf spring 8 and the third leaf spring 19 are connected in parallel with the electromagnetic negative stiffness spring composed of the inner magnetic ring 14, the outer magnetic ring 15 and the electromagnetic coil 18 to form an electromagnetic bistable mechanism with a potential function having two balance points, wherein the potential function is shown in fig. 9, and fig. 9 shows that the electromagnetic bistable mechanism has two balance points, namely balance point 1 and balance point 2, and the electromagnetic bistable mechanism can do reciprocating jumping motion between the two balance points.
When the vibration isolator is used, a vibration-isolated object is fixedly connected on the upper platform 1, the lower platform 21 is connected with an external vibration source, when the external vibration source applies low-frequency large-displacement vibration excitation to the lower platform 21, the upper platform 1 fixedly connected with the vibration-isolated object generates low-frequency large-displacement vibration response relative to the lower platform 21, the central shaft 5 connected with the first sheet spring 4 jumps back and forth between two balance points of the electromagnetic bistable mechanism formed by the second sheet spring 8, the third sheet spring 19, the inner magnetic ring 14, the outer magnetic ring 15 and the electromagnetic coil 18, so that elastic strain energy stored by deformation of the first sheet spring 4 in the vibration process is continuously released to generate an elastic-hysteresis phenomenon, as shown in figure 10, a triangular area with a larger area in figure 10 represents input energy, the input energy is the product of stress and vertical vibration displacement of the vibration isolator, when the vibration excitation is performed by low-frequency large-displacement, the electromagnetic bistable mechanism can do reciprocating snap motion between the balance point 1 and the balance point 2 to generate an elastic-hysteresis loop shown as a parallelogram area in fig. 10, and the parallelogram area with larger area shows that the energy consumption effect is better. The internal degree of freedom is introduced by the series connection of the first sheet spring 4 and the electromagnetic bistable mechanism, so that the loss factor of the invention is independent of the excitation frequency and the inherent damping of the device, and highly depends on the vibration response amplitude, and the invention is favorable for the high-efficiency inhibition of low-frequency large-displacement vibration response.
When the electromagnetic coil 18 is not electrified, the inner magnetic ring 14 and the outer magnetic ring 15 provide permanent magnet negative rigidity; when the electromagnetic coil 18 is electrified, the magnitude of the electrified current is adjusted to realize the real-time regulation and control of the electromagnetic negative rigidity performance, so that the ideal electromagnetic bistable characteristic is obtained, and the active and passive integrated vibration isolation is realized.
Claims (5)
1. An elasticity-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness is characterized in that: the upper platform (1) and the lower platform (21) are connected by all arched beam springs (7) which are distributed on the periphery at equal intervals, and the arched beam springs (7) restrain the upper platform (1) to move relatively to the lower platform (21) only along the axial direction; an electromagnetic negative stiffness spring composed of an inner magnetic ring (14), an outer magnetic ring (15) and an electromagnetic coil (18) is fixedly arranged on the lower platform (21), the electromagnetic negative stiffness spring, a second sheet spring (8) and a third sheet spring (19) are connected in parallel to form a real-time adjustable electromagnetic bistable mechanism, and the electromagnetic bistable mechanism is connected in series with a first sheet spring (4) fixedly connected to the upper platform (1) through a central shaft (5); when the electromagnetic coil (18) is not electrified, the inner magnetic ring (14) and the outer magnetic ring (15) provide permanent magnet negative rigidity; when the electromagnetic coil (18) is electrified, the real-time control of the electromagnetic negative rigidity performance can be realized by adjusting the current, and the required electromagnetic bistable characteristic is obtained; except for the inner magnetic ring (14), the outer magnetic ring (15) and the electromagnetic coil (18), other components of the vibration isolator adopt non-magnetic conductive materials or weak magnetic conductive materials.
2. The elastic-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness as claimed in claim 1, wherein: the outer ring of the first leaf spring (4) is fixed on a first boss (1.2) of the upper platform (1), and a first central hole (4.1) of the first leaf spring (4) is sleeved at the upper end of the central shaft (5) and is matched and fixed with an upper thread section (5.1) of the central shaft (5) through a first nut (6); the second leaf spring (8) and the third leaf spring (19) are fixedly connected with the lower platform (21) through a third screw (9) which sequentially passes through a second peripheral through hole (8.2) in the outer ring of the second leaf spring (8), a third peripheral through hole (12.1) in the outer magnetic ring fixing piece (12), a fourth peripheral through hole (13.1) in the outer magnetic ring clamp (13), a fifth peripheral through hole (19.2) in the outer ring of the third leaf spring (19) and a third threaded through hole (21.2) in the lower platform (21); a second central hole (8.1) of the second sheet spring (8) is sleeved in the middle section of the central shaft (5) and is matched and fixed by a second nut (10) and a middle thread section (5.2) of the central shaft (5); a third central hole (19.1) of the third sheet spring (19) is sleeved on the lower section of the central shaft (5) and is matched and fixed with a lower thread section (5.4) of the central shaft (5) and a second boss (5.3) by a third nut (20).
3. The elastic-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness as claimed in claim 2, wherein: in the electromagnetic bistable mechanism, an external magnetic ring (15) is clamped and fixed on a lower platform (21) by an external magnetic ring clamp (13) and an external magnetic ring fixing piece (12), a sleeve (11), an end cover (16), an internal magnetic ring (14) and an internal magnetic ring clamp (17) are sequentially arranged between a second flake spring (8) and a third flake spring (19) along a central shaft (5), and are fastened between a middle thread section (5.2) and a second boss (5.3) by a second nut (10), the internal magnetic ring (14) is fixed in the internal magnetic ring clamp (17) by the end cover (16), and an electromagnetic coil (18) is arranged on the periphery of the internal magnetic ring clamp (17).
4. The elastic-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness as claimed in claim 1, wherein:
the assembling structure of the arched beam spring (7) is as follows:
the upper end of the arched beam spring (7) is horizontally provided with an upper fixed edge (7.1) and a first through hole (7.3) in the upper fixed edge;
the lower end of the arched beam spring (7) is horizontally a lower fixed edge (7.2); and a second through hole (7.4) in the lower fixing edge;
the bottom surface of the upper platform (1) is provided with a horizontal groove which is matched with the upper fixing edge (7.1) and is provided with a first threaded through hole (1.1);
the bottom surface of the lower platform (21) is provided with a horizontal groove which is matched with the lower fixing edge (7.2) and is provided with a second threaded through hole (21.1);
an upper fixing edge (7.1) of the arched beam spring (7) is embedded with a horizontal groove in the upper platform (1) and is connected by a first screw (2);
the lower fixing edge (7.2) of the arched beam spring (7) is embedded with a horizontal groove in the lower platform (21) and connected by a fourth screw (22).
5. The elastic-hysteresis low-frequency large-displacement vibration isolator based on electromagnetic negative stiffness as claimed in claim 1, wherein: the inner magnetic ring (14) and the outer magnetic ring (15) are made of neodymium iron boron materials magnetized along the axial direction.
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| DE50205778D1 (en) * | 2002-05-03 | 2006-04-20 | Integrated Dynamics Eng Gmbh | Magnetic spring device with negative stiffness |
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